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DOWNCOMER A B A C C C C D E F G H J K L M J N O P Q H WIDTH SUPPORT INTERNAL PIPE DISTRIBUTORS – FEED OPTIONS – ELEVATIONS 1-PASS OPTIONS 2-PASS OPTIONS 358 Pressure Vessel Design Manual
Transcript
Page 1: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

DOWNCOMER

A

B

A

C

C

C

C

D

E

F

G

H

J

K

L

M

J

N

O

P

Q

H

WIDTH SUPPORT

INTERNAL PIPE DISTRIBUTORS ndash FEED OPTIONS ndash ELEVATIONS

1-PASS OPTIONS 2-PASS OPTIONS

358 Pressure Vessel Design Manual

4 INCH MINIMUM

ALTERNATELOCATION

ALTERNATELOCATION

1 4

5

6

7

8

2

1

2

3

Vessel Internals 359

360 Pressure Vessel Design Manual

DOWNCOMER

SPARGER DETAILS

DETAIL 1

DETAIL 3

DETAIL 5 DETAIL 6

DETAIL 4

DETAIL 2

NO

HO

LES

SLO

TSIN

TH

IS A

REA

BLANK OFF ENDSOF HEADER

frac14 DRAIN HOLEAT BOTTOM OF PIPE

frac14 VENT HOLE ATTOP OF PIPE(EACH END)

INSULATING BAFFLESPARGER

SPARGER

SPARGER

SUPT CLIPS

INLET WEIR

5 NPS

SAME AS DOWNCOMER SPACING

5 N

PS +

10

15 NPS

2 N

PS

NPS + 1

15 NPS + 1

INLET BAFFLE

INLET WEIR

SAME ASDOWNCOMER SPACING

5 N

PS

5 NPS

t

t = 025 INCHES + 2 Ca MINIMUM

15

NPS

2 NPS

CL SLOTS OR HOLES

NPS + 2 INCHES

α

α = 30ndash45deg

2

Vessel Internals 361

362 Pressure Vessel Design Manual

Table 5-15Cross sectional area of pipe Ap in

2

Pipe Size

Schedule

10 40 80 160

1 0945 0864 0719 0522

125 1633 1496 1283 1057

15 2222 2036 1767 1404

2 3654 3356 2953 224

25 545 479 424 355

3 835 739 66 541

4 1425 1273 115 928

6 317 289 261 211

8 545 50 457 365

10 853 789 718 567

12 1206 1119 1016 805

14 1431 1353 1227 983

16 1887 1767 1609 129

18 2405 2237 2042 1637

20 2986 278 2527 2027

Table 5-16Size (ID) of equalizing branches inches

Size of Main Pipe Area Ap in2 (2)

Quantity of Branches (3)

2 4 6 8 10 12

2 3356 1461 103

3 739 217 153 125

4 1273 285 201 164 142

6 289 429 303 248 214 192

8 50 564 399 326 282 252

10 789 708 5 409 354 317 289

12 1119 844 597 487 422 377 345

14 1353 928 656 536 464 415 379

16 1767 106 75 612 53 474 433

18 2237 1193 843 688 597 533 487

20 278 133 94 768 711 595 543

Notes

1 The table lists the exact ID required such that the cross sectional area of the main line and the sum of the cross sectional area of the branches is

equal

2 Assumes that main line is Sch 40

3 Quantity of branches shown is total Assume equal quantity for each side

Vessel Internals 363

364 Pressure Vessel Design Manual

27637125

23625

6

DEAD LEG

THIS ENDONLY

BEAMS NOT SHOWN IN ELEVATION FOR CLARITY

361

25

22

185

2244

44

44

195

plusmn0

63

plusmn06

331

75

44

44

44

37125

14oslash

14oslash

24625 2462538125 38125

283

75

38125 38125

R1

R1

DEAD LEG

BEAM NOT SHOWN IN ELEVATION FOR CLARITY

SPRAY HEADERS - EXAMPLES

plusmn07

1

10oslash

6

324375

51 5133625 33625521875 521875 521875

370

TOP OF PACKING

521875

30

30

265

571

457

496

25

602

5

602

560

25

603

75

602

5

388

75

602

5

A2

10oslashA2

Vessel Internals 365

Procedure 5-9 Design of Trays

Typical Tower Dimensions and Nomenclature

1

2

5

4

11

2115

12

29

13

8 10

6

7

322

19

31

2

9

25

24

2318

17

20

22

1413

16

24

30

36 35

27

28

28 26

28

2 PASS

1 PASS

C

E

F

G

A34

4rdquo MIN

33

26 2827

H

2

31

32

C

KL J

N

MP

Q

E

TL

TL

366 Pressure Vessel Design Manual

Tray Types

1 Valve2 Bubble Cap3 Sieve4 Tunnel5 Chimney6 Ripple7 Shower8 Shed Rows9 Disc amp Donut10 Cartridge11 Jet12 Kittle13 Turbogrid14 Dual Flow15 Slotted16 Venturi17 Cascade18 Accumulator

Tray Nomenclature

1 InletFeedReflux2 Inlet Weir3 Inlet Baffle4 Downcomer Clearance5 Weir Height6 Anti-Jump Baffle7 Seal Pan8 Straight Downcomer9 Sloped Downcomer10 Side Downcomer11 Center Downcomer12 Insulating Baffle13 Draw (Off) Nozzle14 Draw (Off) Pan15 Pass Transition16 Total Draw Chimney Tray

17 Chimney18 Chimney Hat19 Return Nozzle20 Sump21 Intermediate Feed Nozzle22 Partial Drawoff Nozzle23 Partition24 Vapor Inlet25 Vapor Inlet Baffle26 Feed Area27 Active Tray Area28 Dowcomer Area (Inactive Tray Area)29 Vapor Outlet30 Baffle31 Internal Pipe32 Support Clips33 Internal Flanges34 End Plate35 Product Outlet Nozzle36 Reboiler Draw Nozzle

Dimensions

A frac14 Short frac14 5 NPSthorn 4 in

Long frac14 5 NPSthorn 10 in

B frac14 Same as middle downcomer

C frac14 5 NPS

D frac14 Same as weir height

E frac14 NPSthorn 6 in

F frac14 NPSthorn 1 in

G frac14 15 NPSthorn 1 in

H frac14 5 NPSthorn 15 in

J frac14 15 NPS

Vessel Internals 367

K frac14 NPS

L frac14 2 NPS

M frac14 Minimum with 21 SE head frac1425 Dthorn tH thorn 15 NPSthorn 2 in

Minimum with hemi head frac14M frac14 5 Dthorn tH thorn 15 NPSthorn 2 in

N frac14 Minimum distance from tangent line to nozzlecenterline See Table 519

P frac14 Minimum skirt height for 21 SE Head SeeTable 5-20

Q frac14 Minimum seal pan depth frac14 tray spacing thorn 6 inR frac14 Downcomer width

Table 5-18Minimum Distance From Tangent Line ldquoNrdquo

Noz Size N Noz Size N

lt2 in 5 12 in 16

3 in 7 14 in 18

4 in 8 16 in 20

6 in 10 18 in 24

8 in 12 20 in 27

10 in 14 24 in 30

Table 5-19Minimum Skirt Height ldquoPrdquo

Dia P Dia P

lt24 in 2 ft e 6 in 114e120 5 ft e 6 in

30e36 3 ft e 0 in 126e132 6 ft e 0 in

48e54 3 ft e 6 in 138e144 6 ft e 6 in

54e60 3 ft e 6 in 150e156 7 ft e 0 in

66e72 4 ft e 0 in 162e168 8 ft e 0 in

78e84 4 ft e 6 in 174e180 8 ft e 6 in

90e106 5 ft e 0 in

368 Pressure Vessel Design Manual

A1 A1

A1

A1 A1

A1 A1

A1 A2

A2A1

A1A1

A1

A1

A1

A1

A2 A2

A2

A2A1

AS AS

AS

AS

AC

AC AC

AQ

D

SIDE DOWNCOMER

CENTERDOWNCOMER

TRAYS

1-PASS TRAY 2-PASS TRAY 3-PASS TRAY 4-PASS TRAY

Vessel Internals 369

TYPICAL TRAY ASSEMBLY

Hex Head Bolt

Manway Lock Clamps

Manway Lock StudsManway Clamps

Seal Plate

Tray Floor (Active)

Tray Floor (Active)Outlet Weir

Downcomer Truss

Standard WasherHex NutFrictional Washer

Downcomer Panel

Downcomer Bolting Bar

Bottom Tray ClampHex Head Bolt DowncomerTruss

Hex NutFrictional Washer

DOWNCOMER BOLTING BAR

Hex Nut

Hex Nut

Hex Nut

Hex Head Bolt

Hex Head Bolt

Frictional Washer

Bottom Tray Clamp

Tray Floor (Inlet Panel)

TRAY FLOOR

(INLET PANEL)

TRAY SUPPORT RING

Tray Support Ring

Manway (Active)

ONE PASS TRAY SHOWN

370 Pressure Vessel Design Manual

Design of Tray Plates

Stress and DeflectionCase 1 Perforated Plate

Reference Roark 5th Edition Table 26 Case 1A

bull Rectangular platebull Uniformly loadedbull All edges simply supported

DATA

a b g frac14 Coefficients from Table 5-21E frac14 Modulus of elasticity at design temperature PSI

t frac14 Corroded thickness of tray inCa frac14 Corrosion allowance inn frac14 Hole efficiencyd frac14 Deflection at center inp frac14 Uniform load PSIs frac14 Bending stress PSI

FORMULAS

bull Stress s

s frac14 b p b4

n t2

BUBBLE-CAPTRAY

VALVELIQUID FLOW

WEIRDOWNCOMER

VAPOR

VAPORVAPOR

VAPOR

VAPOR

TYPES OF TRAYS

CHIMNEY CHIMNEY HAT

SUMPTRUSS

CHIMNEYACCUMULATOR TRAYS

LIQUID

LIQUID

LIQUID

SIEVE TRAY

VALVE TRAY

BUBBLE - CAP TRAY

USUALLY2rsquondash0rdquo

18rdquo MINIMUM

Vessel Internals 371

bull Deflection d

d frac14 a p b4

E n t3

bull Efficiency of holes for perforated plate n

n frac14 1 25 p d2

e C

DIMENSIONAL DATA

a frac14b frac14t frac14a=b frac14b frac14a frac14p frac14d frac14e frac14C frac14E frac14

Tray DesignCase 2 Standard tray plates

LOADS

A DL frac14 Dead load weight of trays and beams

B LL frac14 Live load dynamic load DP

C LL frac14 Liquid load weight of liquid supported

bull Total area AT

AT frac14 p D2=4 frac14 7854 D2

bull Total load PT

PT frac14 DLthorn LLthorn LL

bull Uniform load p

p frac14 PT=AT

LONG EDGE

SHORTEDGEBEAMS (TYP)

c = PITCH60deg

a

b

e

d

Table 5-20Coefficients

ab b a g

10 2874 044 420

12 3762 0616 455

14 4530 0770 478

16 5172 0906 491

18 5688 1017 499

20 6102 1110 503

30 7134 1335 505

40 7410 1400 502

50 7476 1417 501

N 7500 1421 500

372 Pressure Vessel Design Manual

PROPERTIES OF SECTIONS

C frac14 SAY=SA

I frac14 SAY2 thorn SI C SAY

Z frac14 I=C

CALCULATIONS

bull Determine panel area AP

AP frac14 Ln dnbull Load on panel FP

FP frac14 AP p

Uniform Load

bull Uniform load on beam w

w frac14 FP=Ln

bull Moment M

M frac14 w L2

n

8

bull Bending stress fb

fb frac14 M=Z

bull Deflection d

d frac14 5 w L4

n

384 E I

Concentrated Load

bull Moment M

M frac14 ethP LnTHORN=4bull Bending stress fb

fb frac14 M=Z

bull Deflection d

d frac14 P L3

n

48 E I

TYPE 1

1

2

XX

h

dn

t

PART A Y AY AY2 I12sum

C frac14 SAY=SA

I frac14 SAY2 thorn SI C SAY

Z frac14 I=C

TYPE 2

1

32

XX

h

dn

do

t

PART A Y AY AY2 I123sum

L1

DC

DIMENSIONS OF TRAY PANELS

d1 d2 d3 d4

Vessel Internals 373

NOTES1 Design Loads Trays pans drawoff boxes or

similar intemals shall be designed using a corrodedthickness to support their own weight plus thefollowing live loadsa Fractionation trays Design live load shall be the

greater of 20 PSF (98 KgSq meter) or the weightof water 2 (50 mm) over the highest weirsetting

b Areas under downcomers Design live load shallbe the greater of 64 PSF (314 Kg Sq meter) ora head of water one half the height of thedowncomer

c Pans (accumulator and drawoff pans) Designlive load shall be the greater of 1 PSI (700 Kg Sqmeter) or the weight of water at the maximumoperating level of the pan

d Baffles With no operating liquid level shall usea design live load of 1 PSI (700 KgSq meter) onthe projected horizontal area or actual impulseforce whichever is greater

2 Maintenance Loads Tray support members (allbeams support clips etc) shall be designed fora concentrated load of 300 Lbs (135 Kg) at any pointon the installed assembly The design shall be basedon the corroded thicknesses and an allowable stressof 9 Fy For maintenance loads stresses in the trayplates need not be considered

3 Uplift resistance Typical design of uplift for traysand packing is 25 PSI (17 Millibar) For serviceswhere excessive uplift can occur a higher upliftresistance may be used Examples of higher upliftfactors are as follows

a Crude and FCC side strippers 1 PSI (70 millibar)b Vacuum tower stripping trays overflash

collector wash trays or beds 2 PSI (140Millibar)

c Collectiors and packed beds above the washsection of a vacuum Tower 1 PSI (70 Millibar)

4 Failure sequence Tray assemblies wheneverpossible shall be designed so that failure will occurin the following ordera Tray manwaysb Tray deck active areasc Minor beams and downcomersd Major beams (defined as beams 10ft (3 Meters)

or longer or beams which extend across a vesselwithout interruption regardless of length)

5 Allowable stresses Allowable unit stress shall bebased on yield strength Fy at design temperaturewith AISC factors for tension bearing shear etc

6 Allowable Deflection The calculated combineddeflection of trays and support beams due to oper-ating loads shall not exceed the lesser of 1900 of thevessel diameter (in inches) or 316 (5 mm)

RECOMMENDED TRAY SPACING amp MANWAY SIZE

COLUMN DIA

(FT)

TRAY SPACING

(IN)

MANWAY

SPACING

MIN MANWAY

SIZE

25 to 16 24 Every 10 trays 18 in

16 to 24 30 Every 8 trays 20 in

24 to 32 36 Every 6 trays 24 in

32 and larger 42 Every 4 trays 30 in

374 Pressure Vessel Design Manual

Procedure 5-10 Flow Over Weirs

Notation

b frac14 width ftH frac14 static head of liquid ftQ frac14 discharge rate cu ftsecV frac14 velocity of approach ftsecH0 frac14 head correction per Table 5-22

Calculations

Discharge Q

bull For a full-length weir (Case 1)

Q frac14 333beth15 HTHORNbull For a contracted weir (Case 2)

Q frac14 333beth15 HTHORNbull For a V-notch weir (Case 3)

Q frac14 633 H

bull For a Cippoletti weir (Case 4)

Q frac14 3367beth15 HTHORN

Notes

1 Assumes troughs are level

Case 1 Full-Width Weir

V frac14 1ndash2 ftsec at 4 H upstream

Case 2 Contracted Weir

V frac14 1ndash2 ftsec at 3 H upstream

Case 3 V-Notch Weir

V frac14 5 ftsec at 5 H upstream

Case 4 Cippoletti Weir

V frac14 1ndash2 ftsec at 4 H upstream

Table 5-21Head correction for velocity of approach

V 04 06 08 10 12 14 16 18 20

Hrsquo 0002 0005 001 0015 0023 003 004 005 0062

V 22 24 26 28 30 32 34 36 38

Hrsquo 0075 0089 0105 0122 014 015 0179 0201 0213

Vessel Internals 375

Procedure 5-11 Design of Demisters

Demister pads or mist eliminators are important inter-nals in process vessels Anytime there is a continuous twophase flow vapor and liquid there is the possibility forliquid entrainment If it is desirable to separate the liquidand vapor or prevent liquid carryover in the vapor streamthe velocity must be kept sufficiently low to allow the liquiddroplets to fall out of the vapor stream Demister pads areeffective entrainment separators which allow operation atvapor velocities that would otherwise be excessive

ldquoVapor disengagementrdquo can be accomplished withouta demister but the vessel must be made much larger toaccomplish the same degree of separation This is knownas gravity separation

Demister pads are used in a wide variety of processvessels Good performance can be achieved at velocitiesof 30 to 110 of optimum

Demister pads can be used in vertical or horizontalvessels The mesh pad orientation can be either vertical orhorizontal in a vertical or horizontal vessel

A wire mesh demister consists of a knitted wire matmounted on a light weight support grid The mesh is madeby weaving small diameter metal wire into a mesh Padsmay be made out of metal or plastics Metal type includecarbon steel stainless steel monel and others Plasticmaterials include PTFE HDPE and PP

Pressure drop is usually extremely low in the range of1 inch of water column maximum The pressure drop isnormally so low that it is ignored in design

Vapor disengagement is dependent on the velocity ofthe stream The most common equation for determining theallowable vapor velocity for two phase flows is as follows

Va frac14 K frac12ethrL rVTHORN=rV1=2

Where

Va frac14 Allowable vapor velocity FtSecK frac14 Constant or coefficientrL frac14 Density of liquid PCFrV frac14 Density of vapor PCF

Notes

1 The mesh pad shall be in one piece or sectional asrequired for insertion through the vessel manwayEach pad section shall be removable through thevessel manhole

2 Layers shall not be more than 6 inches thick3 Where more than one layer is required all joints

shall be staggered

4 One piece circular pads may be spiral in form5 Each section of mesh shall include a grid on one or

both sides The grid wire andor fastening deviceshall be the same material as the mesh pad Top andbottom grids shall be constructed of frac14 inch diam-eter rods welded to ⅛ inch by 1 inch bars Themaximum gap between mesh pad and grids shall befrac12 inch for diameters less than 84 inches and 1 inchfor larger diameters

6 Estimate grid weights as 3 PSF7 Tie down wires shall be 1=16 inch diameter wire thru

frac14 inch diameter holes on 4 inch centers Tie wiresshould not be pushed through the pad as this couldcause leak paths

8 Pressure drop across mist eliminator shall beassumed as 02 PSI for support design

9 Unless otherwise specified support rings shall be2 inches wide for pads 84 inches in diameter andless and 3 inches wide for larger diameters

10 The mist eliminator shall be a tight fit against theshell or enclosure as well as between sections Meshpads shall be⅜ inches oversize all around for a forcefit against the enclosure No gaps are allowed

11 Vessel fabricator shall provide the mesh and gridsas well as any stiffeners required

12 The Mist eliminator shall be specified as either topor bottom removable

13 ldquoKrdquo is a constant or coefficient that is a functionof the efficiency of the separation K-values rangefrom 04 to 43 but are generally in the 15 to 35range The K-value is affected by pressure type ofpad size of wire type of vessel and disengagingheight For pressure applications the K-valueshould be decreased by 01 for every 100 PSI ofpressure after 100 PSI

14 Wire diameter for the mesh pad itself vary from0003 to 0016 inches

15 The free volume of demisters range from 92 to994

16 The density of the pads ranges from 3 to 33 PCF17 The NSA (nominal surface area) is the surface area

to volume ratio Ft2 Ft3 and is an important indi-cator of performance Ratios range from 50 to 600

18 To obtain higher separation efficiencies the wirediameter is decreased and the density and thicknessare increased

19 Typical width of sections for multi-section pads is12 inches (300 mm) but may vary by manufacturer

376 Pressure Vessel Design Manual

A Horizontal element B Vertical elements

Vertical vessels

Manway

Plate-Pakunit

Meshpad

Drain tubewith seal trap

END VIEW

END VIEW

SIDE VIEW

SIDE VIEW

C Vertical element

Horizontal vessels

D Horizontal element

Figure 5-15 Typical demister configurations in vessels

Vessel Internals 377

d

E Axial entrance

H gt (23) D ndash d

H gt D2 + d(minimum 24rdquo)

H gt D2 ndash d2

H gt D2 + d

H gt D2 ndash d2

h gt d

D

D Side entrance

d

D

B Axial exit

d

D

Φ lt 45ordm

Φ lt 45ordm

C Reverse axial exit

d

A Side exit

D

Figure 5-16 Guidelines for maintaining even flow distribution in vessels with axial flow

378 Pressure Vessel Design Manual

wire mesh

Top grid

Bottom grid

Vertical 14rdquo rodsspaced 12rdquo to 18rdquocenter to center

12rdquo to 18rdquosegmentwidth

18rdquo x 1rdquo flat bars14rdquo rodsspaced 6rdquocenterto center

Manway

Support ring

Support beam

Tie wires

Figure 5-17 Typical mesh pad construction and installation

Vessel Internals 379

Table 5-22Properties of demister pads

Type NSA (1) Ft2 Ft3 Density Pcf Wire Dia in Free Area York Style No Remarks

A 48 5 0011 99 931 High Throughput

B 65 7 0011 986 531 Economy Performance

C 85 9 0011 982 431 Standard - Good All

Around

D 110 108 0011 977 421 Heavy Duty

E 140 8 0006 984 326 Super High Efficiency -

Fine Mist

F 163 0006 94 371 Liquid - Liquid Coalescer

G 450 20 00045 959

H 600 27 00045 945

Notes

1 NSA frac14 Nominal Surface Area

Table 5-23Values of K (Note 13)

Based on Pressure

Pressure (PSIa) Vacuum (In Hg)

Pressure (PSIa) K Vacuum (In Hg) K

15 035 30 035

50 034 20 032

100 032 10 028

200 031 5 023

300 03 1 017

500 028 lt1 017

1000 027

gt1000 027

Based on Disengaging Height

Disengaging Height in K Disengaging Height in K

3 012 9 032

4 015 10 035

5 019 11 038

6 022 12 04

7 025 13 042

8 029 14 043

Based on Application

Vertical Vessels Horizontal Vessels

Type K Type K

General 035 General 035

Compressor Suction Drums 025 Steam Drums 025

Steam Drums 015

380 Pressure Vessel Design Manual

Procedure 5-12 Design of Baffles [10]

Baffles are frequently used in pressure vessels eithervertical or horizontal to divide the interior volume intodifferent compartments These compartments may beused to segregate liquids or provide overflow weirs forthe separation of liquids Baffles may be stiffened orunstiffened When welded across the entire cross sectionof the vessel they must be checked that they are notunduly restricting the diametral expansion of the vesselIf the unrestrained radial expansion of the vessel exceedsthat of the baffle by more than 1=16 in (⅛ in on thediameter) then a ldquoflexiblerdquo type of connection betweenthe vessel shell and the baffle should be utilized Variousflexible attachment designs are shown within theprocedure

Baffles should always be designed in the corrodedcondition It is typical for welded baffles to be designedwith a full corrosion allowance on both sides If the baffleis bolted in then one-half the full corrosion allowancemay be applied to each side the logic being that a boltedbaffle is removable and therefore replaceable

The majority of baffles are flat and as a result are veryinefficient from a strength standpoint Deflection is thegoverning case for flat plates loaded on one side Thepreference is to have unstiffened baffles and they shouldalways be the first choice This will be acceptable forsmall baffles However for larger baffles as the bafflethickness becomes excessive stiffeners offer a moreeconomical design Therefore stiffeners are frequentlyused to stiffen the baffle to prevent the thickness of thebaffle from becoming excessive The number size andspacing of stiffeners are dependent on the baffle thicknessselected There is a continual trade-off between bafflethickness and stiffener parameters

The design of a baffle with stiffeners is an iterativeprocess The procedure for the design of the stiffeners isfirst to divide the baffle into ldquopanelrdquo sections that are rigidenough to withstand the pressure applied on one sideEach individual panel is checked as a flat plate of thedimensions of the panel The stiffeners are assumed to bestrong enough to provide the necessary edge support forthe panel

The stiffeners themselves are designed next A sectionof the baffle is assumed as acting with the stiffener and ascontributing to the overall stiffness This combinedsection is known as the composite stiffener Thecomposite section is checked for stress and deflectionBoth vertical and horizontal stiffeners can be added asrequired

If required an alternate design is assumed based ona thicker or thinner baffle and checked until a satisfactorydesign is found There is no ldquorightrdquo answer however itshould be noted that the thinner the baffle the greater thenumber of stiffeners The lightest overall weight isprobably the ldquobestrdquo design but may not be the leastexpensive due to the welding costs in attaching thestiffeners

One alternative to a flat baffle with stiffeners is to go toa curved baffle A curved baffle works best as a verticalbaffle in a vertical vessel The curved baffle takes pressurefrom either side wall If the pressure is on the concave sidethe baffle is in tension If the pressure is on the convexside the baffle is in compression

There are various tables given in this procedure for flatplate coefficients Flat plate coefficients are utilized todetermine the baffle thickness or a panel thickness Eachtable is specific for a given condition and loading

Vessel Internals 381

Notation

Ap frac14 area of baffle working with stiffener in2

As frac14 area of stiffener in2

Cp frac14 distance from centroid of composite section topanel in

Cs frac14 distance from centroid of composite section tostiffener in

E frac14 modulus of elasticity psiFb frac14 allowable bending stress psiI frac14 moment of inertia composite in4

Is frac14 moment of inertia stiffener in4

l frac14 length of baffle that works with the stiffener inM frac14 moment in-lbn frac14 number of welds attaching stiffenerP frac14 vessel internal pressure psigp frac14 maximum uniform pressure psipn frac14 uniform pressure at any elevation an psiRm frac14 vessel mean radius inSg frac14 specific gravity of contentst frac14 thickness shell intb frac14 thickness baffle ints frac14 thickness stiffener inV frac14 shear load lbw frac14 required fillet weld size ina frac14 thermal coefficient of expansion ininF

bg frac14 flat plate coefficientsDT frac14 differential temperature (design temperature

minus 70F) Fsb frac14 bending stress in baffle psiss frac14 bending stress in stiffener psi

6n frac14 radial expansion ind frac14 deflection inda frac14 maximum allowable deflection in

Baffle Dimensions

382 Pressure Vessel Design Manual

Table 5-24Flat plate coefficients

Vessel Internals 383

Unstiffened Baffle Check

bull Find load p

p frac14 624aSg144

bull Find baffle thickness tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

s

bull Find baffle deflection d

d frac14 pg1b4

Et3b

Limit deflection to the smaller of tb2 or b360 Ifdeflection is excessive then

a Increase the baffle thicknessb Add stiffenersc Go to curved baffle design

If stiffeners are added the first step is to find themaximum ldquoardquo and ldquobrdquo dimensions that will meet theallowable deflection for a given panel size This willestablish the stiffener spacing for both horizontal andvertical stiffeners The ultimate design is a balancebetween baffle thickness stiffener spacing and stiffenersize

Thermal Check of Baffle

bull Vessel radial expansion due to pressure

D1 frac14 085PRm

tE

bull Vessel radial expansion due to temperature

D2 frac14 Rma DT

bull Thermal expansion of baffle

D3 frac14 05ba DT

bull Differential expansion

D4 frac14 D1 thorn D2 D3

Stiffener Design

Divide baffle into panels to limit deflection to the lesserof tb2 or b360 Deflection is calculated based on theappropriate Cases 1 through 3

bull Check baffle for panel size a0 b0bull Check stiffener for length a or b

Recommendations for attaching stiffeners

Benefits Provides added stiffness and no corrosiontrap

Figure 5-18 Example of stiffener layout

384 Pressure Vessel Design Manual

As frac14 tsh

Ap frac14 tbl

IS frac14 tsh3

12

Cp frac14 AsyAs thorn Ap

thorn tb2

Cs frac14 ethhthorn tbTHORN Cp

I frac14 IS thorn Apt2b12

thorn AsApy2

As thorn Ap

lsquo frac14 lesser of 32tb or stiffener spacing

Stresses in BaffleStiffener

sp frac14 MCp

I

ss frac14 MCs

I

Size Welds Attaching Stiffeners

For E70XX Welds

w frac14 Vdy11 200In

Table 5-25Intermittent Welds

Percent of

Continuous Weld

Length of Intermittent Welds

and Distance Between Centers

75 3e4

66 4e6

60 3e5

57 4e7

50 2e4 3e6 4e8

44 4e9

43 3e7

40 2e5 4e10

37 3e8

33 2e6 3e9 4e12

Reprinted by permission of the James F Lincoln Arc Welding

Foundation

Vessel Internals 385

For E60XX Welds

w frac14 Vdy9600In

Sample Problem

bull Given Horizontal vessel with a vertical baffle

P frac14 250 psig

DT frac14 500F

Material frac14 SA-516-70

Ca frac14 0125 in

JE frac14 10

E frac14 273 106 psi

a frac14 7124 10-6 in=in=FFy frac14 308 ksi

D frac14 240 in

Fb frac14 066 Fy frac14 2033 ksi

Rm frac14 120938

ts frac14 175 in

Sg frac14 08

a frac14 15 ft

DT frac14 500 70 frac14 430F

bull Find baffle thickness without stiffener

p frac14 624aSg144

frac14 52 psi

a

bratio frac14 15=20 frac14 075

from Table 5-25 Case 1

b1 frac14 016 g1 frac14 0033

bull Thickness of baffle tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

sfrac14

ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi016eth52THORN2402

20 330

s

tb frac14 153thorn 025 frac14 178

No good Use stiffeners

bull Assume a suitable baffle thickness and determinemaximum panel size

tb frac14 075 in corroded

maximum panel size frac14 4ft 4ft

bull Maximum pressure p

p frac14 13eth624THORN08144

frac14 45 psi

a

bfrac14 4

4frac14 1

See Table 5-25 Case 3

b3 frac14 0287 g3 frac14 00443

sb frac14 b3pb2n

t2

frac14 0287eth45THORN4820752

frac14 5290 psi lt 20 333 psiFigure 5-19 Sample problem

386 Pressure Vessel Design Manual

d frac14 g3

pE

b4nt3

frac14 00443

45

273 106

484

0753

frac14 0092 in lt 0375 in

Balance OK by inspection

bull Assume a layout where the maximum stiffenerspacing is 4 ft

(4) horizontal stiffeners(4) vertical stiffeners(18) panels

bull Check horizontal stiffeners

Dimensions

a1 frac14 3 ft b1 frac14 4 ft

a2 frac14 4 ft b2 frac14 4 ft

a3 frac14 4 ft b3 frac14 12 ft

a4 frac14 4 ft b4 frac14 196 ft

a5 frac14 13 ft

a6 frac14 148ft

bull Assume stiffener size 1 in 4 in

y frac14 2375 in

As frac14 tsh frac14 1eth4THORN frac14 4 in2

l frac14 32tb frac14 32eth075THORN frac14 24 in lt 48 in

AP frac14 tbl frac14 07524 frac14 18 in2

Is frac14 bh3

12frac14 1

43

12frac14 533 in4

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 533thorn 0633thorn 1846 frac14 2442 in4

Cp frac14 AsyAs thorn Ap

thorn tb2

frac14 4eth2375THORN22

thorn 0752

frac14 0807 in

Cs frac14 hthorn tb

Cp

frac14 4thorn 075 0807 frac14 3943

Check deflections

Deflections exceed allowable No good

bull Assume a larger stiffener size WT9 593

tf frac14 106 025 frac14 081

tw frac14 0625 025 frac14 0375

bull Check corroded thickness to find properties ofcorroded section This section would be equivalent toa WT9 30 Properties are

As frac14 882 in2

Is frac14 647 in4

Cs frac14 216 in

H frac14 9 in

Cp frac14 hthorn tb Cs

frac14 9thorn 075 216 frac14 759 in

Figure 5-20 Battle layout for sample problem

Item bn pn d

1 2352 104 149

2 2352 243 349

3 144 381 0767

Vessel Internals 387

y frac14 Cp tb2

frac14 7215 in

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 647thorn 0844thorn 30814 frac14 3737 in4

bull Check stresses and deflections See results in Table5-27

bull Stresses and deflections are acceptablebull Check welds

d frac14 ts thorn 2tw frac14 0375thorn 2eth0323THORN frac14 102

y frac14 7215 in

I frac14 3737 in4

n frac14 2

w frac14 Vdy11 200In

frac14 6681eth102THORN721511 200eth3737THORN2

frac14 0005thorn 0125 frac14 013 in

bull Check thermal expansion of baffle

D1 frac14 085PRm

tEfrac14 085eth250THORN120938

175eth273 106THORNfrac14 000054 in

D2 frac14 Rma DT frac14 1209387124 106430

frac14 0370 in

D3 frac14 05ba DT frac14 05240

7124 106430

frac14 0367 in

D4 frac14 D1 thorn D2 D3 frac14 000054thorn 0370 0367

frac14 00035 lt 006 in

Table 5-26Summary of Results for Stress and Deflection in Composite Stiffeners for Sample Problem

Item Orientation an bn pn M d V sp ss

1 Horiz 2352 d 104 172595 009 2690 3504 997

2 Horiz 2352 d 243 403275 021 6287 8186 2330

3 Horiz 144 d 381 237012 0045 6035 4811 1370

4 Vert d 156 450 154674 0037 5648 3141 894

5 Vert d 1776 513 228539 0072 6681 6681 1320

Figure 5-21 Details of weld attaching stiffener

388 Pressure Vessel Design Manual

Vessel Internals 389

Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 2: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

4 INCH MINIMUM

ALTERNATELOCATION

ALTERNATELOCATION

1 4

5

6

7

8

2

1

2

3

Vessel Internals 359

360 Pressure Vessel Design Manual

DOWNCOMER

SPARGER DETAILS

DETAIL 1

DETAIL 3

DETAIL 5 DETAIL 6

DETAIL 4

DETAIL 2

NO

HO

LES

SLO

TSIN

TH

IS A

REA

BLANK OFF ENDSOF HEADER

frac14 DRAIN HOLEAT BOTTOM OF PIPE

frac14 VENT HOLE ATTOP OF PIPE(EACH END)

INSULATING BAFFLESPARGER

SPARGER

SPARGER

SUPT CLIPS

INLET WEIR

5 NPS

SAME AS DOWNCOMER SPACING

5 N

PS +

10

15 NPS

2 N

PS

NPS + 1

15 NPS + 1

INLET BAFFLE

INLET WEIR

SAME ASDOWNCOMER SPACING

5 N

PS

5 NPS

t

t = 025 INCHES + 2 Ca MINIMUM

15

NPS

2 NPS

CL SLOTS OR HOLES

NPS + 2 INCHES

α

α = 30ndash45deg

2

Vessel Internals 361

362 Pressure Vessel Design Manual

Table 5-15Cross sectional area of pipe Ap in

2

Pipe Size

Schedule

10 40 80 160

1 0945 0864 0719 0522

125 1633 1496 1283 1057

15 2222 2036 1767 1404

2 3654 3356 2953 224

25 545 479 424 355

3 835 739 66 541

4 1425 1273 115 928

6 317 289 261 211

8 545 50 457 365

10 853 789 718 567

12 1206 1119 1016 805

14 1431 1353 1227 983

16 1887 1767 1609 129

18 2405 2237 2042 1637

20 2986 278 2527 2027

Table 5-16Size (ID) of equalizing branches inches

Size of Main Pipe Area Ap in2 (2)

Quantity of Branches (3)

2 4 6 8 10 12

2 3356 1461 103

3 739 217 153 125

4 1273 285 201 164 142

6 289 429 303 248 214 192

8 50 564 399 326 282 252

10 789 708 5 409 354 317 289

12 1119 844 597 487 422 377 345

14 1353 928 656 536 464 415 379

16 1767 106 75 612 53 474 433

18 2237 1193 843 688 597 533 487

20 278 133 94 768 711 595 543

Notes

1 The table lists the exact ID required such that the cross sectional area of the main line and the sum of the cross sectional area of the branches is

equal

2 Assumes that main line is Sch 40

3 Quantity of branches shown is total Assume equal quantity for each side

Vessel Internals 363

364 Pressure Vessel Design Manual

27637125

23625

6

DEAD LEG

THIS ENDONLY

BEAMS NOT SHOWN IN ELEVATION FOR CLARITY

361

25

22

185

2244

44

44

195

plusmn0

63

plusmn06

331

75

44

44

44

37125

14oslash

14oslash

24625 2462538125 38125

283

75

38125 38125

R1

R1

DEAD LEG

BEAM NOT SHOWN IN ELEVATION FOR CLARITY

SPRAY HEADERS - EXAMPLES

plusmn07

1

10oslash

6

324375

51 5133625 33625521875 521875 521875

370

TOP OF PACKING

521875

30

30

265

571

457

496

25

602

5

602

560

25

603

75

602

5

388

75

602

5

A2

10oslashA2

Vessel Internals 365

Procedure 5-9 Design of Trays

Typical Tower Dimensions and Nomenclature

1

2

5

4

11

2115

12

29

13

8 10

6

7

322

19

31

2

9

25

24

2318

17

20

22

1413

16

24

30

36 35

27

28

28 26

28

2 PASS

1 PASS

C

E

F

G

A34

4rdquo MIN

33

26 2827

H

2

31

32

C

KL J

N

MP

Q

E

TL

TL

366 Pressure Vessel Design Manual

Tray Types

1 Valve2 Bubble Cap3 Sieve4 Tunnel5 Chimney6 Ripple7 Shower8 Shed Rows9 Disc amp Donut10 Cartridge11 Jet12 Kittle13 Turbogrid14 Dual Flow15 Slotted16 Venturi17 Cascade18 Accumulator

Tray Nomenclature

1 InletFeedReflux2 Inlet Weir3 Inlet Baffle4 Downcomer Clearance5 Weir Height6 Anti-Jump Baffle7 Seal Pan8 Straight Downcomer9 Sloped Downcomer10 Side Downcomer11 Center Downcomer12 Insulating Baffle13 Draw (Off) Nozzle14 Draw (Off) Pan15 Pass Transition16 Total Draw Chimney Tray

17 Chimney18 Chimney Hat19 Return Nozzle20 Sump21 Intermediate Feed Nozzle22 Partial Drawoff Nozzle23 Partition24 Vapor Inlet25 Vapor Inlet Baffle26 Feed Area27 Active Tray Area28 Dowcomer Area (Inactive Tray Area)29 Vapor Outlet30 Baffle31 Internal Pipe32 Support Clips33 Internal Flanges34 End Plate35 Product Outlet Nozzle36 Reboiler Draw Nozzle

Dimensions

A frac14 Short frac14 5 NPSthorn 4 in

Long frac14 5 NPSthorn 10 in

B frac14 Same as middle downcomer

C frac14 5 NPS

D frac14 Same as weir height

E frac14 NPSthorn 6 in

F frac14 NPSthorn 1 in

G frac14 15 NPSthorn 1 in

H frac14 5 NPSthorn 15 in

J frac14 15 NPS

Vessel Internals 367

K frac14 NPS

L frac14 2 NPS

M frac14 Minimum with 21 SE head frac1425 Dthorn tH thorn 15 NPSthorn 2 in

Minimum with hemi head frac14M frac14 5 Dthorn tH thorn 15 NPSthorn 2 in

N frac14 Minimum distance from tangent line to nozzlecenterline See Table 519

P frac14 Minimum skirt height for 21 SE Head SeeTable 5-20

Q frac14 Minimum seal pan depth frac14 tray spacing thorn 6 inR frac14 Downcomer width

Table 5-18Minimum Distance From Tangent Line ldquoNrdquo

Noz Size N Noz Size N

lt2 in 5 12 in 16

3 in 7 14 in 18

4 in 8 16 in 20

6 in 10 18 in 24

8 in 12 20 in 27

10 in 14 24 in 30

Table 5-19Minimum Skirt Height ldquoPrdquo

Dia P Dia P

lt24 in 2 ft e 6 in 114e120 5 ft e 6 in

30e36 3 ft e 0 in 126e132 6 ft e 0 in

48e54 3 ft e 6 in 138e144 6 ft e 6 in

54e60 3 ft e 6 in 150e156 7 ft e 0 in

66e72 4 ft e 0 in 162e168 8 ft e 0 in

78e84 4 ft e 6 in 174e180 8 ft e 6 in

90e106 5 ft e 0 in

368 Pressure Vessel Design Manual

A1 A1

A1

A1 A1

A1 A1

A1 A2

A2A1

A1A1

A1

A1

A1

A1

A2 A2

A2

A2A1

AS AS

AS

AS

AC

AC AC

AQ

D

SIDE DOWNCOMER

CENTERDOWNCOMER

TRAYS

1-PASS TRAY 2-PASS TRAY 3-PASS TRAY 4-PASS TRAY

Vessel Internals 369

TYPICAL TRAY ASSEMBLY

Hex Head Bolt

Manway Lock Clamps

Manway Lock StudsManway Clamps

Seal Plate

Tray Floor (Active)

Tray Floor (Active)Outlet Weir

Downcomer Truss

Standard WasherHex NutFrictional Washer

Downcomer Panel

Downcomer Bolting Bar

Bottom Tray ClampHex Head Bolt DowncomerTruss

Hex NutFrictional Washer

DOWNCOMER BOLTING BAR

Hex Nut

Hex Nut

Hex Nut

Hex Head Bolt

Hex Head Bolt

Frictional Washer

Bottom Tray Clamp

Tray Floor (Inlet Panel)

TRAY FLOOR

(INLET PANEL)

TRAY SUPPORT RING

Tray Support Ring

Manway (Active)

ONE PASS TRAY SHOWN

370 Pressure Vessel Design Manual

Design of Tray Plates

Stress and DeflectionCase 1 Perforated Plate

Reference Roark 5th Edition Table 26 Case 1A

bull Rectangular platebull Uniformly loadedbull All edges simply supported

DATA

a b g frac14 Coefficients from Table 5-21E frac14 Modulus of elasticity at design temperature PSI

t frac14 Corroded thickness of tray inCa frac14 Corrosion allowance inn frac14 Hole efficiencyd frac14 Deflection at center inp frac14 Uniform load PSIs frac14 Bending stress PSI

FORMULAS

bull Stress s

s frac14 b p b4

n t2

BUBBLE-CAPTRAY

VALVELIQUID FLOW

WEIRDOWNCOMER

VAPOR

VAPORVAPOR

VAPOR

VAPOR

TYPES OF TRAYS

CHIMNEY CHIMNEY HAT

SUMPTRUSS

CHIMNEYACCUMULATOR TRAYS

LIQUID

LIQUID

LIQUID

SIEVE TRAY

VALVE TRAY

BUBBLE - CAP TRAY

USUALLY2rsquondash0rdquo

18rdquo MINIMUM

Vessel Internals 371

bull Deflection d

d frac14 a p b4

E n t3

bull Efficiency of holes for perforated plate n

n frac14 1 25 p d2

e C

DIMENSIONAL DATA

a frac14b frac14t frac14a=b frac14b frac14a frac14p frac14d frac14e frac14C frac14E frac14

Tray DesignCase 2 Standard tray plates

LOADS

A DL frac14 Dead load weight of trays and beams

B LL frac14 Live load dynamic load DP

C LL frac14 Liquid load weight of liquid supported

bull Total area AT

AT frac14 p D2=4 frac14 7854 D2

bull Total load PT

PT frac14 DLthorn LLthorn LL

bull Uniform load p

p frac14 PT=AT

LONG EDGE

SHORTEDGEBEAMS (TYP)

c = PITCH60deg

a

b

e

d

Table 5-20Coefficients

ab b a g

10 2874 044 420

12 3762 0616 455

14 4530 0770 478

16 5172 0906 491

18 5688 1017 499

20 6102 1110 503

30 7134 1335 505

40 7410 1400 502

50 7476 1417 501

N 7500 1421 500

372 Pressure Vessel Design Manual

PROPERTIES OF SECTIONS

C frac14 SAY=SA

I frac14 SAY2 thorn SI C SAY

Z frac14 I=C

CALCULATIONS

bull Determine panel area AP

AP frac14 Ln dnbull Load on panel FP

FP frac14 AP p

Uniform Load

bull Uniform load on beam w

w frac14 FP=Ln

bull Moment M

M frac14 w L2

n

8

bull Bending stress fb

fb frac14 M=Z

bull Deflection d

d frac14 5 w L4

n

384 E I

Concentrated Load

bull Moment M

M frac14 ethP LnTHORN=4bull Bending stress fb

fb frac14 M=Z

bull Deflection d

d frac14 P L3

n

48 E I

TYPE 1

1

2

XX

h

dn

t

PART A Y AY AY2 I12sum

C frac14 SAY=SA

I frac14 SAY2 thorn SI C SAY

Z frac14 I=C

TYPE 2

1

32

XX

h

dn

do

t

PART A Y AY AY2 I123sum

L1

DC

DIMENSIONS OF TRAY PANELS

d1 d2 d3 d4

Vessel Internals 373

NOTES1 Design Loads Trays pans drawoff boxes or

similar intemals shall be designed using a corrodedthickness to support their own weight plus thefollowing live loadsa Fractionation trays Design live load shall be the

greater of 20 PSF (98 KgSq meter) or the weightof water 2 (50 mm) over the highest weirsetting

b Areas under downcomers Design live load shallbe the greater of 64 PSF (314 Kg Sq meter) ora head of water one half the height of thedowncomer

c Pans (accumulator and drawoff pans) Designlive load shall be the greater of 1 PSI (700 Kg Sqmeter) or the weight of water at the maximumoperating level of the pan

d Baffles With no operating liquid level shall usea design live load of 1 PSI (700 KgSq meter) onthe projected horizontal area or actual impulseforce whichever is greater

2 Maintenance Loads Tray support members (allbeams support clips etc) shall be designed fora concentrated load of 300 Lbs (135 Kg) at any pointon the installed assembly The design shall be basedon the corroded thicknesses and an allowable stressof 9 Fy For maintenance loads stresses in the trayplates need not be considered

3 Uplift resistance Typical design of uplift for traysand packing is 25 PSI (17 Millibar) For serviceswhere excessive uplift can occur a higher upliftresistance may be used Examples of higher upliftfactors are as follows

a Crude and FCC side strippers 1 PSI (70 millibar)b Vacuum tower stripping trays overflash

collector wash trays or beds 2 PSI (140Millibar)

c Collectiors and packed beds above the washsection of a vacuum Tower 1 PSI (70 Millibar)

4 Failure sequence Tray assemblies wheneverpossible shall be designed so that failure will occurin the following ordera Tray manwaysb Tray deck active areasc Minor beams and downcomersd Major beams (defined as beams 10ft (3 Meters)

or longer or beams which extend across a vesselwithout interruption regardless of length)

5 Allowable stresses Allowable unit stress shall bebased on yield strength Fy at design temperaturewith AISC factors for tension bearing shear etc

6 Allowable Deflection The calculated combineddeflection of trays and support beams due to oper-ating loads shall not exceed the lesser of 1900 of thevessel diameter (in inches) or 316 (5 mm)

RECOMMENDED TRAY SPACING amp MANWAY SIZE

COLUMN DIA

(FT)

TRAY SPACING

(IN)

MANWAY

SPACING

MIN MANWAY

SIZE

25 to 16 24 Every 10 trays 18 in

16 to 24 30 Every 8 trays 20 in

24 to 32 36 Every 6 trays 24 in

32 and larger 42 Every 4 trays 30 in

374 Pressure Vessel Design Manual

Procedure 5-10 Flow Over Weirs

Notation

b frac14 width ftH frac14 static head of liquid ftQ frac14 discharge rate cu ftsecV frac14 velocity of approach ftsecH0 frac14 head correction per Table 5-22

Calculations

Discharge Q

bull For a full-length weir (Case 1)

Q frac14 333beth15 HTHORNbull For a contracted weir (Case 2)

Q frac14 333beth15 HTHORNbull For a V-notch weir (Case 3)

Q frac14 633 H

bull For a Cippoletti weir (Case 4)

Q frac14 3367beth15 HTHORN

Notes

1 Assumes troughs are level

Case 1 Full-Width Weir

V frac14 1ndash2 ftsec at 4 H upstream

Case 2 Contracted Weir

V frac14 1ndash2 ftsec at 3 H upstream

Case 3 V-Notch Weir

V frac14 5 ftsec at 5 H upstream

Case 4 Cippoletti Weir

V frac14 1ndash2 ftsec at 4 H upstream

Table 5-21Head correction for velocity of approach

V 04 06 08 10 12 14 16 18 20

Hrsquo 0002 0005 001 0015 0023 003 004 005 0062

V 22 24 26 28 30 32 34 36 38

Hrsquo 0075 0089 0105 0122 014 015 0179 0201 0213

Vessel Internals 375

Procedure 5-11 Design of Demisters

Demister pads or mist eliminators are important inter-nals in process vessels Anytime there is a continuous twophase flow vapor and liquid there is the possibility forliquid entrainment If it is desirable to separate the liquidand vapor or prevent liquid carryover in the vapor streamthe velocity must be kept sufficiently low to allow the liquiddroplets to fall out of the vapor stream Demister pads areeffective entrainment separators which allow operation atvapor velocities that would otherwise be excessive

ldquoVapor disengagementrdquo can be accomplished withouta demister but the vessel must be made much larger toaccomplish the same degree of separation This is knownas gravity separation

Demister pads are used in a wide variety of processvessels Good performance can be achieved at velocitiesof 30 to 110 of optimum

Demister pads can be used in vertical or horizontalvessels The mesh pad orientation can be either vertical orhorizontal in a vertical or horizontal vessel

A wire mesh demister consists of a knitted wire matmounted on a light weight support grid The mesh is madeby weaving small diameter metal wire into a mesh Padsmay be made out of metal or plastics Metal type includecarbon steel stainless steel monel and others Plasticmaterials include PTFE HDPE and PP

Pressure drop is usually extremely low in the range of1 inch of water column maximum The pressure drop isnormally so low that it is ignored in design

Vapor disengagement is dependent on the velocity ofthe stream The most common equation for determining theallowable vapor velocity for two phase flows is as follows

Va frac14 K frac12ethrL rVTHORN=rV1=2

Where

Va frac14 Allowable vapor velocity FtSecK frac14 Constant or coefficientrL frac14 Density of liquid PCFrV frac14 Density of vapor PCF

Notes

1 The mesh pad shall be in one piece or sectional asrequired for insertion through the vessel manwayEach pad section shall be removable through thevessel manhole

2 Layers shall not be more than 6 inches thick3 Where more than one layer is required all joints

shall be staggered

4 One piece circular pads may be spiral in form5 Each section of mesh shall include a grid on one or

both sides The grid wire andor fastening deviceshall be the same material as the mesh pad Top andbottom grids shall be constructed of frac14 inch diam-eter rods welded to ⅛ inch by 1 inch bars Themaximum gap between mesh pad and grids shall befrac12 inch for diameters less than 84 inches and 1 inchfor larger diameters

6 Estimate grid weights as 3 PSF7 Tie down wires shall be 1=16 inch diameter wire thru

frac14 inch diameter holes on 4 inch centers Tie wiresshould not be pushed through the pad as this couldcause leak paths

8 Pressure drop across mist eliminator shall beassumed as 02 PSI for support design

9 Unless otherwise specified support rings shall be2 inches wide for pads 84 inches in diameter andless and 3 inches wide for larger diameters

10 The mist eliminator shall be a tight fit against theshell or enclosure as well as between sections Meshpads shall be⅜ inches oversize all around for a forcefit against the enclosure No gaps are allowed

11 Vessel fabricator shall provide the mesh and gridsas well as any stiffeners required

12 The Mist eliminator shall be specified as either topor bottom removable

13 ldquoKrdquo is a constant or coefficient that is a functionof the efficiency of the separation K-values rangefrom 04 to 43 but are generally in the 15 to 35range The K-value is affected by pressure type ofpad size of wire type of vessel and disengagingheight For pressure applications the K-valueshould be decreased by 01 for every 100 PSI ofpressure after 100 PSI

14 Wire diameter for the mesh pad itself vary from0003 to 0016 inches

15 The free volume of demisters range from 92 to994

16 The density of the pads ranges from 3 to 33 PCF17 The NSA (nominal surface area) is the surface area

to volume ratio Ft2 Ft3 and is an important indi-cator of performance Ratios range from 50 to 600

18 To obtain higher separation efficiencies the wirediameter is decreased and the density and thicknessare increased

19 Typical width of sections for multi-section pads is12 inches (300 mm) but may vary by manufacturer

376 Pressure Vessel Design Manual

A Horizontal element B Vertical elements

Vertical vessels

Manway

Plate-Pakunit

Meshpad

Drain tubewith seal trap

END VIEW

END VIEW

SIDE VIEW

SIDE VIEW

C Vertical element

Horizontal vessels

D Horizontal element

Figure 5-15 Typical demister configurations in vessels

Vessel Internals 377

d

E Axial entrance

H gt (23) D ndash d

H gt D2 + d(minimum 24rdquo)

H gt D2 ndash d2

H gt D2 + d

H gt D2 ndash d2

h gt d

D

D Side entrance

d

D

B Axial exit

d

D

Φ lt 45ordm

Φ lt 45ordm

C Reverse axial exit

d

A Side exit

D

Figure 5-16 Guidelines for maintaining even flow distribution in vessels with axial flow

378 Pressure Vessel Design Manual

wire mesh

Top grid

Bottom grid

Vertical 14rdquo rodsspaced 12rdquo to 18rdquocenter to center

12rdquo to 18rdquosegmentwidth

18rdquo x 1rdquo flat bars14rdquo rodsspaced 6rdquocenterto center

Manway

Support ring

Support beam

Tie wires

Figure 5-17 Typical mesh pad construction and installation

Vessel Internals 379

Table 5-22Properties of demister pads

Type NSA (1) Ft2 Ft3 Density Pcf Wire Dia in Free Area York Style No Remarks

A 48 5 0011 99 931 High Throughput

B 65 7 0011 986 531 Economy Performance

C 85 9 0011 982 431 Standard - Good All

Around

D 110 108 0011 977 421 Heavy Duty

E 140 8 0006 984 326 Super High Efficiency -

Fine Mist

F 163 0006 94 371 Liquid - Liquid Coalescer

G 450 20 00045 959

H 600 27 00045 945

Notes

1 NSA frac14 Nominal Surface Area

Table 5-23Values of K (Note 13)

Based on Pressure

Pressure (PSIa) Vacuum (In Hg)

Pressure (PSIa) K Vacuum (In Hg) K

15 035 30 035

50 034 20 032

100 032 10 028

200 031 5 023

300 03 1 017

500 028 lt1 017

1000 027

gt1000 027

Based on Disengaging Height

Disengaging Height in K Disengaging Height in K

3 012 9 032

4 015 10 035

5 019 11 038

6 022 12 04

7 025 13 042

8 029 14 043

Based on Application

Vertical Vessels Horizontal Vessels

Type K Type K

General 035 General 035

Compressor Suction Drums 025 Steam Drums 025

Steam Drums 015

380 Pressure Vessel Design Manual

Procedure 5-12 Design of Baffles [10]

Baffles are frequently used in pressure vessels eithervertical or horizontal to divide the interior volume intodifferent compartments These compartments may beused to segregate liquids or provide overflow weirs forthe separation of liquids Baffles may be stiffened orunstiffened When welded across the entire cross sectionof the vessel they must be checked that they are notunduly restricting the diametral expansion of the vesselIf the unrestrained radial expansion of the vessel exceedsthat of the baffle by more than 1=16 in (⅛ in on thediameter) then a ldquoflexiblerdquo type of connection betweenthe vessel shell and the baffle should be utilized Variousflexible attachment designs are shown within theprocedure

Baffles should always be designed in the corrodedcondition It is typical for welded baffles to be designedwith a full corrosion allowance on both sides If the baffleis bolted in then one-half the full corrosion allowancemay be applied to each side the logic being that a boltedbaffle is removable and therefore replaceable

The majority of baffles are flat and as a result are veryinefficient from a strength standpoint Deflection is thegoverning case for flat plates loaded on one side Thepreference is to have unstiffened baffles and they shouldalways be the first choice This will be acceptable forsmall baffles However for larger baffles as the bafflethickness becomes excessive stiffeners offer a moreeconomical design Therefore stiffeners are frequentlyused to stiffen the baffle to prevent the thickness of thebaffle from becoming excessive The number size andspacing of stiffeners are dependent on the baffle thicknessselected There is a continual trade-off between bafflethickness and stiffener parameters

The design of a baffle with stiffeners is an iterativeprocess The procedure for the design of the stiffeners isfirst to divide the baffle into ldquopanelrdquo sections that are rigidenough to withstand the pressure applied on one sideEach individual panel is checked as a flat plate of thedimensions of the panel The stiffeners are assumed to bestrong enough to provide the necessary edge support forthe panel

The stiffeners themselves are designed next A sectionof the baffle is assumed as acting with the stiffener and ascontributing to the overall stiffness This combinedsection is known as the composite stiffener Thecomposite section is checked for stress and deflectionBoth vertical and horizontal stiffeners can be added asrequired

If required an alternate design is assumed based ona thicker or thinner baffle and checked until a satisfactorydesign is found There is no ldquorightrdquo answer however itshould be noted that the thinner the baffle the greater thenumber of stiffeners The lightest overall weight isprobably the ldquobestrdquo design but may not be the leastexpensive due to the welding costs in attaching thestiffeners

One alternative to a flat baffle with stiffeners is to go toa curved baffle A curved baffle works best as a verticalbaffle in a vertical vessel The curved baffle takes pressurefrom either side wall If the pressure is on the concave sidethe baffle is in tension If the pressure is on the convexside the baffle is in compression

There are various tables given in this procedure for flatplate coefficients Flat plate coefficients are utilized todetermine the baffle thickness or a panel thickness Eachtable is specific for a given condition and loading

Vessel Internals 381

Notation

Ap frac14 area of baffle working with stiffener in2

As frac14 area of stiffener in2

Cp frac14 distance from centroid of composite section topanel in

Cs frac14 distance from centroid of composite section tostiffener in

E frac14 modulus of elasticity psiFb frac14 allowable bending stress psiI frac14 moment of inertia composite in4

Is frac14 moment of inertia stiffener in4

l frac14 length of baffle that works with the stiffener inM frac14 moment in-lbn frac14 number of welds attaching stiffenerP frac14 vessel internal pressure psigp frac14 maximum uniform pressure psipn frac14 uniform pressure at any elevation an psiRm frac14 vessel mean radius inSg frac14 specific gravity of contentst frac14 thickness shell intb frac14 thickness baffle ints frac14 thickness stiffener inV frac14 shear load lbw frac14 required fillet weld size ina frac14 thermal coefficient of expansion ininF

bg frac14 flat plate coefficientsDT frac14 differential temperature (design temperature

minus 70F) Fsb frac14 bending stress in baffle psiss frac14 bending stress in stiffener psi

6n frac14 radial expansion ind frac14 deflection inda frac14 maximum allowable deflection in

Baffle Dimensions

382 Pressure Vessel Design Manual

Table 5-24Flat plate coefficients

Vessel Internals 383

Unstiffened Baffle Check

bull Find load p

p frac14 624aSg144

bull Find baffle thickness tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

s

bull Find baffle deflection d

d frac14 pg1b4

Et3b

Limit deflection to the smaller of tb2 or b360 Ifdeflection is excessive then

a Increase the baffle thicknessb Add stiffenersc Go to curved baffle design

If stiffeners are added the first step is to find themaximum ldquoardquo and ldquobrdquo dimensions that will meet theallowable deflection for a given panel size This willestablish the stiffener spacing for both horizontal andvertical stiffeners The ultimate design is a balancebetween baffle thickness stiffener spacing and stiffenersize

Thermal Check of Baffle

bull Vessel radial expansion due to pressure

D1 frac14 085PRm

tE

bull Vessel radial expansion due to temperature

D2 frac14 Rma DT

bull Thermal expansion of baffle

D3 frac14 05ba DT

bull Differential expansion

D4 frac14 D1 thorn D2 D3

Stiffener Design

Divide baffle into panels to limit deflection to the lesserof tb2 or b360 Deflection is calculated based on theappropriate Cases 1 through 3

bull Check baffle for panel size a0 b0bull Check stiffener for length a or b

Recommendations for attaching stiffeners

Benefits Provides added stiffness and no corrosiontrap

Figure 5-18 Example of stiffener layout

384 Pressure Vessel Design Manual

As frac14 tsh

Ap frac14 tbl

IS frac14 tsh3

12

Cp frac14 AsyAs thorn Ap

thorn tb2

Cs frac14 ethhthorn tbTHORN Cp

I frac14 IS thorn Apt2b12

thorn AsApy2

As thorn Ap

lsquo frac14 lesser of 32tb or stiffener spacing

Stresses in BaffleStiffener

sp frac14 MCp

I

ss frac14 MCs

I

Size Welds Attaching Stiffeners

For E70XX Welds

w frac14 Vdy11 200In

Table 5-25Intermittent Welds

Percent of

Continuous Weld

Length of Intermittent Welds

and Distance Between Centers

75 3e4

66 4e6

60 3e5

57 4e7

50 2e4 3e6 4e8

44 4e9

43 3e7

40 2e5 4e10

37 3e8

33 2e6 3e9 4e12

Reprinted by permission of the James F Lincoln Arc Welding

Foundation

Vessel Internals 385

For E60XX Welds

w frac14 Vdy9600In

Sample Problem

bull Given Horizontal vessel with a vertical baffle

P frac14 250 psig

DT frac14 500F

Material frac14 SA-516-70

Ca frac14 0125 in

JE frac14 10

E frac14 273 106 psi

a frac14 7124 10-6 in=in=FFy frac14 308 ksi

D frac14 240 in

Fb frac14 066 Fy frac14 2033 ksi

Rm frac14 120938

ts frac14 175 in

Sg frac14 08

a frac14 15 ft

DT frac14 500 70 frac14 430F

bull Find baffle thickness without stiffener

p frac14 624aSg144

frac14 52 psi

a

bratio frac14 15=20 frac14 075

from Table 5-25 Case 1

b1 frac14 016 g1 frac14 0033

bull Thickness of baffle tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

sfrac14

ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi016eth52THORN2402

20 330

s

tb frac14 153thorn 025 frac14 178

No good Use stiffeners

bull Assume a suitable baffle thickness and determinemaximum panel size

tb frac14 075 in corroded

maximum panel size frac14 4ft 4ft

bull Maximum pressure p

p frac14 13eth624THORN08144

frac14 45 psi

a

bfrac14 4

4frac14 1

See Table 5-25 Case 3

b3 frac14 0287 g3 frac14 00443

sb frac14 b3pb2n

t2

frac14 0287eth45THORN4820752

frac14 5290 psi lt 20 333 psiFigure 5-19 Sample problem

386 Pressure Vessel Design Manual

d frac14 g3

pE

b4nt3

frac14 00443

45

273 106

484

0753

frac14 0092 in lt 0375 in

Balance OK by inspection

bull Assume a layout where the maximum stiffenerspacing is 4 ft

(4) horizontal stiffeners(4) vertical stiffeners(18) panels

bull Check horizontal stiffeners

Dimensions

a1 frac14 3 ft b1 frac14 4 ft

a2 frac14 4 ft b2 frac14 4 ft

a3 frac14 4 ft b3 frac14 12 ft

a4 frac14 4 ft b4 frac14 196 ft

a5 frac14 13 ft

a6 frac14 148ft

bull Assume stiffener size 1 in 4 in

y frac14 2375 in

As frac14 tsh frac14 1eth4THORN frac14 4 in2

l frac14 32tb frac14 32eth075THORN frac14 24 in lt 48 in

AP frac14 tbl frac14 07524 frac14 18 in2

Is frac14 bh3

12frac14 1

43

12frac14 533 in4

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 533thorn 0633thorn 1846 frac14 2442 in4

Cp frac14 AsyAs thorn Ap

thorn tb2

frac14 4eth2375THORN22

thorn 0752

frac14 0807 in

Cs frac14 hthorn tb

Cp

frac14 4thorn 075 0807 frac14 3943

Check deflections

Deflections exceed allowable No good

bull Assume a larger stiffener size WT9 593

tf frac14 106 025 frac14 081

tw frac14 0625 025 frac14 0375

bull Check corroded thickness to find properties ofcorroded section This section would be equivalent toa WT9 30 Properties are

As frac14 882 in2

Is frac14 647 in4

Cs frac14 216 in

H frac14 9 in

Cp frac14 hthorn tb Cs

frac14 9thorn 075 216 frac14 759 in

Figure 5-20 Battle layout for sample problem

Item bn pn d

1 2352 104 149

2 2352 243 349

3 144 381 0767

Vessel Internals 387

y frac14 Cp tb2

frac14 7215 in

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 647thorn 0844thorn 30814 frac14 3737 in4

bull Check stresses and deflections See results in Table5-27

bull Stresses and deflections are acceptablebull Check welds

d frac14 ts thorn 2tw frac14 0375thorn 2eth0323THORN frac14 102

y frac14 7215 in

I frac14 3737 in4

n frac14 2

w frac14 Vdy11 200In

frac14 6681eth102THORN721511 200eth3737THORN2

frac14 0005thorn 0125 frac14 013 in

bull Check thermal expansion of baffle

D1 frac14 085PRm

tEfrac14 085eth250THORN120938

175eth273 106THORNfrac14 000054 in

D2 frac14 Rma DT frac14 1209387124 106430

frac14 0370 in

D3 frac14 05ba DT frac14 05240

7124 106430

frac14 0367 in

D4 frac14 D1 thorn D2 D3 frac14 000054thorn 0370 0367

frac14 00035 lt 006 in

Table 5-26Summary of Results for Stress and Deflection in Composite Stiffeners for Sample Problem

Item Orientation an bn pn M d V sp ss

1 Horiz 2352 d 104 172595 009 2690 3504 997

2 Horiz 2352 d 243 403275 021 6287 8186 2330

3 Horiz 144 d 381 237012 0045 6035 4811 1370

4 Vert d 156 450 154674 0037 5648 3141 894

5 Vert d 1776 513 228539 0072 6681 6681 1320

Figure 5-21 Details of weld attaching stiffener

388 Pressure Vessel Design Manual

Vessel Internals 389

Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 3: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

360 Pressure Vessel Design Manual

DOWNCOMER

SPARGER DETAILS

DETAIL 1

DETAIL 3

DETAIL 5 DETAIL 6

DETAIL 4

DETAIL 2

NO

HO

LES

SLO

TSIN

TH

IS A

REA

BLANK OFF ENDSOF HEADER

frac14 DRAIN HOLEAT BOTTOM OF PIPE

frac14 VENT HOLE ATTOP OF PIPE(EACH END)

INSULATING BAFFLESPARGER

SPARGER

SPARGER

SUPT CLIPS

INLET WEIR

5 NPS

SAME AS DOWNCOMER SPACING

5 N

PS +

10

15 NPS

2 N

PS

NPS + 1

15 NPS + 1

INLET BAFFLE

INLET WEIR

SAME ASDOWNCOMER SPACING

5 N

PS

5 NPS

t

t = 025 INCHES + 2 Ca MINIMUM

15

NPS

2 NPS

CL SLOTS OR HOLES

NPS + 2 INCHES

α

α = 30ndash45deg

2

Vessel Internals 361

362 Pressure Vessel Design Manual

Table 5-15Cross sectional area of pipe Ap in

2

Pipe Size

Schedule

10 40 80 160

1 0945 0864 0719 0522

125 1633 1496 1283 1057

15 2222 2036 1767 1404

2 3654 3356 2953 224

25 545 479 424 355

3 835 739 66 541

4 1425 1273 115 928

6 317 289 261 211

8 545 50 457 365

10 853 789 718 567

12 1206 1119 1016 805

14 1431 1353 1227 983

16 1887 1767 1609 129

18 2405 2237 2042 1637

20 2986 278 2527 2027

Table 5-16Size (ID) of equalizing branches inches

Size of Main Pipe Area Ap in2 (2)

Quantity of Branches (3)

2 4 6 8 10 12

2 3356 1461 103

3 739 217 153 125

4 1273 285 201 164 142

6 289 429 303 248 214 192

8 50 564 399 326 282 252

10 789 708 5 409 354 317 289

12 1119 844 597 487 422 377 345

14 1353 928 656 536 464 415 379

16 1767 106 75 612 53 474 433

18 2237 1193 843 688 597 533 487

20 278 133 94 768 711 595 543

Notes

1 The table lists the exact ID required such that the cross sectional area of the main line and the sum of the cross sectional area of the branches is

equal

2 Assumes that main line is Sch 40

3 Quantity of branches shown is total Assume equal quantity for each side

Vessel Internals 363

364 Pressure Vessel Design Manual

27637125

23625

6

DEAD LEG

THIS ENDONLY

BEAMS NOT SHOWN IN ELEVATION FOR CLARITY

361

25

22

185

2244

44

44

195

plusmn0

63

plusmn06

331

75

44

44

44

37125

14oslash

14oslash

24625 2462538125 38125

283

75

38125 38125

R1

R1

DEAD LEG

BEAM NOT SHOWN IN ELEVATION FOR CLARITY

SPRAY HEADERS - EXAMPLES

plusmn07

1

10oslash

6

324375

51 5133625 33625521875 521875 521875

370

TOP OF PACKING

521875

30

30

265

571

457

496

25

602

5

602

560

25

603

75

602

5

388

75

602

5

A2

10oslashA2

Vessel Internals 365

Procedure 5-9 Design of Trays

Typical Tower Dimensions and Nomenclature

1

2

5

4

11

2115

12

29

13

8 10

6

7

322

19

31

2

9

25

24

2318

17

20

22

1413

16

24

30

36 35

27

28

28 26

28

2 PASS

1 PASS

C

E

F

G

A34

4rdquo MIN

33

26 2827

H

2

31

32

C

KL J

N

MP

Q

E

TL

TL

366 Pressure Vessel Design Manual

Tray Types

1 Valve2 Bubble Cap3 Sieve4 Tunnel5 Chimney6 Ripple7 Shower8 Shed Rows9 Disc amp Donut10 Cartridge11 Jet12 Kittle13 Turbogrid14 Dual Flow15 Slotted16 Venturi17 Cascade18 Accumulator

Tray Nomenclature

1 InletFeedReflux2 Inlet Weir3 Inlet Baffle4 Downcomer Clearance5 Weir Height6 Anti-Jump Baffle7 Seal Pan8 Straight Downcomer9 Sloped Downcomer10 Side Downcomer11 Center Downcomer12 Insulating Baffle13 Draw (Off) Nozzle14 Draw (Off) Pan15 Pass Transition16 Total Draw Chimney Tray

17 Chimney18 Chimney Hat19 Return Nozzle20 Sump21 Intermediate Feed Nozzle22 Partial Drawoff Nozzle23 Partition24 Vapor Inlet25 Vapor Inlet Baffle26 Feed Area27 Active Tray Area28 Dowcomer Area (Inactive Tray Area)29 Vapor Outlet30 Baffle31 Internal Pipe32 Support Clips33 Internal Flanges34 End Plate35 Product Outlet Nozzle36 Reboiler Draw Nozzle

Dimensions

A frac14 Short frac14 5 NPSthorn 4 in

Long frac14 5 NPSthorn 10 in

B frac14 Same as middle downcomer

C frac14 5 NPS

D frac14 Same as weir height

E frac14 NPSthorn 6 in

F frac14 NPSthorn 1 in

G frac14 15 NPSthorn 1 in

H frac14 5 NPSthorn 15 in

J frac14 15 NPS

Vessel Internals 367

K frac14 NPS

L frac14 2 NPS

M frac14 Minimum with 21 SE head frac1425 Dthorn tH thorn 15 NPSthorn 2 in

Minimum with hemi head frac14M frac14 5 Dthorn tH thorn 15 NPSthorn 2 in

N frac14 Minimum distance from tangent line to nozzlecenterline See Table 519

P frac14 Minimum skirt height for 21 SE Head SeeTable 5-20

Q frac14 Minimum seal pan depth frac14 tray spacing thorn 6 inR frac14 Downcomer width

Table 5-18Minimum Distance From Tangent Line ldquoNrdquo

Noz Size N Noz Size N

lt2 in 5 12 in 16

3 in 7 14 in 18

4 in 8 16 in 20

6 in 10 18 in 24

8 in 12 20 in 27

10 in 14 24 in 30

Table 5-19Minimum Skirt Height ldquoPrdquo

Dia P Dia P

lt24 in 2 ft e 6 in 114e120 5 ft e 6 in

30e36 3 ft e 0 in 126e132 6 ft e 0 in

48e54 3 ft e 6 in 138e144 6 ft e 6 in

54e60 3 ft e 6 in 150e156 7 ft e 0 in

66e72 4 ft e 0 in 162e168 8 ft e 0 in

78e84 4 ft e 6 in 174e180 8 ft e 6 in

90e106 5 ft e 0 in

368 Pressure Vessel Design Manual

A1 A1

A1

A1 A1

A1 A1

A1 A2

A2A1

A1A1

A1

A1

A1

A1

A2 A2

A2

A2A1

AS AS

AS

AS

AC

AC AC

AQ

D

SIDE DOWNCOMER

CENTERDOWNCOMER

TRAYS

1-PASS TRAY 2-PASS TRAY 3-PASS TRAY 4-PASS TRAY

Vessel Internals 369

TYPICAL TRAY ASSEMBLY

Hex Head Bolt

Manway Lock Clamps

Manway Lock StudsManway Clamps

Seal Plate

Tray Floor (Active)

Tray Floor (Active)Outlet Weir

Downcomer Truss

Standard WasherHex NutFrictional Washer

Downcomer Panel

Downcomer Bolting Bar

Bottom Tray ClampHex Head Bolt DowncomerTruss

Hex NutFrictional Washer

DOWNCOMER BOLTING BAR

Hex Nut

Hex Nut

Hex Nut

Hex Head Bolt

Hex Head Bolt

Frictional Washer

Bottom Tray Clamp

Tray Floor (Inlet Panel)

TRAY FLOOR

(INLET PANEL)

TRAY SUPPORT RING

Tray Support Ring

Manway (Active)

ONE PASS TRAY SHOWN

370 Pressure Vessel Design Manual

Design of Tray Plates

Stress and DeflectionCase 1 Perforated Plate

Reference Roark 5th Edition Table 26 Case 1A

bull Rectangular platebull Uniformly loadedbull All edges simply supported

DATA

a b g frac14 Coefficients from Table 5-21E frac14 Modulus of elasticity at design temperature PSI

t frac14 Corroded thickness of tray inCa frac14 Corrosion allowance inn frac14 Hole efficiencyd frac14 Deflection at center inp frac14 Uniform load PSIs frac14 Bending stress PSI

FORMULAS

bull Stress s

s frac14 b p b4

n t2

BUBBLE-CAPTRAY

VALVELIQUID FLOW

WEIRDOWNCOMER

VAPOR

VAPORVAPOR

VAPOR

VAPOR

TYPES OF TRAYS

CHIMNEY CHIMNEY HAT

SUMPTRUSS

CHIMNEYACCUMULATOR TRAYS

LIQUID

LIQUID

LIQUID

SIEVE TRAY

VALVE TRAY

BUBBLE - CAP TRAY

USUALLY2rsquondash0rdquo

18rdquo MINIMUM

Vessel Internals 371

bull Deflection d

d frac14 a p b4

E n t3

bull Efficiency of holes for perforated plate n

n frac14 1 25 p d2

e C

DIMENSIONAL DATA

a frac14b frac14t frac14a=b frac14b frac14a frac14p frac14d frac14e frac14C frac14E frac14

Tray DesignCase 2 Standard tray plates

LOADS

A DL frac14 Dead load weight of trays and beams

B LL frac14 Live load dynamic load DP

C LL frac14 Liquid load weight of liquid supported

bull Total area AT

AT frac14 p D2=4 frac14 7854 D2

bull Total load PT

PT frac14 DLthorn LLthorn LL

bull Uniform load p

p frac14 PT=AT

LONG EDGE

SHORTEDGEBEAMS (TYP)

c = PITCH60deg

a

b

e

d

Table 5-20Coefficients

ab b a g

10 2874 044 420

12 3762 0616 455

14 4530 0770 478

16 5172 0906 491

18 5688 1017 499

20 6102 1110 503

30 7134 1335 505

40 7410 1400 502

50 7476 1417 501

N 7500 1421 500

372 Pressure Vessel Design Manual

PROPERTIES OF SECTIONS

C frac14 SAY=SA

I frac14 SAY2 thorn SI C SAY

Z frac14 I=C

CALCULATIONS

bull Determine panel area AP

AP frac14 Ln dnbull Load on panel FP

FP frac14 AP p

Uniform Load

bull Uniform load on beam w

w frac14 FP=Ln

bull Moment M

M frac14 w L2

n

8

bull Bending stress fb

fb frac14 M=Z

bull Deflection d

d frac14 5 w L4

n

384 E I

Concentrated Load

bull Moment M

M frac14 ethP LnTHORN=4bull Bending stress fb

fb frac14 M=Z

bull Deflection d

d frac14 P L3

n

48 E I

TYPE 1

1

2

XX

h

dn

t

PART A Y AY AY2 I12sum

C frac14 SAY=SA

I frac14 SAY2 thorn SI C SAY

Z frac14 I=C

TYPE 2

1

32

XX

h

dn

do

t

PART A Y AY AY2 I123sum

L1

DC

DIMENSIONS OF TRAY PANELS

d1 d2 d3 d4

Vessel Internals 373

NOTES1 Design Loads Trays pans drawoff boxes or

similar intemals shall be designed using a corrodedthickness to support their own weight plus thefollowing live loadsa Fractionation trays Design live load shall be the

greater of 20 PSF (98 KgSq meter) or the weightof water 2 (50 mm) over the highest weirsetting

b Areas under downcomers Design live load shallbe the greater of 64 PSF (314 Kg Sq meter) ora head of water one half the height of thedowncomer

c Pans (accumulator and drawoff pans) Designlive load shall be the greater of 1 PSI (700 Kg Sqmeter) or the weight of water at the maximumoperating level of the pan

d Baffles With no operating liquid level shall usea design live load of 1 PSI (700 KgSq meter) onthe projected horizontal area or actual impulseforce whichever is greater

2 Maintenance Loads Tray support members (allbeams support clips etc) shall be designed fora concentrated load of 300 Lbs (135 Kg) at any pointon the installed assembly The design shall be basedon the corroded thicknesses and an allowable stressof 9 Fy For maintenance loads stresses in the trayplates need not be considered

3 Uplift resistance Typical design of uplift for traysand packing is 25 PSI (17 Millibar) For serviceswhere excessive uplift can occur a higher upliftresistance may be used Examples of higher upliftfactors are as follows

a Crude and FCC side strippers 1 PSI (70 millibar)b Vacuum tower stripping trays overflash

collector wash trays or beds 2 PSI (140Millibar)

c Collectiors and packed beds above the washsection of a vacuum Tower 1 PSI (70 Millibar)

4 Failure sequence Tray assemblies wheneverpossible shall be designed so that failure will occurin the following ordera Tray manwaysb Tray deck active areasc Minor beams and downcomersd Major beams (defined as beams 10ft (3 Meters)

or longer or beams which extend across a vesselwithout interruption regardless of length)

5 Allowable stresses Allowable unit stress shall bebased on yield strength Fy at design temperaturewith AISC factors for tension bearing shear etc

6 Allowable Deflection The calculated combineddeflection of trays and support beams due to oper-ating loads shall not exceed the lesser of 1900 of thevessel diameter (in inches) or 316 (5 mm)

RECOMMENDED TRAY SPACING amp MANWAY SIZE

COLUMN DIA

(FT)

TRAY SPACING

(IN)

MANWAY

SPACING

MIN MANWAY

SIZE

25 to 16 24 Every 10 trays 18 in

16 to 24 30 Every 8 trays 20 in

24 to 32 36 Every 6 trays 24 in

32 and larger 42 Every 4 trays 30 in

374 Pressure Vessel Design Manual

Procedure 5-10 Flow Over Weirs

Notation

b frac14 width ftH frac14 static head of liquid ftQ frac14 discharge rate cu ftsecV frac14 velocity of approach ftsecH0 frac14 head correction per Table 5-22

Calculations

Discharge Q

bull For a full-length weir (Case 1)

Q frac14 333beth15 HTHORNbull For a contracted weir (Case 2)

Q frac14 333beth15 HTHORNbull For a V-notch weir (Case 3)

Q frac14 633 H

bull For a Cippoletti weir (Case 4)

Q frac14 3367beth15 HTHORN

Notes

1 Assumes troughs are level

Case 1 Full-Width Weir

V frac14 1ndash2 ftsec at 4 H upstream

Case 2 Contracted Weir

V frac14 1ndash2 ftsec at 3 H upstream

Case 3 V-Notch Weir

V frac14 5 ftsec at 5 H upstream

Case 4 Cippoletti Weir

V frac14 1ndash2 ftsec at 4 H upstream

Table 5-21Head correction for velocity of approach

V 04 06 08 10 12 14 16 18 20

Hrsquo 0002 0005 001 0015 0023 003 004 005 0062

V 22 24 26 28 30 32 34 36 38

Hrsquo 0075 0089 0105 0122 014 015 0179 0201 0213

Vessel Internals 375

Procedure 5-11 Design of Demisters

Demister pads or mist eliminators are important inter-nals in process vessels Anytime there is a continuous twophase flow vapor and liquid there is the possibility forliquid entrainment If it is desirable to separate the liquidand vapor or prevent liquid carryover in the vapor streamthe velocity must be kept sufficiently low to allow the liquiddroplets to fall out of the vapor stream Demister pads areeffective entrainment separators which allow operation atvapor velocities that would otherwise be excessive

ldquoVapor disengagementrdquo can be accomplished withouta demister but the vessel must be made much larger toaccomplish the same degree of separation This is knownas gravity separation

Demister pads are used in a wide variety of processvessels Good performance can be achieved at velocitiesof 30 to 110 of optimum

Demister pads can be used in vertical or horizontalvessels The mesh pad orientation can be either vertical orhorizontal in a vertical or horizontal vessel

A wire mesh demister consists of a knitted wire matmounted on a light weight support grid The mesh is madeby weaving small diameter metal wire into a mesh Padsmay be made out of metal or plastics Metal type includecarbon steel stainless steel monel and others Plasticmaterials include PTFE HDPE and PP

Pressure drop is usually extremely low in the range of1 inch of water column maximum The pressure drop isnormally so low that it is ignored in design

Vapor disengagement is dependent on the velocity ofthe stream The most common equation for determining theallowable vapor velocity for two phase flows is as follows

Va frac14 K frac12ethrL rVTHORN=rV1=2

Where

Va frac14 Allowable vapor velocity FtSecK frac14 Constant or coefficientrL frac14 Density of liquid PCFrV frac14 Density of vapor PCF

Notes

1 The mesh pad shall be in one piece or sectional asrequired for insertion through the vessel manwayEach pad section shall be removable through thevessel manhole

2 Layers shall not be more than 6 inches thick3 Where more than one layer is required all joints

shall be staggered

4 One piece circular pads may be spiral in form5 Each section of mesh shall include a grid on one or

both sides The grid wire andor fastening deviceshall be the same material as the mesh pad Top andbottom grids shall be constructed of frac14 inch diam-eter rods welded to ⅛ inch by 1 inch bars Themaximum gap between mesh pad and grids shall befrac12 inch for diameters less than 84 inches and 1 inchfor larger diameters

6 Estimate grid weights as 3 PSF7 Tie down wires shall be 1=16 inch diameter wire thru

frac14 inch diameter holes on 4 inch centers Tie wiresshould not be pushed through the pad as this couldcause leak paths

8 Pressure drop across mist eliminator shall beassumed as 02 PSI for support design

9 Unless otherwise specified support rings shall be2 inches wide for pads 84 inches in diameter andless and 3 inches wide for larger diameters

10 The mist eliminator shall be a tight fit against theshell or enclosure as well as between sections Meshpads shall be⅜ inches oversize all around for a forcefit against the enclosure No gaps are allowed

11 Vessel fabricator shall provide the mesh and gridsas well as any stiffeners required

12 The Mist eliminator shall be specified as either topor bottom removable

13 ldquoKrdquo is a constant or coefficient that is a functionof the efficiency of the separation K-values rangefrom 04 to 43 but are generally in the 15 to 35range The K-value is affected by pressure type ofpad size of wire type of vessel and disengagingheight For pressure applications the K-valueshould be decreased by 01 for every 100 PSI ofpressure after 100 PSI

14 Wire diameter for the mesh pad itself vary from0003 to 0016 inches

15 The free volume of demisters range from 92 to994

16 The density of the pads ranges from 3 to 33 PCF17 The NSA (nominal surface area) is the surface area

to volume ratio Ft2 Ft3 and is an important indi-cator of performance Ratios range from 50 to 600

18 To obtain higher separation efficiencies the wirediameter is decreased and the density and thicknessare increased

19 Typical width of sections for multi-section pads is12 inches (300 mm) but may vary by manufacturer

376 Pressure Vessel Design Manual

A Horizontal element B Vertical elements

Vertical vessels

Manway

Plate-Pakunit

Meshpad

Drain tubewith seal trap

END VIEW

END VIEW

SIDE VIEW

SIDE VIEW

C Vertical element

Horizontal vessels

D Horizontal element

Figure 5-15 Typical demister configurations in vessels

Vessel Internals 377

d

E Axial entrance

H gt (23) D ndash d

H gt D2 + d(minimum 24rdquo)

H gt D2 ndash d2

H gt D2 + d

H gt D2 ndash d2

h gt d

D

D Side entrance

d

D

B Axial exit

d

D

Φ lt 45ordm

Φ lt 45ordm

C Reverse axial exit

d

A Side exit

D

Figure 5-16 Guidelines for maintaining even flow distribution in vessels with axial flow

378 Pressure Vessel Design Manual

wire mesh

Top grid

Bottom grid

Vertical 14rdquo rodsspaced 12rdquo to 18rdquocenter to center

12rdquo to 18rdquosegmentwidth

18rdquo x 1rdquo flat bars14rdquo rodsspaced 6rdquocenterto center

Manway

Support ring

Support beam

Tie wires

Figure 5-17 Typical mesh pad construction and installation

Vessel Internals 379

Table 5-22Properties of demister pads

Type NSA (1) Ft2 Ft3 Density Pcf Wire Dia in Free Area York Style No Remarks

A 48 5 0011 99 931 High Throughput

B 65 7 0011 986 531 Economy Performance

C 85 9 0011 982 431 Standard - Good All

Around

D 110 108 0011 977 421 Heavy Duty

E 140 8 0006 984 326 Super High Efficiency -

Fine Mist

F 163 0006 94 371 Liquid - Liquid Coalescer

G 450 20 00045 959

H 600 27 00045 945

Notes

1 NSA frac14 Nominal Surface Area

Table 5-23Values of K (Note 13)

Based on Pressure

Pressure (PSIa) Vacuum (In Hg)

Pressure (PSIa) K Vacuum (In Hg) K

15 035 30 035

50 034 20 032

100 032 10 028

200 031 5 023

300 03 1 017

500 028 lt1 017

1000 027

gt1000 027

Based on Disengaging Height

Disengaging Height in K Disengaging Height in K

3 012 9 032

4 015 10 035

5 019 11 038

6 022 12 04

7 025 13 042

8 029 14 043

Based on Application

Vertical Vessels Horizontal Vessels

Type K Type K

General 035 General 035

Compressor Suction Drums 025 Steam Drums 025

Steam Drums 015

380 Pressure Vessel Design Manual

Procedure 5-12 Design of Baffles [10]

Baffles are frequently used in pressure vessels eithervertical or horizontal to divide the interior volume intodifferent compartments These compartments may beused to segregate liquids or provide overflow weirs forthe separation of liquids Baffles may be stiffened orunstiffened When welded across the entire cross sectionof the vessel they must be checked that they are notunduly restricting the diametral expansion of the vesselIf the unrestrained radial expansion of the vessel exceedsthat of the baffle by more than 1=16 in (⅛ in on thediameter) then a ldquoflexiblerdquo type of connection betweenthe vessel shell and the baffle should be utilized Variousflexible attachment designs are shown within theprocedure

Baffles should always be designed in the corrodedcondition It is typical for welded baffles to be designedwith a full corrosion allowance on both sides If the baffleis bolted in then one-half the full corrosion allowancemay be applied to each side the logic being that a boltedbaffle is removable and therefore replaceable

The majority of baffles are flat and as a result are veryinefficient from a strength standpoint Deflection is thegoverning case for flat plates loaded on one side Thepreference is to have unstiffened baffles and they shouldalways be the first choice This will be acceptable forsmall baffles However for larger baffles as the bafflethickness becomes excessive stiffeners offer a moreeconomical design Therefore stiffeners are frequentlyused to stiffen the baffle to prevent the thickness of thebaffle from becoming excessive The number size andspacing of stiffeners are dependent on the baffle thicknessselected There is a continual trade-off between bafflethickness and stiffener parameters

The design of a baffle with stiffeners is an iterativeprocess The procedure for the design of the stiffeners isfirst to divide the baffle into ldquopanelrdquo sections that are rigidenough to withstand the pressure applied on one sideEach individual panel is checked as a flat plate of thedimensions of the panel The stiffeners are assumed to bestrong enough to provide the necessary edge support forthe panel

The stiffeners themselves are designed next A sectionof the baffle is assumed as acting with the stiffener and ascontributing to the overall stiffness This combinedsection is known as the composite stiffener Thecomposite section is checked for stress and deflectionBoth vertical and horizontal stiffeners can be added asrequired

If required an alternate design is assumed based ona thicker or thinner baffle and checked until a satisfactorydesign is found There is no ldquorightrdquo answer however itshould be noted that the thinner the baffle the greater thenumber of stiffeners The lightest overall weight isprobably the ldquobestrdquo design but may not be the leastexpensive due to the welding costs in attaching thestiffeners

One alternative to a flat baffle with stiffeners is to go toa curved baffle A curved baffle works best as a verticalbaffle in a vertical vessel The curved baffle takes pressurefrom either side wall If the pressure is on the concave sidethe baffle is in tension If the pressure is on the convexside the baffle is in compression

There are various tables given in this procedure for flatplate coefficients Flat plate coefficients are utilized todetermine the baffle thickness or a panel thickness Eachtable is specific for a given condition and loading

Vessel Internals 381

Notation

Ap frac14 area of baffle working with stiffener in2

As frac14 area of stiffener in2

Cp frac14 distance from centroid of composite section topanel in

Cs frac14 distance from centroid of composite section tostiffener in

E frac14 modulus of elasticity psiFb frac14 allowable bending stress psiI frac14 moment of inertia composite in4

Is frac14 moment of inertia stiffener in4

l frac14 length of baffle that works with the stiffener inM frac14 moment in-lbn frac14 number of welds attaching stiffenerP frac14 vessel internal pressure psigp frac14 maximum uniform pressure psipn frac14 uniform pressure at any elevation an psiRm frac14 vessel mean radius inSg frac14 specific gravity of contentst frac14 thickness shell intb frac14 thickness baffle ints frac14 thickness stiffener inV frac14 shear load lbw frac14 required fillet weld size ina frac14 thermal coefficient of expansion ininF

bg frac14 flat plate coefficientsDT frac14 differential temperature (design temperature

minus 70F) Fsb frac14 bending stress in baffle psiss frac14 bending stress in stiffener psi

6n frac14 radial expansion ind frac14 deflection inda frac14 maximum allowable deflection in

Baffle Dimensions

382 Pressure Vessel Design Manual

Table 5-24Flat plate coefficients

Vessel Internals 383

Unstiffened Baffle Check

bull Find load p

p frac14 624aSg144

bull Find baffle thickness tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

s

bull Find baffle deflection d

d frac14 pg1b4

Et3b

Limit deflection to the smaller of tb2 or b360 Ifdeflection is excessive then

a Increase the baffle thicknessb Add stiffenersc Go to curved baffle design

If stiffeners are added the first step is to find themaximum ldquoardquo and ldquobrdquo dimensions that will meet theallowable deflection for a given panel size This willestablish the stiffener spacing for both horizontal andvertical stiffeners The ultimate design is a balancebetween baffle thickness stiffener spacing and stiffenersize

Thermal Check of Baffle

bull Vessel radial expansion due to pressure

D1 frac14 085PRm

tE

bull Vessel radial expansion due to temperature

D2 frac14 Rma DT

bull Thermal expansion of baffle

D3 frac14 05ba DT

bull Differential expansion

D4 frac14 D1 thorn D2 D3

Stiffener Design

Divide baffle into panels to limit deflection to the lesserof tb2 or b360 Deflection is calculated based on theappropriate Cases 1 through 3

bull Check baffle for panel size a0 b0bull Check stiffener for length a or b

Recommendations for attaching stiffeners

Benefits Provides added stiffness and no corrosiontrap

Figure 5-18 Example of stiffener layout

384 Pressure Vessel Design Manual

As frac14 tsh

Ap frac14 tbl

IS frac14 tsh3

12

Cp frac14 AsyAs thorn Ap

thorn tb2

Cs frac14 ethhthorn tbTHORN Cp

I frac14 IS thorn Apt2b12

thorn AsApy2

As thorn Ap

lsquo frac14 lesser of 32tb or stiffener spacing

Stresses in BaffleStiffener

sp frac14 MCp

I

ss frac14 MCs

I

Size Welds Attaching Stiffeners

For E70XX Welds

w frac14 Vdy11 200In

Table 5-25Intermittent Welds

Percent of

Continuous Weld

Length of Intermittent Welds

and Distance Between Centers

75 3e4

66 4e6

60 3e5

57 4e7

50 2e4 3e6 4e8

44 4e9

43 3e7

40 2e5 4e10

37 3e8

33 2e6 3e9 4e12

Reprinted by permission of the James F Lincoln Arc Welding

Foundation

Vessel Internals 385

For E60XX Welds

w frac14 Vdy9600In

Sample Problem

bull Given Horizontal vessel with a vertical baffle

P frac14 250 psig

DT frac14 500F

Material frac14 SA-516-70

Ca frac14 0125 in

JE frac14 10

E frac14 273 106 psi

a frac14 7124 10-6 in=in=FFy frac14 308 ksi

D frac14 240 in

Fb frac14 066 Fy frac14 2033 ksi

Rm frac14 120938

ts frac14 175 in

Sg frac14 08

a frac14 15 ft

DT frac14 500 70 frac14 430F

bull Find baffle thickness without stiffener

p frac14 624aSg144

frac14 52 psi

a

bratio frac14 15=20 frac14 075

from Table 5-25 Case 1

b1 frac14 016 g1 frac14 0033

bull Thickness of baffle tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

sfrac14

ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi016eth52THORN2402

20 330

s

tb frac14 153thorn 025 frac14 178

No good Use stiffeners

bull Assume a suitable baffle thickness and determinemaximum panel size

tb frac14 075 in corroded

maximum panel size frac14 4ft 4ft

bull Maximum pressure p

p frac14 13eth624THORN08144

frac14 45 psi

a

bfrac14 4

4frac14 1

See Table 5-25 Case 3

b3 frac14 0287 g3 frac14 00443

sb frac14 b3pb2n

t2

frac14 0287eth45THORN4820752

frac14 5290 psi lt 20 333 psiFigure 5-19 Sample problem

386 Pressure Vessel Design Manual

d frac14 g3

pE

b4nt3

frac14 00443

45

273 106

484

0753

frac14 0092 in lt 0375 in

Balance OK by inspection

bull Assume a layout where the maximum stiffenerspacing is 4 ft

(4) horizontal stiffeners(4) vertical stiffeners(18) panels

bull Check horizontal stiffeners

Dimensions

a1 frac14 3 ft b1 frac14 4 ft

a2 frac14 4 ft b2 frac14 4 ft

a3 frac14 4 ft b3 frac14 12 ft

a4 frac14 4 ft b4 frac14 196 ft

a5 frac14 13 ft

a6 frac14 148ft

bull Assume stiffener size 1 in 4 in

y frac14 2375 in

As frac14 tsh frac14 1eth4THORN frac14 4 in2

l frac14 32tb frac14 32eth075THORN frac14 24 in lt 48 in

AP frac14 tbl frac14 07524 frac14 18 in2

Is frac14 bh3

12frac14 1

43

12frac14 533 in4

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 533thorn 0633thorn 1846 frac14 2442 in4

Cp frac14 AsyAs thorn Ap

thorn tb2

frac14 4eth2375THORN22

thorn 0752

frac14 0807 in

Cs frac14 hthorn tb

Cp

frac14 4thorn 075 0807 frac14 3943

Check deflections

Deflections exceed allowable No good

bull Assume a larger stiffener size WT9 593

tf frac14 106 025 frac14 081

tw frac14 0625 025 frac14 0375

bull Check corroded thickness to find properties ofcorroded section This section would be equivalent toa WT9 30 Properties are

As frac14 882 in2

Is frac14 647 in4

Cs frac14 216 in

H frac14 9 in

Cp frac14 hthorn tb Cs

frac14 9thorn 075 216 frac14 759 in

Figure 5-20 Battle layout for sample problem

Item bn pn d

1 2352 104 149

2 2352 243 349

3 144 381 0767

Vessel Internals 387

y frac14 Cp tb2

frac14 7215 in

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 647thorn 0844thorn 30814 frac14 3737 in4

bull Check stresses and deflections See results in Table5-27

bull Stresses and deflections are acceptablebull Check welds

d frac14 ts thorn 2tw frac14 0375thorn 2eth0323THORN frac14 102

y frac14 7215 in

I frac14 3737 in4

n frac14 2

w frac14 Vdy11 200In

frac14 6681eth102THORN721511 200eth3737THORN2

frac14 0005thorn 0125 frac14 013 in

bull Check thermal expansion of baffle

D1 frac14 085PRm

tEfrac14 085eth250THORN120938

175eth273 106THORNfrac14 000054 in

D2 frac14 Rma DT frac14 1209387124 106430

frac14 0370 in

D3 frac14 05ba DT frac14 05240

7124 106430

frac14 0367 in

D4 frac14 D1 thorn D2 D3 frac14 000054thorn 0370 0367

frac14 00035 lt 006 in

Table 5-26Summary of Results for Stress and Deflection in Composite Stiffeners for Sample Problem

Item Orientation an bn pn M d V sp ss

1 Horiz 2352 d 104 172595 009 2690 3504 997

2 Horiz 2352 d 243 403275 021 6287 8186 2330

3 Horiz 144 d 381 237012 0045 6035 4811 1370

4 Vert d 156 450 154674 0037 5648 3141 894

5 Vert d 1776 513 228539 0072 6681 6681 1320

Figure 5-21 Details of weld attaching stiffener

388 Pressure Vessel Design Manual

Vessel Internals 389

Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 4: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

DOWNCOMER

SPARGER DETAILS

DETAIL 1

DETAIL 3

DETAIL 5 DETAIL 6

DETAIL 4

DETAIL 2

NO

HO

LES

SLO

TSIN

TH

IS A

REA

BLANK OFF ENDSOF HEADER

frac14 DRAIN HOLEAT BOTTOM OF PIPE

frac14 VENT HOLE ATTOP OF PIPE(EACH END)

INSULATING BAFFLESPARGER

SPARGER

SPARGER

SUPT CLIPS

INLET WEIR

5 NPS

SAME AS DOWNCOMER SPACING

5 N

PS +

10

15 NPS

2 N

PS

NPS + 1

15 NPS + 1

INLET BAFFLE

INLET WEIR

SAME ASDOWNCOMER SPACING

5 N

PS

5 NPS

t

t = 025 INCHES + 2 Ca MINIMUM

15

NPS

2 NPS

CL SLOTS OR HOLES

NPS + 2 INCHES

α

α = 30ndash45deg

2

Vessel Internals 361

362 Pressure Vessel Design Manual

Table 5-15Cross sectional area of pipe Ap in

2

Pipe Size

Schedule

10 40 80 160

1 0945 0864 0719 0522

125 1633 1496 1283 1057

15 2222 2036 1767 1404

2 3654 3356 2953 224

25 545 479 424 355

3 835 739 66 541

4 1425 1273 115 928

6 317 289 261 211

8 545 50 457 365

10 853 789 718 567

12 1206 1119 1016 805

14 1431 1353 1227 983

16 1887 1767 1609 129

18 2405 2237 2042 1637

20 2986 278 2527 2027

Table 5-16Size (ID) of equalizing branches inches

Size of Main Pipe Area Ap in2 (2)

Quantity of Branches (3)

2 4 6 8 10 12

2 3356 1461 103

3 739 217 153 125

4 1273 285 201 164 142

6 289 429 303 248 214 192

8 50 564 399 326 282 252

10 789 708 5 409 354 317 289

12 1119 844 597 487 422 377 345

14 1353 928 656 536 464 415 379

16 1767 106 75 612 53 474 433

18 2237 1193 843 688 597 533 487

20 278 133 94 768 711 595 543

Notes

1 The table lists the exact ID required such that the cross sectional area of the main line and the sum of the cross sectional area of the branches is

equal

2 Assumes that main line is Sch 40

3 Quantity of branches shown is total Assume equal quantity for each side

Vessel Internals 363

364 Pressure Vessel Design Manual

27637125

23625

6

DEAD LEG

THIS ENDONLY

BEAMS NOT SHOWN IN ELEVATION FOR CLARITY

361

25

22

185

2244

44

44

195

plusmn0

63

plusmn06

331

75

44

44

44

37125

14oslash

14oslash

24625 2462538125 38125

283

75

38125 38125

R1

R1

DEAD LEG

BEAM NOT SHOWN IN ELEVATION FOR CLARITY

SPRAY HEADERS - EXAMPLES

plusmn07

1

10oslash

6

324375

51 5133625 33625521875 521875 521875

370

TOP OF PACKING

521875

30

30

265

571

457

496

25

602

5

602

560

25

603

75

602

5

388

75

602

5

A2

10oslashA2

Vessel Internals 365

Procedure 5-9 Design of Trays

Typical Tower Dimensions and Nomenclature

1

2

5

4

11

2115

12

29

13

8 10

6

7

322

19

31

2

9

25

24

2318

17

20

22

1413

16

24

30

36 35

27

28

28 26

28

2 PASS

1 PASS

C

E

F

G

A34

4rdquo MIN

33

26 2827

H

2

31

32

C

KL J

N

MP

Q

E

TL

TL

366 Pressure Vessel Design Manual

Tray Types

1 Valve2 Bubble Cap3 Sieve4 Tunnel5 Chimney6 Ripple7 Shower8 Shed Rows9 Disc amp Donut10 Cartridge11 Jet12 Kittle13 Turbogrid14 Dual Flow15 Slotted16 Venturi17 Cascade18 Accumulator

Tray Nomenclature

1 InletFeedReflux2 Inlet Weir3 Inlet Baffle4 Downcomer Clearance5 Weir Height6 Anti-Jump Baffle7 Seal Pan8 Straight Downcomer9 Sloped Downcomer10 Side Downcomer11 Center Downcomer12 Insulating Baffle13 Draw (Off) Nozzle14 Draw (Off) Pan15 Pass Transition16 Total Draw Chimney Tray

17 Chimney18 Chimney Hat19 Return Nozzle20 Sump21 Intermediate Feed Nozzle22 Partial Drawoff Nozzle23 Partition24 Vapor Inlet25 Vapor Inlet Baffle26 Feed Area27 Active Tray Area28 Dowcomer Area (Inactive Tray Area)29 Vapor Outlet30 Baffle31 Internal Pipe32 Support Clips33 Internal Flanges34 End Plate35 Product Outlet Nozzle36 Reboiler Draw Nozzle

Dimensions

A frac14 Short frac14 5 NPSthorn 4 in

Long frac14 5 NPSthorn 10 in

B frac14 Same as middle downcomer

C frac14 5 NPS

D frac14 Same as weir height

E frac14 NPSthorn 6 in

F frac14 NPSthorn 1 in

G frac14 15 NPSthorn 1 in

H frac14 5 NPSthorn 15 in

J frac14 15 NPS

Vessel Internals 367

K frac14 NPS

L frac14 2 NPS

M frac14 Minimum with 21 SE head frac1425 Dthorn tH thorn 15 NPSthorn 2 in

Minimum with hemi head frac14M frac14 5 Dthorn tH thorn 15 NPSthorn 2 in

N frac14 Minimum distance from tangent line to nozzlecenterline See Table 519

P frac14 Minimum skirt height for 21 SE Head SeeTable 5-20

Q frac14 Minimum seal pan depth frac14 tray spacing thorn 6 inR frac14 Downcomer width

Table 5-18Minimum Distance From Tangent Line ldquoNrdquo

Noz Size N Noz Size N

lt2 in 5 12 in 16

3 in 7 14 in 18

4 in 8 16 in 20

6 in 10 18 in 24

8 in 12 20 in 27

10 in 14 24 in 30

Table 5-19Minimum Skirt Height ldquoPrdquo

Dia P Dia P

lt24 in 2 ft e 6 in 114e120 5 ft e 6 in

30e36 3 ft e 0 in 126e132 6 ft e 0 in

48e54 3 ft e 6 in 138e144 6 ft e 6 in

54e60 3 ft e 6 in 150e156 7 ft e 0 in

66e72 4 ft e 0 in 162e168 8 ft e 0 in

78e84 4 ft e 6 in 174e180 8 ft e 6 in

90e106 5 ft e 0 in

368 Pressure Vessel Design Manual

A1 A1

A1

A1 A1

A1 A1

A1 A2

A2A1

A1A1

A1

A1

A1

A1

A2 A2

A2

A2A1

AS AS

AS

AS

AC

AC AC

AQ

D

SIDE DOWNCOMER

CENTERDOWNCOMER

TRAYS

1-PASS TRAY 2-PASS TRAY 3-PASS TRAY 4-PASS TRAY

Vessel Internals 369

TYPICAL TRAY ASSEMBLY

Hex Head Bolt

Manway Lock Clamps

Manway Lock StudsManway Clamps

Seal Plate

Tray Floor (Active)

Tray Floor (Active)Outlet Weir

Downcomer Truss

Standard WasherHex NutFrictional Washer

Downcomer Panel

Downcomer Bolting Bar

Bottom Tray ClampHex Head Bolt DowncomerTruss

Hex NutFrictional Washer

DOWNCOMER BOLTING BAR

Hex Nut

Hex Nut

Hex Nut

Hex Head Bolt

Hex Head Bolt

Frictional Washer

Bottom Tray Clamp

Tray Floor (Inlet Panel)

TRAY FLOOR

(INLET PANEL)

TRAY SUPPORT RING

Tray Support Ring

Manway (Active)

ONE PASS TRAY SHOWN

370 Pressure Vessel Design Manual

Design of Tray Plates

Stress and DeflectionCase 1 Perforated Plate

Reference Roark 5th Edition Table 26 Case 1A

bull Rectangular platebull Uniformly loadedbull All edges simply supported

DATA

a b g frac14 Coefficients from Table 5-21E frac14 Modulus of elasticity at design temperature PSI

t frac14 Corroded thickness of tray inCa frac14 Corrosion allowance inn frac14 Hole efficiencyd frac14 Deflection at center inp frac14 Uniform load PSIs frac14 Bending stress PSI

FORMULAS

bull Stress s

s frac14 b p b4

n t2

BUBBLE-CAPTRAY

VALVELIQUID FLOW

WEIRDOWNCOMER

VAPOR

VAPORVAPOR

VAPOR

VAPOR

TYPES OF TRAYS

CHIMNEY CHIMNEY HAT

SUMPTRUSS

CHIMNEYACCUMULATOR TRAYS

LIQUID

LIQUID

LIQUID

SIEVE TRAY

VALVE TRAY

BUBBLE - CAP TRAY

USUALLY2rsquondash0rdquo

18rdquo MINIMUM

Vessel Internals 371

bull Deflection d

d frac14 a p b4

E n t3

bull Efficiency of holes for perforated plate n

n frac14 1 25 p d2

e C

DIMENSIONAL DATA

a frac14b frac14t frac14a=b frac14b frac14a frac14p frac14d frac14e frac14C frac14E frac14

Tray DesignCase 2 Standard tray plates

LOADS

A DL frac14 Dead load weight of trays and beams

B LL frac14 Live load dynamic load DP

C LL frac14 Liquid load weight of liquid supported

bull Total area AT

AT frac14 p D2=4 frac14 7854 D2

bull Total load PT

PT frac14 DLthorn LLthorn LL

bull Uniform load p

p frac14 PT=AT

LONG EDGE

SHORTEDGEBEAMS (TYP)

c = PITCH60deg

a

b

e

d

Table 5-20Coefficients

ab b a g

10 2874 044 420

12 3762 0616 455

14 4530 0770 478

16 5172 0906 491

18 5688 1017 499

20 6102 1110 503

30 7134 1335 505

40 7410 1400 502

50 7476 1417 501

N 7500 1421 500

372 Pressure Vessel Design Manual

PROPERTIES OF SECTIONS

C frac14 SAY=SA

I frac14 SAY2 thorn SI C SAY

Z frac14 I=C

CALCULATIONS

bull Determine panel area AP

AP frac14 Ln dnbull Load on panel FP

FP frac14 AP p

Uniform Load

bull Uniform load on beam w

w frac14 FP=Ln

bull Moment M

M frac14 w L2

n

8

bull Bending stress fb

fb frac14 M=Z

bull Deflection d

d frac14 5 w L4

n

384 E I

Concentrated Load

bull Moment M

M frac14 ethP LnTHORN=4bull Bending stress fb

fb frac14 M=Z

bull Deflection d

d frac14 P L3

n

48 E I

TYPE 1

1

2

XX

h

dn

t

PART A Y AY AY2 I12sum

C frac14 SAY=SA

I frac14 SAY2 thorn SI C SAY

Z frac14 I=C

TYPE 2

1

32

XX

h

dn

do

t

PART A Y AY AY2 I123sum

L1

DC

DIMENSIONS OF TRAY PANELS

d1 d2 d3 d4

Vessel Internals 373

NOTES1 Design Loads Trays pans drawoff boxes or

similar intemals shall be designed using a corrodedthickness to support their own weight plus thefollowing live loadsa Fractionation trays Design live load shall be the

greater of 20 PSF (98 KgSq meter) or the weightof water 2 (50 mm) over the highest weirsetting

b Areas under downcomers Design live load shallbe the greater of 64 PSF (314 Kg Sq meter) ora head of water one half the height of thedowncomer

c Pans (accumulator and drawoff pans) Designlive load shall be the greater of 1 PSI (700 Kg Sqmeter) or the weight of water at the maximumoperating level of the pan

d Baffles With no operating liquid level shall usea design live load of 1 PSI (700 KgSq meter) onthe projected horizontal area or actual impulseforce whichever is greater

2 Maintenance Loads Tray support members (allbeams support clips etc) shall be designed fora concentrated load of 300 Lbs (135 Kg) at any pointon the installed assembly The design shall be basedon the corroded thicknesses and an allowable stressof 9 Fy For maintenance loads stresses in the trayplates need not be considered

3 Uplift resistance Typical design of uplift for traysand packing is 25 PSI (17 Millibar) For serviceswhere excessive uplift can occur a higher upliftresistance may be used Examples of higher upliftfactors are as follows

a Crude and FCC side strippers 1 PSI (70 millibar)b Vacuum tower stripping trays overflash

collector wash trays or beds 2 PSI (140Millibar)

c Collectiors and packed beds above the washsection of a vacuum Tower 1 PSI (70 Millibar)

4 Failure sequence Tray assemblies wheneverpossible shall be designed so that failure will occurin the following ordera Tray manwaysb Tray deck active areasc Minor beams and downcomersd Major beams (defined as beams 10ft (3 Meters)

or longer or beams which extend across a vesselwithout interruption regardless of length)

5 Allowable stresses Allowable unit stress shall bebased on yield strength Fy at design temperaturewith AISC factors for tension bearing shear etc

6 Allowable Deflection The calculated combineddeflection of trays and support beams due to oper-ating loads shall not exceed the lesser of 1900 of thevessel diameter (in inches) or 316 (5 mm)

RECOMMENDED TRAY SPACING amp MANWAY SIZE

COLUMN DIA

(FT)

TRAY SPACING

(IN)

MANWAY

SPACING

MIN MANWAY

SIZE

25 to 16 24 Every 10 trays 18 in

16 to 24 30 Every 8 trays 20 in

24 to 32 36 Every 6 trays 24 in

32 and larger 42 Every 4 trays 30 in

374 Pressure Vessel Design Manual

Procedure 5-10 Flow Over Weirs

Notation

b frac14 width ftH frac14 static head of liquid ftQ frac14 discharge rate cu ftsecV frac14 velocity of approach ftsecH0 frac14 head correction per Table 5-22

Calculations

Discharge Q

bull For a full-length weir (Case 1)

Q frac14 333beth15 HTHORNbull For a contracted weir (Case 2)

Q frac14 333beth15 HTHORNbull For a V-notch weir (Case 3)

Q frac14 633 H

bull For a Cippoletti weir (Case 4)

Q frac14 3367beth15 HTHORN

Notes

1 Assumes troughs are level

Case 1 Full-Width Weir

V frac14 1ndash2 ftsec at 4 H upstream

Case 2 Contracted Weir

V frac14 1ndash2 ftsec at 3 H upstream

Case 3 V-Notch Weir

V frac14 5 ftsec at 5 H upstream

Case 4 Cippoletti Weir

V frac14 1ndash2 ftsec at 4 H upstream

Table 5-21Head correction for velocity of approach

V 04 06 08 10 12 14 16 18 20

Hrsquo 0002 0005 001 0015 0023 003 004 005 0062

V 22 24 26 28 30 32 34 36 38

Hrsquo 0075 0089 0105 0122 014 015 0179 0201 0213

Vessel Internals 375

Procedure 5-11 Design of Demisters

Demister pads or mist eliminators are important inter-nals in process vessels Anytime there is a continuous twophase flow vapor and liquid there is the possibility forliquid entrainment If it is desirable to separate the liquidand vapor or prevent liquid carryover in the vapor streamthe velocity must be kept sufficiently low to allow the liquiddroplets to fall out of the vapor stream Demister pads areeffective entrainment separators which allow operation atvapor velocities that would otherwise be excessive

ldquoVapor disengagementrdquo can be accomplished withouta demister but the vessel must be made much larger toaccomplish the same degree of separation This is knownas gravity separation

Demister pads are used in a wide variety of processvessels Good performance can be achieved at velocitiesof 30 to 110 of optimum

Demister pads can be used in vertical or horizontalvessels The mesh pad orientation can be either vertical orhorizontal in a vertical or horizontal vessel

A wire mesh demister consists of a knitted wire matmounted on a light weight support grid The mesh is madeby weaving small diameter metal wire into a mesh Padsmay be made out of metal or plastics Metal type includecarbon steel stainless steel monel and others Plasticmaterials include PTFE HDPE and PP

Pressure drop is usually extremely low in the range of1 inch of water column maximum The pressure drop isnormally so low that it is ignored in design

Vapor disengagement is dependent on the velocity ofthe stream The most common equation for determining theallowable vapor velocity for two phase flows is as follows

Va frac14 K frac12ethrL rVTHORN=rV1=2

Where

Va frac14 Allowable vapor velocity FtSecK frac14 Constant or coefficientrL frac14 Density of liquid PCFrV frac14 Density of vapor PCF

Notes

1 The mesh pad shall be in one piece or sectional asrequired for insertion through the vessel manwayEach pad section shall be removable through thevessel manhole

2 Layers shall not be more than 6 inches thick3 Where more than one layer is required all joints

shall be staggered

4 One piece circular pads may be spiral in form5 Each section of mesh shall include a grid on one or

both sides The grid wire andor fastening deviceshall be the same material as the mesh pad Top andbottom grids shall be constructed of frac14 inch diam-eter rods welded to ⅛ inch by 1 inch bars Themaximum gap between mesh pad and grids shall befrac12 inch for diameters less than 84 inches and 1 inchfor larger diameters

6 Estimate grid weights as 3 PSF7 Tie down wires shall be 1=16 inch diameter wire thru

frac14 inch diameter holes on 4 inch centers Tie wiresshould not be pushed through the pad as this couldcause leak paths

8 Pressure drop across mist eliminator shall beassumed as 02 PSI for support design

9 Unless otherwise specified support rings shall be2 inches wide for pads 84 inches in diameter andless and 3 inches wide for larger diameters

10 The mist eliminator shall be a tight fit against theshell or enclosure as well as between sections Meshpads shall be⅜ inches oversize all around for a forcefit against the enclosure No gaps are allowed

11 Vessel fabricator shall provide the mesh and gridsas well as any stiffeners required

12 The Mist eliminator shall be specified as either topor bottom removable

13 ldquoKrdquo is a constant or coefficient that is a functionof the efficiency of the separation K-values rangefrom 04 to 43 but are generally in the 15 to 35range The K-value is affected by pressure type ofpad size of wire type of vessel and disengagingheight For pressure applications the K-valueshould be decreased by 01 for every 100 PSI ofpressure after 100 PSI

14 Wire diameter for the mesh pad itself vary from0003 to 0016 inches

15 The free volume of demisters range from 92 to994

16 The density of the pads ranges from 3 to 33 PCF17 The NSA (nominal surface area) is the surface area

to volume ratio Ft2 Ft3 and is an important indi-cator of performance Ratios range from 50 to 600

18 To obtain higher separation efficiencies the wirediameter is decreased and the density and thicknessare increased

19 Typical width of sections for multi-section pads is12 inches (300 mm) but may vary by manufacturer

376 Pressure Vessel Design Manual

A Horizontal element B Vertical elements

Vertical vessels

Manway

Plate-Pakunit

Meshpad

Drain tubewith seal trap

END VIEW

END VIEW

SIDE VIEW

SIDE VIEW

C Vertical element

Horizontal vessels

D Horizontal element

Figure 5-15 Typical demister configurations in vessels

Vessel Internals 377

d

E Axial entrance

H gt (23) D ndash d

H gt D2 + d(minimum 24rdquo)

H gt D2 ndash d2

H gt D2 + d

H gt D2 ndash d2

h gt d

D

D Side entrance

d

D

B Axial exit

d

D

Φ lt 45ordm

Φ lt 45ordm

C Reverse axial exit

d

A Side exit

D

Figure 5-16 Guidelines for maintaining even flow distribution in vessels with axial flow

378 Pressure Vessel Design Manual

wire mesh

Top grid

Bottom grid

Vertical 14rdquo rodsspaced 12rdquo to 18rdquocenter to center

12rdquo to 18rdquosegmentwidth

18rdquo x 1rdquo flat bars14rdquo rodsspaced 6rdquocenterto center

Manway

Support ring

Support beam

Tie wires

Figure 5-17 Typical mesh pad construction and installation

Vessel Internals 379

Table 5-22Properties of demister pads

Type NSA (1) Ft2 Ft3 Density Pcf Wire Dia in Free Area York Style No Remarks

A 48 5 0011 99 931 High Throughput

B 65 7 0011 986 531 Economy Performance

C 85 9 0011 982 431 Standard - Good All

Around

D 110 108 0011 977 421 Heavy Duty

E 140 8 0006 984 326 Super High Efficiency -

Fine Mist

F 163 0006 94 371 Liquid - Liquid Coalescer

G 450 20 00045 959

H 600 27 00045 945

Notes

1 NSA frac14 Nominal Surface Area

Table 5-23Values of K (Note 13)

Based on Pressure

Pressure (PSIa) Vacuum (In Hg)

Pressure (PSIa) K Vacuum (In Hg) K

15 035 30 035

50 034 20 032

100 032 10 028

200 031 5 023

300 03 1 017

500 028 lt1 017

1000 027

gt1000 027

Based on Disengaging Height

Disengaging Height in K Disengaging Height in K

3 012 9 032

4 015 10 035

5 019 11 038

6 022 12 04

7 025 13 042

8 029 14 043

Based on Application

Vertical Vessels Horizontal Vessels

Type K Type K

General 035 General 035

Compressor Suction Drums 025 Steam Drums 025

Steam Drums 015

380 Pressure Vessel Design Manual

Procedure 5-12 Design of Baffles [10]

Baffles are frequently used in pressure vessels eithervertical or horizontal to divide the interior volume intodifferent compartments These compartments may beused to segregate liquids or provide overflow weirs forthe separation of liquids Baffles may be stiffened orunstiffened When welded across the entire cross sectionof the vessel they must be checked that they are notunduly restricting the diametral expansion of the vesselIf the unrestrained radial expansion of the vessel exceedsthat of the baffle by more than 1=16 in (⅛ in on thediameter) then a ldquoflexiblerdquo type of connection betweenthe vessel shell and the baffle should be utilized Variousflexible attachment designs are shown within theprocedure

Baffles should always be designed in the corrodedcondition It is typical for welded baffles to be designedwith a full corrosion allowance on both sides If the baffleis bolted in then one-half the full corrosion allowancemay be applied to each side the logic being that a boltedbaffle is removable and therefore replaceable

The majority of baffles are flat and as a result are veryinefficient from a strength standpoint Deflection is thegoverning case for flat plates loaded on one side Thepreference is to have unstiffened baffles and they shouldalways be the first choice This will be acceptable forsmall baffles However for larger baffles as the bafflethickness becomes excessive stiffeners offer a moreeconomical design Therefore stiffeners are frequentlyused to stiffen the baffle to prevent the thickness of thebaffle from becoming excessive The number size andspacing of stiffeners are dependent on the baffle thicknessselected There is a continual trade-off between bafflethickness and stiffener parameters

The design of a baffle with stiffeners is an iterativeprocess The procedure for the design of the stiffeners isfirst to divide the baffle into ldquopanelrdquo sections that are rigidenough to withstand the pressure applied on one sideEach individual panel is checked as a flat plate of thedimensions of the panel The stiffeners are assumed to bestrong enough to provide the necessary edge support forthe panel

The stiffeners themselves are designed next A sectionof the baffle is assumed as acting with the stiffener and ascontributing to the overall stiffness This combinedsection is known as the composite stiffener Thecomposite section is checked for stress and deflectionBoth vertical and horizontal stiffeners can be added asrequired

If required an alternate design is assumed based ona thicker or thinner baffle and checked until a satisfactorydesign is found There is no ldquorightrdquo answer however itshould be noted that the thinner the baffle the greater thenumber of stiffeners The lightest overall weight isprobably the ldquobestrdquo design but may not be the leastexpensive due to the welding costs in attaching thestiffeners

One alternative to a flat baffle with stiffeners is to go toa curved baffle A curved baffle works best as a verticalbaffle in a vertical vessel The curved baffle takes pressurefrom either side wall If the pressure is on the concave sidethe baffle is in tension If the pressure is on the convexside the baffle is in compression

There are various tables given in this procedure for flatplate coefficients Flat plate coefficients are utilized todetermine the baffle thickness or a panel thickness Eachtable is specific for a given condition and loading

Vessel Internals 381

Notation

Ap frac14 area of baffle working with stiffener in2

As frac14 area of stiffener in2

Cp frac14 distance from centroid of composite section topanel in

Cs frac14 distance from centroid of composite section tostiffener in

E frac14 modulus of elasticity psiFb frac14 allowable bending stress psiI frac14 moment of inertia composite in4

Is frac14 moment of inertia stiffener in4

l frac14 length of baffle that works with the stiffener inM frac14 moment in-lbn frac14 number of welds attaching stiffenerP frac14 vessel internal pressure psigp frac14 maximum uniform pressure psipn frac14 uniform pressure at any elevation an psiRm frac14 vessel mean radius inSg frac14 specific gravity of contentst frac14 thickness shell intb frac14 thickness baffle ints frac14 thickness stiffener inV frac14 shear load lbw frac14 required fillet weld size ina frac14 thermal coefficient of expansion ininF

bg frac14 flat plate coefficientsDT frac14 differential temperature (design temperature

minus 70F) Fsb frac14 bending stress in baffle psiss frac14 bending stress in stiffener psi

6n frac14 radial expansion ind frac14 deflection inda frac14 maximum allowable deflection in

Baffle Dimensions

382 Pressure Vessel Design Manual

Table 5-24Flat plate coefficients

Vessel Internals 383

Unstiffened Baffle Check

bull Find load p

p frac14 624aSg144

bull Find baffle thickness tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

s

bull Find baffle deflection d

d frac14 pg1b4

Et3b

Limit deflection to the smaller of tb2 or b360 Ifdeflection is excessive then

a Increase the baffle thicknessb Add stiffenersc Go to curved baffle design

If stiffeners are added the first step is to find themaximum ldquoardquo and ldquobrdquo dimensions that will meet theallowable deflection for a given panel size This willestablish the stiffener spacing for both horizontal andvertical stiffeners The ultimate design is a balancebetween baffle thickness stiffener spacing and stiffenersize

Thermal Check of Baffle

bull Vessel radial expansion due to pressure

D1 frac14 085PRm

tE

bull Vessel radial expansion due to temperature

D2 frac14 Rma DT

bull Thermal expansion of baffle

D3 frac14 05ba DT

bull Differential expansion

D4 frac14 D1 thorn D2 D3

Stiffener Design

Divide baffle into panels to limit deflection to the lesserof tb2 or b360 Deflection is calculated based on theappropriate Cases 1 through 3

bull Check baffle for panel size a0 b0bull Check stiffener for length a or b

Recommendations for attaching stiffeners

Benefits Provides added stiffness and no corrosiontrap

Figure 5-18 Example of stiffener layout

384 Pressure Vessel Design Manual

As frac14 tsh

Ap frac14 tbl

IS frac14 tsh3

12

Cp frac14 AsyAs thorn Ap

thorn tb2

Cs frac14 ethhthorn tbTHORN Cp

I frac14 IS thorn Apt2b12

thorn AsApy2

As thorn Ap

lsquo frac14 lesser of 32tb or stiffener spacing

Stresses in BaffleStiffener

sp frac14 MCp

I

ss frac14 MCs

I

Size Welds Attaching Stiffeners

For E70XX Welds

w frac14 Vdy11 200In

Table 5-25Intermittent Welds

Percent of

Continuous Weld

Length of Intermittent Welds

and Distance Between Centers

75 3e4

66 4e6

60 3e5

57 4e7

50 2e4 3e6 4e8

44 4e9

43 3e7

40 2e5 4e10

37 3e8

33 2e6 3e9 4e12

Reprinted by permission of the James F Lincoln Arc Welding

Foundation

Vessel Internals 385

For E60XX Welds

w frac14 Vdy9600In

Sample Problem

bull Given Horizontal vessel with a vertical baffle

P frac14 250 psig

DT frac14 500F

Material frac14 SA-516-70

Ca frac14 0125 in

JE frac14 10

E frac14 273 106 psi

a frac14 7124 10-6 in=in=FFy frac14 308 ksi

D frac14 240 in

Fb frac14 066 Fy frac14 2033 ksi

Rm frac14 120938

ts frac14 175 in

Sg frac14 08

a frac14 15 ft

DT frac14 500 70 frac14 430F

bull Find baffle thickness without stiffener

p frac14 624aSg144

frac14 52 psi

a

bratio frac14 15=20 frac14 075

from Table 5-25 Case 1

b1 frac14 016 g1 frac14 0033

bull Thickness of baffle tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

sfrac14

ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi016eth52THORN2402

20 330

s

tb frac14 153thorn 025 frac14 178

No good Use stiffeners

bull Assume a suitable baffle thickness and determinemaximum panel size

tb frac14 075 in corroded

maximum panel size frac14 4ft 4ft

bull Maximum pressure p

p frac14 13eth624THORN08144

frac14 45 psi

a

bfrac14 4

4frac14 1

See Table 5-25 Case 3

b3 frac14 0287 g3 frac14 00443

sb frac14 b3pb2n

t2

frac14 0287eth45THORN4820752

frac14 5290 psi lt 20 333 psiFigure 5-19 Sample problem

386 Pressure Vessel Design Manual

d frac14 g3

pE

b4nt3

frac14 00443

45

273 106

484

0753

frac14 0092 in lt 0375 in

Balance OK by inspection

bull Assume a layout where the maximum stiffenerspacing is 4 ft

(4) horizontal stiffeners(4) vertical stiffeners(18) panels

bull Check horizontal stiffeners

Dimensions

a1 frac14 3 ft b1 frac14 4 ft

a2 frac14 4 ft b2 frac14 4 ft

a3 frac14 4 ft b3 frac14 12 ft

a4 frac14 4 ft b4 frac14 196 ft

a5 frac14 13 ft

a6 frac14 148ft

bull Assume stiffener size 1 in 4 in

y frac14 2375 in

As frac14 tsh frac14 1eth4THORN frac14 4 in2

l frac14 32tb frac14 32eth075THORN frac14 24 in lt 48 in

AP frac14 tbl frac14 07524 frac14 18 in2

Is frac14 bh3

12frac14 1

43

12frac14 533 in4

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 533thorn 0633thorn 1846 frac14 2442 in4

Cp frac14 AsyAs thorn Ap

thorn tb2

frac14 4eth2375THORN22

thorn 0752

frac14 0807 in

Cs frac14 hthorn tb

Cp

frac14 4thorn 075 0807 frac14 3943

Check deflections

Deflections exceed allowable No good

bull Assume a larger stiffener size WT9 593

tf frac14 106 025 frac14 081

tw frac14 0625 025 frac14 0375

bull Check corroded thickness to find properties ofcorroded section This section would be equivalent toa WT9 30 Properties are

As frac14 882 in2

Is frac14 647 in4

Cs frac14 216 in

H frac14 9 in

Cp frac14 hthorn tb Cs

frac14 9thorn 075 216 frac14 759 in

Figure 5-20 Battle layout for sample problem

Item bn pn d

1 2352 104 149

2 2352 243 349

3 144 381 0767

Vessel Internals 387

y frac14 Cp tb2

frac14 7215 in

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 647thorn 0844thorn 30814 frac14 3737 in4

bull Check stresses and deflections See results in Table5-27

bull Stresses and deflections are acceptablebull Check welds

d frac14 ts thorn 2tw frac14 0375thorn 2eth0323THORN frac14 102

y frac14 7215 in

I frac14 3737 in4

n frac14 2

w frac14 Vdy11 200In

frac14 6681eth102THORN721511 200eth3737THORN2

frac14 0005thorn 0125 frac14 013 in

bull Check thermal expansion of baffle

D1 frac14 085PRm

tEfrac14 085eth250THORN120938

175eth273 106THORNfrac14 000054 in

D2 frac14 Rma DT frac14 1209387124 106430

frac14 0370 in

D3 frac14 05ba DT frac14 05240

7124 106430

frac14 0367 in

D4 frac14 D1 thorn D2 D3 frac14 000054thorn 0370 0367

frac14 00035 lt 006 in

Table 5-26Summary of Results for Stress and Deflection in Composite Stiffeners for Sample Problem

Item Orientation an bn pn M d V sp ss

1 Horiz 2352 d 104 172595 009 2690 3504 997

2 Horiz 2352 d 243 403275 021 6287 8186 2330

3 Horiz 144 d 381 237012 0045 6035 4811 1370

4 Vert d 156 450 154674 0037 5648 3141 894

5 Vert d 1776 513 228539 0072 6681 6681 1320

Figure 5-21 Details of weld attaching stiffener

388 Pressure Vessel Design Manual

Vessel Internals 389

Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 5: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

362 Pressure Vessel Design Manual

Table 5-15Cross sectional area of pipe Ap in

2

Pipe Size

Schedule

10 40 80 160

1 0945 0864 0719 0522

125 1633 1496 1283 1057

15 2222 2036 1767 1404

2 3654 3356 2953 224

25 545 479 424 355

3 835 739 66 541

4 1425 1273 115 928

6 317 289 261 211

8 545 50 457 365

10 853 789 718 567

12 1206 1119 1016 805

14 1431 1353 1227 983

16 1887 1767 1609 129

18 2405 2237 2042 1637

20 2986 278 2527 2027

Table 5-16Size (ID) of equalizing branches inches

Size of Main Pipe Area Ap in2 (2)

Quantity of Branches (3)

2 4 6 8 10 12

2 3356 1461 103

3 739 217 153 125

4 1273 285 201 164 142

6 289 429 303 248 214 192

8 50 564 399 326 282 252

10 789 708 5 409 354 317 289

12 1119 844 597 487 422 377 345

14 1353 928 656 536 464 415 379

16 1767 106 75 612 53 474 433

18 2237 1193 843 688 597 533 487

20 278 133 94 768 711 595 543

Notes

1 The table lists the exact ID required such that the cross sectional area of the main line and the sum of the cross sectional area of the branches is

equal

2 Assumes that main line is Sch 40

3 Quantity of branches shown is total Assume equal quantity for each side

Vessel Internals 363

364 Pressure Vessel Design Manual

27637125

23625

6

DEAD LEG

THIS ENDONLY

BEAMS NOT SHOWN IN ELEVATION FOR CLARITY

361

25

22

185

2244

44

44

195

plusmn0

63

plusmn06

331

75

44

44

44

37125

14oslash

14oslash

24625 2462538125 38125

283

75

38125 38125

R1

R1

DEAD LEG

BEAM NOT SHOWN IN ELEVATION FOR CLARITY

SPRAY HEADERS - EXAMPLES

plusmn07

1

10oslash

6

324375

51 5133625 33625521875 521875 521875

370

TOP OF PACKING

521875

30

30

265

571

457

496

25

602

5

602

560

25

603

75

602

5

388

75

602

5

A2

10oslashA2

Vessel Internals 365

Procedure 5-9 Design of Trays

Typical Tower Dimensions and Nomenclature

1

2

5

4

11

2115

12

29

13

8 10

6

7

322

19

31

2

9

25

24

2318

17

20

22

1413

16

24

30

36 35

27

28

28 26

28

2 PASS

1 PASS

C

E

F

G

A34

4rdquo MIN

33

26 2827

H

2

31

32

C

KL J

N

MP

Q

E

TL

TL

366 Pressure Vessel Design Manual

Tray Types

1 Valve2 Bubble Cap3 Sieve4 Tunnel5 Chimney6 Ripple7 Shower8 Shed Rows9 Disc amp Donut10 Cartridge11 Jet12 Kittle13 Turbogrid14 Dual Flow15 Slotted16 Venturi17 Cascade18 Accumulator

Tray Nomenclature

1 InletFeedReflux2 Inlet Weir3 Inlet Baffle4 Downcomer Clearance5 Weir Height6 Anti-Jump Baffle7 Seal Pan8 Straight Downcomer9 Sloped Downcomer10 Side Downcomer11 Center Downcomer12 Insulating Baffle13 Draw (Off) Nozzle14 Draw (Off) Pan15 Pass Transition16 Total Draw Chimney Tray

17 Chimney18 Chimney Hat19 Return Nozzle20 Sump21 Intermediate Feed Nozzle22 Partial Drawoff Nozzle23 Partition24 Vapor Inlet25 Vapor Inlet Baffle26 Feed Area27 Active Tray Area28 Dowcomer Area (Inactive Tray Area)29 Vapor Outlet30 Baffle31 Internal Pipe32 Support Clips33 Internal Flanges34 End Plate35 Product Outlet Nozzle36 Reboiler Draw Nozzle

Dimensions

A frac14 Short frac14 5 NPSthorn 4 in

Long frac14 5 NPSthorn 10 in

B frac14 Same as middle downcomer

C frac14 5 NPS

D frac14 Same as weir height

E frac14 NPSthorn 6 in

F frac14 NPSthorn 1 in

G frac14 15 NPSthorn 1 in

H frac14 5 NPSthorn 15 in

J frac14 15 NPS

Vessel Internals 367

K frac14 NPS

L frac14 2 NPS

M frac14 Minimum with 21 SE head frac1425 Dthorn tH thorn 15 NPSthorn 2 in

Minimum with hemi head frac14M frac14 5 Dthorn tH thorn 15 NPSthorn 2 in

N frac14 Minimum distance from tangent line to nozzlecenterline See Table 519

P frac14 Minimum skirt height for 21 SE Head SeeTable 5-20

Q frac14 Minimum seal pan depth frac14 tray spacing thorn 6 inR frac14 Downcomer width

Table 5-18Minimum Distance From Tangent Line ldquoNrdquo

Noz Size N Noz Size N

lt2 in 5 12 in 16

3 in 7 14 in 18

4 in 8 16 in 20

6 in 10 18 in 24

8 in 12 20 in 27

10 in 14 24 in 30

Table 5-19Minimum Skirt Height ldquoPrdquo

Dia P Dia P

lt24 in 2 ft e 6 in 114e120 5 ft e 6 in

30e36 3 ft e 0 in 126e132 6 ft e 0 in

48e54 3 ft e 6 in 138e144 6 ft e 6 in

54e60 3 ft e 6 in 150e156 7 ft e 0 in

66e72 4 ft e 0 in 162e168 8 ft e 0 in

78e84 4 ft e 6 in 174e180 8 ft e 6 in

90e106 5 ft e 0 in

368 Pressure Vessel Design Manual

A1 A1

A1

A1 A1

A1 A1

A1 A2

A2A1

A1A1

A1

A1

A1

A1

A2 A2

A2

A2A1

AS AS

AS

AS

AC

AC AC

AQ

D

SIDE DOWNCOMER

CENTERDOWNCOMER

TRAYS

1-PASS TRAY 2-PASS TRAY 3-PASS TRAY 4-PASS TRAY

Vessel Internals 369

TYPICAL TRAY ASSEMBLY

Hex Head Bolt

Manway Lock Clamps

Manway Lock StudsManway Clamps

Seal Plate

Tray Floor (Active)

Tray Floor (Active)Outlet Weir

Downcomer Truss

Standard WasherHex NutFrictional Washer

Downcomer Panel

Downcomer Bolting Bar

Bottom Tray ClampHex Head Bolt DowncomerTruss

Hex NutFrictional Washer

DOWNCOMER BOLTING BAR

Hex Nut

Hex Nut

Hex Nut

Hex Head Bolt

Hex Head Bolt

Frictional Washer

Bottom Tray Clamp

Tray Floor (Inlet Panel)

TRAY FLOOR

(INLET PANEL)

TRAY SUPPORT RING

Tray Support Ring

Manway (Active)

ONE PASS TRAY SHOWN

370 Pressure Vessel Design Manual

Design of Tray Plates

Stress and DeflectionCase 1 Perforated Plate

Reference Roark 5th Edition Table 26 Case 1A

bull Rectangular platebull Uniformly loadedbull All edges simply supported

DATA

a b g frac14 Coefficients from Table 5-21E frac14 Modulus of elasticity at design temperature PSI

t frac14 Corroded thickness of tray inCa frac14 Corrosion allowance inn frac14 Hole efficiencyd frac14 Deflection at center inp frac14 Uniform load PSIs frac14 Bending stress PSI

FORMULAS

bull Stress s

s frac14 b p b4

n t2

BUBBLE-CAPTRAY

VALVELIQUID FLOW

WEIRDOWNCOMER

VAPOR

VAPORVAPOR

VAPOR

VAPOR

TYPES OF TRAYS

CHIMNEY CHIMNEY HAT

SUMPTRUSS

CHIMNEYACCUMULATOR TRAYS

LIQUID

LIQUID

LIQUID

SIEVE TRAY

VALVE TRAY

BUBBLE - CAP TRAY

USUALLY2rsquondash0rdquo

18rdquo MINIMUM

Vessel Internals 371

bull Deflection d

d frac14 a p b4

E n t3

bull Efficiency of holes for perforated plate n

n frac14 1 25 p d2

e C

DIMENSIONAL DATA

a frac14b frac14t frac14a=b frac14b frac14a frac14p frac14d frac14e frac14C frac14E frac14

Tray DesignCase 2 Standard tray plates

LOADS

A DL frac14 Dead load weight of trays and beams

B LL frac14 Live load dynamic load DP

C LL frac14 Liquid load weight of liquid supported

bull Total area AT

AT frac14 p D2=4 frac14 7854 D2

bull Total load PT

PT frac14 DLthorn LLthorn LL

bull Uniform load p

p frac14 PT=AT

LONG EDGE

SHORTEDGEBEAMS (TYP)

c = PITCH60deg

a

b

e

d

Table 5-20Coefficients

ab b a g

10 2874 044 420

12 3762 0616 455

14 4530 0770 478

16 5172 0906 491

18 5688 1017 499

20 6102 1110 503

30 7134 1335 505

40 7410 1400 502

50 7476 1417 501

N 7500 1421 500

372 Pressure Vessel Design Manual

PROPERTIES OF SECTIONS

C frac14 SAY=SA

I frac14 SAY2 thorn SI C SAY

Z frac14 I=C

CALCULATIONS

bull Determine panel area AP

AP frac14 Ln dnbull Load on panel FP

FP frac14 AP p

Uniform Load

bull Uniform load on beam w

w frac14 FP=Ln

bull Moment M

M frac14 w L2

n

8

bull Bending stress fb

fb frac14 M=Z

bull Deflection d

d frac14 5 w L4

n

384 E I

Concentrated Load

bull Moment M

M frac14 ethP LnTHORN=4bull Bending stress fb

fb frac14 M=Z

bull Deflection d

d frac14 P L3

n

48 E I

TYPE 1

1

2

XX

h

dn

t

PART A Y AY AY2 I12sum

C frac14 SAY=SA

I frac14 SAY2 thorn SI C SAY

Z frac14 I=C

TYPE 2

1

32

XX

h

dn

do

t

PART A Y AY AY2 I123sum

L1

DC

DIMENSIONS OF TRAY PANELS

d1 d2 d3 d4

Vessel Internals 373

NOTES1 Design Loads Trays pans drawoff boxes or

similar intemals shall be designed using a corrodedthickness to support their own weight plus thefollowing live loadsa Fractionation trays Design live load shall be the

greater of 20 PSF (98 KgSq meter) or the weightof water 2 (50 mm) over the highest weirsetting

b Areas under downcomers Design live load shallbe the greater of 64 PSF (314 Kg Sq meter) ora head of water one half the height of thedowncomer

c Pans (accumulator and drawoff pans) Designlive load shall be the greater of 1 PSI (700 Kg Sqmeter) or the weight of water at the maximumoperating level of the pan

d Baffles With no operating liquid level shall usea design live load of 1 PSI (700 KgSq meter) onthe projected horizontal area or actual impulseforce whichever is greater

2 Maintenance Loads Tray support members (allbeams support clips etc) shall be designed fora concentrated load of 300 Lbs (135 Kg) at any pointon the installed assembly The design shall be basedon the corroded thicknesses and an allowable stressof 9 Fy For maintenance loads stresses in the trayplates need not be considered

3 Uplift resistance Typical design of uplift for traysand packing is 25 PSI (17 Millibar) For serviceswhere excessive uplift can occur a higher upliftresistance may be used Examples of higher upliftfactors are as follows

a Crude and FCC side strippers 1 PSI (70 millibar)b Vacuum tower stripping trays overflash

collector wash trays or beds 2 PSI (140Millibar)

c Collectiors and packed beds above the washsection of a vacuum Tower 1 PSI (70 Millibar)

4 Failure sequence Tray assemblies wheneverpossible shall be designed so that failure will occurin the following ordera Tray manwaysb Tray deck active areasc Minor beams and downcomersd Major beams (defined as beams 10ft (3 Meters)

or longer or beams which extend across a vesselwithout interruption regardless of length)

5 Allowable stresses Allowable unit stress shall bebased on yield strength Fy at design temperaturewith AISC factors for tension bearing shear etc

6 Allowable Deflection The calculated combineddeflection of trays and support beams due to oper-ating loads shall not exceed the lesser of 1900 of thevessel diameter (in inches) or 316 (5 mm)

RECOMMENDED TRAY SPACING amp MANWAY SIZE

COLUMN DIA

(FT)

TRAY SPACING

(IN)

MANWAY

SPACING

MIN MANWAY

SIZE

25 to 16 24 Every 10 trays 18 in

16 to 24 30 Every 8 trays 20 in

24 to 32 36 Every 6 trays 24 in

32 and larger 42 Every 4 trays 30 in

374 Pressure Vessel Design Manual

Procedure 5-10 Flow Over Weirs

Notation

b frac14 width ftH frac14 static head of liquid ftQ frac14 discharge rate cu ftsecV frac14 velocity of approach ftsecH0 frac14 head correction per Table 5-22

Calculations

Discharge Q

bull For a full-length weir (Case 1)

Q frac14 333beth15 HTHORNbull For a contracted weir (Case 2)

Q frac14 333beth15 HTHORNbull For a V-notch weir (Case 3)

Q frac14 633 H

bull For a Cippoletti weir (Case 4)

Q frac14 3367beth15 HTHORN

Notes

1 Assumes troughs are level

Case 1 Full-Width Weir

V frac14 1ndash2 ftsec at 4 H upstream

Case 2 Contracted Weir

V frac14 1ndash2 ftsec at 3 H upstream

Case 3 V-Notch Weir

V frac14 5 ftsec at 5 H upstream

Case 4 Cippoletti Weir

V frac14 1ndash2 ftsec at 4 H upstream

Table 5-21Head correction for velocity of approach

V 04 06 08 10 12 14 16 18 20

Hrsquo 0002 0005 001 0015 0023 003 004 005 0062

V 22 24 26 28 30 32 34 36 38

Hrsquo 0075 0089 0105 0122 014 015 0179 0201 0213

Vessel Internals 375

Procedure 5-11 Design of Demisters

Demister pads or mist eliminators are important inter-nals in process vessels Anytime there is a continuous twophase flow vapor and liquid there is the possibility forliquid entrainment If it is desirable to separate the liquidand vapor or prevent liquid carryover in the vapor streamthe velocity must be kept sufficiently low to allow the liquiddroplets to fall out of the vapor stream Demister pads areeffective entrainment separators which allow operation atvapor velocities that would otherwise be excessive

ldquoVapor disengagementrdquo can be accomplished withouta demister but the vessel must be made much larger toaccomplish the same degree of separation This is knownas gravity separation

Demister pads are used in a wide variety of processvessels Good performance can be achieved at velocitiesof 30 to 110 of optimum

Demister pads can be used in vertical or horizontalvessels The mesh pad orientation can be either vertical orhorizontal in a vertical or horizontal vessel

A wire mesh demister consists of a knitted wire matmounted on a light weight support grid The mesh is madeby weaving small diameter metal wire into a mesh Padsmay be made out of metal or plastics Metal type includecarbon steel stainless steel monel and others Plasticmaterials include PTFE HDPE and PP

Pressure drop is usually extremely low in the range of1 inch of water column maximum The pressure drop isnormally so low that it is ignored in design

Vapor disengagement is dependent on the velocity ofthe stream The most common equation for determining theallowable vapor velocity for two phase flows is as follows

Va frac14 K frac12ethrL rVTHORN=rV1=2

Where

Va frac14 Allowable vapor velocity FtSecK frac14 Constant or coefficientrL frac14 Density of liquid PCFrV frac14 Density of vapor PCF

Notes

1 The mesh pad shall be in one piece or sectional asrequired for insertion through the vessel manwayEach pad section shall be removable through thevessel manhole

2 Layers shall not be more than 6 inches thick3 Where more than one layer is required all joints

shall be staggered

4 One piece circular pads may be spiral in form5 Each section of mesh shall include a grid on one or

both sides The grid wire andor fastening deviceshall be the same material as the mesh pad Top andbottom grids shall be constructed of frac14 inch diam-eter rods welded to ⅛ inch by 1 inch bars Themaximum gap between mesh pad and grids shall befrac12 inch for diameters less than 84 inches and 1 inchfor larger diameters

6 Estimate grid weights as 3 PSF7 Tie down wires shall be 1=16 inch diameter wire thru

frac14 inch diameter holes on 4 inch centers Tie wiresshould not be pushed through the pad as this couldcause leak paths

8 Pressure drop across mist eliminator shall beassumed as 02 PSI for support design

9 Unless otherwise specified support rings shall be2 inches wide for pads 84 inches in diameter andless and 3 inches wide for larger diameters

10 The mist eliminator shall be a tight fit against theshell or enclosure as well as between sections Meshpads shall be⅜ inches oversize all around for a forcefit against the enclosure No gaps are allowed

11 Vessel fabricator shall provide the mesh and gridsas well as any stiffeners required

12 The Mist eliminator shall be specified as either topor bottom removable

13 ldquoKrdquo is a constant or coefficient that is a functionof the efficiency of the separation K-values rangefrom 04 to 43 but are generally in the 15 to 35range The K-value is affected by pressure type ofpad size of wire type of vessel and disengagingheight For pressure applications the K-valueshould be decreased by 01 for every 100 PSI ofpressure after 100 PSI

14 Wire diameter for the mesh pad itself vary from0003 to 0016 inches

15 The free volume of demisters range from 92 to994

16 The density of the pads ranges from 3 to 33 PCF17 The NSA (nominal surface area) is the surface area

to volume ratio Ft2 Ft3 and is an important indi-cator of performance Ratios range from 50 to 600

18 To obtain higher separation efficiencies the wirediameter is decreased and the density and thicknessare increased

19 Typical width of sections for multi-section pads is12 inches (300 mm) but may vary by manufacturer

376 Pressure Vessel Design Manual

A Horizontal element B Vertical elements

Vertical vessels

Manway

Plate-Pakunit

Meshpad

Drain tubewith seal trap

END VIEW

END VIEW

SIDE VIEW

SIDE VIEW

C Vertical element

Horizontal vessels

D Horizontal element

Figure 5-15 Typical demister configurations in vessels

Vessel Internals 377

d

E Axial entrance

H gt (23) D ndash d

H gt D2 + d(minimum 24rdquo)

H gt D2 ndash d2

H gt D2 + d

H gt D2 ndash d2

h gt d

D

D Side entrance

d

D

B Axial exit

d

D

Φ lt 45ordm

Φ lt 45ordm

C Reverse axial exit

d

A Side exit

D

Figure 5-16 Guidelines for maintaining even flow distribution in vessels with axial flow

378 Pressure Vessel Design Manual

wire mesh

Top grid

Bottom grid

Vertical 14rdquo rodsspaced 12rdquo to 18rdquocenter to center

12rdquo to 18rdquosegmentwidth

18rdquo x 1rdquo flat bars14rdquo rodsspaced 6rdquocenterto center

Manway

Support ring

Support beam

Tie wires

Figure 5-17 Typical mesh pad construction and installation

Vessel Internals 379

Table 5-22Properties of demister pads

Type NSA (1) Ft2 Ft3 Density Pcf Wire Dia in Free Area York Style No Remarks

A 48 5 0011 99 931 High Throughput

B 65 7 0011 986 531 Economy Performance

C 85 9 0011 982 431 Standard - Good All

Around

D 110 108 0011 977 421 Heavy Duty

E 140 8 0006 984 326 Super High Efficiency -

Fine Mist

F 163 0006 94 371 Liquid - Liquid Coalescer

G 450 20 00045 959

H 600 27 00045 945

Notes

1 NSA frac14 Nominal Surface Area

Table 5-23Values of K (Note 13)

Based on Pressure

Pressure (PSIa) Vacuum (In Hg)

Pressure (PSIa) K Vacuum (In Hg) K

15 035 30 035

50 034 20 032

100 032 10 028

200 031 5 023

300 03 1 017

500 028 lt1 017

1000 027

gt1000 027

Based on Disengaging Height

Disengaging Height in K Disengaging Height in K

3 012 9 032

4 015 10 035

5 019 11 038

6 022 12 04

7 025 13 042

8 029 14 043

Based on Application

Vertical Vessels Horizontal Vessels

Type K Type K

General 035 General 035

Compressor Suction Drums 025 Steam Drums 025

Steam Drums 015

380 Pressure Vessel Design Manual

Procedure 5-12 Design of Baffles [10]

Baffles are frequently used in pressure vessels eithervertical or horizontal to divide the interior volume intodifferent compartments These compartments may beused to segregate liquids or provide overflow weirs forthe separation of liquids Baffles may be stiffened orunstiffened When welded across the entire cross sectionof the vessel they must be checked that they are notunduly restricting the diametral expansion of the vesselIf the unrestrained radial expansion of the vessel exceedsthat of the baffle by more than 1=16 in (⅛ in on thediameter) then a ldquoflexiblerdquo type of connection betweenthe vessel shell and the baffle should be utilized Variousflexible attachment designs are shown within theprocedure

Baffles should always be designed in the corrodedcondition It is typical for welded baffles to be designedwith a full corrosion allowance on both sides If the baffleis bolted in then one-half the full corrosion allowancemay be applied to each side the logic being that a boltedbaffle is removable and therefore replaceable

The majority of baffles are flat and as a result are veryinefficient from a strength standpoint Deflection is thegoverning case for flat plates loaded on one side Thepreference is to have unstiffened baffles and they shouldalways be the first choice This will be acceptable forsmall baffles However for larger baffles as the bafflethickness becomes excessive stiffeners offer a moreeconomical design Therefore stiffeners are frequentlyused to stiffen the baffle to prevent the thickness of thebaffle from becoming excessive The number size andspacing of stiffeners are dependent on the baffle thicknessselected There is a continual trade-off between bafflethickness and stiffener parameters

The design of a baffle with stiffeners is an iterativeprocess The procedure for the design of the stiffeners isfirst to divide the baffle into ldquopanelrdquo sections that are rigidenough to withstand the pressure applied on one sideEach individual panel is checked as a flat plate of thedimensions of the panel The stiffeners are assumed to bestrong enough to provide the necessary edge support forthe panel

The stiffeners themselves are designed next A sectionof the baffle is assumed as acting with the stiffener and ascontributing to the overall stiffness This combinedsection is known as the composite stiffener Thecomposite section is checked for stress and deflectionBoth vertical and horizontal stiffeners can be added asrequired

If required an alternate design is assumed based ona thicker or thinner baffle and checked until a satisfactorydesign is found There is no ldquorightrdquo answer however itshould be noted that the thinner the baffle the greater thenumber of stiffeners The lightest overall weight isprobably the ldquobestrdquo design but may not be the leastexpensive due to the welding costs in attaching thestiffeners

One alternative to a flat baffle with stiffeners is to go toa curved baffle A curved baffle works best as a verticalbaffle in a vertical vessel The curved baffle takes pressurefrom either side wall If the pressure is on the concave sidethe baffle is in tension If the pressure is on the convexside the baffle is in compression

There are various tables given in this procedure for flatplate coefficients Flat plate coefficients are utilized todetermine the baffle thickness or a panel thickness Eachtable is specific for a given condition and loading

Vessel Internals 381

Notation

Ap frac14 area of baffle working with stiffener in2

As frac14 area of stiffener in2

Cp frac14 distance from centroid of composite section topanel in

Cs frac14 distance from centroid of composite section tostiffener in

E frac14 modulus of elasticity psiFb frac14 allowable bending stress psiI frac14 moment of inertia composite in4

Is frac14 moment of inertia stiffener in4

l frac14 length of baffle that works with the stiffener inM frac14 moment in-lbn frac14 number of welds attaching stiffenerP frac14 vessel internal pressure psigp frac14 maximum uniform pressure psipn frac14 uniform pressure at any elevation an psiRm frac14 vessel mean radius inSg frac14 specific gravity of contentst frac14 thickness shell intb frac14 thickness baffle ints frac14 thickness stiffener inV frac14 shear load lbw frac14 required fillet weld size ina frac14 thermal coefficient of expansion ininF

bg frac14 flat plate coefficientsDT frac14 differential temperature (design temperature

minus 70F) Fsb frac14 bending stress in baffle psiss frac14 bending stress in stiffener psi

6n frac14 radial expansion ind frac14 deflection inda frac14 maximum allowable deflection in

Baffle Dimensions

382 Pressure Vessel Design Manual

Table 5-24Flat plate coefficients

Vessel Internals 383

Unstiffened Baffle Check

bull Find load p

p frac14 624aSg144

bull Find baffle thickness tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

s

bull Find baffle deflection d

d frac14 pg1b4

Et3b

Limit deflection to the smaller of tb2 or b360 Ifdeflection is excessive then

a Increase the baffle thicknessb Add stiffenersc Go to curved baffle design

If stiffeners are added the first step is to find themaximum ldquoardquo and ldquobrdquo dimensions that will meet theallowable deflection for a given panel size This willestablish the stiffener spacing for both horizontal andvertical stiffeners The ultimate design is a balancebetween baffle thickness stiffener spacing and stiffenersize

Thermal Check of Baffle

bull Vessel radial expansion due to pressure

D1 frac14 085PRm

tE

bull Vessel radial expansion due to temperature

D2 frac14 Rma DT

bull Thermal expansion of baffle

D3 frac14 05ba DT

bull Differential expansion

D4 frac14 D1 thorn D2 D3

Stiffener Design

Divide baffle into panels to limit deflection to the lesserof tb2 or b360 Deflection is calculated based on theappropriate Cases 1 through 3

bull Check baffle for panel size a0 b0bull Check stiffener for length a or b

Recommendations for attaching stiffeners

Benefits Provides added stiffness and no corrosiontrap

Figure 5-18 Example of stiffener layout

384 Pressure Vessel Design Manual

As frac14 tsh

Ap frac14 tbl

IS frac14 tsh3

12

Cp frac14 AsyAs thorn Ap

thorn tb2

Cs frac14 ethhthorn tbTHORN Cp

I frac14 IS thorn Apt2b12

thorn AsApy2

As thorn Ap

lsquo frac14 lesser of 32tb or stiffener spacing

Stresses in BaffleStiffener

sp frac14 MCp

I

ss frac14 MCs

I

Size Welds Attaching Stiffeners

For E70XX Welds

w frac14 Vdy11 200In

Table 5-25Intermittent Welds

Percent of

Continuous Weld

Length of Intermittent Welds

and Distance Between Centers

75 3e4

66 4e6

60 3e5

57 4e7

50 2e4 3e6 4e8

44 4e9

43 3e7

40 2e5 4e10

37 3e8

33 2e6 3e9 4e12

Reprinted by permission of the James F Lincoln Arc Welding

Foundation

Vessel Internals 385

For E60XX Welds

w frac14 Vdy9600In

Sample Problem

bull Given Horizontal vessel with a vertical baffle

P frac14 250 psig

DT frac14 500F

Material frac14 SA-516-70

Ca frac14 0125 in

JE frac14 10

E frac14 273 106 psi

a frac14 7124 10-6 in=in=FFy frac14 308 ksi

D frac14 240 in

Fb frac14 066 Fy frac14 2033 ksi

Rm frac14 120938

ts frac14 175 in

Sg frac14 08

a frac14 15 ft

DT frac14 500 70 frac14 430F

bull Find baffle thickness without stiffener

p frac14 624aSg144

frac14 52 psi

a

bratio frac14 15=20 frac14 075

from Table 5-25 Case 1

b1 frac14 016 g1 frac14 0033

bull Thickness of baffle tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

sfrac14

ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi016eth52THORN2402

20 330

s

tb frac14 153thorn 025 frac14 178

No good Use stiffeners

bull Assume a suitable baffle thickness and determinemaximum panel size

tb frac14 075 in corroded

maximum panel size frac14 4ft 4ft

bull Maximum pressure p

p frac14 13eth624THORN08144

frac14 45 psi

a

bfrac14 4

4frac14 1

See Table 5-25 Case 3

b3 frac14 0287 g3 frac14 00443

sb frac14 b3pb2n

t2

frac14 0287eth45THORN4820752

frac14 5290 psi lt 20 333 psiFigure 5-19 Sample problem

386 Pressure Vessel Design Manual

d frac14 g3

pE

b4nt3

frac14 00443

45

273 106

484

0753

frac14 0092 in lt 0375 in

Balance OK by inspection

bull Assume a layout where the maximum stiffenerspacing is 4 ft

(4) horizontal stiffeners(4) vertical stiffeners(18) panels

bull Check horizontal stiffeners

Dimensions

a1 frac14 3 ft b1 frac14 4 ft

a2 frac14 4 ft b2 frac14 4 ft

a3 frac14 4 ft b3 frac14 12 ft

a4 frac14 4 ft b4 frac14 196 ft

a5 frac14 13 ft

a6 frac14 148ft

bull Assume stiffener size 1 in 4 in

y frac14 2375 in

As frac14 tsh frac14 1eth4THORN frac14 4 in2

l frac14 32tb frac14 32eth075THORN frac14 24 in lt 48 in

AP frac14 tbl frac14 07524 frac14 18 in2

Is frac14 bh3

12frac14 1

43

12frac14 533 in4

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 533thorn 0633thorn 1846 frac14 2442 in4

Cp frac14 AsyAs thorn Ap

thorn tb2

frac14 4eth2375THORN22

thorn 0752

frac14 0807 in

Cs frac14 hthorn tb

Cp

frac14 4thorn 075 0807 frac14 3943

Check deflections

Deflections exceed allowable No good

bull Assume a larger stiffener size WT9 593

tf frac14 106 025 frac14 081

tw frac14 0625 025 frac14 0375

bull Check corroded thickness to find properties ofcorroded section This section would be equivalent toa WT9 30 Properties are

As frac14 882 in2

Is frac14 647 in4

Cs frac14 216 in

H frac14 9 in

Cp frac14 hthorn tb Cs

frac14 9thorn 075 216 frac14 759 in

Figure 5-20 Battle layout for sample problem

Item bn pn d

1 2352 104 149

2 2352 243 349

3 144 381 0767

Vessel Internals 387

y frac14 Cp tb2

frac14 7215 in

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 647thorn 0844thorn 30814 frac14 3737 in4

bull Check stresses and deflections See results in Table5-27

bull Stresses and deflections are acceptablebull Check welds

d frac14 ts thorn 2tw frac14 0375thorn 2eth0323THORN frac14 102

y frac14 7215 in

I frac14 3737 in4

n frac14 2

w frac14 Vdy11 200In

frac14 6681eth102THORN721511 200eth3737THORN2

frac14 0005thorn 0125 frac14 013 in

bull Check thermal expansion of baffle

D1 frac14 085PRm

tEfrac14 085eth250THORN120938

175eth273 106THORNfrac14 000054 in

D2 frac14 Rma DT frac14 1209387124 106430

frac14 0370 in

D3 frac14 05ba DT frac14 05240

7124 106430

frac14 0367 in

D4 frac14 D1 thorn D2 D3 frac14 000054thorn 0370 0367

frac14 00035 lt 006 in

Table 5-26Summary of Results for Stress and Deflection in Composite Stiffeners for Sample Problem

Item Orientation an bn pn M d V sp ss

1 Horiz 2352 d 104 172595 009 2690 3504 997

2 Horiz 2352 d 243 403275 021 6287 8186 2330

3 Horiz 144 d 381 237012 0045 6035 4811 1370

4 Vert d 156 450 154674 0037 5648 3141 894

5 Vert d 1776 513 228539 0072 6681 6681 1320

Figure 5-21 Details of weld attaching stiffener

388 Pressure Vessel Design Manual

Vessel Internals 389

Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 6: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

Table 5-15Cross sectional area of pipe Ap in

2

Pipe Size

Schedule

10 40 80 160

1 0945 0864 0719 0522

125 1633 1496 1283 1057

15 2222 2036 1767 1404

2 3654 3356 2953 224

25 545 479 424 355

3 835 739 66 541

4 1425 1273 115 928

6 317 289 261 211

8 545 50 457 365

10 853 789 718 567

12 1206 1119 1016 805

14 1431 1353 1227 983

16 1887 1767 1609 129

18 2405 2237 2042 1637

20 2986 278 2527 2027

Table 5-16Size (ID) of equalizing branches inches

Size of Main Pipe Area Ap in2 (2)

Quantity of Branches (3)

2 4 6 8 10 12

2 3356 1461 103

3 739 217 153 125

4 1273 285 201 164 142

6 289 429 303 248 214 192

8 50 564 399 326 282 252

10 789 708 5 409 354 317 289

12 1119 844 597 487 422 377 345

14 1353 928 656 536 464 415 379

16 1767 106 75 612 53 474 433

18 2237 1193 843 688 597 533 487

20 278 133 94 768 711 595 543

Notes

1 The table lists the exact ID required such that the cross sectional area of the main line and the sum of the cross sectional area of the branches is

equal

2 Assumes that main line is Sch 40

3 Quantity of branches shown is total Assume equal quantity for each side

Vessel Internals 363

364 Pressure Vessel Design Manual

27637125

23625

6

DEAD LEG

THIS ENDONLY

BEAMS NOT SHOWN IN ELEVATION FOR CLARITY

361

25

22

185

2244

44

44

195

plusmn0

63

plusmn06

331

75

44

44

44

37125

14oslash

14oslash

24625 2462538125 38125

283

75

38125 38125

R1

R1

DEAD LEG

BEAM NOT SHOWN IN ELEVATION FOR CLARITY

SPRAY HEADERS - EXAMPLES

plusmn07

1

10oslash

6

324375

51 5133625 33625521875 521875 521875

370

TOP OF PACKING

521875

30

30

265

571

457

496

25

602

5

602

560

25

603

75

602

5

388

75

602

5

A2

10oslashA2

Vessel Internals 365

Procedure 5-9 Design of Trays

Typical Tower Dimensions and Nomenclature

1

2

5

4

11

2115

12

29

13

8 10

6

7

322

19

31

2

9

25

24

2318

17

20

22

1413

16

24

30

36 35

27

28

28 26

28

2 PASS

1 PASS

C

E

F

G

A34

4rdquo MIN

33

26 2827

H

2

31

32

C

KL J

N

MP

Q

E

TL

TL

366 Pressure Vessel Design Manual

Tray Types

1 Valve2 Bubble Cap3 Sieve4 Tunnel5 Chimney6 Ripple7 Shower8 Shed Rows9 Disc amp Donut10 Cartridge11 Jet12 Kittle13 Turbogrid14 Dual Flow15 Slotted16 Venturi17 Cascade18 Accumulator

Tray Nomenclature

1 InletFeedReflux2 Inlet Weir3 Inlet Baffle4 Downcomer Clearance5 Weir Height6 Anti-Jump Baffle7 Seal Pan8 Straight Downcomer9 Sloped Downcomer10 Side Downcomer11 Center Downcomer12 Insulating Baffle13 Draw (Off) Nozzle14 Draw (Off) Pan15 Pass Transition16 Total Draw Chimney Tray

17 Chimney18 Chimney Hat19 Return Nozzle20 Sump21 Intermediate Feed Nozzle22 Partial Drawoff Nozzle23 Partition24 Vapor Inlet25 Vapor Inlet Baffle26 Feed Area27 Active Tray Area28 Dowcomer Area (Inactive Tray Area)29 Vapor Outlet30 Baffle31 Internal Pipe32 Support Clips33 Internal Flanges34 End Plate35 Product Outlet Nozzle36 Reboiler Draw Nozzle

Dimensions

A frac14 Short frac14 5 NPSthorn 4 in

Long frac14 5 NPSthorn 10 in

B frac14 Same as middle downcomer

C frac14 5 NPS

D frac14 Same as weir height

E frac14 NPSthorn 6 in

F frac14 NPSthorn 1 in

G frac14 15 NPSthorn 1 in

H frac14 5 NPSthorn 15 in

J frac14 15 NPS

Vessel Internals 367

K frac14 NPS

L frac14 2 NPS

M frac14 Minimum with 21 SE head frac1425 Dthorn tH thorn 15 NPSthorn 2 in

Minimum with hemi head frac14M frac14 5 Dthorn tH thorn 15 NPSthorn 2 in

N frac14 Minimum distance from tangent line to nozzlecenterline See Table 519

P frac14 Minimum skirt height for 21 SE Head SeeTable 5-20

Q frac14 Minimum seal pan depth frac14 tray spacing thorn 6 inR frac14 Downcomer width

Table 5-18Minimum Distance From Tangent Line ldquoNrdquo

Noz Size N Noz Size N

lt2 in 5 12 in 16

3 in 7 14 in 18

4 in 8 16 in 20

6 in 10 18 in 24

8 in 12 20 in 27

10 in 14 24 in 30

Table 5-19Minimum Skirt Height ldquoPrdquo

Dia P Dia P

lt24 in 2 ft e 6 in 114e120 5 ft e 6 in

30e36 3 ft e 0 in 126e132 6 ft e 0 in

48e54 3 ft e 6 in 138e144 6 ft e 6 in

54e60 3 ft e 6 in 150e156 7 ft e 0 in

66e72 4 ft e 0 in 162e168 8 ft e 0 in

78e84 4 ft e 6 in 174e180 8 ft e 6 in

90e106 5 ft e 0 in

368 Pressure Vessel Design Manual

A1 A1

A1

A1 A1

A1 A1

A1 A2

A2A1

A1A1

A1

A1

A1

A1

A2 A2

A2

A2A1

AS AS

AS

AS

AC

AC AC

AQ

D

SIDE DOWNCOMER

CENTERDOWNCOMER

TRAYS

1-PASS TRAY 2-PASS TRAY 3-PASS TRAY 4-PASS TRAY

Vessel Internals 369

TYPICAL TRAY ASSEMBLY

Hex Head Bolt

Manway Lock Clamps

Manway Lock StudsManway Clamps

Seal Plate

Tray Floor (Active)

Tray Floor (Active)Outlet Weir

Downcomer Truss

Standard WasherHex NutFrictional Washer

Downcomer Panel

Downcomer Bolting Bar

Bottom Tray ClampHex Head Bolt DowncomerTruss

Hex NutFrictional Washer

DOWNCOMER BOLTING BAR

Hex Nut

Hex Nut

Hex Nut

Hex Head Bolt

Hex Head Bolt

Frictional Washer

Bottom Tray Clamp

Tray Floor (Inlet Panel)

TRAY FLOOR

(INLET PANEL)

TRAY SUPPORT RING

Tray Support Ring

Manway (Active)

ONE PASS TRAY SHOWN

370 Pressure Vessel Design Manual

Design of Tray Plates

Stress and DeflectionCase 1 Perforated Plate

Reference Roark 5th Edition Table 26 Case 1A

bull Rectangular platebull Uniformly loadedbull All edges simply supported

DATA

a b g frac14 Coefficients from Table 5-21E frac14 Modulus of elasticity at design temperature PSI

t frac14 Corroded thickness of tray inCa frac14 Corrosion allowance inn frac14 Hole efficiencyd frac14 Deflection at center inp frac14 Uniform load PSIs frac14 Bending stress PSI

FORMULAS

bull Stress s

s frac14 b p b4

n t2

BUBBLE-CAPTRAY

VALVELIQUID FLOW

WEIRDOWNCOMER

VAPOR

VAPORVAPOR

VAPOR

VAPOR

TYPES OF TRAYS

CHIMNEY CHIMNEY HAT

SUMPTRUSS

CHIMNEYACCUMULATOR TRAYS

LIQUID

LIQUID

LIQUID

SIEVE TRAY

VALVE TRAY

BUBBLE - CAP TRAY

USUALLY2rsquondash0rdquo

18rdquo MINIMUM

Vessel Internals 371

bull Deflection d

d frac14 a p b4

E n t3

bull Efficiency of holes for perforated plate n

n frac14 1 25 p d2

e C

DIMENSIONAL DATA

a frac14b frac14t frac14a=b frac14b frac14a frac14p frac14d frac14e frac14C frac14E frac14

Tray DesignCase 2 Standard tray plates

LOADS

A DL frac14 Dead load weight of trays and beams

B LL frac14 Live load dynamic load DP

C LL frac14 Liquid load weight of liquid supported

bull Total area AT

AT frac14 p D2=4 frac14 7854 D2

bull Total load PT

PT frac14 DLthorn LLthorn LL

bull Uniform load p

p frac14 PT=AT

LONG EDGE

SHORTEDGEBEAMS (TYP)

c = PITCH60deg

a

b

e

d

Table 5-20Coefficients

ab b a g

10 2874 044 420

12 3762 0616 455

14 4530 0770 478

16 5172 0906 491

18 5688 1017 499

20 6102 1110 503

30 7134 1335 505

40 7410 1400 502

50 7476 1417 501

N 7500 1421 500

372 Pressure Vessel Design Manual

PROPERTIES OF SECTIONS

C frac14 SAY=SA

I frac14 SAY2 thorn SI C SAY

Z frac14 I=C

CALCULATIONS

bull Determine panel area AP

AP frac14 Ln dnbull Load on panel FP

FP frac14 AP p

Uniform Load

bull Uniform load on beam w

w frac14 FP=Ln

bull Moment M

M frac14 w L2

n

8

bull Bending stress fb

fb frac14 M=Z

bull Deflection d

d frac14 5 w L4

n

384 E I

Concentrated Load

bull Moment M

M frac14 ethP LnTHORN=4bull Bending stress fb

fb frac14 M=Z

bull Deflection d

d frac14 P L3

n

48 E I

TYPE 1

1

2

XX

h

dn

t

PART A Y AY AY2 I12sum

C frac14 SAY=SA

I frac14 SAY2 thorn SI C SAY

Z frac14 I=C

TYPE 2

1

32

XX

h

dn

do

t

PART A Y AY AY2 I123sum

L1

DC

DIMENSIONS OF TRAY PANELS

d1 d2 d3 d4

Vessel Internals 373

NOTES1 Design Loads Trays pans drawoff boxes or

similar intemals shall be designed using a corrodedthickness to support their own weight plus thefollowing live loadsa Fractionation trays Design live load shall be the

greater of 20 PSF (98 KgSq meter) or the weightof water 2 (50 mm) over the highest weirsetting

b Areas under downcomers Design live load shallbe the greater of 64 PSF (314 Kg Sq meter) ora head of water one half the height of thedowncomer

c Pans (accumulator and drawoff pans) Designlive load shall be the greater of 1 PSI (700 Kg Sqmeter) or the weight of water at the maximumoperating level of the pan

d Baffles With no operating liquid level shall usea design live load of 1 PSI (700 KgSq meter) onthe projected horizontal area or actual impulseforce whichever is greater

2 Maintenance Loads Tray support members (allbeams support clips etc) shall be designed fora concentrated load of 300 Lbs (135 Kg) at any pointon the installed assembly The design shall be basedon the corroded thicknesses and an allowable stressof 9 Fy For maintenance loads stresses in the trayplates need not be considered

3 Uplift resistance Typical design of uplift for traysand packing is 25 PSI (17 Millibar) For serviceswhere excessive uplift can occur a higher upliftresistance may be used Examples of higher upliftfactors are as follows

a Crude and FCC side strippers 1 PSI (70 millibar)b Vacuum tower stripping trays overflash

collector wash trays or beds 2 PSI (140Millibar)

c Collectiors and packed beds above the washsection of a vacuum Tower 1 PSI (70 Millibar)

4 Failure sequence Tray assemblies wheneverpossible shall be designed so that failure will occurin the following ordera Tray manwaysb Tray deck active areasc Minor beams and downcomersd Major beams (defined as beams 10ft (3 Meters)

or longer or beams which extend across a vesselwithout interruption regardless of length)

5 Allowable stresses Allowable unit stress shall bebased on yield strength Fy at design temperaturewith AISC factors for tension bearing shear etc

6 Allowable Deflection The calculated combineddeflection of trays and support beams due to oper-ating loads shall not exceed the lesser of 1900 of thevessel diameter (in inches) or 316 (5 mm)

RECOMMENDED TRAY SPACING amp MANWAY SIZE

COLUMN DIA

(FT)

TRAY SPACING

(IN)

MANWAY

SPACING

MIN MANWAY

SIZE

25 to 16 24 Every 10 trays 18 in

16 to 24 30 Every 8 trays 20 in

24 to 32 36 Every 6 trays 24 in

32 and larger 42 Every 4 trays 30 in

374 Pressure Vessel Design Manual

Procedure 5-10 Flow Over Weirs

Notation

b frac14 width ftH frac14 static head of liquid ftQ frac14 discharge rate cu ftsecV frac14 velocity of approach ftsecH0 frac14 head correction per Table 5-22

Calculations

Discharge Q

bull For a full-length weir (Case 1)

Q frac14 333beth15 HTHORNbull For a contracted weir (Case 2)

Q frac14 333beth15 HTHORNbull For a V-notch weir (Case 3)

Q frac14 633 H

bull For a Cippoletti weir (Case 4)

Q frac14 3367beth15 HTHORN

Notes

1 Assumes troughs are level

Case 1 Full-Width Weir

V frac14 1ndash2 ftsec at 4 H upstream

Case 2 Contracted Weir

V frac14 1ndash2 ftsec at 3 H upstream

Case 3 V-Notch Weir

V frac14 5 ftsec at 5 H upstream

Case 4 Cippoletti Weir

V frac14 1ndash2 ftsec at 4 H upstream

Table 5-21Head correction for velocity of approach

V 04 06 08 10 12 14 16 18 20

Hrsquo 0002 0005 001 0015 0023 003 004 005 0062

V 22 24 26 28 30 32 34 36 38

Hrsquo 0075 0089 0105 0122 014 015 0179 0201 0213

Vessel Internals 375

Procedure 5-11 Design of Demisters

Demister pads or mist eliminators are important inter-nals in process vessels Anytime there is a continuous twophase flow vapor and liquid there is the possibility forliquid entrainment If it is desirable to separate the liquidand vapor or prevent liquid carryover in the vapor streamthe velocity must be kept sufficiently low to allow the liquiddroplets to fall out of the vapor stream Demister pads areeffective entrainment separators which allow operation atvapor velocities that would otherwise be excessive

ldquoVapor disengagementrdquo can be accomplished withouta demister but the vessel must be made much larger toaccomplish the same degree of separation This is knownas gravity separation

Demister pads are used in a wide variety of processvessels Good performance can be achieved at velocitiesof 30 to 110 of optimum

Demister pads can be used in vertical or horizontalvessels The mesh pad orientation can be either vertical orhorizontal in a vertical or horizontal vessel

A wire mesh demister consists of a knitted wire matmounted on a light weight support grid The mesh is madeby weaving small diameter metal wire into a mesh Padsmay be made out of metal or plastics Metal type includecarbon steel stainless steel monel and others Plasticmaterials include PTFE HDPE and PP

Pressure drop is usually extremely low in the range of1 inch of water column maximum The pressure drop isnormally so low that it is ignored in design

Vapor disengagement is dependent on the velocity ofthe stream The most common equation for determining theallowable vapor velocity for two phase flows is as follows

Va frac14 K frac12ethrL rVTHORN=rV1=2

Where

Va frac14 Allowable vapor velocity FtSecK frac14 Constant or coefficientrL frac14 Density of liquid PCFrV frac14 Density of vapor PCF

Notes

1 The mesh pad shall be in one piece or sectional asrequired for insertion through the vessel manwayEach pad section shall be removable through thevessel manhole

2 Layers shall not be more than 6 inches thick3 Where more than one layer is required all joints

shall be staggered

4 One piece circular pads may be spiral in form5 Each section of mesh shall include a grid on one or

both sides The grid wire andor fastening deviceshall be the same material as the mesh pad Top andbottom grids shall be constructed of frac14 inch diam-eter rods welded to ⅛ inch by 1 inch bars Themaximum gap between mesh pad and grids shall befrac12 inch for diameters less than 84 inches and 1 inchfor larger diameters

6 Estimate grid weights as 3 PSF7 Tie down wires shall be 1=16 inch diameter wire thru

frac14 inch diameter holes on 4 inch centers Tie wiresshould not be pushed through the pad as this couldcause leak paths

8 Pressure drop across mist eliminator shall beassumed as 02 PSI for support design

9 Unless otherwise specified support rings shall be2 inches wide for pads 84 inches in diameter andless and 3 inches wide for larger diameters

10 The mist eliminator shall be a tight fit against theshell or enclosure as well as between sections Meshpads shall be⅜ inches oversize all around for a forcefit against the enclosure No gaps are allowed

11 Vessel fabricator shall provide the mesh and gridsas well as any stiffeners required

12 The Mist eliminator shall be specified as either topor bottom removable

13 ldquoKrdquo is a constant or coefficient that is a functionof the efficiency of the separation K-values rangefrom 04 to 43 but are generally in the 15 to 35range The K-value is affected by pressure type ofpad size of wire type of vessel and disengagingheight For pressure applications the K-valueshould be decreased by 01 for every 100 PSI ofpressure after 100 PSI

14 Wire diameter for the mesh pad itself vary from0003 to 0016 inches

15 The free volume of demisters range from 92 to994

16 The density of the pads ranges from 3 to 33 PCF17 The NSA (nominal surface area) is the surface area

to volume ratio Ft2 Ft3 and is an important indi-cator of performance Ratios range from 50 to 600

18 To obtain higher separation efficiencies the wirediameter is decreased and the density and thicknessare increased

19 Typical width of sections for multi-section pads is12 inches (300 mm) but may vary by manufacturer

376 Pressure Vessel Design Manual

A Horizontal element B Vertical elements

Vertical vessels

Manway

Plate-Pakunit

Meshpad

Drain tubewith seal trap

END VIEW

END VIEW

SIDE VIEW

SIDE VIEW

C Vertical element

Horizontal vessels

D Horizontal element

Figure 5-15 Typical demister configurations in vessels

Vessel Internals 377

d

E Axial entrance

H gt (23) D ndash d

H gt D2 + d(minimum 24rdquo)

H gt D2 ndash d2

H gt D2 + d

H gt D2 ndash d2

h gt d

D

D Side entrance

d

D

B Axial exit

d

D

Φ lt 45ordm

Φ lt 45ordm

C Reverse axial exit

d

A Side exit

D

Figure 5-16 Guidelines for maintaining even flow distribution in vessels with axial flow

378 Pressure Vessel Design Manual

wire mesh

Top grid

Bottom grid

Vertical 14rdquo rodsspaced 12rdquo to 18rdquocenter to center

12rdquo to 18rdquosegmentwidth

18rdquo x 1rdquo flat bars14rdquo rodsspaced 6rdquocenterto center

Manway

Support ring

Support beam

Tie wires

Figure 5-17 Typical mesh pad construction and installation

Vessel Internals 379

Table 5-22Properties of demister pads

Type NSA (1) Ft2 Ft3 Density Pcf Wire Dia in Free Area York Style No Remarks

A 48 5 0011 99 931 High Throughput

B 65 7 0011 986 531 Economy Performance

C 85 9 0011 982 431 Standard - Good All

Around

D 110 108 0011 977 421 Heavy Duty

E 140 8 0006 984 326 Super High Efficiency -

Fine Mist

F 163 0006 94 371 Liquid - Liquid Coalescer

G 450 20 00045 959

H 600 27 00045 945

Notes

1 NSA frac14 Nominal Surface Area

Table 5-23Values of K (Note 13)

Based on Pressure

Pressure (PSIa) Vacuum (In Hg)

Pressure (PSIa) K Vacuum (In Hg) K

15 035 30 035

50 034 20 032

100 032 10 028

200 031 5 023

300 03 1 017

500 028 lt1 017

1000 027

gt1000 027

Based on Disengaging Height

Disengaging Height in K Disengaging Height in K

3 012 9 032

4 015 10 035

5 019 11 038

6 022 12 04

7 025 13 042

8 029 14 043

Based on Application

Vertical Vessels Horizontal Vessels

Type K Type K

General 035 General 035

Compressor Suction Drums 025 Steam Drums 025

Steam Drums 015

380 Pressure Vessel Design Manual

Procedure 5-12 Design of Baffles [10]

Baffles are frequently used in pressure vessels eithervertical or horizontal to divide the interior volume intodifferent compartments These compartments may beused to segregate liquids or provide overflow weirs forthe separation of liquids Baffles may be stiffened orunstiffened When welded across the entire cross sectionof the vessel they must be checked that they are notunduly restricting the diametral expansion of the vesselIf the unrestrained radial expansion of the vessel exceedsthat of the baffle by more than 1=16 in (⅛ in on thediameter) then a ldquoflexiblerdquo type of connection betweenthe vessel shell and the baffle should be utilized Variousflexible attachment designs are shown within theprocedure

Baffles should always be designed in the corrodedcondition It is typical for welded baffles to be designedwith a full corrosion allowance on both sides If the baffleis bolted in then one-half the full corrosion allowancemay be applied to each side the logic being that a boltedbaffle is removable and therefore replaceable

The majority of baffles are flat and as a result are veryinefficient from a strength standpoint Deflection is thegoverning case for flat plates loaded on one side Thepreference is to have unstiffened baffles and they shouldalways be the first choice This will be acceptable forsmall baffles However for larger baffles as the bafflethickness becomes excessive stiffeners offer a moreeconomical design Therefore stiffeners are frequentlyused to stiffen the baffle to prevent the thickness of thebaffle from becoming excessive The number size andspacing of stiffeners are dependent on the baffle thicknessselected There is a continual trade-off between bafflethickness and stiffener parameters

The design of a baffle with stiffeners is an iterativeprocess The procedure for the design of the stiffeners isfirst to divide the baffle into ldquopanelrdquo sections that are rigidenough to withstand the pressure applied on one sideEach individual panel is checked as a flat plate of thedimensions of the panel The stiffeners are assumed to bestrong enough to provide the necessary edge support forthe panel

The stiffeners themselves are designed next A sectionof the baffle is assumed as acting with the stiffener and ascontributing to the overall stiffness This combinedsection is known as the composite stiffener Thecomposite section is checked for stress and deflectionBoth vertical and horizontal stiffeners can be added asrequired

If required an alternate design is assumed based ona thicker or thinner baffle and checked until a satisfactorydesign is found There is no ldquorightrdquo answer however itshould be noted that the thinner the baffle the greater thenumber of stiffeners The lightest overall weight isprobably the ldquobestrdquo design but may not be the leastexpensive due to the welding costs in attaching thestiffeners

One alternative to a flat baffle with stiffeners is to go toa curved baffle A curved baffle works best as a verticalbaffle in a vertical vessel The curved baffle takes pressurefrom either side wall If the pressure is on the concave sidethe baffle is in tension If the pressure is on the convexside the baffle is in compression

There are various tables given in this procedure for flatplate coefficients Flat plate coefficients are utilized todetermine the baffle thickness or a panel thickness Eachtable is specific for a given condition and loading

Vessel Internals 381

Notation

Ap frac14 area of baffle working with stiffener in2

As frac14 area of stiffener in2

Cp frac14 distance from centroid of composite section topanel in

Cs frac14 distance from centroid of composite section tostiffener in

E frac14 modulus of elasticity psiFb frac14 allowable bending stress psiI frac14 moment of inertia composite in4

Is frac14 moment of inertia stiffener in4

l frac14 length of baffle that works with the stiffener inM frac14 moment in-lbn frac14 number of welds attaching stiffenerP frac14 vessel internal pressure psigp frac14 maximum uniform pressure psipn frac14 uniform pressure at any elevation an psiRm frac14 vessel mean radius inSg frac14 specific gravity of contentst frac14 thickness shell intb frac14 thickness baffle ints frac14 thickness stiffener inV frac14 shear load lbw frac14 required fillet weld size ina frac14 thermal coefficient of expansion ininF

bg frac14 flat plate coefficientsDT frac14 differential temperature (design temperature

minus 70F) Fsb frac14 bending stress in baffle psiss frac14 bending stress in stiffener psi

6n frac14 radial expansion ind frac14 deflection inda frac14 maximum allowable deflection in

Baffle Dimensions

382 Pressure Vessel Design Manual

Table 5-24Flat plate coefficients

Vessel Internals 383

Unstiffened Baffle Check

bull Find load p

p frac14 624aSg144

bull Find baffle thickness tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

s

bull Find baffle deflection d

d frac14 pg1b4

Et3b

Limit deflection to the smaller of tb2 or b360 Ifdeflection is excessive then

a Increase the baffle thicknessb Add stiffenersc Go to curved baffle design

If stiffeners are added the first step is to find themaximum ldquoardquo and ldquobrdquo dimensions that will meet theallowable deflection for a given panel size This willestablish the stiffener spacing for both horizontal andvertical stiffeners The ultimate design is a balancebetween baffle thickness stiffener spacing and stiffenersize

Thermal Check of Baffle

bull Vessel radial expansion due to pressure

D1 frac14 085PRm

tE

bull Vessel radial expansion due to temperature

D2 frac14 Rma DT

bull Thermal expansion of baffle

D3 frac14 05ba DT

bull Differential expansion

D4 frac14 D1 thorn D2 D3

Stiffener Design

Divide baffle into panels to limit deflection to the lesserof tb2 or b360 Deflection is calculated based on theappropriate Cases 1 through 3

bull Check baffle for panel size a0 b0bull Check stiffener for length a or b

Recommendations for attaching stiffeners

Benefits Provides added stiffness and no corrosiontrap

Figure 5-18 Example of stiffener layout

384 Pressure Vessel Design Manual

As frac14 tsh

Ap frac14 tbl

IS frac14 tsh3

12

Cp frac14 AsyAs thorn Ap

thorn tb2

Cs frac14 ethhthorn tbTHORN Cp

I frac14 IS thorn Apt2b12

thorn AsApy2

As thorn Ap

lsquo frac14 lesser of 32tb or stiffener spacing

Stresses in BaffleStiffener

sp frac14 MCp

I

ss frac14 MCs

I

Size Welds Attaching Stiffeners

For E70XX Welds

w frac14 Vdy11 200In

Table 5-25Intermittent Welds

Percent of

Continuous Weld

Length of Intermittent Welds

and Distance Between Centers

75 3e4

66 4e6

60 3e5

57 4e7

50 2e4 3e6 4e8

44 4e9

43 3e7

40 2e5 4e10

37 3e8

33 2e6 3e9 4e12

Reprinted by permission of the James F Lincoln Arc Welding

Foundation

Vessel Internals 385

For E60XX Welds

w frac14 Vdy9600In

Sample Problem

bull Given Horizontal vessel with a vertical baffle

P frac14 250 psig

DT frac14 500F

Material frac14 SA-516-70

Ca frac14 0125 in

JE frac14 10

E frac14 273 106 psi

a frac14 7124 10-6 in=in=FFy frac14 308 ksi

D frac14 240 in

Fb frac14 066 Fy frac14 2033 ksi

Rm frac14 120938

ts frac14 175 in

Sg frac14 08

a frac14 15 ft

DT frac14 500 70 frac14 430F

bull Find baffle thickness without stiffener

p frac14 624aSg144

frac14 52 psi

a

bratio frac14 15=20 frac14 075

from Table 5-25 Case 1

b1 frac14 016 g1 frac14 0033

bull Thickness of baffle tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

sfrac14

ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi016eth52THORN2402

20 330

s

tb frac14 153thorn 025 frac14 178

No good Use stiffeners

bull Assume a suitable baffle thickness and determinemaximum panel size

tb frac14 075 in corroded

maximum panel size frac14 4ft 4ft

bull Maximum pressure p

p frac14 13eth624THORN08144

frac14 45 psi

a

bfrac14 4

4frac14 1

See Table 5-25 Case 3

b3 frac14 0287 g3 frac14 00443

sb frac14 b3pb2n

t2

frac14 0287eth45THORN4820752

frac14 5290 psi lt 20 333 psiFigure 5-19 Sample problem

386 Pressure Vessel Design Manual

d frac14 g3

pE

b4nt3

frac14 00443

45

273 106

484

0753

frac14 0092 in lt 0375 in

Balance OK by inspection

bull Assume a layout where the maximum stiffenerspacing is 4 ft

(4) horizontal stiffeners(4) vertical stiffeners(18) panels

bull Check horizontal stiffeners

Dimensions

a1 frac14 3 ft b1 frac14 4 ft

a2 frac14 4 ft b2 frac14 4 ft

a3 frac14 4 ft b3 frac14 12 ft

a4 frac14 4 ft b4 frac14 196 ft

a5 frac14 13 ft

a6 frac14 148ft

bull Assume stiffener size 1 in 4 in

y frac14 2375 in

As frac14 tsh frac14 1eth4THORN frac14 4 in2

l frac14 32tb frac14 32eth075THORN frac14 24 in lt 48 in

AP frac14 tbl frac14 07524 frac14 18 in2

Is frac14 bh3

12frac14 1

43

12frac14 533 in4

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 533thorn 0633thorn 1846 frac14 2442 in4

Cp frac14 AsyAs thorn Ap

thorn tb2

frac14 4eth2375THORN22

thorn 0752

frac14 0807 in

Cs frac14 hthorn tb

Cp

frac14 4thorn 075 0807 frac14 3943

Check deflections

Deflections exceed allowable No good

bull Assume a larger stiffener size WT9 593

tf frac14 106 025 frac14 081

tw frac14 0625 025 frac14 0375

bull Check corroded thickness to find properties ofcorroded section This section would be equivalent toa WT9 30 Properties are

As frac14 882 in2

Is frac14 647 in4

Cs frac14 216 in

H frac14 9 in

Cp frac14 hthorn tb Cs

frac14 9thorn 075 216 frac14 759 in

Figure 5-20 Battle layout for sample problem

Item bn pn d

1 2352 104 149

2 2352 243 349

3 144 381 0767

Vessel Internals 387

y frac14 Cp tb2

frac14 7215 in

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 647thorn 0844thorn 30814 frac14 3737 in4

bull Check stresses and deflections See results in Table5-27

bull Stresses and deflections are acceptablebull Check welds

d frac14 ts thorn 2tw frac14 0375thorn 2eth0323THORN frac14 102

y frac14 7215 in

I frac14 3737 in4

n frac14 2

w frac14 Vdy11 200In

frac14 6681eth102THORN721511 200eth3737THORN2

frac14 0005thorn 0125 frac14 013 in

bull Check thermal expansion of baffle

D1 frac14 085PRm

tEfrac14 085eth250THORN120938

175eth273 106THORNfrac14 000054 in

D2 frac14 Rma DT frac14 1209387124 106430

frac14 0370 in

D3 frac14 05ba DT frac14 05240

7124 106430

frac14 0367 in

D4 frac14 D1 thorn D2 D3 frac14 000054thorn 0370 0367

frac14 00035 lt 006 in

Table 5-26Summary of Results for Stress and Deflection in Composite Stiffeners for Sample Problem

Item Orientation an bn pn M d V sp ss

1 Horiz 2352 d 104 172595 009 2690 3504 997

2 Horiz 2352 d 243 403275 021 6287 8186 2330

3 Horiz 144 d 381 237012 0045 6035 4811 1370

4 Vert d 156 450 154674 0037 5648 3141 894

5 Vert d 1776 513 228539 0072 6681 6681 1320

Figure 5-21 Details of weld attaching stiffener

388 Pressure Vessel Design Manual

Vessel Internals 389

Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 7: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

364 Pressure Vessel Design Manual

27637125

23625

6

DEAD LEG

THIS ENDONLY

BEAMS NOT SHOWN IN ELEVATION FOR CLARITY

361

25

22

185

2244

44

44

195

plusmn0

63

plusmn06

331

75

44

44

44

37125

14oslash

14oslash

24625 2462538125 38125

283

75

38125 38125

R1

R1

DEAD LEG

BEAM NOT SHOWN IN ELEVATION FOR CLARITY

SPRAY HEADERS - EXAMPLES

plusmn07

1

10oslash

6

324375

51 5133625 33625521875 521875 521875

370

TOP OF PACKING

521875

30

30

265

571

457

496

25

602

5

602

560

25

603

75

602

5

388

75

602

5

A2

10oslashA2

Vessel Internals 365

Procedure 5-9 Design of Trays

Typical Tower Dimensions and Nomenclature

1

2

5

4

11

2115

12

29

13

8 10

6

7

322

19

31

2

9

25

24

2318

17

20

22

1413

16

24

30

36 35

27

28

28 26

28

2 PASS

1 PASS

C

E

F

G

A34

4rdquo MIN

33

26 2827

H

2

31

32

C

KL J

N

MP

Q

E

TL

TL

366 Pressure Vessel Design Manual

Tray Types

1 Valve2 Bubble Cap3 Sieve4 Tunnel5 Chimney6 Ripple7 Shower8 Shed Rows9 Disc amp Donut10 Cartridge11 Jet12 Kittle13 Turbogrid14 Dual Flow15 Slotted16 Venturi17 Cascade18 Accumulator

Tray Nomenclature

1 InletFeedReflux2 Inlet Weir3 Inlet Baffle4 Downcomer Clearance5 Weir Height6 Anti-Jump Baffle7 Seal Pan8 Straight Downcomer9 Sloped Downcomer10 Side Downcomer11 Center Downcomer12 Insulating Baffle13 Draw (Off) Nozzle14 Draw (Off) Pan15 Pass Transition16 Total Draw Chimney Tray

17 Chimney18 Chimney Hat19 Return Nozzle20 Sump21 Intermediate Feed Nozzle22 Partial Drawoff Nozzle23 Partition24 Vapor Inlet25 Vapor Inlet Baffle26 Feed Area27 Active Tray Area28 Dowcomer Area (Inactive Tray Area)29 Vapor Outlet30 Baffle31 Internal Pipe32 Support Clips33 Internal Flanges34 End Plate35 Product Outlet Nozzle36 Reboiler Draw Nozzle

Dimensions

A frac14 Short frac14 5 NPSthorn 4 in

Long frac14 5 NPSthorn 10 in

B frac14 Same as middle downcomer

C frac14 5 NPS

D frac14 Same as weir height

E frac14 NPSthorn 6 in

F frac14 NPSthorn 1 in

G frac14 15 NPSthorn 1 in

H frac14 5 NPSthorn 15 in

J frac14 15 NPS

Vessel Internals 367

K frac14 NPS

L frac14 2 NPS

M frac14 Minimum with 21 SE head frac1425 Dthorn tH thorn 15 NPSthorn 2 in

Minimum with hemi head frac14M frac14 5 Dthorn tH thorn 15 NPSthorn 2 in

N frac14 Minimum distance from tangent line to nozzlecenterline See Table 519

P frac14 Minimum skirt height for 21 SE Head SeeTable 5-20

Q frac14 Minimum seal pan depth frac14 tray spacing thorn 6 inR frac14 Downcomer width

Table 5-18Minimum Distance From Tangent Line ldquoNrdquo

Noz Size N Noz Size N

lt2 in 5 12 in 16

3 in 7 14 in 18

4 in 8 16 in 20

6 in 10 18 in 24

8 in 12 20 in 27

10 in 14 24 in 30

Table 5-19Minimum Skirt Height ldquoPrdquo

Dia P Dia P

lt24 in 2 ft e 6 in 114e120 5 ft e 6 in

30e36 3 ft e 0 in 126e132 6 ft e 0 in

48e54 3 ft e 6 in 138e144 6 ft e 6 in

54e60 3 ft e 6 in 150e156 7 ft e 0 in

66e72 4 ft e 0 in 162e168 8 ft e 0 in

78e84 4 ft e 6 in 174e180 8 ft e 6 in

90e106 5 ft e 0 in

368 Pressure Vessel Design Manual

A1 A1

A1

A1 A1

A1 A1

A1 A2

A2A1

A1A1

A1

A1

A1

A1

A2 A2

A2

A2A1

AS AS

AS

AS

AC

AC AC

AQ

D

SIDE DOWNCOMER

CENTERDOWNCOMER

TRAYS

1-PASS TRAY 2-PASS TRAY 3-PASS TRAY 4-PASS TRAY

Vessel Internals 369

TYPICAL TRAY ASSEMBLY

Hex Head Bolt

Manway Lock Clamps

Manway Lock StudsManway Clamps

Seal Plate

Tray Floor (Active)

Tray Floor (Active)Outlet Weir

Downcomer Truss

Standard WasherHex NutFrictional Washer

Downcomer Panel

Downcomer Bolting Bar

Bottom Tray ClampHex Head Bolt DowncomerTruss

Hex NutFrictional Washer

DOWNCOMER BOLTING BAR

Hex Nut

Hex Nut

Hex Nut

Hex Head Bolt

Hex Head Bolt

Frictional Washer

Bottom Tray Clamp

Tray Floor (Inlet Panel)

TRAY FLOOR

(INLET PANEL)

TRAY SUPPORT RING

Tray Support Ring

Manway (Active)

ONE PASS TRAY SHOWN

370 Pressure Vessel Design Manual

Design of Tray Plates

Stress and DeflectionCase 1 Perforated Plate

Reference Roark 5th Edition Table 26 Case 1A

bull Rectangular platebull Uniformly loadedbull All edges simply supported

DATA

a b g frac14 Coefficients from Table 5-21E frac14 Modulus of elasticity at design temperature PSI

t frac14 Corroded thickness of tray inCa frac14 Corrosion allowance inn frac14 Hole efficiencyd frac14 Deflection at center inp frac14 Uniform load PSIs frac14 Bending stress PSI

FORMULAS

bull Stress s

s frac14 b p b4

n t2

BUBBLE-CAPTRAY

VALVELIQUID FLOW

WEIRDOWNCOMER

VAPOR

VAPORVAPOR

VAPOR

VAPOR

TYPES OF TRAYS

CHIMNEY CHIMNEY HAT

SUMPTRUSS

CHIMNEYACCUMULATOR TRAYS

LIQUID

LIQUID

LIQUID

SIEVE TRAY

VALVE TRAY

BUBBLE - CAP TRAY

USUALLY2rsquondash0rdquo

18rdquo MINIMUM

Vessel Internals 371

bull Deflection d

d frac14 a p b4

E n t3

bull Efficiency of holes for perforated plate n

n frac14 1 25 p d2

e C

DIMENSIONAL DATA

a frac14b frac14t frac14a=b frac14b frac14a frac14p frac14d frac14e frac14C frac14E frac14

Tray DesignCase 2 Standard tray plates

LOADS

A DL frac14 Dead load weight of trays and beams

B LL frac14 Live load dynamic load DP

C LL frac14 Liquid load weight of liquid supported

bull Total area AT

AT frac14 p D2=4 frac14 7854 D2

bull Total load PT

PT frac14 DLthorn LLthorn LL

bull Uniform load p

p frac14 PT=AT

LONG EDGE

SHORTEDGEBEAMS (TYP)

c = PITCH60deg

a

b

e

d

Table 5-20Coefficients

ab b a g

10 2874 044 420

12 3762 0616 455

14 4530 0770 478

16 5172 0906 491

18 5688 1017 499

20 6102 1110 503

30 7134 1335 505

40 7410 1400 502

50 7476 1417 501

N 7500 1421 500

372 Pressure Vessel Design Manual

PROPERTIES OF SECTIONS

C frac14 SAY=SA

I frac14 SAY2 thorn SI C SAY

Z frac14 I=C

CALCULATIONS

bull Determine panel area AP

AP frac14 Ln dnbull Load on panel FP

FP frac14 AP p

Uniform Load

bull Uniform load on beam w

w frac14 FP=Ln

bull Moment M

M frac14 w L2

n

8

bull Bending stress fb

fb frac14 M=Z

bull Deflection d

d frac14 5 w L4

n

384 E I

Concentrated Load

bull Moment M

M frac14 ethP LnTHORN=4bull Bending stress fb

fb frac14 M=Z

bull Deflection d

d frac14 P L3

n

48 E I

TYPE 1

1

2

XX

h

dn

t

PART A Y AY AY2 I12sum

C frac14 SAY=SA

I frac14 SAY2 thorn SI C SAY

Z frac14 I=C

TYPE 2

1

32

XX

h

dn

do

t

PART A Y AY AY2 I123sum

L1

DC

DIMENSIONS OF TRAY PANELS

d1 d2 d3 d4

Vessel Internals 373

NOTES1 Design Loads Trays pans drawoff boxes or

similar intemals shall be designed using a corrodedthickness to support their own weight plus thefollowing live loadsa Fractionation trays Design live load shall be the

greater of 20 PSF (98 KgSq meter) or the weightof water 2 (50 mm) over the highest weirsetting

b Areas under downcomers Design live load shallbe the greater of 64 PSF (314 Kg Sq meter) ora head of water one half the height of thedowncomer

c Pans (accumulator and drawoff pans) Designlive load shall be the greater of 1 PSI (700 Kg Sqmeter) or the weight of water at the maximumoperating level of the pan

d Baffles With no operating liquid level shall usea design live load of 1 PSI (700 KgSq meter) onthe projected horizontal area or actual impulseforce whichever is greater

2 Maintenance Loads Tray support members (allbeams support clips etc) shall be designed fora concentrated load of 300 Lbs (135 Kg) at any pointon the installed assembly The design shall be basedon the corroded thicknesses and an allowable stressof 9 Fy For maintenance loads stresses in the trayplates need not be considered

3 Uplift resistance Typical design of uplift for traysand packing is 25 PSI (17 Millibar) For serviceswhere excessive uplift can occur a higher upliftresistance may be used Examples of higher upliftfactors are as follows

a Crude and FCC side strippers 1 PSI (70 millibar)b Vacuum tower stripping trays overflash

collector wash trays or beds 2 PSI (140Millibar)

c Collectiors and packed beds above the washsection of a vacuum Tower 1 PSI (70 Millibar)

4 Failure sequence Tray assemblies wheneverpossible shall be designed so that failure will occurin the following ordera Tray manwaysb Tray deck active areasc Minor beams and downcomersd Major beams (defined as beams 10ft (3 Meters)

or longer or beams which extend across a vesselwithout interruption regardless of length)

5 Allowable stresses Allowable unit stress shall bebased on yield strength Fy at design temperaturewith AISC factors for tension bearing shear etc

6 Allowable Deflection The calculated combineddeflection of trays and support beams due to oper-ating loads shall not exceed the lesser of 1900 of thevessel diameter (in inches) or 316 (5 mm)

RECOMMENDED TRAY SPACING amp MANWAY SIZE

COLUMN DIA

(FT)

TRAY SPACING

(IN)

MANWAY

SPACING

MIN MANWAY

SIZE

25 to 16 24 Every 10 trays 18 in

16 to 24 30 Every 8 trays 20 in

24 to 32 36 Every 6 trays 24 in

32 and larger 42 Every 4 trays 30 in

374 Pressure Vessel Design Manual

Procedure 5-10 Flow Over Weirs

Notation

b frac14 width ftH frac14 static head of liquid ftQ frac14 discharge rate cu ftsecV frac14 velocity of approach ftsecH0 frac14 head correction per Table 5-22

Calculations

Discharge Q

bull For a full-length weir (Case 1)

Q frac14 333beth15 HTHORNbull For a contracted weir (Case 2)

Q frac14 333beth15 HTHORNbull For a V-notch weir (Case 3)

Q frac14 633 H

bull For a Cippoletti weir (Case 4)

Q frac14 3367beth15 HTHORN

Notes

1 Assumes troughs are level

Case 1 Full-Width Weir

V frac14 1ndash2 ftsec at 4 H upstream

Case 2 Contracted Weir

V frac14 1ndash2 ftsec at 3 H upstream

Case 3 V-Notch Weir

V frac14 5 ftsec at 5 H upstream

Case 4 Cippoletti Weir

V frac14 1ndash2 ftsec at 4 H upstream

Table 5-21Head correction for velocity of approach

V 04 06 08 10 12 14 16 18 20

Hrsquo 0002 0005 001 0015 0023 003 004 005 0062

V 22 24 26 28 30 32 34 36 38

Hrsquo 0075 0089 0105 0122 014 015 0179 0201 0213

Vessel Internals 375

Procedure 5-11 Design of Demisters

Demister pads or mist eliminators are important inter-nals in process vessels Anytime there is a continuous twophase flow vapor and liquid there is the possibility forliquid entrainment If it is desirable to separate the liquidand vapor or prevent liquid carryover in the vapor streamthe velocity must be kept sufficiently low to allow the liquiddroplets to fall out of the vapor stream Demister pads areeffective entrainment separators which allow operation atvapor velocities that would otherwise be excessive

ldquoVapor disengagementrdquo can be accomplished withouta demister but the vessel must be made much larger toaccomplish the same degree of separation This is knownas gravity separation

Demister pads are used in a wide variety of processvessels Good performance can be achieved at velocitiesof 30 to 110 of optimum

Demister pads can be used in vertical or horizontalvessels The mesh pad orientation can be either vertical orhorizontal in a vertical or horizontal vessel

A wire mesh demister consists of a knitted wire matmounted on a light weight support grid The mesh is madeby weaving small diameter metal wire into a mesh Padsmay be made out of metal or plastics Metal type includecarbon steel stainless steel monel and others Plasticmaterials include PTFE HDPE and PP

Pressure drop is usually extremely low in the range of1 inch of water column maximum The pressure drop isnormally so low that it is ignored in design

Vapor disengagement is dependent on the velocity ofthe stream The most common equation for determining theallowable vapor velocity for two phase flows is as follows

Va frac14 K frac12ethrL rVTHORN=rV1=2

Where

Va frac14 Allowable vapor velocity FtSecK frac14 Constant or coefficientrL frac14 Density of liquid PCFrV frac14 Density of vapor PCF

Notes

1 The mesh pad shall be in one piece or sectional asrequired for insertion through the vessel manwayEach pad section shall be removable through thevessel manhole

2 Layers shall not be more than 6 inches thick3 Where more than one layer is required all joints

shall be staggered

4 One piece circular pads may be spiral in form5 Each section of mesh shall include a grid on one or

both sides The grid wire andor fastening deviceshall be the same material as the mesh pad Top andbottom grids shall be constructed of frac14 inch diam-eter rods welded to ⅛ inch by 1 inch bars Themaximum gap between mesh pad and grids shall befrac12 inch for diameters less than 84 inches and 1 inchfor larger diameters

6 Estimate grid weights as 3 PSF7 Tie down wires shall be 1=16 inch diameter wire thru

frac14 inch diameter holes on 4 inch centers Tie wiresshould not be pushed through the pad as this couldcause leak paths

8 Pressure drop across mist eliminator shall beassumed as 02 PSI for support design

9 Unless otherwise specified support rings shall be2 inches wide for pads 84 inches in diameter andless and 3 inches wide for larger diameters

10 The mist eliminator shall be a tight fit against theshell or enclosure as well as between sections Meshpads shall be⅜ inches oversize all around for a forcefit against the enclosure No gaps are allowed

11 Vessel fabricator shall provide the mesh and gridsas well as any stiffeners required

12 The Mist eliminator shall be specified as either topor bottom removable

13 ldquoKrdquo is a constant or coefficient that is a functionof the efficiency of the separation K-values rangefrom 04 to 43 but are generally in the 15 to 35range The K-value is affected by pressure type ofpad size of wire type of vessel and disengagingheight For pressure applications the K-valueshould be decreased by 01 for every 100 PSI ofpressure after 100 PSI

14 Wire diameter for the mesh pad itself vary from0003 to 0016 inches

15 The free volume of demisters range from 92 to994

16 The density of the pads ranges from 3 to 33 PCF17 The NSA (nominal surface area) is the surface area

to volume ratio Ft2 Ft3 and is an important indi-cator of performance Ratios range from 50 to 600

18 To obtain higher separation efficiencies the wirediameter is decreased and the density and thicknessare increased

19 Typical width of sections for multi-section pads is12 inches (300 mm) but may vary by manufacturer

376 Pressure Vessel Design Manual

A Horizontal element B Vertical elements

Vertical vessels

Manway

Plate-Pakunit

Meshpad

Drain tubewith seal trap

END VIEW

END VIEW

SIDE VIEW

SIDE VIEW

C Vertical element

Horizontal vessels

D Horizontal element

Figure 5-15 Typical demister configurations in vessels

Vessel Internals 377

d

E Axial entrance

H gt (23) D ndash d

H gt D2 + d(minimum 24rdquo)

H gt D2 ndash d2

H gt D2 + d

H gt D2 ndash d2

h gt d

D

D Side entrance

d

D

B Axial exit

d

D

Φ lt 45ordm

Φ lt 45ordm

C Reverse axial exit

d

A Side exit

D

Figure 5-16 Guidelines for maintaining even flow distribution in vessels with axial flow

378 Pressure Vessel Design Manual

wire mesh

Top grid

Bottom grid

Vertical 14rdquo rodsspaced 12rdquo to 18rdquocenter to center

12rdquo to 18rdquosegmentwidth

18rdquo x 1rdquo flat bars14rdquo rodsspaced 6rdquocenterto center

Manway

Support ring

Support beam

Tie wires

Figure 5-17 Typical mesh pad construction and installation

Vessel Internals 379

Table 5-22Properties of demister pads

Type NSA (1) Ft2 Ft3 Density Pcf Wire Dia in Free Area York Style No Remarks

A 48 5 0011 99 931 High Throughput

B 65 7 0011 986 531 Economy Performance

C 85 9 0011 982 431 Standard - Good All

Around

D 110 108 0011 977 421 Heavy Duty

E 140 8 0006 984 326 Super High Efficiency -

Fine Mist

F 163 0006 94 371 Liquid - Liquid Coalescer

G 450 20 00045 959

H 600 27 00045 945

Notes

1 NSA frac14 Nominal Surface Area

Table 5-23Values of K (Note 13)

Based on Pressure

Pressure (PSIa) Vacuum (In Hg)

Pressure (PSIa) K Vacuum (In Hg) K

15 035 30 035

50 034 20 032

100 032 10 028

200 031 5 023

300 03 1 017

500 028 lt1 017

1000 027

gt1000 027

Based on Disengaging Height

Disengaging Height in K Disengaging Height in K

3 012 9 032

4 015 10 035

5 019 11 038

6 022 12 04

7 025 13 042

8 029 14 043

Based on Application

Vertical Vessels Horizontal Vessels

Type K Type K

General 035 General 035

Compressor Suction Drums 025 Steam Drums 025

Steam Drums 015

380 Pressure Vessel Design Manual

Procedure 5-12 Design of Baffles [10]

Baffles are frequently used in pressure vessels eithervertical or horizontal to divide the interior volume intodifferent compartments These compartments may beused to segregate liquids or provide overflow weirs forthe separation of liquids Baffles may be stiffened orunstiffened When welded across the entire cross sectionof the vessel they must be checked that they are notunduly restricting the diametral expansion of the vesselIf the unrestrained radial expansion of the vessel exceedsthat of the baffle by more than 1=16 in (⅛ in on thediameter) then a ldquoflexiblerdquo type of connection betweenthe vessel shell and the baffle should be utilized Variousflexible attachment designs are shown within theprocedure

Baffles should always be designed in the corrodedcondition It is typical for welded baffles to be designedwith a full corrosion allowance on both sides If the baffleis bolted in then one-half the full corrosion allowancemay be applied to each side the logic being that a boltedbaffle is removable and therefore replaceable

The majority of baffles are flat and as a result are veryinefficient from a strength standpoint Deflection is thegoverning case for flat plates loaded on one side Thepreference is to have unstiffened baffles and they shouldalways be the first choice This will be acceptable forsmall baffles However for larger baffles as the bafflethickness becomes excessive stiffeners offer a moreeconomical design Therefore stiffeners are frequentlyused to stiffen the baffle to prevent the thickness of thebaffle from becoming excessive The number size andspacing of stiffeners are dependent on the baffle thicknessselected There is a continual trade-off between bafflethickness and stiffener parameters

The design of a baffle with stiffeners is an iterativeprocess The procedure for the design of the stiffeners isfirst to divide the baffle into ldquopanelrdquo sections that are rigidenough to withstand the pressure applied on one sideEach individual panel is checked as a flat plate of thedimensions of the panel The stiffeners are assumed to bestrong enough to provide the necessary edge support forthe panel

The stiffeners themselves are designed next A sectionof the baffle is assumed as acting with the stiffener and ascontributing to the overall stiffness This combinedsection is known as the composite stiffener Thecomposite section is checked for stress and deflectionBoth vertical and horizontal stiffeners can be added asrequired

If required an alternate design is assumed based ona thicker or thinner baffle and checked until a satisfactorydesign is found There is no ldquorightrdquo answer however itshould be noted that the thinner the baffle the greater thenumber of stiffeners The lightest overall weight isprobably the ldquobestrdquo design but may not be the leastexpensive due to the welding costs in attaching thestiffeners

One alternative to a flat baffle with stiffeners is to go toa curved baffle A curved baffle works best as a verticalbaffle in a vertical vessel The curved baffle takes pressurefrom either side wall If the pressure is on the concave sidethe baffle is in tension If the pressure is on the convexside the baffle is in compression

There are various tables given in this procedure for flatplate coefficients Flat plate coefficients are utilized todetermine the baffle thickness or a panel thickness Eachtable is specific for a given condition and loading

Vessel Internals 381

Notation

Ap frac14 area of baffle working with stiffener in2

As frac14 area of stiffener in2

Cp frac14 distance from centroid of composite section topanel in

Cs frac14 distance from centroid of composite section tostiffener in

E frac14 modulus of elasticity psiFb frac14 allowable bending stress psiI frac14 moment of inertia composite in4

Is frac14 moment of inertia stiffener in4

l frac14 length of baffle that works with the stiffener inM frac14 moment in-lbn frac14 number of welds attaching stiffenerP frac14 vessel internal pressure psigp frac14 maximum uniform pressure psipn frac14 uniform pressure at any elevation an psiRm frac14 vessel mean radius inSg frac14 specific gravity of contentst frac14 thickness shell intb frac14 thickness baffle ints frac14 thickness stiffener inV frac14 shear load lbw frac14 required fillet weld size ina frac14 thermal coefficient of expansion ininF

bg frac14 flat plate coefficientsDT frac14 differential temperature (design temperature

minus 70F) Fsb frac14 bending stress in baffle psiss frac14 bending stress in stiffener psi

6n frac14 radial expansion ind frac14 deflection inda frac14 maximum allowable deflection in

Baffle Dimensions

382 Pressure Vessel Design Manual

Table 5-24Flat plate coefficients

Vessel Internals 383

Unstiffened Baffle Check

bull Find load p

p frac14 624aSg144

bull Find baffle thickness tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

s

bull Find baffle deflection d

d frac14 pg1b4

Et3b

Limit deflection to the smaller of tb2 or b360 Ifdeflection is excessive then

a Increase the baffle thicknessb Add stiffenersc Go to curved baffle design

If stiffeners are added the first step is to find themaximum ldquoardquo and ldquobrdquo dimensions that will meet theallowable deflection for a given panel size This willestablish the stiffener spacing for both horizontal andvertical stiffeners The ultimate design is a balancebetween baffle thickness stiffener spacing and stiffenersize

Thermal Check of Baffle

bull Vessel radial expansion due to pressure

D1 frac14 085PRm

tE

bull Vessel radial expansion due to temperature

D2 frac14 Rma DT

bull Thermal expansion of baffle

D3 frac14 05ba DT

bull Differential expansion

D4 frac14 D1 thorn D2 D3

Stiffener Design

Divide baffle into panels to limit deflection to the lesserof tb2 or b360 Deflection is calculated based on theappropriate Cases 1 through 3

bull Check baffle for panel size a0 b0bull Check stiffener for length a or b

Recommendations for attaching stiffeners

Benefits Provides added stiffness and no corrosiontrap

Figure 5-18 Example of stiffener layout

384 Pressure Vessel Design Manual

As frac14 tsh

Ap frac14 tbl

IS frac14 tsh3

12

Cp frac14 AsyAs thorn Ap

thorn tb2

Cs frac14 ethhthorn tbTHORN Cp

I frac14 IS thorn Apt2b12

thorn AsApy2

As thorn Ap

lsquo frac14 lesser of 32tb or stiffener spacing

Stresses in BaffleStiffener

sp frac14 MCp

I

ss frac14 MCs

I

Size Welds Attaching Stiffeners

For E70XX Welds

w frac14 Vdy11 200In

Table 5-25Intermittent Welds

Percent of

Continuous Weld

Length of Intermittent Welds

and Distance Between Centers

75 3e4

66 4e6

60 3e5

57 4e7

50 2e4 3e6 4e8

44 4e9

43 3e7

40 2e5 4e10

37 3e8

33 2e6 3e9 4e12

Reprinted by permission of the James F Lincoln Arc Welding

Foundation

Vessel Internals 385

For E60XX Welds

w frac14 Vdy9600In

Sample Problem

bull Given Horizontal vessel with a vertical baffle

P frac14 250 psig

DT frac14 500F

Material frac14 SA-516-70

Ca frac14 0125 in

JE frac14 10

E frac14 273 106 psi

a frac14 7124 10-6 in=in=FFy frac14 308 ksi

D frac14 240 in

Fb frac14 066 Fy frac14 2033 ksi

Rm frac14 120938

ts frac14 175 in

Sg frac14 08

a frac14 15 ft

DT frac14 500 70 frac14 430F

bull Find baffle thickness without stiffener

p frac14 624aSg144

frac14 52 psi

a

bratio frac14 15=20 frac14 075

from Table 5-25 Case 1

b1 frac14 016 g1 frac14 0033

bull Thickness of baffle tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

sfrac14

ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi016eth52THORN2402

20 330

s

tb frac14 153thorn 025 frac14 178

No good Use stiffeners

bull Assume a suitable baffle thickness and determinemaximum panel size

tb frac14 075 in corroded

maximum panel size frac14 4ft 4ft

bull Maximum pressure p

p frac14 13eth624THORN08144

frac14 45 psi

a

bfrac14 4

4frac14 1

See Table 5-25 Case 3

b3 frac14 0287 g3 frac14 00443

sb frac14 b3pb2n

t2

frac14 0287eth45THORN4820752

frac14 5290 psi lt 20 333 psiFigure 5-19 Sample problem

386 Pressure Vessel Design Manual

d frac14 g3

pE

b4nt3

frac14 00443

45

273 106

484

0753

frac14 0092 in lt 0375 in

Balance OK by inspection

bull Assume a layout where the maximum stiffenerspacing is 4 ft

(4) horizontal stiffeners(4) vertical stiffeners(18) panels

bull Check horizontal stiffeners

Dimensions

a1 frac14 3 ft b1 frac14 4 ft

a2 frac14 4 ft b2 frac14 4 ft

a3 frac14 4 ft b3 frac14 12 ft

a4 frac14 4 ft b4 frac14 196 ft

a5 frac14 13 ft

a6 frac14 148ft

bull Assume stiffener size 1 in 4 in

y frac14 2375 in

As frac14 tsh frac14 1eth4THORN frac14 4 in2

l frac14 32tb frac14 32eth075THORN frac14 24 in lt 48 in

AP frac14 tbl frac14 07524 frac14 18 in2

Is frac14 bh3

12frac14 1

43

12frac14 533 in4

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 533thorn 0633thorn 1846 frac14 2442 in4

Cp frac14 AsyAs thorn Ap

thorn tb2

frac14 4eth2375THORN22

thorn 0752

frac14 0807 in

Cs frac14 hthorn tb

Cp

frac14 4thorn 075 0807 frac14 3943

Check deflections

Deflections exceed allowable No good

bull Assume a larger stiffener size WT9 593

tf frac14 106 025 frac14 081

tw frac14 0625 025 frac14 0375

bull Check corroded thickness to find properties ofcorroded section This section would be equivalent toa WT9 30 Properties are

As frac14 882 in2

Is frac14 647 in4

Cs frac14 216 in

H frac14 9 in

Cp frac14 hthorn tb Cs

frac14 9thorn 075 216 frac14 759 in

Figure 5-20 Battle layout for sample problem

Item bn pn d

1 2352 104 149

2 2352 243 349

3 144 381 0767

Vessel Internals 387

y frac14 Cp tb2

frac14 7215 in

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 647thorn 0844thorn 30814 frac14 3737 in4

bull Check stresses and deflections See results in Table5-27

bull Stresses and deflections are acceptablebull Check welds

d frac14 ts thorn 2tw frac14 0375thorn 2eth0323THORN frac14 102

y frac14 7215 in

I frac14 3737 in4

n frac14 2

w frac14 Vdy11 200In

frac14 6681eth102THORN721511 200eth3737THORN2

frac14 0005thorn 0125 frac14 013 in

bull Check thermal expansion of baffle

D1 frac14 085PRm

tEfrac14 085eth250THORN120938

175eth273 106THORNfrac14 000054 in

D2 frac14 Rma DT frac14 1209387124 106430

frac14 0370 in

D3 frac14 05ba DT frac14 05240

7124 106430

frac14 0367 in

D4 frac14 D1 thorn D2 D3 frac14 000054thorn 0370 0367

frac14 00035 lt 006 in

Table 5-26Summary of Results for Stress and Deflection in Composite Stiffeners for Sample Problem

Item Orientation an bn pn M d V sp ss

1 Horiz 2352 d 104 172595 009 2690 3504 997

2 Horiz 2352 d 243 403275 021 6287 8186 2330

3 Horiz 144 d 381 237012 0045 6035 4811 1370

4 Vert d 156 450 154674 0037 5648 3141 894

5 Vert d 1776 513 228539 0072 6681 6681 1320

Figure 5-21 Details of weld attaching stiffener

388 Pressure Vessel Design Manual

Vessel Internals 389

Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 8: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

27637125

23625

6

DEAD LEG

THIS ENDONLY

BEAMS NOT SHOWN IN ELEVATION FOR CLARITY

361

25

22

185

2244

44

44

195

plusmn0

63

plusmn06

331

75

44

44

44

37125

14oslash

14oslash

24625 2462538125 38125

283

75

38125 38125

R1

R1

DEAD LEG

BEAM NOT SHOWN IN ELEVATION FOR CLARITY

SPRAY HEADERS - EXAMPLES

plusmn07

1

10oslash

6

324375

51 5133625 33625521875 521875 521875

370

TOP OF PACKING

521875

30

30

265

571

457

496

25

602

5

602

560

25

603

75

602

5

388

75

602

5

A2

10oslashA2

Vessel Internals 365

Procedure 5-9 Design of Trays

Typical Tower Dimensions and Nomenclature

1

2

5

4

11

2115

12

29

13

8 10

6

7

322

19

31

2

9

25

24

2318

17

20

22

1413

16

24

30

36 35

27

28

28 26

28

2 PASS

1 PASS

C

E

F

G

A34

4rdquo MIN

33

26 2827

H

2

31

32

C

KL J

N

MP

Q

E

TL

TL

366 Pressure Vessel Design Manual

Tray Types

1 Valve2 Bubble Cap3 Sieve4 Tunnel5 Chimney6 Ripple7 Shower8 Shed Rows9 Disc amp Donut10 Cartridge11 Jet12 Kittle13 Turbogrid14 Dual Flow15 Slotted16 Venturi17 Cascade18 Accumulator

Tray Nomenclature

1 InletFeedReflux2 Inlet Weir3 Inlet Baffle4 Downcomer Clearance5 Weir Height6 Anti-Jump Baffle7 Seal Pan8 Straight Downcomer9 Sloped Downcomer10 Side Downcomer11 Center Downcomer12 Insulating Baffle13 Draw (Off) Nozzle14 Draw (Off) Pan15 Pass Transition16 Total Draw Chimney Tray

17 Chimney18 Chimney Hat19 Return Nozzle20 Sump21 Intermediate Feed Nozzle22 Partial Drawoff Nozzle23 Partition24 Vapor Inlet25 Vapor Inlet Baffle26 Feed Area27 Active Tray Area28 Dowcomer Area (Inactive Tray Area)29 Vapor Outlet30 Baffle31 Internal Pipe32 Support Clips33 Internal Flanges34 End Plate35 Product Outlet Nozzle36 Reboiler Draw Nozzle

Dimensions

A frac14 Short frac14 5 NPSthorn 4 in

Long frac14 5 NPSthorn 10 in

B frac14 Same as middle downcomer

C frac14 5 NPS

D frac14 Same as weir height

E frac14 NPSthorn 6 in

F frac14 NPSthorn 1 in

G frac14 15 NPSthorn 1 in

H frac14 5 NPSthorn 15 in

J frac14 15 NPS

Vessel Internals 367

K frac14 NPS

L frac14 2 NPS

M frac14 Minimum with 21 SE head frac1425 Dthorn tH thorn 15 NPSthorn 2 in

Minimum with hemi head frac14M frac14 5 Dthorn tH thorn 15 NPSthorn 2 in

N frac14 Minimum distance from tangent line to nozzlecenterline See Table 519

P frac14 Minimum skirt height for 21 SE Head SeeTable 5-20

Q frac14 Minimum seal pan depth frac14 tray spacing thorn 6 inR frac14 Downcomer width

Table 5-18Minimum Distance From Tangent Line ldquoNrdquo

Noz Size N Noz Size N

lt2 in 5 12 in 16

3 in 7 14 in 18

4 in 8 16 in 20

6 in 10 18 in 24

8 in 12 20 in 27

10 in 14 24 in 30

Table 5-19Minimum Skirt Height ldquoPrdquo

Dia P Dia P

lt24 in 2 ft e 6 in 114e120 5 ft e 6 in

30e36 3 ft e 0 in 126e132 6 ft e 0 in

48e54 3 ft e 6 in 138e144 6 ft e 6 in

54e60 3 ft e 6 in 150e156 7 ft e 0 in

66e72 4 ft e 0 in 162e168 8 ft e 0 in

78e84 4 ft e 6 in 174e180 8 ft e 6 in

90e106 5 ft e 0 in

368 Pressure Vessel Design Manual

A1 A1

A1

A1 A1

A1 A1

A1 A2

A2A1

A1A1

A1

A1

A1

A1

A2 A2

A2

A2A1

AS AS

AS

AS

AC

AC AC

AQ

D

SIDE DOWNCOMER

CENTERDOWNCOMER

TRAYS

1-PASS TRAY 2-PASS TRAY 3-PASS TRAY 4-PASS TRAY

Vessel Internals 369

TYPICAL TRAY ASSEMBLY

Hex Head Bolt

Manway Lock Clamps

Manway Lock StudsManway Clamps

Seal Plate

Tray Floor (Active)

Tray Floor (Active)Outlet Weir

Downcomer Truss

Standard WasherHex NutFrictional Washer

Downcomer Panel

Downcomer Bolting Bar

Bottom Tray ClampHex Head Bolt DowncomerTruss

Hex NutFrictional Washer

DOWNCOMER BOLTING BAR

Hex Nut

Hex Nut

Hex Nut

Hex Head Bolt

Hex Head Bolt

Frictional Washer

Bottom Tray Clamp

Tray Floor (Inlet Panel)

TRAY FLOOR

(INLET PANEL)

TRAY SUPPORT RING

Tray Support Ring

Manway (Active)

ONE PASS TRAY SHOWN

370 Pressure Vessel Design Manual

Design of Tray Plates

Stress and DeflectionCase 1 Perforated Plate

Reference Roark 5th Edition Table 26 Case 1A

bull Rectangular platebull Uniformly loadedbull All edges simply supported

DATA

a b g frac14 Coefficients from Table 5-21E frac14 Modulus of elasticity at design temperature PSI

t frac14 Corroded thickness of tray inCa frac14 Corrosion allowance inn frac14 Hole efficiencyd frac14 Deflection at center inp frac14 Uniform load PSIs frac14 Bending stress PSI

FORMULAS

bull Stress s

s frac14 b p b4

n t2

BUBBLE-CAPTRAY

VALVELIQUID FLOW

WEIRDOWNCOMER

VAPOR

VAPORVAPOR

VAPOR

VAPOR

TYPES OF TRAYS

CHIMNEY CHIMNEY HAT

SUMPTRUSS

CHIMNEYACCUMULATOR TRAYS

LIQUID

LIQUID

LIQUID

SIEVE TRAY

VALVE TRAY

BUBBLE - CAP TRAY

USUALLY2rsquondash0rdquo

18rdquo MINIMUM

Vessel Internals 371

bull Deflection d

d frac14 a p b4

E n t3

bull Efficiency of holes for perforated plate n

n frac14 1 25 p d2

e C

DIMENSIONAL DATA

a frac14b frac14t frac14a=b frac14b frac14a frac14p frac14d frac14e frac14C frac14E frac14

Tray DesignCase 2 Standard tray plates

LOADS

A DL frac14 Dead load weight of trays and beams

B LL frac14 Live load dynamic load DP

C LL frac14 Liquid load weight of liquid supported

bull Total area AT

AT frac14 p D2=4 frac14 7854 D2

bull Total load PT

PT frac14 DLthorn LLthorn LL

bull Uniform load p

p frac14 PT=AT

LONG EDGE

SHORTEDGEBEAMS (TYP)

c = PITCH60deg

a

b

e

d

Table 5-20Coefficients

ab b a g

10 2874 044 420

12 3762 0616 455

14 4530 0770 478

16 5172 0906 491

18 5688 1017 499

20 6102 1110 503

30 7134 1335 505

40 7410 1400 502

50 7476 1417 501

N 7500 1421 500

372 Pressure Vessel Design Manual

PROPERTIES OF SECTIONS

C frac14 SAY=SA

I frac14 SAY2 thorn SI C SAY

Z frac14 I=C

CALCULATIONS

bull Determine panel area AP

AP frac14 Ln dnbull Load on panel FP

FP frac14 AP p

Uniform Load

bull Uniform load on beam w

w frac14 FP=Ln

bull Moment M

M frac14 w L2

n

8

bull Bending stress fb

fb frac14 M=Z

bull Deflection d

d frac14 5 w L4

n

384 E I

Concentrated Load

bull Moment M

M frac14 ethP LnTHORN=4bull Bending stress fb

fb frac14 M=Z

bull Deflection d

d frac14 P L3

n

48 E I

TYPE 1

1

2

XX

h

dn

t

PART A Y AY AY2 I12sum

C frac14 SAY=SA

I frac14 SAY2 thorn SI C SAY

Z frac14 I=C

TYPE 2

1

32

XX

h

dn

do

t

PART A Y AY AY2 I123sum

L1

DC

DIMENSIONS OF TRAY PANELS

d1 d2 d3 d4

Vessel Internals 373

NOTES1 Design Loads Trays pans drawoff boxes or

similar intemals shall be designed using a corrodedthickness to support their own weight plus thefollowing live loadsa Fractionation trays Design live load shall be the

greater of 20 PSF (98 KgSq meter) or the weightof water 2 (50 mm) over the highest weirsetting

b Areas under downcomers Design live load shallbe the greater of 64 PSF (314 Kg Sq meter) ora head of water one half the height of thedowncomer

c Pans (accumulator and drawoff pans) Designlive load shall be the greater of 1 PSI (700 Kg Sqmeter) or the weight of water at the maximumoperating level of the pan

d Baffles With no operating liquid level shall usea design live load of 1 PSI (700 KgSq meter) onthe projected horizontal area or actual impulseforce whichever is greater

2 Maintenance Loads Tray support members (allbeams support clips etc) shall be designed fora concentrated load of 300 Lbs (135 Kg) at any pointon the installed assembly The design shall be basedon the corroded thicknesses and an allowable stressof 9 Fy For maintenance loads stresses in the trayplates need not be considered

3 Uplift resistance Typical design of uplift for traysand packing is 25 PSI (17 Millibar) For serviceswhere excessive uplift can occur a higher upliftresistance may be used Examples of higher upliftfactors are as follows

a Crude and FCC side strippers 1 PSI (70 millibar)b Vacuum tower stripping trays overflash

collector wash trays or beds 2 PSI (140Millibar)

c Collectiors and packed beds above the washsection of a vacuum Tower 1 PSI (70 Millibar)

4 Failure sequence Tray assemblies wheneverpossible shall be designed so that failure will occurin the following ordera Tray manwaysb Tray deck active areasc Minor beams and downcomersd Major beams (defined as beams 10ft (3 Meters)

or longer or beams which extend across a vesselwithout interruption regardless of length)

5 Allowable stresses Allowable unit stress shall bebased on yield strength Fy at design temperaturewith AISC factors for tension bearing shear etc

6 Allowable Deflection The calculated combineddeflection of trays and support beams due to oper-ating loads shall not exceed the lesser of 1900 of thevessel diameter (in inches) or 316 (5 mm)

RECOMMENDED TRAY SPACING amp MANWAY SIZE

COLUMN DIA

(FT)

TRAY SPACING

(IN)

MANWAY

SPACING

MIN MANWAY

SIZE

25 to 16 24 Every 10 trays 18 in

16 to 24 30 Every 8 trays 20 in

24 to 32 36 Every 6 trays 24 in

32 and larger 42 Every 4 trays 30 in

374 Pressure Vessel Design Manual

Procedure 5-10 Flow Over Weirs

Notation

b frac14 width ftH frac14 static head of liquid ftQ frac14 discharge rate cu ftsecV frac14 velocity of approach ftsecH0 frac14 head correction per Table 5-22

Calculations

Discharge Q

bull For a full-length weir (Case 1)

Q frac14 333beth15 HTHORNbull For a contracted weir (Case 2)

Q frac14 333beth15 HTHORNbull For a V-notch weir (Case 3)

Q frac14 633 H

bull For a Cippoletti weir (Case 4)

Q frac14 3367beth15 HTHORN

Notes

1 Assumes troughs are level

Case 1 Full-Width Weir

V frac14 1ndash2 ftsec at 4 H upstream

Case 2 Contracted Weir

V frac14 1ndash2 ftsec at 3 H upstream

Case 3 V-Notch Weir

V frac14 5 ftsec at 5 H upstream

Case 4 Cippoletti Weir

V frac14 1ndash2 ftsec at 4 H upstream

Table 5-21Head correction for velocity of approach

V 04 06 08 10 12 14 16 18 20

Hrsquo 0002 0005 001 0015 0023 003 004 005 0062

V 22 24 26 28 30 32 34 36 38

Hrsquo 0075 0089 0105 0122 014 015 0179 0201 0213

Vessel Internals 375

Procedure 5-11 Design of Demisters

Demister pads or mist eliminators are important inter-nals in process vessels Anytime there is a continuous twophase flow vapor and liquid there is the possibility forliquid entrainment If it is desirable to separate the liquidand vapor or prevent liquid carryover in the vapor streamthe velocity must be kept sufficiently low to allow the liquiddroplets to fall out of the vapor stream Demister pads areeffective entrainment separators which allow operation atvapor velocities that would otherwise be excessive

ldquoVapor disengagementrdquo can be accomplished withouta demister but the vessel must be made much larger toaccomplish the same degree of separation This is knownas gravity separation

Demister pads are used in a wide variety of processvessels Good performance can be achieved at velocitiesof 30 to 110 of optimum

Demister pads can be used in vertical or horizontalvessels The mesh pad orientation can be either vertical orhorizontal in a vertical or horizontal vessel

A wire mesh demister consists of a knitted wire matmounted on a light weight support grid The mesh is madeby weaving small diameter metal wire into a mesh Padsmay be made out of metal or plastics Metal type includecarbon steel stainless steel monel and others Plasticmaterials include PTFE HDPE and PP

Pressure drop is usually extremely low in the range of1 inch of water column maximum The pressure drop isnormally so low that it is ignored in design

Vapor disengagement is dependent on the velocity ofthe stream The most common equation for determining theallowable vapor velocity for two phase flows is as follows

Va frac14 K frac12ethrL rVTHORN=rV1=2

Where

Va frac14 Allowable vapor velocity FtSecK frac14 Constant or coefficientrL frac14 Density of liquid PCFrV frac14 Density of vapor PCF

Notes

1 The mesh pad shall be in one piece or sectional asrequired for insertion through the vessel manwayEach pad section shall be removable through thevessel manhole

2 Layers shall not be more than 6 inches thick3 Where more than one layer is required all joints

shall be staggered

4 One piece circular pads may be spiral in form5 Each section of mesh shall include a grid on one or

both sides The grid wire andor fastening deviceshall be the same material as the mesh pad Top andbottom grids shall be constructed of frac14 inch diam-eter rods welded to ⅛ inch by 1 inch bars Themaximum gap between mesh pad and grids shall befrac12 inch for diameters less than 84 inches and 1 inchfor larger diameters

6 Estimate grid weights as 3 PSF7 Tie down wires shall be 1=16 inch diameter wire thru

frac14 inch diameter holes on 4 inch centers Tie wiresshould not be pushed through the pad as this couldcause leak paths

8 Pressure drop across mist eliminator shall beassumed as 02 PSI for support design

9 Unless otherwise specified support rings shall be2 inches wide for pads 84 inches in diameter andless and 3 inches wide for larger diameters

10 The mist eliminator shall be a tight fit against theshell or enclosure as well as between sections Meshpads shall be⅜ inches oversize all around for a forcefit against the enclosure No gaps are allowed

11 Vessel fabricator shall provide the mesh and gridsas well as any stiffeners required

12 The Mist eliminator shall be specified as either topor bottom removable

13 ldquoKrdquo is a constant or coefficient that is a functionof the efficiency of the separation K-values rangefrom 04 to 43 but are generally in the 15 to 35range The K-value is affected by pressure type ofpad size of wire type of vessel and disengagingheight For pressure applications the K-valueshould be decreased by 01 for every 100 PSI ofpressure after 100 PSI

14 Wire diameter for the mesh pad itself vary from0003 to 0016 inches

15 The free volume of demisters range from 92 to994

16 The density of the pads ranges from 3 to 33 PCF17 The NSA (nominal surface area) is the surface area

to volume ratio Ft2 Ft3 and is an important indi-cator of performance Ratios range from 50 to 600

18 To obtain higher separation efficiencies the wirediameter is decreased and the density and thicknessare increased

19 Typical width of sections for multi-section pads is12 inches (300 mm) but may vary by manufacturer

376 Pressure Vessel Design Manual

A Horizontal element B Vertical elements

Vertical vessels

Manway

Plate-Pakunit

Meshpad

Drain tubewith seal trap

END VIEW

END VIEW

SIDE VIEW

SIDE VIEW

C Vertical element

Horizontal vessels

D Horizontal element

Figure 5-15 Typical demister configurations in vessels

Vessel Internals 377

d

E Axial entrance

H gt (23) D ndash d

H gt D2 + d(minimum 24rdquo)

H gt D2 ndash d2

H gt D2 + d

H gt D2 ndash d2

h gt d

D

D Side entrance

d

D

B Axial exit

d

D

Φ lt 45ordm

Φ lt 45ordm

C Reverse axial exit

d

A Side exit

D

Figure 5-16 Guidelines for maintaining even flow distribution in vessels with axial flow

378 Pressure Vessel Design Manual

wire mesh

Top grid

Bottom grid

Vertical 14rdquo rodsspaced 12rdquo to 18rdquocenter to center

12rdquo to 18rdquosegmentwidth

18rdquo x 1rdquo flat bars14rdquo rodsspaced 6rdquocenterto center

Manway

Support ring

Support beam

Tie wires

Figure 5-17 Typical mesh pad construction and installation

Vessel Internals 379

Table 5-22Properties of demister pads

Type NSA (1) Ft2 Ft3 Density Pcf Wire Dia in Free Area York Style No Remarks

A 48 5 0011 99 931 High Throughput

B 65 7 0011 986 531 Economy Performance

C 85 9 0011 982 431 Standard - Good All

Around

D 110 108 0011 977 421 Heavy Duty

E 140 8 0006 984 326 Super High Efficiency -

Fine Mist

F 163 0006 94 371 Liquid - Liquid Coalescer

G 450 20 00045 959

H 600 27 00045 945

Notes

1 NSA frac14 Nominal Surface Area

Table 5-23Values of K (Note 13)

Based on Pressure

Pressure (PSIa) Vacuum (In Hg)

Pressure (PSIa) K Vacuum (In Hg) K

15 035 30 035

50 034 20 032

100 032 10 028

200 031 5 023

300 03 1 017

500 028 lt1 017

1000 027

gt1000 027

Based on Disengaging Height

Disengaging Height in K Disengaging Height in K

3 012 9 032

4 015 10 035

5 019 11 038

6 022 12 04

7 025 13 042

8 029 14 043

Based on Application

Vertical Vessels Horizontal Vessels

Type K Type K

General 035 General 035

Compressor Suction Drums 025 Steam Drums 025

Steam Drums 015

380 Pressure Vessel Design Manual

Procedure 5-12 Design of Baffles [10]

Baffles are frequently used in pressure vessels eithervertical or horizontal to divide the interior volume intodifferent compartments These compartments may beused to segregate liquids or provide overflow weirs forthe separation of liquids Baffles may be stiffened orunstiffened When welded across the entire cross sectionof the vessel they must be checked that they are notunduly restricting the diametral expansion of the vesselIf the unrestrained radial expansion of the vessel exceedsthat of the baffle by more than 1=16 in (⅛ in on thediameter) then a ldquoflexiblerdquo type of connection betweenthe vessel shell and the baffle should be utilized Variousflexible attachment designs are shown within theprocedure

Baffles should always be designed in the corrodedcondition It is typical for welded baffles to be designedwith a full corrosion allowance on both sides If the baffleis bolted in then one-half the full corrosion allowancemay be applied to each side the logic being that a boltedbaffle is removable and therefore replaceable

The majority of baffles are flat and as a result are veryinefficient from a strength standpoint Deflection is thegoverning case for flat plates loaded on one side Thepreference is to have unstiffened baffles and they shouldalways be the first choice This will be acceptable forsmall baffles However for larger baffles as the bafflethickness becomes excessive stiffeners offer a moreeconomical design Therefore stiffeners are frequentlyused to stiffen the baffle to prevent the thickness of thebaffle from becoming excessive The number size andspacing of stiffeners are dependent on the baffle thicknessselected There is a continual trade-off between bafflethickness and stiffener parameters

The design of a baffle with stiffeners is an iterativeprocess The procedure for the design of the stiffeners isfirst to divide the baffle into ldquopanelrdquo sections that are rigidenough to withstand the pressure applied on one sideEach individual panel is checked as a flat plate of thedimensions of the panel The stiffeners are assumed to bestrong enough to provide the necessary edge support forthe panel

The stiffeners themselves are designed next A sectionof the baffle is assumed as acting with the stiffener and ascontributing to the overall stiffness This combinedsection is known as the composite stiffener Thecomposite section is checked for stress and deflectionBoth vertical and horizontal stiffeners can be added asrequired

If required an alternate design is assumed based ona thicker or thinner baffle and checked until a satisfactorydesign is found There is no ldquorightrdquo answer however itshould be noted that the thinner the baffle the greater thenumber of stiffeners The lightest overall weight isprobably the ldquobestrdquo design but may not be the leastexpensive due to the welding costs in attaching thestiffeners

One alternative to a flat baffle with stiffeners is to go toa curved baffle A curved baffle works best as a verticalbaffle in a vertical vessel The curved baffle takes pressurefrom either side wall If the pressure is on the concave sidethe baffle is in tension If the pressure is on the convexside the baffle is in compression

There are various tables given in this procedure for flatplate coefficients Flat plate coefficients are utilized todetermine the baffle thickness or a panel thickness Eachtable is specific for a given condition and loading

Vessel Internals 381

Notation

Ap frac14 area of baffle working with stiffener in2

As frac14 area of stiffener in2

Cp frac14 distance from centroid of composite section topanel in

Cs frac14 distance from centroid of composite section tostiffener in

E frac14 modulus of elasticity psiFb frac14 allowable bending stress psiI frac14 moment of inertia composite in4

Is frac14 moment of inertia stiffener in4

l frac14 length of baffle that works with the stiffener inM frac14 moment in-lbn frac14 number of welds attaching stiffenerP frac14 vessel internal pressure psigp frac14 maximum uniform pressure psipn frac14 uniform pressure at any elevation an psiRm frac14 vessel mean radius inSg frac14 specific gravity of contentst frac14 thickness shell intb frac14 thickness baffle ints frac14 thickness stiffener inV frac14 shear load lbw frac14 required fillet weld size ina frac14 thermal coefficient of expansion ininF

bg frac14 flat plate coefficientsDT frac14 differential temperature (design temperature

minus 70F) Fsb frac14 bending stress in baffle psiss frac14 bending stress in stiffener psi

6n frac14 radial expansion ind frac14 deflection inda frac14 maximum allowable deflection in

Baffle Dimensions

382 Pressure Vessel Design Manual

Table 5-24Flat plate coefficients

Vessel Internals 383

Unstiffened Baffle Check

bull Find load p

p frac14 624aSg144

bull Find baffle thickness tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

s

bull Find baffle deflection d

d frac14 pg1b4

Et3b

Limit deflection to the smaller of tb2 or b360 Ifdeflection is excessive then

a Increase the baffle thicknessb Add stiffenersc Go to curved baffle design

If stiffeners are added the first step is to find themaximum ldquoardquo and ldquobrdquo dimensions that will meet theallowable deflection for a given panel size This willestablish the stiffener spacing for both horizontal andvertical stiffeners The ultimate design is a balancebetween baffle thickness stiffener spacing and stiffenersize

Thermal Check of Baffle

bull Vessel radial expansion due to pressure

D1 frac14 085PRm

tE

bull Vessel radial expansion due to temperature

D2 frac14 Rma DT

bull Thermal expansion of baffle

D3 frac14 05ba DT

bull Differential expansion

D4 frac14 D1 thorn D2 D3

Stiffener Design

Divide baffle into panels to limit deflection to the lesserof tb2 or b360 Deflection is calculated based on theappropriate Cases 1 through 3

bull Check baffle for panel size a0 b0bull Check stiffener for length a or b

Recommendations for attaching stiffeners

Benefits Provides added stiffness and no corrosiontrap

Figure 5-18 Example of stiffener layout

384 Pressure Vessel Design Manual

As frac14 tsh

Ap frac14 tbl

IS frac14 tsh3

12

Cp frac14 AsyAs thorn Ap

thorn tb2

Cs frac14 ethhthorn tbTHORN Cp

I frac14 IS thorn Apt2b12

thorn AsApy2

As thorn Ap

lsquo frac14 lesser of 32tb or stiffener spacing

Stresses in BaffleStiffener

sp frac14 MCp

I

ss frac14 MCs

I

Size Welds Attaching Stiffeners

For E70XX Welds

w frac14 Vdy11 200In

Table 5-25Intermittent Welds

Percent of

Continuous Weld

Length of Intermittent Welds

and Distance Between Centers

75 3e4

66 4e6

60 3e5

57 4e7

50 2e4 3e6 4e8

44 4e9

43 3e7

40 2e5 4e10

37 3e8

33 2e6 3e9 4e12

Reprinted by permission of the James F Lincoln Arc Welding

Foundation

Vessel Internals 385

For E60XX Welds

w frac14 Vdy9600In

Sample Problem

bull Given Horizontal vessel with a vertical baffle

P frac14 250 psig

DT frac14 500F

Material frac14 SA-516-70

Ca frac14 0125 in

JE frac14 10

E frac14 273 106 psi

a frac14 7124 10-6 in=in=FFy frac14 308 ksi

D frac14 240 in

Fb frac14 066 Fy frac14 2033 ksi

Rm frac14 120938

ts frac14 175 in

Sg frac14 08

a frac14 15 ft

DT frac14 500 70 frac14 430F

bull Find baffle thickness without stiffener

p frac14 624aSg144

frac14 52 psi

a

bratio frac14 15=20 frac14 075

from Table 5-25 Case 1

b1 frac14 016 g1 frac14 0033

bull Thickness of baffle tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

sfrac14

ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi016eth52THORN2402

20 330

s

tb frac14 153thorn 025 frac14 178

No good Use stiffeners

bull Assume a suitable baffle thickness and determinemaximum panel size

tb frac14 075 in corroded

maximum panel size frac14 4ft 4ft

bull Maximum pressure p

p frac14 13eth624THORN08144

frac14 45 psi

a

bfrac14 4

4frac14 1

See Table 5-25 Case 3

b3 frac14 0287 g3 frac14 00443

sb frac14 b3pb2n

t2

frac14 0287eth45THORN4820752

frac14 5290 psi lt 20 333 psiFigure 5-19 Sample problem

386 Pressure Vessel Design Manual

d frac14 g3

pE

b4nt3

frac14 00443

45

273 106

484

0753

frac14 0092 in lt 0375 in

Balance OK by inspection

bull Assume a layout where the maximum stiffenerspacing is 4 ft

(4) horizontal stiffeners(4) vertical stiffeners(18) panels

bull Check horizontal stiffeners

Dimensions

a1 frac14 3 ft b1 frac14 4 ft

a2 frac14 4 ft b2 frac14 4 ft

a3 frac14 4 ft b3 frac14 12 ft

a4 frac14 4 ft b4 frac14 196 ft

a5 frac14 13 ft

a6 frac14 148ft

bull Assume stiffener size 1 in 4 in

y frac14 2375 in

As frac14 tsh frac14 1eth4THORN frac14 4 in2

l frac14 32tb frac14 32eth075THORN frac14 24 in lt 48 in

AP frac14 tbl frac14 07524 frac14 18 in2

Is frac14 bh3

12frac14 1

43

12frac14 533 in4

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 533thorn 0633thorn 1846 frac14 2442 in4

Cp frac14 AsyAs thorn Ap

thorn tb2

frac14 4eth2375THORN22

thorn 0752

frac14 0807 in

Cs frac14 hthorn tb

Cp

frac14 4thorn 075 0807 frac14 3943

Check deflections

Deflections exceed allowable No good

bull Assume a larger stiffener size WT9 593

tf frac14 106 025 frac14 081

tw frac14 0625 025 frac14 0375

bull Check corroded thickness to find properties ofcorroded section This section would be equivalent toa WT9 30 Properties are

As frac14 882 in2

Is frac14 647 in4

Cs frac14 216 in

H frac14 9 in

Cp frac14 hthorn tb Cs

frac14 9thorn 075 216 frac14 759 in

Figure 5-20 Battle layout for sample problem

Item bn pn d

1 2352 104 149

2 2352 243 349

3 144 381 0767

Vessel Internals 387

y frac14 Cp tb2

frac14 7215 in

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 647thorn 0844thorn 30814 frac14 3737 in4

bull Check stresses and deflections See results in Table5-27

bull Stresses and deflections are acceptablebull Check welds

d frac14 ts thorn 2tw frac14 0375thorn 2eth0323THORN frac14 102

y frac14 7215 in

I frac14 3737 in4

n frac14 2

w frac14 Vdy11 200In

frac14 6681eth102THORN721511 200eth3737THORN2

frac14 0005thorn 0125 frac14 013 in

bull Check thermal expansion of baffle

D1 frac14 085PRm

tEfrac14 085eth250THORN120938

175eth273 106THORNfrac14 000054 in

D2 frac14 Rma DT frac14 1209387124 106430

frac14 0370 in

D3 frac14 05ba DT frac14 05240

7124 106430

frac14 0367 in

D4 frac14 D1 thorn D2 D3 frac14 000054thorn 0370 0367

frac14 00035 lt 006 in

Table 5-26Summary of Results for Stress and Deflection in Composite Stiffeners for Sample Problem

Item Orientation an bn pn M d V sp ss

1 Horiz 2352 d 104 172595 009 2690 3504 997

2 Horiz 2352 d 243 403275 021 6287 8186 2330

3 Horiz 144 d 381 237012 0045 6035 4811 1370

4 Vert d 156 450 154674 0037 5648 3141 894

5 Vert d 1776 513 228539 0072 6681 6681 1320

Figure 5-21 Details of weld attaching stiffener

388 Pressure Vessel Design Manual

Vessel Internals 389

Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 9: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

Procedure 5-9 Design of Trays

Typical Tower Dimensions and Nomenclature

1

2

5

4

11

2115

12

29

13

8 10

6

7

322

19

31

2

9

25

24

2318

17

20

22

1413

16

24

30

36 35

27

28

28 26

28

2 PASS

1 PASS

C

E

F

G

A34

4rdquo MIN

33

26 2827

H

2

31

32

C

KL J

N

MP

Q

E

TL

TL

366 Pressure Vessel Design Manual

Tray Types

1 Valve2 Bubble Cap3 Sieve4 Tunnel5 Chimney6 Ripple7 Shower8 Shed Rows9 Disc amp Donut10 Cartridge11 Jet12 Kittle13 Turbogrid14 Dual Flow15 Slotted16 Venturi17 Cascade18 Accumulator

Tray Nomenclature

1 InletFeedReflux2 Inlet Weir3 Inlet Baffle4 Downcomer Clearance5 Weir Height6 Anti-Jump Baffle7 Seal Pan8 Straight Downcomer9 Sloped Downcomer10 Side Downcomer11 Center Downcomer12 Insulating Baffle13 Draw (Off) Nozzle14 Draw (Off) Pan15 Pass Transition16 Total Draw Chimney Tray

17 Chimney18 Chimney Hat19 Return Nozzle20 Sump21 Intermediate Feed Nozzle22 Partial Drawoff Nozzle23 Partition24 Vapor Inlet25 Vapor Inlet Baffle26 Feed Area27 Active Tray Area28 Dowcomer Area (Inactive Tray Area)29 Vapor Outlet30 Baffle31 Internal Pipe32 Support Clips33 Internal Flanges34 End Plate35 Product Outlet Nozzle36 Reboiler Draw Nozzle

Dimensions

A frac14 Short frac14 5 NPSthorn 4 in

Long frac14 5 NPSthorn 10 in

B frac14 Same as middle downcomer

C frac14 5 NPS

D frac14 Same as weir height

E frac14 NPSthorn 6 in

F frac14 NPSthorn 1 in

G frac14 15 NPSthorn 1 in

H frac14 5 NPSthorn 15 in

J frac14 15 NPS

Vessel Internals 367

K frac14 NPS

L frac14 2 NPS

M frac14 Minimum with 21 SE head frac1425 Dthorn tH thorn 15 NPSthorn 2 in

Minimum with hemi head frac14M frac14 5 Dthorn tH thorn 15 NPSthorn 2 in

N frac14 Minimum distance from tangent line to nozzlecenterline See Table 519

P frac14 Minimum skirt height for 21 SE Head SeeTable 5-20

Q frac14 Minimum seal pan depth frac14 tray spacing thorn 6 inR frac14 Downcomer width

Table 5-18Minimum Distance From Tangent Line ldquoNrdquo

Noz Size N Noz Size N

lt2 in 5 12 in 16

3 in 7 14 in 18

4 in 8 16 in 20

6 in 10 18 in 24

8 in 12 20 in 27

10 in 14 24 in 30

Table 5-19Minimum Skirt Height ldquoPrdquo

Dia P Dia P

lt24 in 2 ft e 6 in 114e120 5 ft e 6 in

30e36 3 ft e 0 in 126e132 6 ft e 0 in

48e54 3 ft e 6 in 138e144 6 ft e 6 in

54e60 3 ft e 6 in 150e156 7 ft e 0 in

66e72 4 ft e 0 in 162e168 8 ft e 0 in

78e84 4 ft e 6 in 174e180 8 ft e 6 in

90e106 5 ft e 0 in

368 Pressure Vessel Design Manual

A1 A1

A1

A1 A1

A1 A1

A1 A2

A2A1

A1A1

A1

A1

A1

A1

A2 A2

A2

A2A1

AS AS

AS

AS

AC

AC AC

AQ

D

SIDE DOWNCOMER

CENTERDOWNCOMER

TRAYS

1-PASS TRAY 2-PASS TRAY 3-PASS TRAY 4-PASS TRAY

Vessel Internals 369

TYPICAL TRAY ASSEMBLY

Hex Head Bolt

Manway Lock Clamps

Manway Lock StudsManway Clamps

Seal Plate

Tray Floor (Active)

Tray Floor (Active)Outlet Weir

Downcomer Truss

Standard WasherHex NutFrictional Washer

Downcomer Panel

Downcomer Bolting Bar

Bottom Tray ClampHex Head Bolt DowncomerTruss

Hex NutFrictional Washer

DOWNCOMER BOLTING BAR

Hex Nut

Hex Nut

Hex Nut

Hex Head Bolt

Hex Head Bolt

Frictional Washer

Bottom Tray Clamp

Tray Floor (Inlet Panel)

TRAY FLOOR

(INLET PANEL)

TRAY SUPPORT RING

Tray Support Ring

Manway (Active)

ONE PASS TRAY SHOWN

370 Pressure Vessel Design Manual

Design of Tray Plates

Stress and DeflectionCase 1 Perforated Plate

Reference Roark 5th Edition Table 26 Case 1A

bull Rectangular platebull Uniformly loadedbull All edges simply supported

DATA

a b g frac14 Coefficients from Table 5-21E frac14 Modulus of elasticity at design temperature PSI

t frac14 Corroded thickness of tray inCa frac14 Corrosion allowance inn frac14 Hole efficiencyd frac14 Deflection at center inp frac14 Uniform load PSIs frac14 Bending stress PSI

FORMULAS

bull Stress s

s frac14 b p b4

n t2

BUBBLE-CAPTRAY

VALVELIQUID FLOW

WEIRDOWNCOMER

VAPOR

VAPORVAPOR

VAPOR

VAPOR

TYPES OF TRAYS

CHIMNEY CHIMNEY HAT

SUMPTRUSS

CHIMNEYACCUMULATOR TRAYS

LIQUID

LIQUID

LIQUID

SIEVE TRAY

VALVE TRAY

BUBBLE - CAP TRAY

USUALLY2rsquondash0rdquo

18rdquo MINIMUM

Vessel Internals 371

bull Deflection d

d frac14 a p b4

E n t3

bull Efficiency of holes for perforated plate n

n frac14 1 25 p d2

e C

DIMENSIONAL DATA

a frac14b frac14t frac14a=b frac14b frac14a frac14p frac14d frac14e frac14C frac14E frac14

Tray DesignCase 2 Standard tray plates

LOADS

A DL frac14 Dead load weight of trays and beams

B LL frac14 Live load dynamic load DP

C LL frac14 Liquid load weight of liquid supported

bull Total area AT

AT frac14 p D2=4 frac14 7854 D2

bull Total load PT

PT frac14 DLthorn LLthorn LL

bull Uniform load p

p frac14 PT=AT

LONG EDGE

SHORTEDGEBEAMS (TYP)

c = PITCH60deg

a

b

e

d

Table 5-20Coefficients

ab b a g

10 2874 044 420

12 3762 0616 455

14 4530 0770 478

16 5172 0906 491

18 5688 1017 499

20 6102 1110 503

30 7134 1335 505

40 7410 1400 502

50 7476 1417 501

N 7500 1421 500

372 Pressure Vessel Design Manual

PROPERTIES OF SECTIONS

C frac14 SAY=SA

I frac14 SAY2 thorn SI C SAY

Z frac14 I=C

CALCULATIONS

bull Determine panel area AP

AP frac14 Ln dnbull Load on panel FP

FP frac14 AP p

Uniform Load

bull Uniform load on beam w

w frac14 FP=Ln

bull Moment M

M frac14 w L2

n

8

bull Bending stress fb

fb frac14 M=Z

bull Deflection d

d frac14 5 w L4

n

384 E I

Concentrated Load

bull Moment M

M frac14 ethP LnTHORN=4bull Bending stress fb

fb frac14 M=Z

bull Deflection d

d frac14 P L3

n

48 E I

TYPE 1

1

2

XX

h

dn

t

PART A Y AY AY2 I12sum

C frac14 SAY=SA

I frac14 SAY2 thorn SI C SAY

Z frac14 I=C

TYPE 2

1

32

XX

h

dn

do

t

PART A Y AY AY2 I123sum

L1

DC

DIMENSIONS OF TRAY PANELS

d1 d2 d3 d4

Vessel Internals 373

NOTES1 Design Loads Trays pans drawoff boxes or

similar intemals shall be designed using a corrodedthickness to support their own weight plus thefollowing live loadsa Fractionation trays Design live load shall be the

greater of 20 PSF (98 KgSq meter) or the weightof water 2 (50 mm) over the highest weirsetting

b Areas under downcomers Design live load shallbe the greater of 64 PSF (314 Kg Sq meter) ora head of water one half the height of thedowncomer

c Pans (accumulator and drawoff pans) Designlive load shall be the greater of 1 PSI (700 Kg Sqmeter) or the weight of water at the maximumoperating level of the pan

d Baffles With no operating liquid level shall usea design live load of 1 PSI (700 KgSq meter) onthe projected horizontal area or actual impulseforce whichever is greater

2 Maintenance Loads Tray support members (allbeams support clips etc) shall be designed fora concentrated load of 300 Lbs (135 Kg) at any pointon the installed assembly The design shall be basedon the corroded thicknesses and an allowable stressof 9 Fy For maintenance loads stresses in the trayplates need not be considered

3 Uplift resistance Typical design of uplift for traysand packing is 25 PSI (17 Millibar) For serviceswhere excessive uplift can occur a higher upliftresistance may be used Examples of higher upliftfactors are as follows

a Crude and FCC side strippers 1 PSI (70 millibar)b Vacuum tower stripping trays overflash

collector wash trays or beds 2 PSI (140Millibar)

c Collectiors and packed beds above the washsection of a vacuum Tower 1 PSI (70 Millibar)

4 Failure sequence Tray assemblies wheneverpossible shall be designed so that failure will occurin the following ordera Tray manwaysb Tray deck active areasc Minor beams and downcomersd Major beams (defined as beams 10ft (3 Meters)

or longer or beams which extend across a vesselwithout interruption regardless of length)

5 Allowable stresses Allowable unit stress shall bebased on yield strength Fy at design temperaturewith AISC factors for tension bearing shear etc

6 Allowable Deflection The calculated combineddeflection of trays and support beams due to oper-ating loads shall not exceed the lesser of 1900 of thevessel diameter (in inches) or 316 (5 mm)

RECOMMENDED TRAY SPACING amp MANWAY SIZE

COLUMN DIA

(FT)

TRAY SPACING

(IN)

MANWAY

SPACING

MIN MANWAY

SIZE

25 to 16 24 Every 10 trays 18 in

16 to 24 30 Every 8 trays 20 in

24 to 32 36 Every 6 trays 24 in

32 and larger 42 Every 4 trays 30 in

374 Pressure Vessel Design Manual

Procedure 5-10 Flow Over Weirs

Notation

b frac14 width ftH frac14 static head of liquid ftQ frac14 discharge rate cu ftsecV frac14 velocity of approach ftsecH0 frac14 head correction per Table 5-22

Calculations

Discharge Q

bull For a full-length weir (Case 1)

Q frac14 333beth15 HTHORNbull For a contracted weir (Case 2)

Q frac14 333beth15 HTHORNbull For a V-notch weir (Case 3)

Q frac14 633 H

bull For a Cippoletti weir (Case 4)

Q frac14 3367beth15 HTHORN

Notes

1 Assumes troughs are level

Case 1 Full-Width Weir

V frac14 1ndash2 ftsec at 4 H upstream

Case 2 Contracted Weir

V frac14 1ndash2 ftsec at 3 H upstream

Case 3 V-Notch Weir

V frac14 5 ftsec at 5 H upstream

Case 4 Cippoletti Weir

V frac14 1ndash2 ftsec at 4 H upstream

Table 5-21Head correction for velocity of approach

V 04 06 08 10 12 14 16 18 20

Hrsquo 0002 0005 001 0015 0023 003 004 005 0062

V 22 24 26 28 30 32 34 36 38

Hrsquo 0075 0089 0105 0122 014 015 0179 0201 0213

Vessel Internals 375

Procedure 5-11 Design of Demisters

Demister pads or mist eliminators are important inter-nals in process vessels Anytime there is a continuous twophase flow vapor and liquid there is the possibility forliquid entrainment If it is desirable to separate the liquidand vapor or prevent liquid carryover in the vapor streamthe velocity must be kept sufficiently low to allow the liquiddroplets to fall out of the vapor stream Demister pads areeffective entrainment separators which allow operation atvapor velocities that would otherwise be excessive

ldquoVapor disengagementrdquo can be accomplished withouta demister but the vessel must be made much larger toaccomplish the same degree of separation This is knownas gravity separation

Demister pads are used in a wide variety of processvessels Good performance can be achieved at velocitiesof 30 to 110 of optimum

Demister pads can be used in vertical or horizontalvessels The mesh pad orientation can be either vertical orhorizontal in a vertical or horizontal vessel

A wire mesh demister consists of a knitted wire matmounted on a light weight support grid The mesh is madeby weaving small diameter metal wire into a mesh Padsmay be made out of metal or plastics Metal type includecarbon steel stainless steel monel and others Plasticmaterials include PTFE HDPE and PP

Pressure drop is usually extremely low in the range of1 inch of water column maximum The pressure drop isnormally so low that it is ignored in design

Vapor disengagement is dependent on the velocity ofthe stream The most common equation for determining theallowable vapor velocity for two phase flows is as follows

Va frac14 K frac12ethrL rVTHORN=rV1=2

Where

Va frac14 Allowable vapor velocity FtSecK frac14 Constant or coefficientrL frac14 Density of liquid PCFrV frac14 Density of vapor PCF

Notes

1 The mesh pad shall be in one piece or sectional asrequired for insertion through the vessel manwayEach pad section shall be removable through thevessel manhole

2 Layers shall not be more than 6 inches thick3 Where more than one layer is required all joints

shall be staggered

4 One piece circular pads may be spiral in form5 Each section of mesh shall include a grid on one or

both sides The grid wire andor fastening deviceshall be the same material as the mesh pad Top andbottom grids shall be constructed of frac14 inch diam-eter rods welded to ⅛ inch by 1 inch bars Themaximum gap between mesh pad and grids shall befrac12 inch for diameters less than 84 inches and 1 inchfor larger diameters

6 Estimate grid weights as 3 PSF7 Tie down wires shall be 1=16 inch diameter wire thru

frac14 inch diameter holes on 4 inch centers Tie wiresshould not be pushed through the pad as this couldcause leak paths

8 Pressure drop across mist eliminator shall beassumed as 02 PSI for support design

9 Unless otherwise specified support rings shall be2 inches wide for pads 84 inches in diameter andless and 3 inches wide for larger diameters

10 The mist eliminator shall be a tight fit against theshell or enclosure as well as between sections Meshpads shall be⅜ inches oversize all around for a forcefit against the enclosure No gaps are allowed

11 Vessel fabricator shall provide the mesh and gridsas well as any stiffeners required

12 The Mist eliminator shall be specified as either topor bottom removable

13 ldquoKrdquo is a constant or coefficient that is a functionof the efficiency of the separation K-values rangefrom 04 to 43 but are generally in the 15 to 35range The K-value is affected by pressure type ofpad size of wire type of vessel and disengagingheight For pressure applications the K-valueshould be decreased by 01 for every 100 PSI ofpressure after 100 PSI

14 Wire diameter for the mesh pad itself vary from0003 to 0016 inches

15 The free volume of demisters range from 92 to994

16 The density of the pads ranges from 3 to 33 PCF17 The NSA (nominal surface area) is the surface area

to volume ratio Ft2 Ft3 and is an important indi-cator of performance Ratios range from 50 to 600

18 To obtain higher separation efficiencies the wirediameter is decreased and the density and thicknessare increased

19 Typical width of sections for multi-section pads is12 inches (300 mm) but may vary by manufacturer

376 Pressure Vessel Design Manual

A Horizontal element B Vertical elements

Vertical vessels

Manway

Plate-Pakunit

Meshpad

Drain tubewith seal trap

END VIEW

END VIEW

SIDE VIEW

SIDE VIEW

C Vertical element

Horizontal vessels

D Horizontal element

Figure 5-15 Typical demister configurations in vessels

Vessel Internals 377

d

E Axial entrance

H gt (23) D ndash d

H gt D2 + d(minimum 24rdquo)

H gt D2 ndash d2

H gt D2 + d

H gt D2 ndash d2

h gt d

D

D Side entrance

d

D

B Axial exit

d

D

Φ lt 45ordm

Φ lt 45ordm

C Reverse axial exit

d

A Side exit

D

Figure 5-16 Guidelines for maintaining even flow distribution in vessels with axial flow

378 Pressure Vessel Design Manual

wire mesh

Top grid

Bottom grid

Vertical 14rdquo rodsspaced 12rdquo to 18rdquocenter to center

12rdquo to 18rdquosegmentwidth

18rdquo x 1rdquo flat bars14rdquo rodsspaced 6rdquocenterto center

Manway

Support ring

Support beam

Tie wires

Figure 5-17 Typical mesh pad construction and installation

Vessel Internals 379

Table 5-22Properties of demister pads

Type NSA (1) Ft2 Ft3 Density Pcf Wire Dia in Free Area York Style No Remarks

A 48 5 0011 99 931 High Throughput

B 65 7 0011 986 531 Economy Performance

C 85 9 0011 982 431 Standard - Good All

Around

D 110 108 0011 977 421 Heavy Duty

E 140 8 0006 984 326 Super High Efficiency -

Fine Mist

F 163 0006 94 371 Liquid - Liquid Coalescer

G 450 20 00045 959

H 600 27 00045 945

Notes

1 NSA frac14 Nominal Surface Area

Table 5-23Values of K (Note 13)

Based on Pressure

Pressure (PSIa) Vacuum (In Hg)

Pressure (PSIa) K Vacuum (In Hg) K

15 035 30 035

50 034 20 032

100 032 10 028

200 031 5 023

300 03 1 017

500 028 lt1 017

1000 027

gt1000 027

Based on Disengaging Height

Disengaging Height in K Disengaging Height in K

3 012 9 032

4 015 10 035

5 019 11 038

6 022 12 04

7 025 13 042

8 029 14 043

Based on Application

Vertical Vessels Horizontal Vessels

Type K Type K

General 035 General 035

Compressor Suction Drums 025 Steam Drums 025

Steam Drums 015

380 Pressure Vessel Design Manual

Procedure 5-12 Design of Baffles [10]

Baffles are frequently used in pressure vessels eithervertical or horizontal to divide the interior volume intodifferent compartments These compartments may beused to segregate liquids or provide overflow weirs forthe separation of liquids Baffles may be stiffened orunstiffened When welded across the entire cross sectionof the vessel they must be checked that they are notunduly restricting the diametral expansion of the vesselIf the unrestrained radial expansion of the vessel exceedsthat of the baffle by more than 1=16 in (⅛ in on thediameter) then a ldquoflexiblerdquo type of connection betweenthe vessel shell and the baffle should be utilized Variousflexible attachment designs are shown within theprocedure

Baffles should always be designed in the corrodedcondition It is typical for welded baffles to be designedwith a full corrosion allowance on both sides If the baffleis bolted in then one-half the full corrosion allowancemay be applied to each side the logic being that a boltedbaffle is removable and therefore replaceable

The majority of baffles are flat and as a result are veryinefficient from a strength standpoint Deflection is thegoverning case for flat plates loaded on one side Thepreference is to have unstiffened baffles and they shouldalways be the first choice This will be acceptable forsmall baffles However for larger baffles as the bafflethickness becomes excessive stiffeners offer a moreeconomical design Therefore stiffeners are frequentlyused to stiffen the baffle to prevent the thickness of thebaffle from becoming excessive The number size andspacing of stiffeners are dependent on the baffle thicknessselected There is a continual trade-off between bafflethickness and stiffener parameters

The design of a baffle with stiffeners is an iterativeprocess The procedure for the design of the stiffeners isfirst to divide the baffle into ldquopanelrdquo sections that are rigidenough to withstand the pressure applied on one sideEach individual panel is checked as a flat plate of thedimensions of the panel The stiffeners are assumed to bestrong enough to provide the necessary edge support forthe panel

The stiffeners themselves are designed next A sectionof the baffle is assumed as acting with the stiffener and ascontributing to the overall stiffness This combinedsection is known as the composite stiffener Thecomposite section is checked for stress and deflectionBoth vertical and horizontal stiffeners can be added asrequired

If required an alternate design is assumed based ona thicker or thinner baffle and checked until a satisfactorydesign is found There is no ldquorightrdquo answer however itshould be noted that the thinner the baffle the greater thenumber of stiffeners The lightest overall weight isprobably the ldquobestrdquo design but may not be the leastexpensive due to the welding costs in attaching thestiffeners

One alternative to a flat baffle with stiffeners is to go toa curved baffle A curved baffle works best as a verticalbaffle in a vertical vessel The curved baffle takes pressurefrom either side wall If the pressure is on the concave sidethe baffle is in tension If the pressure is on the convexside the baffle is in compression

There are various tables given in this procedure for flatplate coefficients Flat plate coefficients are utilized todetermine the baffle thickness or a panel thickness Eachtable is specific for a given condition and loading

Vessel Internals 381

Notation

Ap frac14 area of baffle working with stiffener in2

As frac14 area of stiffener in2

Cp frac14 distance from centroid of composite section topanel in

Cs frac14 distance from centroid of composite section tostiffener in

E frac14 modulus of elasticity psiFb frac14 allowable bending stress psiI frac14 moment of inertia composite in4

Is frac14 moment of inertia stiffener in4

l frac14 length of baffle that works with the stiffener inM frac14 moment in-lbn frac14 number of welds attaching stiffenerP frac14 vessel internal pressure psigp frac14 maximum uniform pressure psipn frac14 uniform pressure at any elevation an psiRm frac14 vessel mean radius inSg frac14 specific gravity of contentst frac14 thickness shell intb frac14 thickness baffle ints frac14 thickness stiffener inV frac14 shear load lbw frac14 required fillet weld size ina frac14 thermal coefficient of expansion ininF

bg frac14 flat plate coefficientsDT frac14 differential temperature (design temperature

minus 70F) Fsb frac14 bending stress in baffle psiss frac14 bending stress in stiffener psi

6n frac14 radial expansion ind frac14 deflection inda frac14 maximum allowable deflection in

Baffle Dimensions

382 Pressure Vessel Design Manual

Table 5-24Flat plate coefficients

Vessel Internals 383

Unstiffened Baffle Check

bull Find load p

p frac14 624aSg144

bull Find baffle thickness tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

s

bull Find baffle deflection d

d frac14 pg1b4

Et3b

Limit deflection to the smaller of tb2 or b360 Ifdeflection is excessive then

a Increase the baffle thicknessb Add stiffenersc Go to curved baffle design

If stiffeners are added the first step is to find themaximum ldquoardquo and ldquobrdquo dimensions that will meet theallowable deflection for a given panel size This willestablish the stiffener spacing for both horizontal andvertical stiffeners The ultimate design is a balancebetween baffle thickness stiffener spacing and stiffenersize

Thermal Check of Baffle

bull Vessel radial expansion due to pressure

D1 frac14 085PRm

tE

bull Vessel radial expansion due to temperature

D2 frac14 Rma DT

bull Thermal expansion of baffle

D3 frac14 05ba DT

bull Differential expansion

D4 frac14 D1 thorn D2 D3

Stiffener Design

Divide baffle into panels to limit deflection to the lesserof tb2 or b360 Deflection is calculated based on theappropriate Cases 1 through 3

bull Check baffle for panel size a0 b0bull Check stiffener for length a or b

Recommendations for attaching stiffeners

Benefits Provides added stiffness and no corrosiontrap

Figure 5-18 Example of stiffener layout

384 Pressure Vessel Design Manual

As frac14 tsh

Ap frac14 tbl

IS frac14 tsh3

12

Cp frac14 AsyAs thorn Ap

thorn tb2

Cs frac14 ethhthorn tbTHORN Cp

I frac14 IS thorn Apt2b12

thorn AsApy2

As thorn Ap

lsquo frac14 lesser of 32tb or stiffener spacing

Stresses in BaffleStiffener

sp frac14 MCp

I

ss frac14 MCs

I

Size Welds Attaching Stiffeners

For E70XX Welds

w frac14 Vdy11 200In

Table 5-25Intermittent Welds

Percent of

Continuous Weld

Length of Intermittent Welds

and Distance Between Centers

75 3e4

66 4e6

60 3e5

57 4e7

50 2e4 3e6 4e8

44 4e9

43 3e7

40 2e5 4e10

37 3e8

33 2e6 3e9 4e12

Reprinted by permission of the James F Lincoln Arc Welding

Foundation

Vessel Internals 385

For E60XX Welds

w frac14 Vdy9600In

Sample Problem

bull Given Horizontal vessel with a vertical baffle

P frac14 250 psig

DT frac14 500F

Material frac14 SA-516-70

Ca frac14 0125 in

JE frac14 10

E frac14 273 106 psi

a frac14 7124 10-6 in=in=FFy frac14 308 ksi

D frac14 240 in

Fb frac14 066 Fy frac14 2033 ksi

Rm frac14 120938

ts frac14 175 in

Sg frac14 08

a frac14 15 ft

DT frac14 500 70 frac14 430F

bull Find baffle thickness without stiffener

p frac14 624aSg144

frac14 52 psi

a

bratio frac14 15=20 frac14 075

from Table 5-25 Case 1

b1 frac14 016 g1 frac14 0033

bull Thickness of baffle tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

sfrac14

ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi016eth52THORN2402

20 330

s

tb frac14 153thorn 025 frac14 178

No good Use stiffeners

bull Assume a suitable baffle thickness and determinemaximum panel size

tb frac14 075 in corroded

maximum panel size frac14 4ft 4ft

bull Maximum pressure p

p frac14 13eth624THORN08144

frac14 45 psi

a

bfrac14 4

4frac14 1

See Table 5-25 Case 3

b3 frac14 0287 g3 frac14 00443

sb frac14 b3pb2n

t2

frac14 0287eth45THORN4820752

frac14 5290 psi lt 20 333 psiFigure 5-19 Sample problem

386 Pressure Vessel Design Manual

d frac14 g3

pE

b4nt3

frac14 00443

45

273 106

484

0753

frac14 0092 in lt 0375 in

Balance OK by inspection

bull Assume a layout where the maximum stiffenerspacing is 4 ft

(4) horizontal stiffeners(4) vertical stiffeners(18) panels

bull Check horizontal stiffeners

Dimensions

a1 frac14 3 ft b1 frac14 4 ft

a2 frac14 4 ft b2 frac14 4 ft

a3 frac14 4 ft b3 frac14 12 ft

a4 frac14 4 ft b4 frac14 196 ft

a5 frac14 13 ft

a6 frac14 148ft

bull Assume stiffener size 1 in 4 in

y frac14 2375 in

As frac14 tsh frac14 1eth4THORN frac14 4 in2

l frac14 32tb frac14 32eth075THORN frac14 24 in lt 48 in

AP frac14 tbl frac14 07524 frac14 18 in2

Is frac14 bh3

12frac14 1

43

12frac14 533 in4

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 533thorn 0633thorn 1846 frac14 2442 in4

Cp frac14 AsyAs thorn Ap

thorn tb2

frac14 4eth2375THORN22

thorn 0752

frac14 0807 in

Cs frac14 hthorn tb

Cp

frac14 4thorn 075 0807 frac14 3943

Check deflections

Deflections exceed allowable No good

bull Assume a larger stiffener size WT9 593

tf frac14 106 025 frac14 081

tw frac14 0625 025 frac14 0375

bull Check corroded thickness to find properties ofcorroded section This section would be equivalent toa WT9 30 Properties are

As frac14 882 in2

Is frac14 647 in4

Cs frac14 216 in

H frac14 9 in

Cp frac14 hthorn tb Cs

frac14 9thorn 075 216 frac14 759 in

Figure 5-20 Battle layout for sample problem

Item bn pn d

1 2352 104 149

2 2352 243 349

3 144 381 0767

Vessel Internals 387

y frac14 Cp tb2

frac14 7215 in

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 647thorn 0844thorn 30814 frac14 3737 in4

bull Check stresses and deflections See results in Table5-27

bull Stresses and deflections are acceptablebull Check welds

d frac14 ts thorn 2tw frac14 0375thorn 2eth0323THORN frac14 102

y frac14 7215 in

I frac14 3737 in4

n frac14 2

w frac14 Vdy11 200In

frac14 6681eth102THORN721511 200eth3737THORN2

frac14 0005thorn 0125 frac14 013 in

bull Check thermal expansion of baffle

D1 frac14 085PRm

tEfrac14 085eth250THORN120938

175eth273 106THORNfrac14 000054 in

D2 frac14 Rma DT frac14 1209387124 106430

frac14 0370 in

D3 frac14 05ba DT frac14 05240

7124 106430

frac14 0367 in

D4 frac14 D1 thorn D2 D3 frac14 000054thorn 0370 0367

frac14 00035 lt 006 in

Table 5-26Summary of Results for Stress and Deflection in Composite Stiffeners for Sample Problem

Item Orientation an bn pn M d V sp ss

1 Horiz 2352 d 104 172595 009 2690 3504 997

2 Horiz 2352 d 243 403275 021 6287 8186 2330

3 Horiz 144 d 381 237012 0045 6035 4811 1370

4 Vert d 156 450 154674 0037 5648 3141 894

5 Vert d 1776 513 228539 0072 6681 6681 1320

Figure 5-21 Details of weld attaching stiffener

388 Pressure Vessel Design Manual

Vessel Internals 389

Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 10: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

Tray Types

1 Valve2 Bubble Cap3 Sieve4 Tunnel5 Chimney6 Ripple7 Shower8 Shed Rows9 Disc amp Donut10 Cartridge11 Jet12 Kittle13 Turbogrid14 Dual Flow15 Slotted16 Venturi17 Cascade18 Accumulator

Tray Nomenclature

1 InletFeedReflux2 Inlet Weir3 Inlet Baffle4 Downcomer Clearance5 Weir Height6 Anti-Jump Baffle7 Seal Pan8 Straight Downcomer9 Sloped Downcomer10 Side Downcomer11 Center Downcomer12 Insulating Baffle13 Draw (Off) Nozzle14 Draw (Off) Pan15 Pass Transition16 Total Draw Chimney Tray

17 Chimney18 Chimney Hat19 Return Nozzle20 Sump21 Intermediate Feed Nozzle22 Partial Drawoff Nozzle23 Partition24 Vapor Inlet25 Vapor Inlet Baffle26 Feed Area27 Active Tray Area28 Dowcomer Area (Inactive Tray Area)29 Vapor Outlet30 Baffle31 Internal Pipe32 Support Clips33 Internal Flanges34 End Plate35 Product Outlet Nozzle36 Reboiler Draw Nozzle

Dimensions

A frac14 Short frac14 5 NPSthorn 4 in

Long frac14 5 NPSthorn 10 in

B frac14 Same as middle downcomer

C frac14 5 NPS

D frac14 Same as weir height

E frac14 NPSthorn 6 in

F frac14 NPSthorn 1 in

G frac14 15 NPSthorn 1 in

H frac14 5 NPSthorn 15 in

J frac14 15 NPS

Vessel Internals 367

K frac14 NPS

L frac14 2 NPS

M frac14 Minimum with 21 SE head frac1425 Dthorn tH thorn 15 NPSthorn 2 in

Minimum with hemi head frac14M frac14 5 Dthorn tH thorn 15 NPSthorn 2 in

N frac14 Minimum distance from tangent line to nozzlecenterline See Table 519

P frac14 Minimum skirt height for 21 SE Head SeeTable 5-20

Q frac14 Minimum seal pan depth frac14 tray spacing thorn 6 inR frac14 Downcomer width

Table 5-18Minimum Distance From Tangent Line ldquoNrdquo

Noz Size N Noz Size N

lt2 in 5 12 in 16

3 in 7 14 in 18

4 in 8 16 in 20

6 in 10 18 in 24

8 in 12 20 in 27

10 in 14 24 in 30

Table 5-19Minimum Skirt Height ldquoPrdquo

Dia P Dia P

lt24 in 2 ft e 6 in 114e120 5 ft e 6 in

30e36 3 ft e 0 in 126e132 6 ft e 0 in

48e54 3 ft e 6 in 138e144 6 ft e 6 in

54e60 3 ft e 6 in 150e156 7 ft e 0 in

66e72 4 ft e 0 in 162e168 8 ft e 0 in

78e84 4 ft e 6 in 174e180 8 ft e 6 in

90e106 5 ft e 0 in

368 Pressure Vessel Design Manual

A1 A1

A1

A1 A1

A1 A1

A1 A2

A2A1

A1A1

A1

A1

A1

A1

A2 A2

A2

A2A1

AS AS

AS

AS

AC

AC AC

AQ

D

SIDE DOWNCOMER

CENTERDOWNCOMER

TRAYS

1-PASS TRAY 2-PASS TRAY 3-PASS TRAY 4-PASS TRAY

Vessel Internals 369

TYPICAL TRAY ASSEMBLY

Hex Head Bolt

Manway Lock Clamps

Manway Lock StudsManway Clamps

Seal Plate

Tray Floor (Active)

Tray Floor (Active)Outlet Weir

Downcomer Truss

Standard WasherHex NutFrictional Washer

Downcomer Panel

Downcomer Bolting Bar

Bottom Tray ClampHex Head Bolt DowncomerTruss

Hex NutFrictional Washer

DOWNCOMER BOLTING BAR

Hex Nut

Hex Nut

Hex Nut

Hex Head Bolt

Hex Head Bolt

Frictional Washer

Bottom Tray Clamp

Tray Floor (Inlet Panel)

TRAY FLOOR

(INLET PANEL)

TRAY SUPPORT RING

Tray Support Ring

Manway (Active)

ONE PASS TRAY SHOWN

370 Pressure Vessel Design Manual

Design of Tray Plates

Stress and DeflectionCase 1 Perforated Plate

Reference Roark 5th Edition Table 26 Case 1A

bull Rectangular platebull Uniformly loadedbull All edges simply supported

DATA

a b g frac14 Coefficients from Table 5-21E frac14 Modulus of elasticity at design temperature PSI

t frac14 Corroded thickness of tray inCa frac14 Corrosion allowance inn frac14 Hole efficiencyd frac14 Deflection at center inp frac14 Uniform load PSIs frac14 Bending stress PSI

FORMULAS

bull Stress s

s frac14 b p b4

n t2

BUBBLE-CAPTRAY

VALVELIQUID FLOW

WEIRDOWNCOMER

VAPOR

VAPORVAPOR

VAPOR

VAPOR

TYPES OF TRAYS

CHIMNEY CHIMNEY HAT

SUMPTRUSS

CHIMNEYACCUMULATOR TRAYS

LIQUID

LIQUID

LIQUID

SIEVE TRAY

VALVE TRAY

BUBBLE - CAP TRAY

USUALLY2rsquondash0rdquo

18rdquo MINIMUM

Vessel Internals 371

bull Deflection d

d frac14 a p b4

E n t3

bull Efficiency of holes for perforated plate n

n frac14 1 25 p d2

e C

DIMENSIONAL DATA

a frac14b frac14t frac14a=b frac14b frac14a frac14p frac14d frac14e frac14C frac14E frac14

Tray DesignCase 2 Standard tray plates

LOADS

A DL frac14 Dead load weight of trays and beams

B LL frac14 Live load dynamic load DP

C LL frac14 Liquid load weight of liquid supported

bull Total area AT

AT frac14 p D2=4 frac14 7854 D2

bull Total load PT

PT frac14 DLthorn LLthorn LL

bull Uniform load p

p frac14 PT=AT

LONG EDGE

SHORTEDGEBEAMS (TYP)

c = PITCH60deg

a

b

e

d

Table 5-20Coefficients

ab b a g

10 2874 044 420

12 3762 0616 455

14 4530 0770 478

16 5172 0906 491

18 5688 1017 499

20 6102 1110 503

30 7134 1335 505

40 7410 1400 502

50 7476 1417 501

N 7500 1421 500

372 Pressure Vessel Design Manual

PROPERTIES OF SECTIONS

C frac14 SAY=SA

I frac14 SAY2 thorn SI C SAY

Z frac14 I=C

CALCULATIONS

bull Determine panel area AP

AP frac14 Ln dnbull Load on panel FP

FP frac14 AP p

Uniform Load

bull Uniform load on beam w

w frac14 FP=Ln

bull Moment M

M frac14 w L2

n

8

bull Bending stress fb

fb frac14 M=Z

bull Deflection d

d frac14 5 w L4

n

384 E I

Concentrated Load

bull Moment M

M frac14 ethP LnTHORN=4bull Bending stress fb

fb frac14 M=Z

bull Deflection d

d frac14 P L3

n

48 E I

TYPE 1

1

2

XX

h

dn

t

PART A Y AY AY2 I12sum

C frac14 SAY=SA

I frac14 SAY2 thorn SI C SAY

Z frac14 I=C

TYPE 2

1

32

XX

h

dn

do

t

PART A Y AY AY2 I123sum

L1

DC

DIMENSIONS OF TRAY PANELS

d1 d2 d3 d4

Vessel Internals 373

NOTES1 Design Loads Trays pans drawoff boxes or

similar intemals shall be designed using a corrodedthickness to support their own weight plus thefollowing live loadsa Fractionation trays Design live load shall be the

greater of 20 PSF (98 KgSq meter) or the weightof water 2 (50 mm) over the highest weirsetting

b Areas under downcomers Design live load shallbe the greater of 64 PSF (314 Kg Sq meter) ora head of water one half the height of thedowncomer

c Pans (accumulator and drawoff pans) Designlive load shall be the greater of 1 PSI (700 Kg Sqmeter) or the weight of water at the maximumoperating level of the pan

d Baffles With no operating liquid level shall usea design live load of 1 PSI (700 KgSq meter) onthe projected horizontal area or actual impulseforce whichever is greater

2 Maintenance Loads Tray support members (allbeams support clips etc) shall be designed fora concentrated load of 300 Lbs (135 Kg) at any pointon the installed assembly The design shall be basedon the corroded thicknesses and an allowable stressof 9 Fy For maintenance loads stresses in the trayplates need not be considered

3 Uplift resistance Typical design of uplift for traysand packing is 25 PSI (17 Millibar) For serviceswhere excessive uplift can occur a higher upliftresistance may be used Examples of higher upliftfactors are as follows

a Crude and FCC side strippers 1 PSI (70 millibar)b Vacuum tower stripping trays overflash

collector wash trays or beds 2 PSI (140Millibar)

c Collectiors and packed beds above the washsection of a vacuum Tower 1 PSI (70 Millibar)

4 Failure sequence Tray assemblies wheneverpossible shall be designed so that failure will occurin the following ordera Tray manwaysb Tray deck active areasc Minor beams and downcomersd Major beams (defined as beams 10ft (3 Meters)

or longer or beams which extend across a vesselwithout interruption regardless of length)

5 Allowable stresses Allowable unit stress shall bebased on yield strength Fy at design temperaturewith AISC factors for tension bearing shear etc

6 Allowable Deflection The calculated combineddeflection of trays and support beams due to oper-ating loads shall not exceed the lesser of 1900 of thevessel diameter (in inches) or 316 (5 mm)

RECOMMENDED TRAY SPACING amp MANWAY SIZE

COLUMN DIA

(FT)

TRAY SPACING

(IN)

MANWAY

SPACING

MIN MANWAY

SIZE

25 to 16 24 Every 10 trays 18 in

16 to 24 30 Every 8 trays 20 in

24 to 32 36 Every 6 trays 24 in

32 and larger 42 Every 4 trays 30 in

374 Pressure Vessel Design Manual

Procedure 5-10 Flow Over Weirs

Notation

b frac14 width ftH frac14 static head of liquid ftQ frac14 discharge rate cu ftsecV frac14 velocity of approach ftsecH0 frac14 head correction per Table 5-22

Calculations

Discharge Q

bull For a full-length weir (Case 1)

Q frac14 333beth15 HTHORNbull For a contracted weir (Case 2)

Q frac14 333beth15 HTHORNbull For a V-notch weir (Case 3)

Q frac14 633 H

bull For a Cippoletti weir (Case 4)

Q frac14 3367beth15 HTHORN

Notes

1 Assumes troughs are level

Case 1 Full-Width Weir

V frac14 1ndash2 ftsec at 4 H upstream

Case 2 Contracted Weir

V frac14 1ndash2 ftsec at 3 H upstream

Case 3 V-Notch Weir

V frac14 5 ftsec at 5 H upstream

Case 4 Cippoletti Weir

V frac14 1ndash2 ftsec at 4 H upstream

Table 5-21Head correction for velocity of approach

V 04 06 08 10 12 14 16 18 20

Hrsquo 0002 0005 001 0015 0023 003 004 005 0062

V 22 24 26 28 30 32 34 36 38

Hrsquo 0075 0089 0105 0122 014 015 0179 0201 0213

Vessel Internals 375

Procedure 5-11 Design of Demisters

Demister pads or mist eliminators are important inter-nals in process vessels Anytime there is a continuous twophase flow vapor and liquid there is the possibility forliquid entrainment If it is desirable to separate the liquidand vapor or prevent liquid carryover in the vapor streamthe velocity must be kept sufficiently low to allow the liquiddroplets to fall out of the vapor stream Demister pads areeffective entrainment separators which allow operation atvapor velocities that would otherwise be excessive

ldquoVapor disengagementrdquo can be accomplished withouta demister but the vessel must be made much larger toaccomplish the same degree of separation This is knownas gravity separation

Demister pads are used in a wide variety of processvessels Good performance can be achieved at velocitiesof 30 to 110 of optimum

Demister pads can be used in vertical or horizontalvessels The mesh pad orientation can be either vertical orhorizontal in a vertical or horizontal vessel

A wire mesh demister consists of a knitted wire matmounted on a light weight support grid The mesh is madeby weaving small diameter metal wire into a mesh Padsmay be made out of metal or plastics Metal type includecarbon steel stainless steel monel and others Plasticmaterials include PTFE HDPE and PP

Pressure drop is usually extremely low in the range of1 inch of water column maximum The pressure drop isnormally so low that it is ignored in design

Vapor disengagement is dependent on the velocity ofthe stream The most common equation for determining theallowable vapor velocity for two phase flows is as follows

Va frac14 K frac12ethrL rVTHORN=rV1=2

Where

Va frac14 Allowable vapor velocity FtSecK frac14 Constant or coefficientrL frac14 Density of liquid PCFrV frac14 Density of vapor PCF

Notes

1 The mesh pad shall be in one piece or sectional asrequired for insertion through the vessel manwayEach pad section shall be removable through thevessel manhole

2 Layers shall not be more than 6 inches thick3 Where more than one layer is required all joints

shall be staggered

4 One piece circular pads may be spiral in form5 Each section of mesh shall include a grid on one or

both sides The grid wire andor fastening deviceshall be the same material as the mesh pad Top andbottom grids shall be constructed of frac14 inch diam-eter rods welded to ⅛ inch by 1 inch bars Themaximum gap between mesh pad and grids shall befrac12 inch for diameters less than 84 inches and 1 inchfor larger diameters

6 Estimate grid weights as 3 PSF7 Tie down wires shall be 1=16 inch diameter wire thru

frac14 inch diameter holes on 4 inch centers Tie wiresshould not be pushed through the pad as this couldcause leak paths

8 Pressure drop across mist eliminator shall beassumed as 02 PSI for support design

9 Unless otherwise specified support rings shall be2 inches wide for pads 84 inches in diameter andless and 3 inches wide for larger diameters

10 The mist eliminator shall be a tight fit against theshell or enclosure as well as between sections Meshpads shall be⅜ inches oversize all around for a forcefit against the enclosure No gaps are allowed

11 Vessel fabricator shall provide the mesh and gridsas well as any stiffeners required

12 The Mist eliminator shall be specified as either topor bottom removable

13 ldquoKrdquo is a constant or coefficient that is a functionof the efficiency of the separation K-values rangefrom 04 to 43 but are generally in the 15 to 35range The K-value is affected by pressure type ofpad size of wire type of vessel and disengagingheight For pressure applications the K-valueshould be decreased by 01 for every 100 PSI ofpressure after 100 PSI

14 Wire diameter for the mesh pad itself vary from0003 to 0016 inches

15 The free volume of demisters range from 92 to994

16 The density of the pads ranges from 3 to 33 PCF17 The NSA (nominal surface area) is the surface area

to volume ratio Ft2 Ft3 and is an important indi-cator of performance Ratios range from 50 to 600

18 To obtain higher separation efficiencies the wirediameter is decreased and the density and thicknessare increased

19 Typical width of sections for multi-section pads is12 inches (300 mm) but may vary by manufacturer

376 Pressure Vessel Design Manual

A Horizontal element B Vertical elements

Vertical vessels

Manway

Plate-Pakunit

Meshpad

Drain tubewith seal trap

END VIEW

END VIEW

SIDE VIEW

SIDE VIEW

C Vertical element

Horizontal vessels

D Horizontal element

Figure 5-15 Typical demister configurations in vessels

Vessel Internals 377

d

E Axial entrance

H gt (23) D ndash d

H gt D2 + d(minimum 24rdquo)

H gt D2 ndash d2

H gt D2 + d

H gt D2 ndash d2

h gt d

D

D Side entrance

d

D

B Axial exit

d

D

Φ lt 45ordm

Φ lt 45ordm

C Reverse axial exit

d

A Side exit

D

Figure 5-16 Guidelines for maintaining even flow distribution in vessels with axial flow

378 Pressure Vessel Design Manual

wire mesh

Top grid

Bottom grid

Vertical 14rdquo rodsspaced 12rdquo to 18rdquocenter to center

12rdquo to 18rdquosegmentwidth

18rdquo x 1rdquo flat bars14rdquo rodsspaced 6rdquocenterto center

Manway

Support ring

Support beam

Tie wires

Figure 5-17 Typical mesh pad construction and installation

Vessel Internals 379

Table 5-22Properties of demister pads

Type NSA (1) Ft2 Ft3 Density Pcf Wire Dia in Free Area York Style No Remarks

A 48 5 0011 99 931 High Throughput

B 65 7 0011 986 531 Economy Performance

C 85 9 0011 982 431 Standard - Good All

Around

D 110 108 0011 977 421 Heavy Duty

E 140 8 0006 984 326 Super High Efficiency -

Fine Mist

F 163 0006 94 371 Liquid - Liquid Coalescer

G 450 20 00045 959

H 600 27 00045 945

Notes

1 NSA frac14 Nominal Surface Area

Table 5-23Values of K (Note 13)

Based on Pressure

Pressure (PSIa) Vacuum (In Hg)

Pressure (PSIa) K Vacuum (In Hg) K

15 035 30 035

50 034 20 032

100 032 10 028

200 031 5 023

300 03 1 017

500 028 lt1 017

1000 027

gt1000 027

Based on Disengaging Height

Disengaging Height in K Disengaging Height in K

3 012 9 032

4 015 10 035

5 019 11 038

6 022 12 04

7 025 13 042

8 029 14 043

Based on Application

Vertical Vessels Horizontal Vessels

Type K Type K

General 035 General 035

Compressor Suction Drums 025 Steam Drums 025

Steam Drums 015

380 Pressure Vessel Design Manual

Procedure 5-12 Design of Baffles [10]

Baffles are frequently used in pressure vessels eithervertical or horizontal to divide the interior volume intodifferent compartments These compartments may beused to segregate liquids or provide overflow weirs forthe separation of liquids Baffles may be stiffened orunstiffened When welded across the entire cross sectionof the vessel they must be checked that they are notunduly restricting the diametral expansion of the vesselIf the unrestrained radial expansion of the vessel exceedsthat of the baffle by more than 1=16 in (⅛ in on thediameter) then a ldquoflexiblerdquo type of connection betweenthe vessel shell and the baffle should be utilized Variousflexible attachment designs are shown within theprocedure

Baffles should always be designed in the corrodedcondition It is typical for welded baffles to be designedwith a full corrosion allowance on both sides If the baffleis bolted in then one-half the full corrosion allowancemay be applied to each side the logic being that a boltedbaffle is removable and therefore replaceable

The majority of baffles are flat and as a result are veryinefficient from a strength standpoint Deflection is thegoverning case for flat plates loaded on one side Thepreference is to have unstiffened baffles and they shouldalways be the first choice This will be acceptable forsmall baffles However for larger baffles as the bafflethickness becomes excessive stiffeners offer a moreeconomical design Therefore stiffeners are frequentlyused to stiffen the baffle to prevent the thickness of thebaffle from becoming excessive The number size andspacing of stiffeners are dependent on the baffle thicknessselected There is a continual trade-off between bafflethickness and stiffener parameters

The design of a baffle with stiffeners is an iterativeprocess The procedure for the design of the stiffeners isfirst to divide the baffle into ldquopanelrdquo sections that are rigidenough to withstand the pressure applied on one sideEach individual panel is checked as a flat plate of thedimensions of the panel The stiffeners are assumed to bestrong enough to provide the necessary edge support forthe panel

The stiffeners themselves are designed next A sectionof the baffle is assumed as acting with the stiffener and ascontributing to the overall stiffness This combinedsection is known as the composite stiffener Thecomposite section is checked for stress and deflectionBoth vertical and horizontal stiffeners can be added asrequired

If required an alternate design is assumed based ona thicker or thinner baffle and checked until a satisfactorydesign is found There is no ldquorightrdquo answer however itshould be noted that the thinner the baffle the greater thenumber of stiffeners The lightest overall weight isprobably the ldquobestrdquo design but may not be the leastexpensive due to the welding costs in attaching thestiffeners

One alternative to a flat baffle with stiffeners is to go toa curved baffle A curved baffle works best as a verticalbaffle in a vertical vessel The curved baffle takes pressurefrom either side wall If the pressure is on the concave sidethe baffle is in tension If the pressure is on the convexside the baffle is in compression

There are various tables given in this procedure for flatplate coefficients Flat plate coefficients are utilized todetermine the baffle thickness or a panel thickness Eachtable is specific for a given condition and loading

Vessel Internals 381

Notation

Ap frac14 area of baffle working with stiffener in2

As frac14 area of stiffener in2

Cp frac14 distance from centroid of composite section topanel in

Cs frac14 distance from centroid of composite section tostiffener in

E frac14 modulus of elasticity psiFb frac14 allowable bending stress psiI frac14 moment of inertia composite in4

Is frac14 moment of inertia stiffener in4

l frac14 length of baffle that works with the stiffener inM frac14 moment in-lbn frac14 number of welds attaching stiffenerP frac14 vessel internal pressure psigp frac14 maximum uniform pressure psipn frac14 uniform pressure at any elevation an psiRm frac14 vessel mean radius inSg frac14 specific gravity of contentst frac14 thickness shell intb frac14 thickness baffle ints frac14 thickness stiffener inV frac14 shear load lbw frac14 required fillet weld size ina frac14 thermal coefficient of expansion ininF

bg frac14 flat plate coefficientsDT frac14 differential temperature (design temperature

minus 70F) Fsb frac14 bending stress in baffle psiss frac14 bending stress in stiffener psi

6n frac14 radial expansion ind frac14 deflection inda frac14 maximum allowable deflection in

Baffle Dimensions

382 Pressure Vessel Design Manual

Table 5-24Flat plate coefficients

Vessel Internals 383

Unstiffened Baffle Check

bull Find load p

p frac14 624aSg144

bull Find baffle thickness tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

s

bull Find baffle deflection d

d frac14 pg1b4

Et3b

Limit deflection to the smaller of tb2 or b360 Ifdeflection is excessive then

a Increase the baffle thicknessb Add stiffenersc Go to curved baffle design

If stiffeners are added the first step is to find themaximum ldquoardquo and ldquobrdquo dimensions that will meet theallowable deflection for a given panel size This willestablish the stiffener spacing for both horizontal andvertical stiffeners The ultimate design is a balancebetween baffle thickness stiffener spacing and stiffenersize

Thermal Check of Baffle

bull Vessel radial expansion due to pressure

D1 frac14 085PRm

tE

bull Vessel radial expansion due to temperature

D2 frac14 Rma DT

bull Thermal expansion of baffle

D3 frac14 05ba DT

bull Differential expansion

D4 frac14 D1 thorn D2 D3

Stiffener Design

Divide baffle into panels to limit deflection to the lesserof tb2 or b360 Deflection is calculated based on theappropriate Cases 1 through 3

bull Check baffle for panel size a0 b0bull Check stiffener for length a or b

Recommendations for attaching stiffeners

Benefits Provides added stiffness and no corrosiontrap

Figure 5-18 Example of stiffener layout

384 Pressure Vessel Design Manual

As frac14 tsh

Ap frac14 tbl

IS frac14 tsh3

12

Cp frac14 AsyAs thorn Ap

thorn tb2

Cs frac14 ethhthorn tbTHORN Cp

I frac14 IS thorn Apt2b12

thorn AsApy2

As thorn Ap

lsquo frac14 lesser of 32tb or stiffener spacing

Stresses in BaffleStiffener

sp frac14 MCp

I

ss frac14 MCs

I

Size Welds Attaching Stiffeners

For E70XX Welds

w frac14 Vdy11 200In

Table 5-25Intermittent Welds

Percent of

Continuous Weld

Length of Intermittent Welds

and Distance Between Centers

75 3e4

66 4e6

60 3e5

57 4e7

50 2e4 3e6 4e8

44 4e9

43 3e7

40 2e5 4e10

37 3e8

33 2e6 3e9 4e12

Reprinted by permission of the James F Lincoln Arc Welding

Foundation

Vessel Internals 385

For E60XX Welds

w frac14 Vdy9600In

Sample Problem

bull Given Horizontal vessel with a vertical baffle

P frac14 250 psig

DT frac14 500F

Material frac14 SA-516-70

Ca frac14 0125 in

JE frac14 10

E frac14 273 106 psi

a frac14 7124 10-6 in=in=FFy frac14 308 ksi

D frac14 240 in

Fb frac14 066 Fy frac14 2033 ksi

Rm frac14 120938

ts frac14 175 in

Sg frac14 08

a frac14 15 ft

DT frac14 500 70 frac14 430F

bull Find baffle thickness without stiffener

p frac14 624aSg144

frac14 52 psi

a

bratio frac14 15=20 frac14 075

from Table 5-25 Case 1

b1 frac14 016 g1 frac14 0033

bull Thickness of baffle tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

sfrac14

ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi016eth52THORN2402

20 330

s

tb frac14 153thorn 025 frac14 178

No good Use stiffeners

bull Assume a suitable baffle thickness and determinemaximum panel size

tb frac14 075 in corroded

maximum panel size frac14 4ft 4ft

bull Maximum pressure p

p frac14 13eth624THORN08144

frac14 45 psi

a

bfrac14 4

4frac14 1

See Table 5-25 Case 3

b3 frac14 0287 g3 frac14 00443

sb frac14 b3pb2n

t2

frac14 0287eth45THORN4820752

frac14 5290 psi lt 20 333 psiFigure 5-19 Sample problem

386 Pressure Vessel Design Manual

d frac14 g3

pE

b4nt3

frac14 00443

45

273 106

484

0753

frac14 0092 in lt 0375 in

Balance OK by inspection

bull Assume a layout where the maximum stiffenerspacing is 4 ft

(4) horizontal stiffeners(4) vertical stiffeners(18) panels

bull Check horizontal stiffeners

Dimensions

a1 frac14 3 ft b1 frac14 4 ft

a2 frac14 4 ft b2 frac14 4 ft

a3 frac14 4 ft b3 frac14 12 ft

a4 frac14 4 ft b4 frac14 196 ft

a5 frac14 13 ft

a6 frac14 148ft

bull Assume stiffener size 1 in 4 in

y frac14 2375 in

As frac14 tsh frac14 1eth4THORN frac14 4 in2

l frac14 32tb frac14 32eth075THORN frac14 24 in lt 48 in

AP frac14 tbl frac14 07524 frac14 18 in2

Is frac14 bh3

12frac14 1

43

12frac14 533 in4

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 533thorn 0633thorn 1846 frac14 2442 in4

Cp frac14 AsyAs thorn Ap

thorn tb2

frac14 4eth2375THORN22

thorn 0752

frac14 0807 in

Cs frac14 hthorn tb

Cp

frac14 4thorn 075 0807 frac14 3943

Check deflections

Deflections exceed allowable No good

bull Assume a larger stiffener size WT9 593

tf frac14 106 025 frac14 081

tw frac14 0625 025 frac14 0375

bull Check corroded thickness to find properties ofcorroded section This section would be equivalent toa WT9 30 Properties are

As frac14 882 in2

Is frac14 647 in4

Cs frac14 216 in

H frac14 9 in

Cp frac14 hthorn tb Cs

frac14 9thorn 075 216 frac14 759 in

Figure 5-20 Battle layout for sample problem

Item bn pn d

1 2352 104 149

2 2352 243 349

3 144 381 0767

Vessel Internals 387

y frac14 Cp tb2

frac14 7215 in

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 647thorn 0844thorn 30814 frac14 3737 in4

bull Check stresses and deflections See results in Table5-27

bull Stresses and deflections are acceptablebull Check welds

d frac14 ts thorn 2tw frac14 0375thorn 2eth0323THORN frac14 102

y frac14 7215 in

I frac14 3737 in4

n frac14 2

w frac14 Vdy11 200In

frac14 6681eth102THORN721511 200eth3737THORN2

frac14 0005thorn 0125 frac14 013 in

bull Check thermal expansion of baffle

D1 frac14 085PRm

tEfrac14 085eth250THORN120938

175eth273 106THORNfrac14 000054 in

D2 frac14 Rma DT frac14 1209387124 106430

frac14 0370 in

D3 frac14 05ba DT frac14 05240

7124 106430

frac14 0367 in

D4 frac14 D1 thorn D2 D3 frac14 000054thorn 0370 0367

frac14 00035 lt 006 in

Table 5-26Summary of Results for Stress and Deflection in Composite Stiffeners for Sample Problem

Item Orientation an bn pn M d V sp ss

1 Horiz 2352 d 104 172595 009 2690 3504 997

2 Horiz 2352 d 243 403275 021 6287 8186 2330

3 Horiz 144 d 381 237012 0045 6035 4811 1370

4 Vert d 156 450 154674 0037 5648 3141 894

5 Vert d 1776 513 228539 0072 6681 6681 1320

Figure 5-21 Details of weld attaching stiffener

388 Pressure Vessel Design Manual

Vessel Internals 389

Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 11: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

K frac14 NPS

L frac14 2 NPS

M frac14 Minimum with 21 SE head frac1425 Dthorn tH thorn 15 NPSthorn 2 in

Minimum with hemi head frac14M frac14 5 Dthorn tH thorn 15 NPSthorn 2 in

N frac14 Minimum distance from tangent line to nozzlecenterline See Table 519

P frac14 Minimum skirt height for 21 SE Head SeeTable 5-20

Q frac14 Minimum seal pan depth frac14 tray spacing thorn 6 inR frac14 Downcomer width

Table 5-18Minimum Distance From Tangent Line ldquoNrdquo

Noz Size N Noz Size N

lt2 in 5 12 in 16

3 in 7 14 in 18

4 in 8 16 in 20

6 in 10 18 in 24

8 in 12 20 in 27

10 in 14 24 in 30

Table 5-19Minimum Skirt Height ldquoPrdquo

Dia P Dia P

lt24 in 2 ft e 6 in 114e120 5 ft e 6 in

30e36 3 ft e 0 in 126e132 6 ft e 0 in

48e54 3 ft e 6 in 138e144 6 ft e 6 in

54e60 3 ft e 6 in 150e156 7 ft e 0 in

66e72 4 ft e 0 in 162e168 8 ft e 0 in

78e84 4 ft e 6 in 174e180 8 ft e 6 in

90e106 5 ft e 0 in

368 Pressure Vessel Design Manual

A1 A1

A1

A1 A1

A1 A1

A1 A2

A2A1

A1A1

A1

A1

A1

A1

A2 A2

A2

A2A1

AS AS

AS

AS

AC

AC AC

AQ

D

SIDE DOWNCOMER

CENTERDOWNCOMER

TRAYS

1-PASS TRAY 2-PASS TRAY 3-PASS TRAY 4-PASS TRAY

Vessel Internals 369

TYPICAL TRAY ASSEMBLY

Hex Head Bolt

Manway Lock Clamps

Manway Lock StudsManway Clamps

Seal Plate

Tray Floor (Active)

Tray Floor (Active)Outlet Weir

Downcomer Truss

Standard WasherHex NutFrictional Washer

Downcomer Panel

Downcomer Bolting Bar

Bottom Tray ClampHex Head Bolt DowncomerTruss

Hex NutFrictional Washer

DOWNCOMER BOLTING BAR

Hex Nut

Hex Nut

Hex Nut

Hex Head Bolt

Hex Head Bolt

Frictional Washer

Bottom Tray Clamp

Tray Floor (Inlet Panel)

TRAY FLOOR

(INLET PANEL)

TRAY SUPPORT RING

Tray Support Ring

Manway (Active)

ONE PASS TRAY SHOWN

370 Pressure Vessel Design Manual

Design of Tray Plates

Stress and DeflectionCase 1 Perforated Plate

Reference Roark 5th Edition Table 26 Case 1A

bull Rectangular platebull Uniformly loadedbull All edges simply supported

DATA

a b g frac14 Coefficients from Table 5-21E frac14 Modulus of elasticity at design temperature PSI

t frac14 Corroded thickness of tray inCa frac14 Corrosion allowance inn frac14 Hole efficiencyd frac14 Deflection at center inp frac14 Uniform load PSIs frac14 Bending stress PSI

FORMULAS

bull Stress s

s frac14 b p b4

n t2

BUBBLE-CAPTRAY

VALVELIQUID FLOW

WEIRDOWNCOMER

VAPOR

VAPORVAPOR

VAPOR

VAPOR

TYPES OF TRAYS

CHIMNEY CHIMNEY HAT

SUMPTRUSS

CHIMNEYACCUMULATOR TRAYS

LIQUID

LIQUID

LIQUID

SIEVE TRAY

VALVE TRAY

BUBBLE - CAP TRAY

USUALLY2rsquondash0rdquo

18rdquo MINIMUM

Vessel Internals 371

bull Deflection d

d frac14 a p b4

E n t3

bull Efficiency of holes for perforated plate n

n frac14 1 25 p d2

e C

DIMENSIONAL DATA

a frac14b frac14t frac14a=b frac14b frac14a frac14p frac14d frac14e frac14C frac14E frac14

Tray DesignCase 2 Standard tray plates

LOADS

A DL frac14 Dead load weight of trays and beams

B LL frac14 Live load dynamic load DP

C LL frac14 Liquid load weight of liquid supported

bull Total area AT

AT frac14 p D2=4 frac14 7854 D2

bull Total load PT

PT frac14 DLthorn LLthorn LL

bull Uniform load p

p frac14 PT=AT

LONG EDGE

SHORTEDGEBEAMS (TYP)

c = PITCH60deg

a

b

e

d

Table 5-20Coefficients

ab b a g

10 2874 044 420

12 3762 0616 455

14 4530 0770 478

16 5172 0906 491

18 5688 1017 499

20 6102 1110 503

30 7134 1335 505

40 7410 1400 502

50 7476 1417 501

N 7500 1421 500

372 Pressure Vessel Design Manual

PROPERTIES OF SECTIONS

C frac14 SAY=SA

I frac14 SAY2 thorn SI C SAY

Z frac14 I=C

CALCULATIONS

bull Determine panel area AP

AP frac14 Ln dnbull Load on panel FP

FP frac14 AP p

Uniform Load

bull Uniform load on beam w

w frac14 FP=Ln

bull Moment M

M frac14 w L2

n

8

bull Bending stress fb

fb frac14 M=Z

bull Deflection d

d frac14 5 w L4

n

384 E I

Concentrated Load

bull Moment M

M frac14 ethP LnTHORN=4bull Bending stress fb

fb frac14 M=Z

bull Deflection d

d frac14 P L3

n

48 E I

TYPE 1

1

2

XX

h

dn

t

PART A Y AY AY2 I12sum

C frac14 SAY=SA

I frac14 SAY2 thorn SI C SAY

Z frac14 I=C

TYPE 2

1

32

XX

h

dn

do

t

PART A Y AY AY2 I123sum

L1

DC

DIMENSIONS OF TRAY PANELS

d1 d2 d3 d4

Vessel Internals 373

NOTES1 Design Loads Trays pans drawoff boxes or

similar intemals shall be designed using a corrodedthickness to support their own weight plus thefollowing live loadsa Fractionation trays Design live load shall be the

greater of 20 PSF (98 KgSq meter) or the weightof water 2 (50 mm) over the highest weirsetting

b Areas under downcomers Design live load shallbe the greater of 64 PSF (314 Kg Sq meter) ora head of water one half the height of thedowncomer

c Pans (accumulator and drawoff pans) Designlive load shall be the greater of 1 PSI (700 Kg Sqmeter) or the weight of water at the maximumoperating level of the pan

d Baffles With no operating liquid level shall usea design live load of 1 PSI (700 KgSq meter) onthe projected horizontal area or actual impulseforce whichever is greater

2 Maintenance Loads Tray support members (allbeams support clips etc) shall be designed fora concentrated load of 300 Lbs (135 Kg) at any pointon the installed assembly The design shall be basedon the corroded thicknesses and an allowable stressof 9 Fy For maintenance loads stresses in the trayplates need not be considered

3 Uplift resistance Typical design of uplift for traysand packing is 25 PSI (17 Millibar) For serviceswhere excessive uplift can occur a higher upliftresistance may be used Examples of higher upliftfactors are as follows

a Crude and FCC side strippers 1 PSI (70 millibar)b Vacuum tower stripping trays overflash

collector wash trays or beds 2 PSI (140Millibar)

c Collectiors and packed beds above the washsection of a vacuum Tower 1 PSI (70 Millibar)

4 Failure sequence Tray assemblies wheneverpossible shall be designed so that failure will occurin the following ordera Tray manwaysb Tray deck active areasc Minor beams and downcomersd Major beams (defined as beams 10ft (3 Meters)

or longer or beams which extend across a vesselwithout interruption regardless of length)

5 Allowable stresses Allowable unit stress shall bebased on yield strength Fy at design temperaturewith AISC factors for tension bearing shear etc

6 Allowable Deflection The calculated combineddeflection of trays and support beams due to oper-ating loads shall not exceed the lesser of 1900 of thevessel diameter (in inches) or 316 (5 mm)

RECOMMENDED TRAY SPACING amp MANWAY SIZE

COLUMN DIA

(FT)

TRAY SPACING

(IN)

MANWAY

SPACING

MIN MANWAY

SIZE

25 to 16 24 Every 10 trays 18 in

16 to 24 30 Every 8 trays 20 in

24 to 32 36 Every 6 trays 24 in

32 and larger 42 Every 4 trays 30 in

374 Pressure Vessel Design Manual

Procedure 5-10 Flow Over Weirs

Notation

b frac14 width ftH frac14 static head of liquid ftQ frac14 discharge rate cu ftsecV frac14 velocity of approach ftsecH0 frac14 head correction per Table 5-22

Calculations

Discharge Q

bull For a full-length weir (Case 1)

Q frac14 333beth15 HTHORNbull For a contracted weir (Case 2)

Q frac14 333beth15 HTHORNbull For a V-notch weir (Case 3)

Q frac14 633 H

bull For a Cippoletti weir (Case 4)

Q frac14 3367beth15 HTHORN

Notes

1 Assumes troughs are level

Case 1 Full-Width Weir

V frac14 1ndash2 ftsec at 4 H upstream

Case 2 Contracted Weir

V frac14 1ndash2 ftsec at 3 H upstream

Case 3 V-Notch Weir

V frac14 5 ftsec at 5 H upstream

Case 4 Cippoletti Weir

V frac14 1ndash2 ftsec at 4 H upstream

Table 5-21Head correction for velocity of approach

V 04 06 08 10 12 14 16 18 20

Hrsquo 0002 0005 001 0015 0023 003 004 005 0062

V 22 24 26 28 30 32 34 36 38

Hrsquo 0075 0089 0105 0122 014 015 0179 0201 0213

Vessel Internals 375

Procedure 5-11 Design of Demisters

Demister pads or mist eliminators are important inter-nals in process vessels Anytime there is a continuous twophase flow vapor and liquid there is the possibility forliquid entrainment If it is desirable to separate the liquidand vapor or prevent liquid carryover in the vapor streamthe velocity must be kept sufficiently low to allow the liquiddroplets to fall out of the vapor stream Demister pads areeffective entrainment separators which allow operation atvapor velocities that would otherwise be excessive

ldquoVapor disengagementrdquo can be accomplished withouta demister but the vessel must be made much larger toaccomplish the same degree of separation This is knownas gravity separation

Demister pads are used in a wide variety of processvessels Good performance can be achieved at velocitiesof 30 to 110 of optimum

Demister pads can be used in vertical or horizontalvessels The mesh pad orientation can be either vertical orhorizontal in a vertical or horizontal vessel

A wire mesh demister consists of a knitted wire matmounted on a light weight support grid The mesh is madeby weaving small diameter metal wire into a mesh Padsmay be made out of metal or plastics Metal type includecarbon steel stainless steel monel and others Plasticmaterials include PTFE HDPE and PP

Pressure drop is usually extremely low in the range of1 inch of water column maximum The pressure drop isnormally so low that it is ignored in design

Vapor disengagement is dependent on the velocity ofthe stream The most common equation for determining theallowable vapor velocity for two phase flows is as follows

Va frac14 K frac12ethrL rVTHORN=rV1=2

Where

Va frac14 Allowable vapor velocity FtSecK frac14 Constant or coefficientrL frac14 Density of liquid PCFrV frac14 Density of vapor PCF

Notes

1 The mesh pad shall be in one piece or sectional asrequired for insertion through the vessel manwayEach pad section shall be removable through thevessel manhole

2 Layers shall not be more than 6 inches thick3 Where more than one layer is required all joints

shall be staggered

4 One piece circular pads may be spiral in form5 Each section of mesh shall include a grid on one or

both sides The grid wire andor fastening deviceshall be the same material as the mesh pad Top andbottom grids shall be constructed of frac14 inch diam-eter rods welded to ⅛ inch by 1 inch bars Themaximum gap between mesh pad and grids shall befrac12 inch for diameters less than 84 inches and 1 inchfor larger diameters

6 Estimate grid weights as 3 PSF7 Tie down wires shall be 1=16 inch diameter wire thru

frac14 inch diameter holes on 4 inch centers Tie wiresshould not be pushed through the pad as this couldcause leak paths

8 Pressure drop across mist eliminator shall beassumed as 02 PSI for support design

9 Unless otherwise specified support rings shall be2 inches wide for pads 84 inches in diameter andless and 3 inches wide for larger diameters

10 The mist eliminator shall be a tight fit against theshell or enclosure as well as between sections Meshpads shall be⅜ inches oversize all around for a forcefit against the enclosure No gaps are allowed

11 Vessel fabricator shall provide the mesh and gridsas well as any stiffeners required

12 The Mist eliminator shall be specified as either topor bottom removable

13 ldquoKrdquo is a constant or coefficient that is a functionof the efficiency of the separation K-values rangefrom 04 to 43 but are generally in the 15 to 35range The K-value is affected by pressure type ofpad size of wire type of vessel and disengagingheight For pressure applications the K-valueshould be decreased by 01 for every 100 PSI ofpressure after 100 PSI

14 Wire diameter for the mesh pad itself vary from0003 to 0016 inches

15 The free volume of demisters range from 92 to994

16 The density of the pads ranges from 3 to 33 PCF17 The NSA (nominal surface area) is the surface area

to volume ratio Ft2 Ft3 and is an important indi-cator of performance Ratios range from 50 to 600

18 To obtain higher separation efficiencies the wirediameter is decreased and the density and thicknessare increased

19 Typical width of sections for multi-section pads is12 inches (300 mm) but may vary by manufacturer

376 Pressure Vessel Design Manual

A Horizontal element B Vertical elements

Vertical vessels

Manway

Plate-Pakunit

Meshpad

Drain tubewith seal trap

END VIEW

END VIEW

SIDE VIEW

SIDE VIEW

C Vertical element

Horizontal vessels

D Horizontal element

Figure 5-15 Typical demister configurations in vessels

Vessel Internals 377

d

E Axial entrance

H gt (23) D ndash d

H gt D2 + d(minimum 24rdquo)

H gt D2 ndash d2

H gt D2 + d

H gt D2 ndash d2

h gt d

D

D Side entrance

d

D

B Axial exit

d

D

Φ lt 45ordm

Φ lt 45ordm

C Reverse axial exit

d

A Side exit

D

Figure 5-16 Guidelines for maintaining even flow distribution in vessels with axial flow

378 Pressure Vessel Design Manual

wire mesh

Top grid

Bottom grid

Vertical 14rdquo rodsspaced 12rdquo to 18rdquocenter to center

12rdquo to 18rdquosegmentwidth

18rdquo x 1rdquo flat bars14rdquo rodsspaced 6rdquocenterto center

Manway

Support ring

Support beam

Tie wires

Figure 5-17 Typical mesh pad construction and installation

Vessel Internals 379

Table 5-22Properties of demister pads

Type NSA (1) Ft2 Ft3 Density Pcf Wire Dia in Free Area York Style No Remarks

A 48 5 0011 99 931 High Throughput

B 65 7 0011 986 531 Economy Performance

C 85 9 0011 982 431 Standard - Good All

Around

D 110 108 0011 977 421 Heavy Duty

E 140 8 0006 984 326 Super High Efficiency -

Fine Mist

F 163 0006 94 371 Liquid - Liquid Coalescer

G 450 20 00045 959

H 600 27 00045 945

Notes

1 NSA frac14 Nominal Surface Area

Table 5-23Values of K (Note 13)

Based on Pressure

Pressure (PSIa) Vacuum (In Hg)

Pressure (PSIa) K Vacuum (In Hg) K

15 035 30 035

50 034 20 032

100 032 10 028

200 031 5 023

300 03 1 017

500 028 lt1 017

1000 027

gt1000 027

Based on Disengaging Height

Disengaging Height in K Disengaging Height in K

3 012 9 032

4 015 10 035

5 019 11 038

6 022 12 04

7 025 13 042

8 029 14 043

Based on Application

Vertical Vessels Horizontal Vessels

Type K Type K

General 035 General 035

Compressor Suction Drums 025 Steam Drums 025

Steam Drums 015

380 Pressure Vessel Design Manual

Procedure 5-12 Design of Baffles [10]

Baffles are frequently used in pressure vessels eithervertical or horizontal to divide the interior volume intodifferent compartments These compartments may beused to segregate liquids or provide overflow weirs forthe separation of liquids Baffles may be stiffened orunstiffened When welded across the entire cross sectionof the vessel they must be checked that they are notunduly restricting the diametral expansion of the vesselIf the unrestrained radial expansion of the vessel exceedsthat of the baffle by more than 1=16 in (⅛ in on thediameter) then a ldquoflexiblerdquo type of connection betweenthe vessel shell and the baffle should be utilized Variousflexible attachment designs are shown within theprocedure

Baffles should always be designed in the corrodedcondition It is typical for welded baffles to be designedwith a full corrosion allowance on both sides If the baffleis bolted in then one-half the full corrosion allowancemay be applied to each side the logic being that a boltedbaffle is removable and therefore replaceable

The majority of baffles are flat and as a result are veryinefficient from a strength standpoint Deflection is thegoverning case for flat plates loaded on one side Thepreference is to have unstiffened baffles and they shouldalways be the first choice This will be acceptable forsmall baffles However for larger baffles as the bafflethickness becomes excessive stiffeners offer a moreeconomical design Therefore stiffeners are frequentlyused to stiffen the baffle to prevent the thickness of thebaffle from becoming excessive The number size andspacing of stiffeners are dependent on the baffle thicknessselected There is a continual trade-off between bafflethickness and stiffener parameters

The design of a baffle with stiffeners is an iterativeprocess The procedure for the design of the stiffeners isfirst to divide the baffle into ldquopanelrdquo sections that are rigidenough to withstand the pressure applied on one sideEach individual panel is checked as a flat plate of thedimensions of the panel The stiffeners are assumed to bestrong enough to provide the necessary edge support forthe panel

The stiffeners themselves are designed next A sectionof the baffle is assumed as acting with the stiffener and ascontributing to the overall stiffness This combinedsection is known as the composite stiffener Thecomposite section is checked for stress and deflectionBoth vertical and horizontal stiffeners can be added asrequired

If required an alternate design is assumed based ona thicker or thinner baffle and checked until a satisfactorydesign is found There is no ldquorightrdquo answer however itshould be noted that the thinner the baffle the greater thenumber of stiffeners The lightest overall weight isprobably the ldquobestrdquo design but may not be the leastexpensive due to the welding costs in attaching thestiffeners

One alternative to a flat baffle with stiffeners is to go toa curved baffle A curved baffle works best as a verticalbaffle in a vertical vessel The curved baffle takes pressurefrom either side wall If the pressure is on the concave sidethe baffle is in tension If the pressure is on the convexside the baffle is in compression

There are various tables given in this procedure for flatplate coefficients Flat plate coefficients are utilized todetermine the baffle thickness or a panel thickness Eachtable is specific for a given condition and loading

Vessel Internals 381

Notation

Ap frac14 area of baffle working with stiffener in2

As frac14 area of stiffener in2

Cp frac14 distance from centroid of composite section topanel in

Cs frac14 distance from centroid of composite section tostiffener in

E frac14 modulus of elasticity psiFb frac14 allowable bending stress psiI frac14 moment of inertia composite in4

Is frac14 moment of inertia stiffener in4

l frac14 length of baffle that works with the stiffener inM frac14 moment in-lbn frac14 number of welds attaching stiffenerP frac14 vessel internal pressure psigp frac14 maximum uniform pressure psipn frac14 uniform pressure at any elevation an psiRm frac14 vessel mean radius inSg frac14 specific gravity of contentst frac14 thickness shell intb frac14 thickness baffle ints frac14 thickness stiffener inV frac14 shear load lbw frac14 required fillet weld size ina frac14 thermal coefficient of expansion ininF

bg frac14 flat plate coefficientsDT frac14 differential temperature (design temperature

minus 70F) Fsb frac14 bending stress in baffle psiss frac14 bending stress in stiffener psi

6n frac14 radial expansion ind frac14 deflection inda frac14 maximum allowable deflection in

Baffle Dimensions

382 Pressure Vessel Design Manual

Table 5-24Flat plate coefficients

Vessel Internals 383

Unstiffened Baffle Check

bull Find load p

p frac14 624aSg144

bull Find baffle thickness tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

s

bull Find baffle deflection d

d frac14 pg1b4

Et3b

Limit deflection to the smaller of tb2 or b360 Ifdeflection is excessive then

a Increase the baffle thicknessb Add stiffenersc Go to curved baffle design

If stiffeners are added the first step is to find themaximum ldquoardquo and ldquobrdquo dimensions that will meet theallowable deflection for a given panel size This willestablish the stiffener spacing for both horizontal andvertical stiffeners The ultimate design is a balancebetween baffle thickness stiffener spacing and stiffenersize

Thermal Check of Baffle

bull Vessel radial expansion due to pressure

D1 frac14 085PRm

tE

bull Vessel radial expansion due to temperature

D2 frac14 Rma DT

bull Thermal expansion of baffle

D3 frac14 05ba DT

bull Differential expansion

D4 frac14 D1 thorn D2 D3

Stiffener Design

Divide baffle into panels to limit deflection to the lesserof tb2 or b360 Deflection is calculated based on theappropriate Cases 1 through 3

bull Check baffle for panel size a0 b0bull Check stiffener for length a or b

Recommendations for attaching stiffeners

Benefits Provides added stiffness and no corrosiontrap

Figure 5-18 Example of stiffener layout

384 Pressure Vessel Design Manual

As frac14 tsh

Ap frac14 tbl

IS frac14 tsh3

12

Cp frac14 AsyAs thorn Ap

thorn tb2

Cs frac14 ethhthorn tbTHORN Cp

I frac14 IS thorn Apt2b12

thorn AsApy2

As thorn Ap

lsquo frac14 lesser of 32tb or stiffener spacing

Stresses in BaffleStiffener

sp frac14 MCp

I

ss frac14 MCs

I

Size Welds Attaching Stiffeners

For E70XX Welds

w frac14 Vdy11 200In

Table 5-25Intermittent Welds

Percent of

Continuous Weld

Length of Intermittent Welds

and Distance Between Centers

75 3e4

66 4e6

60 3e5

57 4e7

50 2e4 3e6 4e8

44 4e9

43 3e7

40 2e5 4e10

37 3e8

33 2e6 3e9 4e12

Reprinted by permission of the James F Lincoln Arc Welding

Foundation

Vessel Internals 385

For E60XX Welds

w frac14 Vdy9600In

Sample Problem

bull Given Horizontal vessel with a vertical baffle

P frac14 250 psig

DT frac14 500F

Material frac14 SA-516-70

Ca frac14 0125 in

JE frac14 10

E frac14 273 106 psi

a frac14 7124 10-6 in=in=FFy frac14 308 ksi

D frac14 240 in

Fb frac14 066 Fy frac14 2033 ksi

Rm frac14 120938

ts frac14 175 in

Sg frac14 08

a frac14 15 ft

DT frac14 500 70 frac14 430F

bull Find baffle thickness without stiffener

p frac14 624aSg144

frac14 52 psi

a

bratio frac14 15=20 frac14 075

from Table 5-25 Case 1

b1 frac14 016 g1 frac14 0033

bull Thickness of baffle tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

sfrac14

ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi016eth52THORN2402

20 330

s

tb frac14 153thorn 025 frac14 178

No good Use stiffeners

bull Assume a suitable baffle thickness and determinemaximum panel size

tb frac14 075 in corroded

maximum panel size frac14 4ft 4ft

bull Maximum pressure p

p frac14 13eth624THORN08144

frac14 45 psi

a

bfrac14 4

4frac14 1

See Table 5-25 Case 3

b3 frac14 0287 g3 frac14 00443

sb frac14 b3pb2n

t2

frac14 0287eth45THORN4820752

frac14 5290 psi lt 20 333 psiFigure 5-19 Sample problem

386 Pressure Vessel Design Manual

d frac14 g3

pE

b4nt3

frac14 00443

45

273 106

484

0753

frac14 0092 in lt 0375 in

Balance OK by inspection

bull Assume a layout where the maximum stiffenerspacing is 4 ft

(4) horizontal stiffeners(4) vertical stiffeners(18) panels

bull Check horizontal stiffeners

Dimensions

a1 frac14 3 ft b1 frac14 4 ft

a2 frac14 4 ft b2 frac14 4 ft

a3 frac14 4 ft b3 frac14 12 ft

a4 frac14 4 ft b4 frac14 196 ft

a5 frac14 13 ft

a6 frac14 148ft

bull Assume stiffener size 1 in 4 in

y frac14 2375 in

As frac14 tsh frac14 1eth4THORN frac14 4 in2

l frac14 32tb frac14 32eth075THORN frac14 24 in lt 48 in

AP frac14 tbl frac14 07524 frac14 18 in2

Is frac14 bh3

12frac14 1

43

12frac14 533 in4

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 533thorn 0633thorn 1846 frac14 2442 in4

Cp frac14 AsyAs thorn Ap

thorn tb2

frac14 4eth2375THORN22

thorn 0752

frac14 0807 in

Cs frac14 hthorn tb

Cp

frac14 4thorn 075 0807 frac14 3943

Check deflections

Deflections exceed allowable No good

bull Assume a larger stiffener size WT9 593

tf frac14 106 025 frac14 081

tw frac14 0625 025 frac14 0375

bull Check corroded thickness to find properties ofcorroded section This section would be equivalent toa WT9 30 Properties are

As frac14 882 in2

Is frac14 647 in4

Cs frac14 216 in

H frac14 9 in

Cp frac14 hthorn tb Cs

frac14 9thorn 075 216 frac14 759 in

Figure 5-20 Battle layout for sample problem

Item bn pn d

1 2352 104 149

2 2352 243 349

3 144 381 0767

Vessel Internals 387

y frac14 Cp tb2

frac14 7215 in

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 647thorn 0844thorn 30814 frac14 3737 in4

bull Check stresses and deflections See results in Table5-27

bull Stresses and deflections are acceptablebull Check welds

d frac14 ts thorn 2tw frac14 0375thorn 2eth0323THORN frac14 102

y frac14 7215 in

I frac14 3737 in4

n frac14 2

w frac14 Vdy11 200In

frac14 6681eth102THORN721511 200eth3737THORN2

frac14 0005thorn 0125 frac14 013 in

bull Check thermal expansion of baffle

D1 frac14 085PRm

tEfrac14 085eth250THORN120938

175eth273 106THORNfrac14 000054 in

D2 frac14 Rma DT frac14 1209387124 106430

frac14 0370 in

D3 frac14 05ba DT frac14 05240

7124 106430

frac14 0367 in

D4 frac14 D1 thorn D2 D3 frac14 000054thorn 0370 0367

frac14 00035 lt 006 in

Table 5-26Summary of Results for Stress and Deflection in Composite Stiffeners for Sample Problem

Item Orientation an bn pn M d V sp ss

1 Horiz 2352 d 104 172595 009 2690 3504 997

2 Horiz 2352 d 243 403275 021 6287 8186 2330

3 Horiz 144 d 381 237012 0045 6035 4811 1370

4 Vert d 156 450 154674 0037 5648 3141 894

5 Vert d 1776 513 228539 0072 6681 6681 1320

Figure 5-21 Details of weld attaching stiffener

388 Pressure Vessel Design Manual

Vessel Internals 389

Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 12: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

A1 A1

A1

A1 A1

A1 A1

A1 A2

A2A1

A1A1

A1

A1

A1

A1

A2 A2

A2

A2A1

AS AS

AS

AS

AC

AC AC

AQ

D

SIDE DOWNCOMER

CENTERDOWNCOMER

TRAYS

1-PASS TRAY 2-PASS TRAY 3-PASS TRAY 4-PASS TRAY

Vessel Internals 369

TYPICAL TRAY ASSEMBLY

Hex Head Bolt

Manway Lock Clamps

Manway Lock StudsManway Clamps

Seal Plate

Tray Floor (Active)

Tray Floor (Active)Outlet Weir

Downcomer Truss

Standard WasherHex NutFrictional Washer

Downcomer Panel

Downcomer Bolting Bar

Bottom Tray ClampHex Head Bolt DowncomerTruss

Hex NutFrictional Washer

DOWNCOMER BOLTING BAR

Hex Nut

Hex Nut

Hex Nut

Hex Head Bolt

Hex Head Bolt

Frictional Washer

Bottom Tray Clamp

Tray Floor (Inlet Panel)

TRAY FLOOR

(INLET PANEL)

TRAY SUPPORT RING

Tray Support Ring

Manway (Active)

ONE PASS TRAY SHOWN

370 Pressure Vessel Design Manual

Design of Tray Plates

Stress and DeflectionCase 1 Perforated Plate

Reference Roark 5th Edition Table 26 Case 1A

bull Rectangular platebull Uniformly loadedbull All edges simply supported

DATA

a b g frac14 Coefficients from Table 5-21E frac14 Modulus of elasticity at design temperature PSI

t frac14 Corroded thickness of tray inCa frac14 Corrosion allowance inn frac14 Hole efficiencyd frac14 Deflection at center inp frac14 Uniform load PSIs frac14 Bending stress PSI

FORMULAS

bull Stress s

s frac14 b p b4

n t2

BUBBLE-CAPTRAY

VALVELIQUID FLOW

WEIRDOWNCOMER

VAPOR

VAPORVAPOR

VAPOR

VAPOR

TYPES OF TRAYS

CHIMNEY CHIMNEY HAT

SUMPTRUSS

CHIMNEYACCUMULATOR TRAYS

LIQUID

LIQUID

LIQUID

SIEVE TRAY

VALVE TRAY

BUBBLE - CAP TRAY

USUALLY2rsquondash0rdquo

18rdquo MINIMUM

Vessel Internals 371

bull Deflection d

d frac14 a p b4

E n t3

bull Efficiency of holes for perforated plate n

n frac14 1 25 p d2

e C

DIMENSIONAL DATA

a frac14b frac14t frac14a=b frac14b frac14a frac14p frac14d frac14e frac14C frac14E frac14

Tray DesignCase 2 Standard tray plates

LOADS

A DL frac14 Dead load weight of trays and beams

B LL frac14 Live load dynamic load DP

C LL frac14 Liquid load weight of liquid supported

bull Total area AT

AT frac14 p D2=4 frac14 7854 D2

bull Total load PT

PT frac14 DLthorn LLthorn LL

bull Uniform load p

p frac14 PT=AT

LONG EDGE

SHORTEDGEBEAMS (TYP)

c = PITCH60deg

a

b

e

d

Table 5-20Coefficients

ab b a g

10 2874 044 420

12 3762 0616 455

14 4530 0770 478

16 5172 0906 491

18 5688 1017 499

20 6102 1110 503

30 7134 1335 505

40 7410 1400 502

50 7476 1417 501

N 7500 1421 500

372 Pressure Vessel Design Manual

PROPERTIES OF SECTIONS

C frac14 SAY=SA

I frac14 SAY2 thorn SI C SAY

Z frac14 I=C

CALCULATIONS

bull Determine panel area AP

AP frac14 Ln dnbull Load on panel FP

FP frac14 AP p

Uniform Load

bull Uniform load on beam w

w frac14 FP=Ln

bull Moment M

M frac14 w L2

n

8

bull Bending stress fb

fb frac14 M=Z

bull Deflection d

d frac14 5 w L4

n

384 E I

Concentrated Load

bull Moment M

M frac14 ethP LnTHORN=4bull Bending stress fb

fb frac14 M=Z

bull Deflection d

d frac14 P L3

n

48 E I

TYPE 1

1

2

XX

h

dn

t

PART A Y AY AY2 I12sum

C frac14 SAY=SA

I frac14 SAY2 thorn SI C SAY

Z frac14 I=C

TYPE 2

1

32

XX

h

dn

do

t

PART A Y AY AY2 I123sum

L1

DC

DIMENSIONS OF TRAY PANELS

d1 d2 d3 d4

Vessel Internals 373

NOTES1 Design Loads Trays pans drawoff boxes or

similar intemals shall be designed using a corrodedthickness to support their own weight plus thefollowing live loadsa Fractionation trays Design live load shall be the

greater of 20 PSF (98 KgSq meter) or the weightof water 2 (50 mm) over the highest weirsetting

b Areas under downcomers Design live load shallbe the greater of 64 PSF (314 Kg Sq meter) ora head of water one half the height of thedowncomer

c Pans (accumulator and drawoff pans) Designlive load shall be the greater of 1 PSI (700 Kg Sqmeter) or the weight of water at the maximumoperating level of the pan

d Baffles With no operating liquid level shall usea design live load of 1 PSI (700 KgSq meter) onthe projected horizontal area or actual impulseforce whichever is greater

2 Maintenance Loads Tray support members (allbeams support clips etc) shall be designed fora concentrated load of 300 Lbs (135 Kg) at any pointon the installed assembly The design shall be basedon the corroded thicknesses and an allowable stressof 9 Fy For maintenance loads stresses in the trayplates need not be considered

3 Uplift resistance Typical design of uplift for traysand packing is 25 PSI (17 Millibar) For serviceswhere excessive uplift can occur a higher upliftresistance may be used Examples of higher upliftfactors are as follows

a Crude and FCC side strippers 1 PSI (70 millibar)b Vacuum tower stripping trays overflash

collector wash trays or beds 2 PSI (140Millibar)

c Collectiors and packed beds above the washsection of a vacuum Tower 1 PSI (70 Millibar)

4 Failure sequence Tray assemblies wheneverpossible shall be designed so that failure will occurin the following ordera Tray manwaysb Tray deck active areasc Minor beams and downcomersd Major beams (defined as beams 10ft (3 Meters)

or longer or beams which extend across a vesselwithout interruption regardless of length)

5 Allowable stresses Allowable unit stress shall bebased on yield strength Fy at design temperaturewith AISC factors for tension bearing shear etc

6 Allowable Deflection The calculated combineddeflection of trays and support beams due to oper-ating loads shall not exceed the lesser of 1900 of thevessel diameter (in inches) or 316 (5 mm)

RECOMMENDED TRAY SPACING amp MANWAY SIZE

COLUMN DIA

(FT)

TRAY SPACING

(IN)

MANWAY

SPACING

MIN MANWAY

SIZE

25 to 16 24 Every 10 trays 18 in

16 to 24 30 Every 8 trays 20 in

24 to 32 36 Every 6 trays 24 in

32 and larger 42 Every 4 trays 30 in

374 Pressure Vessel Design Manual

Procedure 5-10 Flow Over Weirs

Notation

b frac14 width ftH frac14 static head of liquid ftQ frac14 discharge rate cu ftsecV frac14 velocity of approach ftsecH0 frac14 head correction per Table 5-22

Calculations

Discharge Q

bull For a full-length weir (Case 1)

Q frac14 333beth15 HTHORNbull For a contracted weir (Case 2)

Q frac14 333beth15 HTHORNbull For a V-notch weir (Case 3)

Q frac14 633 H

bull For a Cippoletti weir (Case 4)

Q frac14 3367beth15 HTHORN

Notes

1 Assumes troughs are level

Case 1 Full-Width Weir

V frac14 1ndash2 ftsec at 4 H upstream

Case 2 Contracted Weir

V frac14 1ndash2 ftsec at 3 H upstream

Case 3 V-Notch Weir

V frac14 5 ftsec at 5 H upstream

Case 4 Cippoletti Weir

V frac14 1ndash2 ftsec at 4 H upstream

Table 5-21Head correction for velocity of approach

V 04 06 08 10 12 14 16 18 20

Hrsquo 0002 0005 001 0015 0023 003 004 005 0062

V 22 24 26 28 30 32 34 36 38

Hrsquo 0075 0089 0105 0122 014 015 0179 0201 0213

Vessel Internals 375

Procedure 5-11 Design of Demisters

Demister pads or mist eliminators are important inter-nals in process vessels Anytime there is a continuous twophase flow vapor and liquid there is the possibility forliquid entrainment If it is desirable to separate the liquidand vapor or prevent liquid carryover in the vapor streamthe velocity must be kept sufficiently low to allow the liquiddroplets to fall out of the vapor stream Demister pads areeffective entrainment separators which allow operation atvapor velocities that would otherwise be excessive

ldquoVapor disengagementrdquo can be accomplished withouta demister but the vessel must be made much larger toaccomplish the same degree of separation This is knownas gravity separation

Demister pads are used in a wide variety of processvessels Good performance can be achieved at velocitiesof 30 to 110 of optimum

Demister pads can be used in vertical or horizontalvessels The mesh pad orientation can be either vertical orhorizontal in a vertical or horizontal vessel

A wire mesh demister consists of a knitted wire matmounted on a light weight support grid The mesh is madeby weaving small diameter metal wire into a mesh Padsmay be made out of metal or plastics Metal type includecarbon steel stainless steel monel and others Plasticmaterials include PTFE HDPE and PP

Pressure drop is usually extremely low in the range of1 inch of water column maximum The pressure drop isnormally so low that it is ignored in design

Vapor disengagement is dependent on the velocity ofthe stream The most common equation for determining theallowable vapor velocity for two phase flows is as follows

Va frac14 K frac12ethrL rVTHORN=rV1=2

Where

Va frac14 Allowable vapor velocity FtSecK frac14 Constant or coefficientrL frac14 Density of liquid PCFrV frac14 Density of vapor PCF

Notes

1 The mesh pad shall be in one piece or sectional asrequired for insertion through the vessel manwayEach pad section shall be removable through thevessel manhole

2 Layers shall not be more than 6 inches thick3 Where more than one layer is required all joints

shall be staggered

4 One piece circular pads may be spiral in form5 Each section of mesh shall include a grid on one or

both sides The grid wire andor fastening deviceshall be the same material as the mesh pad Top andbottom grids shall be constructed of frac14 inch diam-eter rods welded to ⅛ inch by 1 inch bars Themaximum gap between mesh pad and grids shall befrac12 inch for diameters less than 84 inches and 1 inchfor larger diameters

6 Estimate grid weights as 3 PSF7 Tie down wires shall be 1=16 inch diameter wire thru

frac14 inch diameter holes on 4 inch centers Tie wiresshould not be pushed through the pad as this couldcause leak paths

8 Pressure drop across mist eliminator shall beassumed as 02 PSI for support design

9 Unless otherwise specified support rings shall be2 inches wide for pads 84 inches in diameter andless and 3 inches wide for larger diameters

10 The mist eliminator shall be a tight fit against theshell or enclosure as well as between sections Meshpads shall be⅜ inches oversize all around for a forcefit against the enclosure No gaps are allowed

11 Vessel fabricator shall provide the mesh and gridsas well as any stiffeners required

12 The Mist eliminator shall be specified as either topor bottom removable

13 ldquoKrdquo is a constant or coefficient that is a functionof the efficiency of the separation K-values rangefrom 04 to 43 but are generally in the 15 to 35range The K-value is affected by pressure type ofpad size of wire type of vessel and disengagingheight For pressure applications the K-valueshould be decreased by 01 for every 100 PSI ofpressure after 100 PSI

14 Wire diameter for the mesh pad itself vary from0003 to 0016 inches

15 The free volume of demisters range from 92 to994

16 The density of the pads ranges from 3 to 33 PCF17 The NSA (nominal surface area) is the surface area

to volume ratio Ft2 Ft3 and is an important indi-cator of performance Ratios range from 50 to 600

18 To obtain higher separation efficiencies the wirediameter is decreased and the density and thicknessare increased

19 Typical width of sections for multi-section pads is12 inches (300 mm) but may vary by manufacturer

376 Pressure Vessel Design Manual

A Horizontal element B Vertical elements

Vertical vessels

Manway

Plate-Pakunit

Meshpad

Drain tubewith seal trap

END VIEW

END VIEW

SIDE VIEW

SIDE VIEW

C Vertical element

Horizontal vessels

D Horizontal element

Figure 5-15 Typical demister configurations in vessels

Vessel Internals 377

d

E Axial entrance

H gt (23) D ndash d

H gt D2 + d(minimum 24rdquo)

H gt D2 ndash d2

H gt D2 + d

H gt D2 ndash d2

h gt d

D

D Side entrance

d

D

B Axial exit

d

D

Φ lt 45ordm

Φ lt 45ordm

C Reverse axial exit

d

A Side exit

D

Figure 5-16 Guidelines for maintaining even flow distribution in vessels with axial flow

378 Pressure Vessel Design Manual

wire mesh

Top grid

Bottom grid

Vertical 14rdquo rodsspaced 12rdquo to 18rdquocenter to center

12rdquo to 18rdquosegmentwidth

18rdquo x 1rdquo flat bars14rdquo rodsspaced 6rdquocenterto center

Manway

Support ring

Support beam

Tie wires

Figure 5-17 Typical mesh pad construction and installation

Vessel Internals 379

Table 5-22Properties of demister pads

Type NSA (1) Ft2 Ft3 Density Pcf Wire Dia in Free Area York Style No Remarks

A 48 5 0011 99 931 High Throughput

B 65 7 0011 986 531 Economy Performance

C 85 9 0011 982 431 Standard - Good All

Around

D 110 108 0011 977 421 Heavy Duty

E 140 8 0006 984 326 Super High Efficiency -

Fine Mist

F 163 0006 94 371 Liquid - Liquid Coalescer

G 450 20 00045 959

H 600 27 00045 945

Notes

1 NSA frac14 Nominal Surface Area

Table 5-23Values of K (Note 13)

Based on Pressure

Pressure (PSIa) Vacuum (In Hg)

Pressure (PSIa) K Vacuum (In Hg) K

15 035 30 035

50 034 20 032

100 032 10 028

200 031 5 023

300 03 1 017

500 028 lt1 017

1000 027

gt1000 027

Based on Disengaging Height

Disengaging Height in K Disengaging Height in K

3 012 9 032

4 015 10 035

5 019 11 038

6 022 12 04

7 025 13 042

8 029 14 043

Based on Application

Vertical Vessels Horizontal Vessels

Type K Type K

General 035 General 035

Compressor Suction Drums 025 Steam Drums 025

Steam Drums 015

380 Pressure Vessel Design Manual

Procedure 5-12 Design of Baffles [10]

Baffles are frequently used in pressure vessels eithervertical or horizontal to divide the interior volume intodifferent compartments These compartments may beused to segregate liquids or provide overflow weirs forthe separation of liquids Baffles may be stiffened orunstiffened When welded across the entire cross sectionof the vessel they must be checked that they are notunduly restricting the diametral expansion of the vesselIf the unrestrained radial expansion of the vessel exceedsthat of the baffle by more than 1=16 in (⅛ in on thediameter) then a ldquoflexiblerdquo type of connection betweenthe vessel shell and the baffle should be utilized Variousflexible attachment designs are shown within theprocedure

Baffles should always be designed in the corrodedcondition It is typical for welded baffles to be designedwith a full corrosion allowance on both sides If the baffleis bolted in then one-half the full corrosion allowancemay be applied to each side the logic being that a boltedbaffle is removable and therefore replaceable

The majority of baffles are flat and as a result are veryinefficient from a strength standpoint Deflection is thegoverning case for flat plates loaded on one side Thepreference is to have unstiffened baffles and they shouldalways be the first choice This will be acceptable forsmall baffles However for larger baffles as the bafflethickness becomes excessive stiffeners offer a moreeconomical design Therefore stiffeners are frequentlyused to stiffen the baffle to prevent the thickness of thebaffle from becoming excessive The number size andspacing of stiffeners are dependent on the baffle thicknessselected There is a continual trade-off between bafflethickness and stiffener parameters

The design of a baffle with stiffeners is an iterativeprocess The procedure for the design of the stiffeners isfirst to divide the baffle into ldquopanelrdquo sections that are rigidenough to withstand the pressure applied on one sideEach individual panel is checked as a flat plate of thedimensions of the panel The stiffeners are assumed to bestrong enough to provide the necessary edge support forthe panel

The stiffeners themselves are designed next A sectionof the baffle is assumed as acting with the stiffener and ascontributing to the overall stiffness This combinedsection is known as the composite stiffener Thecomposite section is checked for stress and deflectionBoth vertical and horizontal stiffeners can be added asrequired

If required an alternate design is assumed based ona thicker or thinner baffle and checked until a satisfactorydesign is found There is no ldquorightrdquo answer however itshould be noted that the thinner the baffle the greater thenumber of stiffeners The lightest overall weight isprobably the ldquobestrdquo design but may not be the leastexpensive due to the welding costs in attaching thestiffeners

One alternative to a flat baffle with stiffeners is to go toa curved baffle A curved baffle works best as a verticalbaffle in a vertical vessel The curved baffle takes pressurefrom either side wall If the pressure is on the concave sidethe baffle is in tension If the pressure is on the convexside the baffle is in compression

There are various tables given in this procedure for flatplate coefficients Flat plate coefficients are utilized todetermine the baffle thickness or a panel thickness Eachtable is specific for a given condition and loading

Vessel Internals 381

Notation

Ap frac14 area of baffle working with stiffener in2

As frac14 area of stiffener in2

Cp frac14 distance from centroid of composite section topanel in

Cs frac14 distance from centroid of composite section tostiffener in

E frac14 modulus of elasticity psiFb frac14 allowable bending stress psiI frac14 moment of inertia composite in4

Is frac14 moment of inertia stiffener in4

l frac14 length of baffle that works with the stiffener inM frac14 moment in-lbn frac14 number of welds attaching stiffenerP frac14 vessel internal pressure psigp frac14 maximum uniform pressure psipn frac14 uniform pressure at any elevation an psiRm frac14 vessel mean radius inSg frac14 specific gravity of contentst frac14 thickness shell intb frac14 thickness baffle ints frac14 thickness stiffener inV frac14 shear load lbw frac14 required fillet weld size ina frac14 thermal coefficient of expansion ininF

bg frac14 flat plate coefficientsDT frac14 differential temperature (design temperature

minus 70F) Fsb frac14 bending stress in baffle psiss frac14 bending stress in stiffener psi

6n frac14 radial expansion ind frac14 deflection inda frac14 maximum allowable deflection in

Baffle Dimensions

382 Pressure Vessel Design Manual

Table 5-24Flat plate coefficients

Vessel Internals 383

Unstiffened Baffle Check

bull Find load p

p frac14 624aSg144

bull Find baffle thickness tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

s

bull Find baffle deflection d

d frac14 pg1b4

Et3b

Limit deflection to the smaller of tb2 or b360 Ifdeflection is excessive then

a Increase the baffle thicknessb Add stiffenersc Go to curved baffle design

If stiffeners are added the first step is to find themaximum ldquoardquo and ldquobrdquo dimensions that will meet theallowable deflection for a given panel size This willestablish the stiffener spacing for both horizontal andvertical stiffeners The ultimate design is a balancebetween baffle thickness stiffener spacing and stiffenersize

Thermal Check of Baffle

bull Vessel radial expansion due to pressure

D1 frac14 085PRm

tE

bull Vessel radial expansion due to temperature

D2 frac14 Rma DT

bull Thermal expansion of baffle

D3 frac14 05ba DT

bull Differential expansion

D4 frac14 D1 thorn D2 D3

Stiffener Design

Divide baffle into panels to limit deflection to the lesserof tb2 or b360 Deflection is calculated based on theappropriate Cases 1 through 3

bull Check baffle for panel size a0 b0bull Check stiffener for length a or b

Recommendations for attaching stiffeners

Benefits Provides added stiffness and no corrosiontrap

Figure 5-18 Example of stiffener layout

384 Pressure Vessel Design Manual

As frac14 tsh

Ap frac14 tbl

IS frac14 tsh3

12

Cp frac14 AsyAs thorn Ap

thorn tb2

Cs frac14 ethhthorn tbTHORN Cp

I frac14 IS thorn Apt2b12

thorn AsApy2

As thorn Ap

lsquo frac14 lesser of 32tb or stiffener spacing

Stresses in BaffleStiffener

sp frac14 MCp

I

ss frac14 MCs

I

Size Welds Attaching Stiffeners

For E70XX Welds

w frac14 Vdy11 200In

Table 5-25Intermittent Welds

Percent of

Continuous Weld

Length of Intermittent Welds

and Distance Between Centers

75 3e4

66 4e6

60 3e5

57 4e7

50 2e4 3e6 4e8

44 4e9

43 3e7

40 2e5 4e10

37 3e8

33 2e6 3e9 4e12

Reprinted by permission of the James F Lincoln Arc Welding

Foundation

Vessel Internals 385

For E60XX Welds

w frac14 Vdy9600In

Sample Problem

bull Given Horizontal vessel with a vertical baffle

P frac14 250 psig

DT frac14 500F

Material frac14 SA-516-70

Ca frac14 0125 in

JE frac14 10

E frac14 273 106 psi

a frac14 7124 10-6 in=in=FFy frac14 308 ksi

D frac14 240 in

Fb frac14 066 Fy frac14 2033 ksi

Rm frac14 120938

ts frac14 175 in

Sg frac14 08

a frac14 15 ft

DT frac14 500 70 frac14 430F

bull Find baffle thickness without stiffener

p frac14 624aSg144

frac14 52 psi

a

bratio frac14 15=20 frac14 075

from Table 5-25 Case 1

b1 frac14 016 g1 frac14 0033

bull Thickness of baffle tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

sfrac14

ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi016eth52THORN2402

20 330

s

tb frac14 153thorn 025 frac14 178

No good Use stiffeners

bull Assume a suitable baffle thickness and determinemaximum panel size

tb frac14 075 in corroded

maximum panel size frac14 4ft 4ft

bull Maximum pressure p

p frac14 13eth624THORN08144

frac14 45 psi

a

bfrac14 4

4frac14 1

See Table 5-25 Case 3

b3 frac14 0287 g3 frac14 00443

sb frac14 b3pb2n

t2

frac14 0287eth45THORN4820752

frac14 5290 psi lt 20 333 psiFigure 5-19 Sample problem

386 Pressure Vessel Design Manual

d frac14 g3

pE

b4nt3

frac14 00443

45

273 106

484

0753

frac14 0092 in lt 0375 in

Balance OK by inspection

bull Assume a layout where the maximum stiffenerspacing is 4 ft

(4) horizontal stiffeners(4) vertical stiffeners(18) panels

bull Check horizontal stiffeners

Dimensions

a1 frac14 3 ft b1 frac14 4 ft

a2 frac14 4 ft b2 frac14 4 ft

a3 frac14 4 ft b3 frac14 12 ft

a4 frac14 4 ft b4 frac14 196 ft

a5 frac14 13 ft

a6 frac14 148ft

bull Assume stiffener size 1 in 4 in

y frac14 2375 in

As frac14 tsh frac14 1eth4THORN frac14 4 in2

l frac14 32tb frac14 32eth075THORN frac14 24 in lt 48 in

AP frac14 tbl frac14 07524 frac14 18 in2

Is frac14 bh3

12frac14 1

43

12frac14 533 in4

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 533thorn 0633thorn 1846 frac14 2442 in4

Cp frac14 AsyAs thorn Ap

thorn tb2

frac14 4eth2375THORN22

thorn 0752

frac14 0807 in

Cs frac14 hthorn tb

Cp

frac14 4thorn 075 0807 frac14 3943

Check deflections

Deflections exceed allowable No good

bull Assume a larger stiffener size WT9 593

tf frac14 106 025 frac14 081

tw frac14 0625 025 frac14 0375

bull Check corroded thickness to find properties ofcorroded section This section would be equivalent toa WT9 30 Properties are

As frac14 882 in2

Is frac14 647 in4

Cs frac14 216 in

H frac14 9 in

Cp frac14 hthorn tb Cs

frac14 9thorn 075 216 frac14 759 in

Figure 5-20 Battle layout for sample problem

Item bn pn d

1 2352 104 149

2 2352 243 349

3 144 381 0767

Vessel Internals 387

y frac14 Cp tb2

frac14 7215 in

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 647thorn 0844thorn 30814 frac14 3737 in4

bull Check stresses and deflections See results in Table5-27

bull Stresses and deflections are acceptablebull Check welds

d frac14 ts thorn 2tw frac14 0375thorn 2eth0323THORN frac14 102

y frac14 7215 in

I frac14 3737 in4

n frac14 2

w frac14 Vdy11 200In

frac14 6681eth102THORN721511 200eth3737THORN2

frac14 0005thorn 0125 frac14 013 in

bull Check thermal expansion of baffle

D1 frac14 085PRm

tEfrac14 085eth250THORN120938

175eth273 106THORNfrac14 000054 in

D2 frac14 Rma DT frac14 1209387124 106430

frac14 0370 in

D3 frac14 05ba DT frac14 05240

7124 106430

frac14 0367 in

D4 frac14 D1 thorn D2 D3 frac14 000054thorn 0370 0367

frac14 00035 lt 006 in

Table 5-26Summary of Results for Stress and Deflection in Composite Stiffeners for Sample Problem

Item Orientation an bn pn M d V sp ss

1 Horiz 2352 d 104 172595 009 2690 3504 997

2 Horiz 2352 d 243 403275 021 6287 8186 2330

3 Horiz 144 d 381 237012 0045 6035 4811 1370

4 Vert d 156 450 154674 0037 5648 3141 894

5 Vert d 1776 513 228539 0072 6681 6681 1320

Figure 5-21 Details of weld attaching stiffener

388 Pressure Vessel Design Manual

Vessel Internals 389

Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 13: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

TYPICAL TRAY ASSEMBLY

Hex Head Bolt

Manway Lock Clamps

Manway Lock StudsManway Clamps

Seal Plate

Tray Floor (Active)

Tray Floor (Active)Outlet Weir

Downcomer Truss

Standard WasherHex NutFrictional Washer

Downcomer Panel

Downcomer Bolting Bar

Bottom Tray ClampHex Head Bolt DowncomerTruss

Hex NutFrictional Washer

DOWNCOMER BOLTING BAR

Hex Nut

Hex Nut

Hex Nut

Hex Head Bolt

Hex Head Bolt

Frictional Washer

Bottom Tray Clamp

Tray Floor (Inlet Panel)

TRAY FLOOR

(INLET PANEL)

TRAY SUPPORT RING

Tray Support Ring

Manway (Active)

ONE PASS TRAY SHOWN

370 Pressure Vessel Design Manual

Design of Tray Plates

Stress and DeflectionCase 1 Perforated Plate

Reference Roark 5th Edition Table 26 Case 1A

bull Rectangular platebull Uniformly loadedbull All edges simply supported

DATA

a b g frac14 Coefficients from Table 5-21E frac14 Modulus of elasticity at design temperature PSI

t frac14 Corroded thickness of tray inCa frac14 Corrosion allowance inn frac14 Hole efficiencyd frac14 Deflection at center inp frac14 Uniform load PSIs frac14 Bending stress PSI

FORMULAS

bull Stress s

s frac14 b p b4

n t2

BUBBLE-CAPTRAY

VALVELIQUID FLOW

WEIRDOWNCOMER

VAPOR

VAPORVAPOR

VAPOR

VAPOR

TYPES OF TRAYS

CHIMNEY CHIMNEY HAT

SUMPTRUSS

CHIMNEYACCUMULATOR TRAYS

LIQUID

LIQUID

LIQUID

SIEVE TRAY

VALVE TRAY

BUBBLE - CAP TRAY

USUALLY2rsquondash0rdquo

18rdquo MINIMUM

Vessel Internals 371

bull Deflection d

d frac14 a p b4

E n t3

bull Efficiency of holes for perforated plate n

n frac14 1 25 p d2

e C

DIMENSIONAL DATA

a frac14b frac14t frac14a=b frac14b frac14a frac14p frac14d frac14e frac14C frac14E frac14

Tray DesignCase 2 Standard tray plates

LOADS

A DL frac14 Dead load weight of trays and beams

B LL frac14 Live load dynamic load DP

C LL frac14 Liquid load weight of liquid supported

bull Total area AT

AT frac14 p D2=4 frac14 7854 D2

bull Total load PT

PT frac14 DLthorn LLthorn LL

bull Uniform load p

p frac14 PT=AT

LONG EDGE

SHORTEDGEBEAMS (TYP)

c = PITCH60deg

a

b

e

d

Table 5-20Coefficients

ab b a g

10 2874 044 420

12 3762 0616 455

14 4530 0770 478

16 5172 0906 491

18 5688 1017 499

20 6102 1110 503

30 7134 1335 505

40 7410 1400 502

50 7476 1417 501

N 7500 1421 500

372 Pressure Vessel Design Manual

PROPERTIES OF SECTIONS

C frac14 SAY=SA

I frac14 SAY2 thorn SI C SAY

Z frac14 I=C

CALCULATIONS

bull Determine panel area AP

AP frac14 Ln dnbull Load on panel FP

FP frac14 AP p

Uniform Load

bull Uniform load on beam w

w frac14 FP=Ln

bull Moment M

M frac14 w L2

n

8

bull Bending stress fb

fb frac14 M=Z

bull Deflection d

d frac14 5 w L4

n

384 E I

Concentrated Load

bull Moment M

M frac14 ethP LnTHORN=4bull Bending stress fb

fb frac14 M=Z

bull Deflection d

d frac14 P L3

n

48 E I

TYPE 1

1

2

XX

h

dn

t

PART A Y AY AY2 I12sum

C frac14 SAY=SA

I frac14 SAY2 thorn SI C SAY

Z frac14 I=C

TYPE 2

1

32

XX

h

dn

do

t

PART A Y AY AY2 I123sum

L1

DC

DIMENSIONS OF TRAY PANELS

d1 d2 d3 d4

Vessel Internals 373

NOTES1 Design Loads Trays pans drawoff boxes or

similar intemals shall be designed using a corrodedthickness to support their own weight plus thefollowing live loadsa Fractionation trays Design live load shall be the

greater of 20 PSF (98 KgSq meter) or the weightof water 2 (50 mm) over the highest weirsetting

b Areas under downcomers Design live load shallbe the greater of 64 PSF (314 Kg Sq meter) ora head of water one half the height of thedowncomer

c Pans (accumulator and drawoff pans) Designlive load shall be the greater of 1 PSI (700 Kg Sqmeter) or the weight of water at the maximumoperating level of the pan

d Baffles With no operating liquid level shall usea design live load of 1 PSI (700 KgSq meter) onthe projected horizontal area or actual impulseforce whichever is greater

2 Maintenance Loads Tray support members (allbeams support clips etc) shall be designed fora concentrated load of 300 Lbs (135 Kg) at any pointon the installed assembly The design shall be basedon the corroded thicknesses and an allowable stressof 9 Fy For maintenance loads stresses in the trayplates need not be considered

3 Uplift resistance Typical design of uplift for traysand packing is 25 PSI (17 Millibar) For serviceswhere excessive uplift can occur a higher upliftresistance may be used Examples of higher upliftfactors are as follows

a Crude and FCC side strippers 1 PSI (70 millibar)b Vacuum tower stripping trays overflash

collector wash trays or beds 2 PSI (140Millibar)

c Collectiors and packed beds above the washsection of a vacuum Tower 1 PSI (70 Millibar)

4 Failure sequence Tray assemblies wheneverpossible shall be designed so that failure will occurin the following ordera Tray manwaysb Tray deck active areasc Minor beams and downcomersd Major beams (defined as beams 10ft (3 Meters)

or longer or beams which extend across a vesselwithout interruption regardless of length)

5 Allowable stresses Allowable unit stress shall bebased on yield strength Fy at design temperaturewith AISC factors for tension bearing shear etc

6 Allowable Deflection The calculated combineddeflection of trays and support beams due to oper-ating loads shall not exceed the lesser of 1900 of thevessel diameter (in inches) or 316 (5 mm)

RECOMMENDED TRAY SPACING amp MANWAY SIZE

COLUMN DIA

(FT)

TRAY SPACING

(IN)

MANWAY

SPACING

MIN MANWAY

SIZE

25 to 16 24 Every 10 trays 18 in

16 to 24 30 Every 8 trays 20 in

24 to 32 36 Every 6 trays 24 in

32 and larger 42 Every 4 trays 30 in

374 Pressure Vessel Design Manual

Procedure 5-10 Flow Over Weirs

Notation

b frac14 width ftH frac14 static head of liquid ftQ frac14 discharge rate cu ftsecV frac14 velocity of approach ftsecH0 frac14 head correction per Table 5-22

Calculations

Discharge Q

bull For a full-length weir (Case 1)

Q frac14 333beth15 HTHORNbull For a contracted weir (Case 2)

Q frac14 333beth15 HTHORNbull For a V-notch weir (Case 3)

Q frac14 633 H

bull For a Cippoletti weir (Case 4)

Q frac14 3367beth15 HTHORN

Notes

1 Assumes troughs are level

Case 1 Full-Width Weir

V frac14 1ndash2 ftsec at 4 H upstream

Case 2 Contracted Weir

V frac14 1ndash2 ftsec at 3 H upstream

Case 3 V-Notch Weir

V frac14 5 ftsec at 5 H upstream

Case 4 Cippoletti Weir

V frac14 1ndash2 ftsec at 4 H upstream

Table 5-21Head correction for velocity of approach

V 04 06 08 10 12 14 16 18 20

Hrsquo 0002 0005 001 0015 0023 003 004 005 0062

V 22 24 26 28 30 32 34 36 38

Hrsquo 0075 0089 0105 0122 014 015 0179 0201 0213

Vessel Internals 375

Procedure 5-11 Design of Demisters

Demister pads or mist eliminators are important inter-nals in process vessels Anytime there is a continuous twophase flow vapor and liquid there is the possibility forliquid entrainment If it is desirable to separate the liquidand vapor or prevent liquid carryover in the vapor streamthe velocity must be kept sufficiently low to allow the liquiddroplets to fall out of the vapor stream Demister pads areeffective entrainment separators which allow operation atvapor velocities that would otherwise be excessive

ldquoVapor disengagementrdquo can be accomplished withouta demister but the vessel must be made much larger toaccomplish the same degree of separation This is knownas gravity separation

Demister pads are used in a wide variety of processvessels Good performance can be achieved at velocitiesof 30 to 110 of optimum

Demister pads can be used in vertical or horizontalvessels The mesh pad orientation can be either vertical orhorizontal in a vertical or horizontal vessel

A wire mesh demister consists of a knitted wire matmounted on a light weight support grid The mesh is madeby weaving small diameter metal wire into a mesh Padsmay be made out of metal or plastics Metal type includecarbon steel stainless steel monel and others Plasticmaterials include PTFE HDPE and PP

Pressure drop is usually extremely low in the range of1 inch of water column maximum The pressure drop isnormally so low that it is ignored in design

Vapor disengagement is dependent on the velocity ofthe stream The most common equation for determining theallowable vapor velocity for two phase flows is as follows

Va frac14 K frac12ethrL rVTHORN=rV1=2

Where

Va frac14 Allowable vapor velocity FtSecK frac14 Constant or coefficientrL frac14 Density of liquid PCFrV frac14 Density of vapor PCF

Notes

1 The mesh pad shall be in one piece or sectional asrequired for insertion through the vessel manwayEach pad section shall be removable through thevessel manhole

2 Layers shall not be more than 6 inches thick3 Where more than one layer is required all joints

shall be staggered

4 One piece circular pads may be spiral in form5 Each section of mesh shall include a grid on one or

both sides The grid wire andor fastening deviceshall be the same material as the mesh pad Top andbottom grids shall be constructed of frac14 inch diam-eter rods welded to ⅛ inch by 1 inch bars Themaximum gap between mesh pad and grids shall befrac12 inch for diameters less than 84 inches and 1 inchfor larger diameters

6 Estimate grid weights as 3 PSF7 Tie down wires shall be 1=16 inch diameter wire thru

frac14 inch diameter holes on 4 inch centers Tie wiresshould not be pushed through the pad as this couldcause leak paths

8 Pressure drop across mist eliminator shall beassumed as 02 PSI for support design

9 Unless otherwise specified support rings shall be2 inches wide for pads 84 inches in diameter andless and 3 inches wide for larger diameters

10 The mist eliminator shall be a tight fit against theshell or enclosure as well as between sections Meshpads shall be⅜ inches oversize all around for a forcefit against the enclosure No gaps are allowed

11 Vessel fabricator shall provide the mesh and gridsas well as any stiffeners required

12 The Mist eliminator shall be specified as either topor bottom removable

13 ldquoKrdquo is a constant or coefficient that is a functionof the efficiency of the separation K-values rangefrom 04 to 43 but are generally in the 15 to 35range The K-value is affected by pressure type ofpad size of wire type of vessel and disengagingheight For pressure applications the K-valueshould be decreased by 01 for every 100 PSI ofpressure after 100 PSI

14 Wire diameter for the mesh pad itself vary from0003 to 0016 inches

15 The free volume of demisters range from 92 to994

16 The density of the pads ranges from 3 to 33 PCF17 The NSA (nominal surface area) is the surface area

to volume ratio Ft2 Ft3 and is an important indi-cator of performance Ratios range from 50 to 600

18 To obtain higher separation efficiencies the wirediameter is decreased and the density and thicknessare increased

19 Typical width of sections for multi-section pads is12 inches (300 mm) but may vary by manufacturer

376 Pressure Vessel Design Manual

A Horizontal element B Vertical elements

Vertical vessels

Manway

Plate-Pakunit

Meshpad

Drain tubewith seal trap

END VIEW

END VIEW

SIDE VIEW

SIDE VIEW

C Vertical element

Horizontal vessels

D Horizontal element

Figure 5-15 Typical demister configurations in vessels

Vessel Internals 377

d

E Axial entrance

H gt (23) D ndash d

H gt D2 + d(minimum 24rdquo)

H gt D2 ndash d2

H gt D2 + d

H gt D2 ndash d2

h gt d

D

D Side entrance

d

D

B Axial exit

d

D

Φ lt 45ordm

Φ lt 45ordm

C Reverse axial exit

d

A Side exit

D

Figure 5-16 Guidelines for maintaining even flow distribution in vessels with axial flow

378 Pressure Vessel Design Manual

wire mesh

Top grid

Bottom grid

Vertical 14rdquo rodsspaced 12rdquo to 18rdquocenter to center

12rdquo to 18rdquosegmentwidth

18rdquo x 1rdquo flat bars14rdquo rodsspaced 6rdquocenterto center

Manway

Support ring

Support beam

Tie wires

Figure 5-17 Typical mesh pad construction and installation

Vessel Internals 379

Table 5-22Properties of demister pads

Type NSA (1) Ft2 Ft3 Density Pcf Wire Dia in Free Area York Style No Remarks

A 48 5 0011 99 931 High Throughput

B 65 7 0011 986 531 Economy Performance

C 85 9 0011 982 431 Standard - Good All

Around

D 110 108 0011 977 421 Heavy Duty

E 140 8 0006 984 326 Super High Efficiency -

Fine Mist

F 163 0006 94 371 Liquid - Liquid Coalescer

G 450 20 00045 959

H 600 27 00045 945

Notes

1 NSA frac14 Nominal Surface Area

Table 5-23Values of K (Note 13)

Based on Pressure

Pressure (PSIa) Vacuum (In Hg)

Pressure (PSIa) K Vacuum (In Hg) K

15 035 30 035

50 034 20 032

100 032 10 028

200 031 5 023

300 03 1 017

500 028 lt1 017

1000 027

gt1000 027

Based on Disengaging Height

Disengaging Height in K Disengaging Height in K

3 012 9 032

4 015 10 035

5 019 11 038

6 022 12 04

7 025 13 042

8 029 14 043

Based on Application

Vertical Vessels Horizontal Vessels

Type K Type K

General 035 General 035

Compressor Suction Drums 025 Steam Drums 025

Steam Drums 015

380 Pressure Vessel Design Manual

Procedure 5-12 Design of Baffles [10]

Baffles are frequently used in pressure vessels eithervertical or horizontal to divide the interior volume intodifferent compartments These compartments may beused to segregate liquids or provide overflow weirs forthe separation of liquids Baffles may be stiffened orunstiffened When welded across the entire cross sectionof the vessel they must be checked that they are notunduly restricting the diametral expansion of the vesselIf the unrestrained radial expansion of the vessel exceedsthat of the baffle by more than 1=16 in (⅛ in on thediameter) then a ldquoflexiblerdquo type of connection betweenthe vessel shell and the baffle should be utilized Variousflexible attachment designs are shown within theprocedure

Baffles should always be designed in the corrodedcondition It is typical for welded baffles to be designedwith a full corrosion allowance on both sides If the baffleis bolted in then one-half the full corrosion allowancemay be applied to each side the logic being that a boltedbaffle is removable and therefore replaceable

The majority of baffles are flat and as a result are veryinefficient from a strength standpoint Deflection is thegoverning case for flat plates loaded on one side Thepreference is to have unstiffened baffles and they shouldalways be the first choice This will be acceptable forsmall baffles However for larger baffles as the bafflethickness becomes excessive stiffeners offer a moreeconomical design Therefore stiffeners are frequentlyused to stiffen the baffle to prevent the thickness of thebaffle from becoming excessive The number size andspacing of stiffeners are dependent on the baffle thicknessselected There is a continual trade-off between bafflethickness and stiffener parameters

The design of a baffle with stiffeners is an iterativeprocess The procedure for the design of the stiffeners isfirst to divide the baffle into ldquopanelrdquo sections that are rigidenough to withstand the pressure applied on one sideEach individual panel is checked as a flat plate of thedimensions of the panel The stiffeners are assumed to bestrong enough to provide the necessary edge support forthe panel

The stiffeners themselves are designed next A sectionof the baffle is assumed as acting with the stiffener and ascontributing to the overall stiffness This combinedsection is known as the composite stiffener Thecomposite section is checked for stress and deflectionBoth vertical and horizontal stiffeners can be added asrequired

If required an alternate design is assumed based ona thicker or thinner baffle and checked until a satisfactorydesign is found There is no ldquorightrdquo answer however itshould be noted that the thinner the baffle the greater thenumber of stiffeners The lightest overall weight isprobably the ldquobestrdquo design but may not be the leastexpensive due to the welding costs in attaching thestiffeners

One alternative to a flat baffle with stiffeners is to go toa curved baffle A curved baffle works best as a verticalbaffle in a vertical vessel The curved baffle takes pressurefrom either side wall If the pressure is on the concave sidethe baffle is in tension If the pressure is on the convexside the baffle is in compression

There are various tables given in this procedure for flatplate coefficients Flat plate coefficients are utilized todetermine the baffle thickness or a panel thickness Eachtable is specific for a given condition and loading

Vessel Internals 381

Notation

Ap frac14 area of baffle working with stiffener in2

As frac14 area of stiffener in2

Cp frac14 distance from centroid of composite section topanel in

Cs frac14 distance from centroid of composite section tostiffener in

E frac14 modulus of elasticity psiFb frac14 allowable bending stress psiI frac14 moment of inertia composite in4

Is frac14 moment of inertia stiffener in4

l frac14 length of baffle that works with the stiffener inM frac14 moment in-lbn frac14 number of welds attaching stiffenerP frac14 vessel internal pressure psigp frac14 maximum uniform pressure psipn frac14 uniform pressure at any elevation an psiRm frac14 vessel mean radius inSg frac14 specific gravity of contentst frac14 thickness shell intb frac14 thickness baffle ints frac14 thickness stiffener inV frac14 shear load lbw frac14 required fillet weld size ina frac14 thermal coefficient of expansion ininF

bg frac14 flat plate coefficientsDT frac14 differential temperature (design temperature

minus 70F) Fsb frac14 bending stress in baffle psiss frac14 bending stress in stiffener psi

6n frac14 radial expansion ind frac14 deflection inda frac14 maximum allowable deflection in

Baffle Dimensions

382 Pressure Vessel Design Manual

Table 5-24Flat plate coefficients

Vessel Internals 383

Unstiffened Baffle Check

bull Find load p

p frac14 624aSg144

bull Find baffle thickness tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

s

bull Find baffle deflection d

d frac14 pg1b4

Et3b

Limit deflection to the smaller of tb2 or b360 Ifdeflection is excessive then

a Increase the baffle thicknessb Add stiffenersc Go to curved baffle design

If stiffeners are added the first step is to find themaximum ldquoardquo and ldquobrdquo dimensions that will meet theallowable deflection for a given panel size This willestablish the stiffener spacing for both horizontal andvertical stiffeners The ultimate design is a balancebetween baffle thickness stiffener spacing and stiffenersize

Thermal Check of Baffle

bull Vessel radial expansion due to pressure

D1 frac14 085PRm

tE

bull Vessel radial expansion due to temperature

D2 frac14 Rma DT

bull Thermal expansion of baffle

D3 frac14 05ba DT

bull Differential expansion

D4 frac14 D1 thorn D2 D3

Stiffener Design

Divide baffle into panels to limit deflection to the lesserof tb2 or b360 Deflection is calculated based on theappropriate Cases 1 through 3

bull Check baffle for panel size a0 b0bull Check stiffener for length a or b

Recommendations for attaching stiffeners

Benefits Provides added stiffness and no corrosiontrap

Figure 5-18 Example of stiffener layout

384 Pressure Vessel Design Manual

As frac14 tsh

Ap frac14 tbl

IS frac14 tsh3

12

Cp frac14 AsyAs thorn Ap

thorn tb2

Cs frac14 ethhthorn tbTHORN Cp

I frac14 IS thorn Apt2b12

thorn AsApy2

As thorn Ap

lsquo frac14 lesser of 32tb or stiffener spacing

Stresses in BaffleStiffener

sp frac14 MCp

I

ss frac14 MCs

I

Size Welds Attaching Stiffeners

For E70XX Welds

w frac14 Vdy11 200In

Table 5-25Intermittent Welds

Percent of

Continuous Weld

Length of Intermittent Welds

and Distance Between Centers

75 3e4

66 4e6

60 3e5

57 4e7

50 2e4 3e6 4e8

44 4e9

43 3e7

40 2e5 4e10

37 3e8

33 2e6 3e9 4e12

Reprinted by permission of the James F Lincoln Arc Welding

Foundation

Vessel Internals 385

For E60XX Welds

w frac14 Vdy9600In

Sample Problem

bull Given Horizontal vessel with a vertical baffle

P frac14 250 psig

DT frac14 500F

Material frac14 SA-516-70

Ca frac14 0125 in

JE frac14 10

E frac14 273 106 psi

a frac14 7124 10-6 in=in=FFy frac14 308 ksi

D frac14 240 in

Fb frac14 066 Fy frac14 2033 ksi

Rm frac14 120938

ts frac14 175 in

Sg frac14 08

a frac14 15 ft

DT frac14 500 70 frac14 430F

bull Find baffle thickness without stiffener

p frac14 624aSg144

frac14 52 psi

a

bratio frac14 15=20 frac14 075

from Table 5-25 Case 1

b1 frac14 016 g1 frac14 0033

bull Thickness of baffle tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

sfrac14

ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi016eth52THORN2402

20 330

s

tb frac14 153thorn 025 frac14 178

No good Use stiffeners

bull Assume a suitable baffle thickness and determinemaximum panel size

tb frac14 075 in corroded

maximum panel size frac14 4ft 4ft

bull Maximum pressure p

p frac14 13eth624THORN08144

frac14 45 psi

a

bfrac14 4

4frac14 1

See Table 5-25 Case 3

b3 frac14 0287 g3 frac14 00443

sb frac14 b3pb2n

t2

frac14 0287eth45THORN4820752

frac14 5290 psi lt 20 333 psiFigure 5-19 Sample problem

386 Pressure Vessel Design Manual

d frac14 g3

pE

b4nt3

frac14 00443

45

273 106

484

0753

frac14 0092 in lt 0375 in

Balance OK by inspection

bull Assume a layout where the maximum stiffenerspacing is 4 ft

(4) horizontal stiffeners(4) vertical stiffeners(18) panels

bull Check horizontal stiffeners

Dimensions

a1 frac14 3 ft b1 frac14 4 ft

a2 frac14 4 ft b2 frac14 4 ft

a3 frac14 4 ft b3 frac14 12 ft

a4 frac14 4 ft b4 frac14 196 ft

a5 frac14 13 ft

a6 frac14 148ft

bull Assume stiffener size 1 in 4 in

y frac14 2375 in

As frac14 tsh frac14 1eth4THORN frac14 4 in2

l frac14 32tb frac14 32eth075THORN frac14 24 in lt 48 in

AP frac14 tbl frac14 07524 frac14 18 in2

Is frac14 bh3

12frac14 1

43

12frac14 533 in4

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 533thorn 0633thorn 1846 frac14 2442 in4

Cp frac14 AsyAs thorn Ap

thorn tb2

frac14 4eth2375THORN22

thorn 0752

frac14 0807 in

Cs frac14 hthorn tb

Cp

frac14 4thorn 075 0807 frac14 3943

Check deflections

Deflections exceed allowable No good

bull Assume a larger stiffener size WT9 593

tf frac14 106 025 frac14 081

tw frac14 0625 025 frac14 0375

bull Check corroded thickness to find properties ofcorroded section This section would be equivalent toa WT9 30 Properties are

As frac14 882 in2

Is frac14 647 in4

Cs frac14 216 in

H frac14 9 in

Cp frac14 hthorn tb Cs

frac14 9thorn 075 216 frac14 759 in

Figure 5-20 Battle layout for sample problem

Item bn pn d

1 2352 104 149

2 2352 243 349

3 144 381 0767

Vessel Internals 387

y frac14 Cp tb2

frac14 7215 in

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 647thorn 0844thorn 30814 frac14 3737 in4

bull Check stresses and deflections See results in Table5-27

bull Stresses and deflections are acceptablebull Check welds

d frac14 ts thorn 2tw frac14 0375thorn 2eth0323THORN frac14 102

y frac14 7215 in

I frac14 3737 in4

n frac14 2

w frac14 Vdy11 200In

frac14 6681eth102THORN721511 200eth3737THORN2

frac14 0005thorn 0125 frac14 013 in

bull Check thermal expansion of baffle

D1 frac14 085PRm

tEfrac14 085eth250THORN120938

175eth273 106THORNfrac14 000054 in

D2 frac14 Rma DT frac14 1209387124 106430

frac14 0370 in

D3 frac14 05ba DT frac14 05240

7124 106430

frac14 0367 in

D4 frac14 D1 thorn D2 D3 frac14 000054thorn 0370 0367

frac14 00035 lt 006 in

Table 5-26Summary of Results for Stress and Deflection in Composite Stiffeners for Sample Problem

Item Orientation an bn pn M d V sp ss

1 Horiz 2352 d 104 172595 009 2690 3504 997

2 Horiz 2352 d 243 403275 021 6287 8186 2330

3 Horiz 144 d 381 237012 0045 6035 4811 1370

4 Vert d 156 450 154674 0037 5648 3141 894

5 Vert d 1776 513 228539 0072 6681 6681 1320

Figure 5-21 Details of weld attaching stiffener

388 Pressure Vessel Design Manual

Vessel Internals 389

Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 14: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

Design of Tray Plates

Stress and DeflectionCase 1 Perforated Plate

Reference Roark 5th Edition Table 26 Case 1A

bull Rectangular platebull Uniformly loadedbull All edges simply supported

DATA

a b g frac14 Coefficients from Table 5-21E frac14 Modulus of elasticity at design temperature PSI

t frac14 Corroded thickness of tray inCa frac14 Corrosion allowance inn frac14 Hole efficiencyd frac14 Deflection at center inp frac14 Uniform load PSIs frac14 Bending stress PSI

FORMULAS

bull Stress s

s frac14 b p b4

n t2

BUBBLE-CAPTRAY

VALVELIQUID FLOW

WEIRDOWNCOMER

VAPOR

VAPORVAPOR

VAPOR

VAPOR

TYPES OF TRAYS

CHIMNEY CHIMNEY HAT

SUMPTRUSS

CHIMNEYACCUMULATOR TRAYS

LIQUID

LIQUID

LIQUID

SIEVE TRAY

VALVE TRAY

BUBBLE - CAP TRAY

USUALLY2rsquondash0rdquo

18rdquo MINIMUM

Vessel Internals 371

bull Deflection d

d frac14 a p b4

E n t3

bull Efficiency of holes for perforated plate n

n frac14 1 25 p d2

e C

DIMENSIONAL DATA

a frac14b frac14t frac14a=b frac14b frac14a frac14p frac14d frac14e frac14C frac14E frac14

Tray DesignCase 2 Standard tray plates

LOADS

A DL frac14 Dead load weight of trays and beams

B LL frac14 Live load dynamic load DP

C LL frac14 Liquid load weight of liquid supported

bull Total area AT

AT frac14 p D2=4 frac14 7854 D2

bull Total load PT

PT frac14 DLthorn LLthorn LL

bull Uniform load p

p frac14 PT=AT

LONG EDGE

SHORTEDGEBEAMS (TYP)

c = PITCH60deg

a

b

e

d

Table 5-20Coefficients

ab b a g

10 2874 044 420

12 3762 0616 455

14 4530 0770 478

16 5172 0906 491

18 5688 1017 499

20 6102 1110 503

30 7134 1335 505

40 7410 1400 502

50 7476 1417 501

N 7500 1421 500

372 Pressure Vessel Design Manual

PROPERTIES OF SECTIONS

C frac14 SAY=SA

I frac14 SAY2 thorn SI C SAY

Z frac14 I=C

CALCULATIONS

bull Determine panel area AP

AP frac14 Ln dnbull Load on panel FP

FP frac14 AP p

Uniform Load

bull Uniform load on beam w

w frac14 FP=Ln

bull Moment M

M frac14 w L2

n

8

bull Bending stress fb

fb frac14 M=Z

bull Deflection d

d frac14 5 w L4

n

384 E I

Concentrated Load

bull Moment M

M frac14 ethP LnTHORN=4bull Bending stress fb

fb frac14 M=Z

bull Deflection d

d frac14 P L3

n

48 E I

TYPE 1

1

2

XX

h

dn

t

PART A Y AY AY2 I12sum

C frac14 SAY=SA

I frac14 SAY2 thorn SI C SAY

Z frac14 I=C

TYPE 2

1

32

XX

h

dn

do

t

PART A Y AY AY2 I123sum

L1

DC

DIMENSIONS OF TRAY PANELS

d1 d2 d3 d4

Vessel Internals 373

NOTES1 Design Loads Trays pans drawoff boxes or

similar intemals shall be designed using a corrodedthickness to support their own weight plus thefollowing live loadsa Fractionation trays Design live load shall be the

greater of 20 PSF (98 KgSq meter) or the weightof water 2 (50 mm) over the highest weirsetting

b Areas under downcomers Design live load shallbe the greater of 64 PSF (314 Kg Sq meter) ora head of water one half the height of thedowncomer

c Pans (accumulator and drawoff pans) Designlive load shall be the greater of 1 PSI (700 Kg Sqmeter) or the weight of water at the maximumoperating level of the pan

d Baffles With no operating liquid level shall usea design live load of 1 PSI (700 KgSq meter) onthe projected horizontal area or actual impulseforce whichever is greater

2 Maintenance Loads Tray support members (allbeams support clips etc) shall be designed fora concentrated load of 300 Lbs (135 Kg) at any pointon the installed assembly The design shall be basedon the corroded thicknesses and an allowable stressof 9 Fy For maintenance loads stresses in the trayplates need not be considered

3 Uplift resistance Typical design of uplift for traysand packing is 25 PSI (17 Millibar) For serviceswhere excessive uplift can occur a higher upliftresistance may be used Examples of higher upliftfactors are as follows

a Crude and FCC side strippers 1 PSI (70 millibar)b Vacuum tower stripping trays overflash

collector wash trays or beds 2 PSI (140Millibar)

c Collectiors and packed beds above the washsection of a vacuum Tower 1 PSI (70 Millibar)

4 Failure sequence Tray assemblies wheneverpossible shall be designed so that failure will occurin the following ordera Tray manwaysb Tray deck active areasc Minor beams and downcomersd Major beams (defined as beams 10ft (3 Meters)

or longer or beams which extend across a vesselwithout interruption regardless of length)

5 Allowable stresses Allowable unit stress shall bebased on yield strength Fy at design temperaturewith AISC factors for tension bearing shear etc

6 Allowable Deflection The calculated combineddeflection of trays and support beams due to oper-ating loads shall not exceed the lesser of 1900 of thevessel diameter (in inches) or 316 (5 mm)

RECOMMENDED TRAY SPACING amp MANWAY SIZE

COLUMN DIA

(FT)

TRAY SPACING

(IN)

MANWAY

SPACING

MIN MANWAY

SIZE

25 to 16 24 Every 10 trays 18 in

16 to 24 30 Every 8 trays 20 in

24 to 32 36 Every 6 trays 24 in

32 and larger 42 Every 4 trays 30 in

374 Pressure Vessel Design Manual

Procedure 5-10 Flow Over Weirs

Notation

b frac14 width ftH frac14 static head of liquid ftQ frac14 discharge rate cu ftsecV frac14 velocity of approach ftsecH0 frac14 head correction per Table 5-22

Calculations

Discharge Q

bull For a full-length weir (Case 1)

Q frac14 333beth15 HTHORNbull For a contracted weir (Case 2)

Q frac14 333beth15 HTHORNbull For a V-notch weir (Case 3)

Q frac14 633 H

bull For a Cippoletti weir (Case 4)

Q frac14 3367beth15 HTHORN

Notes

1 Assumes troughs are level

Case 1 Full-Width Weir

V frac14 1ndash2 ftsec at 4 H upstream

Case 2 Contracted Weir

V frac14 1ndash2 ftsec at 3 H upstream

Case 3 V-Notch Weir

V frac14 5 ftsec at 5 H upstream

Case 4 Cippoletti Weir

V frac14 1ndash2 ftsec at 4 H upstream

Table 5-21Head correction for velocity of approach

V 04 06 08 10 12 14 16 18 20

Hrsquo 0002 0005 001 0015 0023 003 004 005 0062

V 22 24 26 28 30 32 34 36 38

Hrsquo 0075 0089 0105 0122 014 015 0179 0201 0213

Vessel Internals 375

Procedure 5-11 Design of Demisters

Demister pads or mist eliminators are important inter-nals in process vessels Anytime there is a continuous twophase flow vapor and liquid there is the possibility forliquid entrainment If it is desirable to separate the liquidand vapor or prevent liquid carryover in the vapor streamthe velocity must be kept sufficiently low to allow the liquiddroplets to fall out of the vapor stream Demister pads areeffective entrainment separators which allow operation atvapor velocities that would otherwise be excessive

ldquoVapor disengagementrdquo can be accomplished withouta demister but the vessel must be made much larger toaccomplish the same degree of separation This is knownas gravity separation

Demister pads are used in a wide variety of processvessels Good performance can be achieved at velocitiesof 30 to 110 of optimum

Demister pads can be used in vertical or horizontalvessels The mesh pad orientation can be either vertical orhorizontal in a vertical or horizontal vessel

A wire mesh demister consists of a knitted wire matmounted on a light weight support grid The mesh is madeby weaving small diameter metal wire into a mesh Padsmay be made out of metal or plastics Metal type includecarbon steel stainless steel monel and others Plasticmaterials include PTFE HDPE and PP

Pressure drop is usually extremely low in the range of1 inch of water column maximum The pressure drop isnormally so low that it is ignored in design

Vapor disengagement is dependent on the velocity ofthe stream The most common equation for determining theallowable vapor velocity for two phase flows is as follows

Va frac14 K frac12ethrL rVTHORN=rV1=2

Where

Va frac14 Allowable vapor velocity FtSecK frac14 Constant or coefficientrL frac14 Density of liquid PCFrV frac14 Density of vapor PCF

Notes

1 The mesh pad shall be in one piece or sectional asrequired for insertion through the vessel manwayEach pad section shall be removable through thevessel manhole

2 Layers shall not be more than 6 inches thick3 Where more than one layer is required all joints

shall be staggered

4 One piece circular pads may be spiral in form5 Each section of mesh shall include a grid on one or

both sides The grid wire andor fastening deviceshall be the same material as the mesh pad Top andbottom grids shall be constructed of frac14 inch diam-eter rods welded to ⅛ inch by 1 inch bars Themaximum gap between mesh pad and grids shall befrac12 inch for diameters less than 84 inches and 1 inchfor larger diameters

6 Estimate grid weights as 3 PSF7 Tie down wires shall be 1=16 inch diameter wire thru

frac14 inch diameter holes on 4 inch centers Tie wiresshould not be pushed through the pad as this couldcause leak paths

8 Pressure drop across mist eliminator shall beassumed as 02 PSI for support design

9 Unless otherwise specified support rings shall be2 inches wide for pads 84 inches in diameter andless and 3 inches wide for larger diameters

10 The mist eliminator shall be a tight fit against theshell or enclosure as well as between sections Meshpads shall be⅜ inches oversize all around for a forcefit against the enclosure No gaps are allowed

11 Vessel fabricator shall provide the mesh and gridsas well as any stiffeners required

12 The Mist eliminator shall be specified as either topor bottom removable

13 ldquoKrdquo is a constant or coefficient that is a functionof the efficiency of the separation K-values rangefrom 04 to 43 but are generally in the 15 to 35range The K-value is affected by pressure type ofpad size of wire type of vessel and disengagingheight For pressure applications the K-valueshould be decreased by 01 for every 100 PSI ofpressure after 100 PSI

14 Wire diameter for the mesh pad itself vary from0003 to 0016 inches

15 The free volume of demisters range from 92 to994

16 The density of the pads ranges from 3 to 33 PCF17 The NSA (nominal surface area) is the surface area

to volume ratio Ft2 Ft3 and is an important indi-cator of performance Ratios range from 50 to 600

18 To obtain higher separation efficiencies the wirediameter is decreased and the density and thicknessare increased

19 Typical width of sections for multi-section pads is12 inches (300 mm) but may vary by manufacturer

376 Pressure Vessel Design Manual

A Horizontal element B Vertical elements

Vertical vessels

Manway

Plate-Pakunit

Meshpad

Drain tubewith seal trap

END VIEW

END VIEW

SIDE VIEW

SIDE VIEW

C Vertical element

Horizontal vessels

D Horizontal element

Figure 5-15 Typical demister configurations in vessels

Vessel Internals 377

d

E Axial entrance

H gt (23) D ndash d

H gt D2 + d(minimum 24rdquo)

H gt D2 ndash d2

H gt D2 + d

H gt D2 ndash d2

h gt d

D

D Side entrance

d

D

B Axial exit

d

D

Φ lt 45ordm

Φ lt 45ordm

C Reverse axial exit

d

A Side exit

D

Figure 5-16 Guidelines for maintaining even flow distribution in vessels with axial flow

378 Pressure Vessel Design Manual

wire mesh

Top grid

Bottom grid

Vertical 14rdquo rodsspaced 12rdquo to 18rdquocenter to center

12rdquo to 18rdquosegmentwidth

18rdquo x 1rdquo flat bars14rdquo rodsspaced 6rdquocenterto center

Manway

Support ring

Support beam

Tie wires

Figure 5-17 Typical mesh pad construction and installation

Vessel Internals 379

Table 5-22Properties of demister pads

Type NSA (1) Ft2 Ft3 Density Pcf Wire Dia in Free Area York Style No Remarks

A 48 5 0011 99 931 High Throughput

B 65 7 0011 986 531 Economy Performance

C 85 9 0011 982 431 Standard - Good All

Around

D 110 108 0011 977 421 Heavy Duty

E 140 8 0006 984 326 Super High Efficiency -

Fine Mist

F 163 0006 94 371 Liquid - Liquid Coalescer

G 450 20 00045 959

H 600 27 00045 945

Notes

1 NSA frac14 Nominal Surface Area

Table 5-23Values of K (Note 13)

Based on Pressure

Pressure (PSIa) Vacuum (In Hg)

Pressure (PSIa) K Vacuum (In Hg) K

15 035 30 035

50 034 20 032

100 032 10 028

200 031 5 023

300 03 1 017

500 028 lt1 017

1000 027

gt1000 027

Based on Disengaging Height

Disengaging Height in K Disengaging Height in K

3 012 9 032

4 015 10 035

5 019 11 038

6 022 12 04

7 025 13 042

8 029 14 043

Based on Application

Vertical Vessels Horizontal Vessels

Type K Type K

General 035 General 035

Compressor Suction Drums 025 Steam Drums 025

Steam Drums 015

380 Pressure Vessel Design Manual

Procedure 5-12 Design of Baffles [10]

Baffles are frequently used in pressure vessels eithervertical or horizontal to divide the interior volume intodifferent compartments These compartments may beused to segregate liquids or provide overflow weirs forthe separation of liquids Baffles may be stiffened orunstiffened When welded across the entire cross sectionof the vessel they must be checked that they are notunduly restricting the diametral expansion of the vesselIf the unrestrained radial expansion of the vessel exceedsthat of the baffle by more than 1=16 in (⅛ in on thediameter) then a ldquoflexiblerdquo type of connection betweenthe vessel shell and the baffle should be utilized Variousflexible attachment designs are shown within theprocedure

Baffles should always be designed in the corrodedcondition It is typical for welded baffles to be designedwith a full corrosion allowance on both sides If the baffleis bolted in then one-half the full corrosion allowancemay be applied to each side the logic being that a boltedbaffle is removable and therefore replaceable

The majority of baffles are flat and as a result are veryinefficient from a strength standpoint Deflection is thegoverning case for flat plates loaded on one side Thepreference is to have unstiffened baffles and they shouldalways be the first choice This will be acceptable forsmall baffles However for larger baffles as the bafflethickness becomes excessive stiffeners offer a moreeconomical design Therefore stiffeners are frequentlyused to stiffen the baffle to prevent the thickness of thebaffle from becoming excessive The number size andspacing of stiffeners are dependent on the baffle thicknessselected There is a continual trade-off between bafflethickness and stiffener parameters

The design of a baffle with stiffeners is an iterativeprocess The procedure for the design of the stiffeners isfirst to divide the baffle into ldquopanelrdquo sections that are rigidenough to withstand the pressure applied on one sideEach individual panel is checked as a flat plate of thedimensions of the panel The stiffeners are assumed to bestrong enough to provide the necessary edge support forthe panel

The stiffeners themselves are designed next A sectionof the baffle is assumed as acting with the stiffener and ascontributing to the overall stiffness This combinedsection is known as the composite stiffener Thecomposite section is checked for stress and deflectionBoth vertical and horizontal stiffeners can be added asrequired

If required an alternate design is assumed based ona thicker or thinner baffle and checked until a satisfactorydesign is found There is no ldquorightrdquo answer however itshould be noted that the thinner the baffle the greater thenumber of stiffeners The lightest overall weight isprobably the ldquobestrdquo design but may not be the leastexpensive due to the welding costs in attaching thestiffeners

One alternative to a flat baffle with stiffeners is to go toa curved baffle A curved baffle works best as a verticalbaffle in a vertical vessel The curved baffle takes pressurefrom either side wall If the pressure is on the concave sidethe baffle is in tension If the pressure is on the convexside the baffle is in compression

There are various tables given in this procedure for flatplate coefficients Flat plate coefficients are utilized todetermine the baffle thickness or a panel thickness Eachtable is specific for a given condition and loading

Vessel Internals 381

Notation

Ap frac14 area of baffle working with stiffener in2

As frac14 area of stiffener in2

Cp frac14 distance from centroid of composite section topanel in

Cs frac14 distance from centroid of composite section tostiffener in

E frac14 modulus of elasticity psiFb frac14 allowable bending stress psiI frac14 moment of inertia composite in4

Is frac14 moment of inertia stiffener in4

l frac14 length of baffle that works with the stiffener inM frac14 moment in-lbn frac14 number of welds attaching stiffenerP frac14 vessel internal pressure psigp frac14 maximum uniform pressure psipn frac14 uniform pressure at any elevation an psiRm frac14 vessel mean radius inSg frac14 specific gravity of contentst frac14 thickness shell intb frac14 thickness baffle ints frac14 thickness stiffener inV frac14 shear load lbw frac14 required fillet weld size ina frac14 thermal coefficient of expansion ininF

bg frac14 flat plate coefficientsDT frac14 differential temperature (design temperature

minus 70F) Fsb frac14 bending stress in baffle psiss frac14 bending stress in stiffener psi

6n frac14 radial expansion ind frac14 deflection inda frac14 maximum allowable deflection in

Baffle Dimensions

382 Pressure Vessel Design Manual

Table 5-24Flat plate coefficients

Vessel Internals 383

Unstiffened Baffle Check

bull Find load p

p frac14 624aSg144

bull Find baffle thickness tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

s

bull Find baffle deflection d

d frac14 pg1b4

Et3b

Limit deflection to the smaller of tb2 or b360 Ifdeflection is excessive then

a Increase the baffle thicknessb Add stiffenersc Go to curved baffle design

If stiffeners are added the first step is to find themaximum ldquoardquo and ldquobrdquo dimensions that will meet theallowable deflection for a given panel size This willestablish the stiffener spacing for both horizontal andvertical stiffeners The ultimate design is a balancebetween baffle thickness stiffener spacing and stiffenersize

Thermal Check of Baffle

bull Vessel radial expansion due to pressure

D1 frac14 085PRm

tE

bull Vessel radial expansion due to temperature

D2 frac14 Rma DT

bull Thermal expansion of baffle

D3 frac14 05ba DT

bull Differential expansion

D4 frac14 D1 thorn D2 D3

Stiffener Design

Divide baffle into panels to limit deflection to the lesserof tb2 or b360 Deflection is calculated based on theappropriate Cases 1 through 3

bull Check baffle for panel size a0 b0bull Check stiffener for length a or b

Recommendations for attaching stiffeners

Benefits Provides added stiffness and no corrosiontrap

Figure 5-18 Example of stiffener layout

384 Pressure Vessel Design Manual

As frac14 tsh

Ap frac14 tbl

IS frac14 tsh3

12

Cp frac14 AsyAs thorn Ap

thorn tb2

Cs frac14 ethhthorn tbTHORN Cp

I frac14 IS thorn Apt2b12

thorn AsApy2

As thorn Ap

lsquo frac14 lesser of 32tb or stiffener spacing

Stresses in BaffleStiffener

sp frac14 MCp

I

ss frac14 MCs

I

Size Welds Attaching Stiffeners

For E70XX Welds

w frac14 Vdy11 200In

Table 5-25Intermittent Welds

Percent of

Continuous Weld

Length of Intermittent Welds

and Distance Between Centers

75 3e4

66 4e6

60 3e5

57 4e7

50 2e4 3e6 4e8

44 4e9

43 3e7

40 2e5 4e10

37 3e8

33 2e6 3e9 4e12

Reprinted by permission of the James F Lincoln Arc Welding

Foundation

Vessel Internals 385

For E60XX Welds

w frac14 Vdy9600In

Sample Problem

bull Given Horizontal vessel with a vertical baffle

P frac14 250 psig

DT frac14 500F

Material frac14 SA-516-70

Ca frac14 0125 in

JE frac14 10

E frac14 273 106 psi

a frac14 7124 10-6 in=in=FFy frac14 308 ksi

D frac14 240 in

Fb frac14 066 Fy frac14 2033 ksi

Rm frac14 120938

ts frac14 175 in

Sg frac14 08

a frac14 15 ft

DT frac14 500 70 frac14 430F

bull Find baffle thickness without stiffener

p frac14 624aSg144

frac14 52 psi

a

bratio frac14 15=20 frac14 075

from Table 5-25 Case 1

b1 frac14 016 g1 frac14 0033

bull Thickness of baffle tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

sfrac14

ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi016eth52THORN2402

20 330

s

tb frac14 153thorn 025 frac14 178

No good Use stiffeners

bull Assume a suitable baffle thickness and determinemaximum panel size

tb frac14 075 in corroded

maximum panel size frac14 4ft 4ft

bull Maximum pressure p

p frac14 13eth624THORN08144

frac14 45 psi

a

bfrac14 4

4frac14 1

See Table 5-25 Case 3

b3 frac14 0287 g3 frac14 00443

sb frac14 b3pb2n

t2

frac14 0287eth45THORN4820752

frac14 5290 psi lt 20 333 psiFigure 5-19 Sample problem

386 Pressure Vessel Design Manual

d frac14 g3

pE

b4nt3

frac14 00443

45

273 106

484

0753

frac14 0092 in lt 0375 in

Balance OK by inspection

bull Assume a layout where the maximum stiffenerspacing is 4 ft

(4) horizontal stiffeners(4) vertical stiffeners(18) panels

bull Check horizontal stiffeners

Dimensions

a1 frac14 3 ft b1 frac14 4 ft

a2 frac14 4 ft b2 frac14 4 ft

a3 frac14 4 ft b3 frac14 12 ft

a4 frac14 4 ft b4 frac14 196 ft

a5 frac14 13 ft

a6 frac14 148ft

bull Assume stiffener size 1 in 4 in

y frac14 2375 in

As frac14 tsh frac14 1eth4THORN frac14 4 in2

l frac14 32tb frac14 32eth075THORN frac14 24 in lt 48 in

AP frac14 tbl frac14 07524 frac14 18 in2

Is frac14 bh3

12frac14 1

43

12frac14 533 in4

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 533thorn 0633thorn 1846 frac14 2442 in4

Cp frac14 AsyAs thorn Ap

thorn tb2

frac14 4eth2375THORN22

thorn 0752

frac14 0807 in

Cs frac14 hthorn tb

Cp

frac14 4thorn 075 0807 frac14 3943

Check deflections

Deflections exceed allowable No good

bull Assume a larger stiffener size WT9 593

tf frac14 106 025 frac14 081

tw frac14 0625 025 frac14 0375

bull Check corroded thickness to find properties ofcorroded section This section would be equivalent toa WT9 30 Properties are

As frac14 882 in2

Is frac14 647 in4

Cs frac14 216 in

H frac14 9 in

Cp frac14 hthorn tb Cs

frac14 9thorn 075 216 frac14 759 in

Figure 5-20 Battle layout for sample problem

Item bn pn d

1 2352 104 149

2 2352 243 349

3 144 381 0767

Vessel Internals 387

y frac14 Cp tb2

frac14 7215 in

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 647thorn 0844thorn 30814 frac14 3737 in4

bull Check stresses and deflections See results in Table5-27

bull Stresses and deflections are acceptablebull Check welds

d frac14 ts thorn 2tw frac14 0375thorn 2eth0323THORN frac14 102

y frac14 7215 in

I frac14 3737 in4

n frac14 2

w frac14 Vdy11 200In

frac14 6681eth102THORN721511 200eth3737THORN2

frac14 0005thorn 0125 frac14 013 in

bull Check thermal expansion of baffle

D1 frac14 085PRm

tEfrac14 085eth250THORN120938

175eth273 106THORNfrac14 000054 in

D2 frac14 Rma DT frac14 1209387124 106430

frac14 0370 in

D3 frac14 05ba DT frac14 05240

7124 106430

frac14 0367 in

D4 frac14 D1 thorn D2 D3 frac14 000054thorn 0370 0367

frac14 00035 lt 006 in

Table 5-26Summary of Results for Stress and Deflection in Composite Stiffeners for Sample Problem

Item Orientation an bn pn M d V sp ss

1 Horiz 2352 d 104 172595 009 2690 3504 997

2 Horiz 2352 d 243 403275 021 6287 8186 2330

3 Horiz 144 d 381 237012 0045 6035 4811 1370

4 Vert d 156 450 154674 0037 5648 3141 894

5 Vert d 1776 513 228539 0072 6681 6681 1320

Figure 5-21 Details of weld attaching stiffener

388 Pressure Vessel Design Manual

Vessel Internals 389

Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 15: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

bull Deflection d

d frac14 a p b4

E n t3

bull Efficiency of holes for perforated plate n

n frac14 1 25 p d2

e C

DIMENSIONAL DATA

a frac14b frac14t frac14a=b frac14b frac14a frac14p frac14d frac14e frac14C frac14E frac14

Tray DesignCase 2 Standard tray plates

LOADS

A DL frac14 Dead load weight of trays and beams

B LL frac14 Live load dynamic load DP

C LL frac14 Liquid load weight of liquid supported

bull Total area AT

AT frac14 p D2=4 frac14 7854 D2

bull Total load PT

PT frac14 DLthorn LLthorn LL

bull Uniform load p

p frac14 PT=AT

LONG EDGE

SHORTEDGEBEAMS (TYP)

c = PITCH60deg

a

b

e

d

Table 5-20Coefficients

ab b a g

10 2874 044 420

12 3762 0616 455

14 4530 0770 478

16 5172 0906 491

18 5688 1017 499

20 6102 1110 503

30 7134 1335 505

40 7410 1400 502

50 7476 1417 501

N 7500 1421 500

372 Pressure Vessel Design Manual

PROPERTIES OF SECTIONS

C frac14 SAY=SA

I frac14 SAY2 thorn SI C SAY

Z frac14 I=C

CALCULATIONS

bull Determine panel area AP

AP frac14 Ln dnbull Load on panel FP

FP frac14 AP p

Uniform Load

bull Uniform load on beam w

w frac14 FP=Ln

bull Moment M

M frac14 w L2

n

8

bull Bending stress fb

fb frac14 M=Z

bull Deflection d

d frac14 5 w L4

n

384 E I

Concentrated Load

bull Moment M

M frac14 ethP LnTHORN=4bull Bending stress fb

fb frac14 M=Z

bull Deflection d

d frac14 P L3

n

48 E I

TYPE 1

1

2

XX

h

dn

t

PART A Y AY AY2 I12sum

C frac14 SAY=SA

I frac14 SAY2 thorn SI C SAY

Z frac14 I=C

TYPE 2

1

32

XX

h

dn

do

t

PART A Y AY AY2 I123sum

L1

DC

DIMENSIONS OF TRAY PANELS

d1 d2 d3 d4

Vessel Internals 373

NOTES1 Design Loads Trays pans drawoff boxes or

similar intemals shall be designed using a corrodedthickness to support their own weight plus thefollowing live loadsa Fractionation trays Design live load shall be the

greater of 20 PSF (98 KgSq meter) or the weightof water 2 (50 mm) over the highest weirsetting

b Areas under downcomers Design live load shallbe the greater of 64 PSF (314 Kg Sq meter) ora head of water one half the height of thedowncomer

c Pans (accumulator and drawoff pans) Designlive load shall be the greater of 1 PSI (700 Kg Sqmeter) or the weight of water at the maximumoperating level of the pan

d Baffles With no operating liquid level shall usea design live load of 1 PSI (700 KgSq meter) onthe projected horizontal area or actual impulseforce whichever is greater

2 Maintenance Loads Tray support members (allbeams support clips etc) shall be designed fora concentrated load of 300 Lbs (135 Kg) at any pointon the installed assembly The design shall be basedon the corroded thicknesses and an allowable stressof 9 Fy For maintenance loads stresses in the trayplates need not be considered

3 Uplift resistance Typical design of uplift for traysand packing is 25 PSI (17 Millibar) For serviceswhere excessive uplift can occur a higher upliftresistance may be used Examples of higher upliftfactors are as follows

a Crude and FCC side strippers 1 PSI (70 millibar)b Vacuum tower stripping trays overflash

collector wash trays or beds 2 PSI (140Millibar)

c Collectiors and packed beds above the washsection of a vacuum Tower 1 PSI (70 Millibar)

4 Failure sequence Tray assemblies wheneverpossible shall be designed so that failure will occurin the following ordera Tray manwaysb Tray deck active areasc Minor beams and downcomersd Major beams (defined as beams 10ft (3 Meters)

or longer or beams which extend across a vesselwithout interruption regardless of length)

5 Allowable stresses Allowable unit stress shall bebased on yield strength Fy at design temperaturewith AISC factors for tension bearing shear etc

6 Allowable Deflection The calculated combineddeflection of trays and support beams due to oper-ating loads shall not exceed the lesser of 1900 of thevessel diameter (in inches) or 316 (5 mm)

RECOMMENDED TRAY SPACING amp MANWAY SIZE

COLUMN DIA

(FT)

TRAY SPACING

(IN)

MANWAY

SPACING

MIN MANWAY

SIZE

25 to 16 24 Every 10 trays 18 in

16 to 24 30 Every 8 trays 20 in

24 to 32 36 Every 6 trays 24 in

32 and larger 42 Every 4 trays 30 in

374 Pressure Vessel Design Manual

Procedure 5-10 Flow Over Weirs

Notation

b frac14 width ftH frac14 static head of liquid ftQ frac14 discharge rate cu ftsecV frac14 velocity of approach ftsecH0 frac14 head correction per Table 5-22

Calculations

Discharge Q

bull For a full-length weir (Case 1)

Q frac14 333beth15 HTHORNbull For a contracted weir (Case 2)

Q frac14 333beth15 HTHORNbull For a V-notch weir (Case 3)

Q frac14 633 H

bull For a Cippoletti weir (Case 4)

Q frac14 3367beth15 HTHORN

Notes

1 Assumes troughs are level

Case 1 Full-Width Weir

V frac14 1ndash2 ftsec at 4 H upstream

Case 2 Contracted Weir

V frac14 1ndash2 ftsec at 3 H upstream

Case 3 V-Notch Weir

V frac14 5 ftsec at 5 H upstream

Case 4 Cippoletti Weir

V frac14 1ndash2 ftsec at 4 H upstream

Table 5-21Head correction for velocity of approach

V 04 06 08 10 12 14 16 18 20

Hrsquo 0002 0005 001 0015 0023 003 004 005 0062

V 22 24 26 28 30 32 34 36 38

Hrsquo 0075 0089 0105 0122 014 015 0179 0201 0213

Vessel Internals 375

Procedure 5-11 Design of Demisters

Demister pads or mist eliminators are important inter-nals in process vessels Anytime there is a continuous twophase flow vapor and liquid there is the possibility forliquid entrainment If it is desirable to separate the liquidand vapor or prevent liquid carryover in the vapor streamthe velocity must be kept sufficiently low to allow the liquiddroplets to fall out of the vapor stream Demister pads areeffective entrainment separators which allow operation atvapor velocities that would otherwise be excessive

ldquoVapor disengagementrdquo can be accomplished withouta demister but the vessel must be made much larger toaccomplish the same degree of separation This is knownas gravity separation

Demister pads are used in a wide variety of processvessels Good performance can be achieved at velocitiesof 30 to 110 of optimum

Demister pads can be used in vertical or horizontalvessels The mesh pad orientation can be either vertical orhorizontal in a vertical or horizontal vessel

A wire mesh demister consists of a knitted wire matmounted on a light weight support grid The mesh is madeby weaving small diameter metal wire into a mesh Padsmay be made out of metal or plastics Metal type includecarbon steel stainless steel monel and others Plasticmaterials include PTFE HDPE and PP

Pressure drop is usually extremely low in the range of1 inch of water column maximum The pressure drop isnormally so low that it is ignored in design

Vapor disengagement is dependent on the velocity ofthe stream The most common equation for determining theallowable vapor velocity for two phase flows is as follows

Va frac14 K frac12ethrL rVTHORN=rV1=2

Where

Va frac14 Allowable vapor velocity FtSecK frac14 Constant or coefficientrL frac14 Density of liquid PCFrV frac14 Density of vapor PCF

Notes

1 The mesh pad shall be in one piece or sectional asrequired for insertion through the vessel manwayEach pad section shall be removable through thevessel manhole

2 Layers shall not be more than 6 inches thick3 Where more than one layer is required all joints

shall be staggered

4 One piece circular pads may be spiral in form5 Each section of mesh shall include a grid on one or

both sides The grid wire andor fastening deviceshall be the same material as the mesh pad Top andbottom grids shall be constructed of frac14 inch diam-eter rods welded to ⅛ inch by 1 inch bars Themaximum gap between mesh pad and grids shall befrac12 inch for diameters less than 84 inches and 1 inchfor larger diameters

6 Estimate grid weights as 3 PSF7 Tie down wires shall be 1=16 inch diameter wire thru

frac14 inch diameter holes on 4 inch centers Tie wiresshould not be pushed through the pad as this couldcause leak paths

8 Pressure drop across mist eliminator shall beassumed as 02 PSI for support design

9 Unless otherwise specified support rings shall be2 inches wide for pads 84 inches in diameter andless and 3 inches wide for larger diameters

10 The mist eliminator shall be a tight fit against theshell or enclosure as well as between sections Meshpads shall be⅜ inches oversize all around for a forcefit against the enclosure No gaps are allowed

11 Vessel fabricator shall provide the mesh and gridsas well as any stiffeners required

12 The Mist eliminator shall be specified as either topor bottom removable

13 ldquoKrdquo is a constant or coefficient that is a functionof the efficiency of the separation K-values rangefrom 04 to 43 but are generally in the 15 to 35range The K-value is affected by pressure type ofpad size of wire type of vessel and disengagingheight For pressure applications the K-valueshould be decreased by 01 for every 100 PSI ofpressure after 100 PSI

14 Wire diameter for the mesh pad itself vary from0003 to 0016 inches

15 The free volume of demisters range from 92 to994

16 The density of the pads ranges from 3 to 33 PCF17 The NSA (nominal surface area) is the surface area

to volume ratio Ft2 Ft3 and is an important indi-cator of performance Ratios range from 50 to 600

18 To obtain higher separation efficiencies the wirediameter is decreased and the density and thicknessare increased

19 Typical width of sections for multi-section pads is12 inches (300 mm) but may vary by manufacturer

376 Pressure Vessel Design Manual

A Horizontal element B Vertical elements

Vertical vessels

Manway

Plate-Pakunit

Meshpad

Drain tubewith seal trap

END VIEW

END VIEW

SIDE VIEW

SIDE VIEW

C Vertical element

Horizontal vessels

D Horizontal element

Figure 5-15 Typical demister configurations in vessels

Vessel Internals 377

d

E Axial entrance

H gt (23) D ndash d

H gt D2 + d(minimum 24rdquo)

H gt D2 ndash d2

H gt D2 + d

H gt D2 ndash d2

h gt d

D

D Side entrance

d

D

B Axial exit

d

D

Φ lt 45ordm

Φ lt 45ordm

C Reverse axial exit

d

A Side exit

D

Figure 5-16 Guidelines for maintaining even flow distribution in vessels with axial flow

378 Pressure Vessel Design Manual

wire mesh

Top grid

Bottom grid

Vertical 14rdquo rodsspaced 12rdquo to 18rdquocenter to center

12rdquo to 18rdquosegmentwidth

18rdquo x 1rdquo flat bars14rdquo rodsspaced 6rdquocenterto center

Manway

Support ring

Support beam

Tie wires

Figure 5-17 Typical mesh pad construction and installation

Vessel Internals 379

Table 5-22Properties of demister pads

Type NSA (1) Ft2 Ft3 Density Pcf Wire Dia in Free Area York Style No Remarks

A 48 5 0011 99 931 High Throughput

B 65 7 0011 986 531 Economy Performance

C 85 9 0011 982 431 Standard - Good All

Around

D 110 108 0011 977 421 Heavy Duty

E 140 8 0006 984 326 Super High Efficiency -

Fine Mist

F 163 0006 94 371 Liquid - Liquid Coalescer

G 450 20 00045 959

H 600 27 00045 945

Notes

1 NSA frac14 Nominal Surface Area

Table 5-23Values of K (Note 13)

Based on Pressure

Pressure (PSIa) Vacuum (In Hg)

Pressure (PSIa) K Vacuum (In Hg) K

15 035 30 035

50 034 20 032

100 032 10 028

200 031 5 023

300 03 1 017

500 028 lt1 017

1000 027

gt1000 027

Based on Disengaging Height

Disengaging Height in K Disengaging Height in K

3 012 9 032

4 015 10 035

5 019 11 038

6 022 12 04

7 025 13 042

8 029 14 043

Based on Application

Vertical Vessels Horizontal Vessels

Type K Type K

General 035 General 035

Compressor Suction Drums 025 Steam Drums 025

Steam Drums 015

380 Pressure Vessel Design Manual

Procedure 5-12 Design of Baffles [10]

Baffles are frequently used in pressure vessels eithervertical or horizontal to divide the interior volume intodifferent compartments These compartments may beused to segregate liquids or provide overflow weirs forthe separation of liquids Baffles may be stiffened orunstiffened When welded across the entire cross sectionof the vessel they must be checked that they are notunduly restricting the diametral expansion of the vesselIf the unrestrained radial expansion of the vessel exceedsthat of the baffle by more than 1=16 in (⅛ in on thediameter) then a ldquoflexiblerdquo type of connection betweenthe vessel shell and the baffle should be utilized Variousflexible attachment designs are shown within theprocedure

Baffles should always be designed in the corrodedcondition It is typical for welded baffles to be designedwith a full corrosion allowance on both sides If the baffleis bolted in then one-half the full corrosion allowancemay be applied to each side the logic being that a boltedbaffle is removable and therefore replaceable

The majority of baffles are flat and as a result are veryinefficient from a strength standpoint Deflection is thegoverning case for flat plates loaded on one side Thepreference is to have unstiffened baffles and they shouldalways be the first choice This will be acceptable forsmall baffles However for larger baffles as the bafflethickness becomes excessive stiffeners offer a moreeconomical design Therefore stiffeners are frequentlyused to stiffen the baffle to prevent the thickness of thebaffle from becoming excessive The number size andspacing of stiffeners are dependent on the baffle thicknessselected There is a continual trade-off between bafflethickness and stiffener parameters

The design of a baffle with stiffeners is an iterativeprocess The procedure for the design of the stiffeners isfirst to divide the baffle into ldquopanelrdquo sections that are rigidenough to withstand the pressure applied on one sideEach individual panel is checked as a flat plate of thedimensions of the panel The stiffeners are assumed to bestrong enough to provide the necessary edge support forthe panel

The stiffeners themselves are designed next A sectionof the baffle is assumed as acting with the stiffener and ascontributing to the overall stiffness This combinedsection is known as the composite stiffener Thecomposite section is checked for stress and deflectionBoth vertical and horizontal stiffeners can be added asrequired

If required an alternate design is assumed based ona thicker or thinner baffle and checked until a satisfactorydesign is found There is no ldquorightrdquo answer however itshould be noted that the thinner the baffle the greater thenumber of stiffeners The lightest overall weight isprobably the ldquobestrdquo design but may not be the leastexpensive due to the welding costs in attaching thestiffeners

One alternative to a flat baffle with stiffeners is to go toa curved baffle A curved baffle works best as a verticalbaffle in a vertical vessel The curved baffle takes pressurefrom either side wall If the pressure is on the concave sidethe baffle is in tension If the pressure is on the convexside the baffle is in compression

There are various tables given in this procedure for flatplate coefficients Flat plate coefficients are utilized todetermine the baffle thickness or a panel thickness Eachtable is specific for a given condition and loading

Vessel Internals 381

Notation

Ap frac14 area of baffle working with stiffener in2

As frac14 area of stiffener in2

Cp frac14 distance from centroid of composite section topanel in

Cs frac14 distance from centroid of composite section tostiffener in

E frac14 modulus of elasticity psiFb frac14 allowable bending stress psiI frac14 moment of inertia composite in4

Is frac14 moment of inertia stiffener in4

l frac14 length of baffle that works with the stiffener inM frac14 moment in-lbn frac14 number of welds attaching stiffenerP frac14 vessel internal pressure psigp frac14 maximum uniform pressure psipn frac14 uniform pressure at any elevation an psiRm frac14 vessel mean radius inSg frac14 specific gravity of contentst frac14 thickness shell intb frac14 thickness baffle ints frac14 thickness stiffener inV frac14 shear load lbw frac14 required fillet weld size ina frac14 thermal coefficient of expansion ininF

bg frac14 flat plate coefficientsDT frac14 differential temperature (design temperature

minus 70F) Fsb frac14 bending stress in baffle psiss frac14 bending stress in stiffener psi

6n frac14 radial expansion ind frac14 deflection inda frac14 maximum allowable deflection in

Baffle Dimensions

382 Pressure Vessel Design Manual

Table 5-24Flat plate coefficients

Vessel Internals 383

Unstiffened Baffle Check

bull Find load p

p frac14 624aSg144

bull Find baffle thickness tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

s

bull Find baffle deflection d

d frac14 pg1b4

Et3b

Limit deflection to the smaller of tb2 or b360 Ifdeflection is excessive then

a Increase the baffle thicknessb Add stiffenersc Go to curved baffle design

If stiffeners are added the first step is to find themaximum ldquoardquo and ldquobrdquo dimensions that will meet theallowable deflection for a given panel size This willestablish the stiffener spacing for both horizontal andvertical stiffeners The ultimate design is a balancebetween baffle thickness stiffener spacing and stiffenersize

Thermal Check of Baffle

bull Vessel radial expansion due to pressure

D1 frac14 085PRm

tE

bull Vessel radial expansion due to temperature

D2 frac14 Rma DT

bull Thermal expansion of baffle

D3 frac14 05ba DT

bull Differential expansion

D4 frac14 D1 thorn D2 D3

Stiffener Design

Divide baffle into panels to limit deflection to the lesserof tb2 or b360 Deflection is calculated based on theappropriate Cases 1 through 3

bull Check baffle for panel size a0 b0bull Check stiffener for length a or b

Recommendations for attaching stiffeners

Benefits Provides added stiffness and no corrosiontrap

Figure 5-18 Example of stiffener layout

384 Pressure Vessel Design Manual

As frac14 tsh

Ap frac14 tbl

IS frac14 tsh3

12

Cp frac14 AsyAs thorn Ap

thorn tb2

Cs frac14 ethhthorn tbTHORN Cp

I frac14 IS thorn Apt2b12

thorn AsApy2

As thorn Ap

lsquo frac14 lesser of 32tb or stiffener spacing

Stresses in BaffleStiffener

sp frac14 MCp

I

ss frac14 MCs

I

Size Welds Attaching Stiffeners

For E70XX Welds

w frac14 Vdy11 200In

Table 5-25Intermittent Welds

Percent of

Continuous Weld

Length of Intermittent Welds

and Distance Between Centers

75 3e4

66 4e6

60 3e5

57 4e7

50 2e4 3e6 4e8

44 4e9

43 3e7

40 2e5 4e10

37 3e8

33 2e6 3e9 4e12

Reprinted by permission of the James F Lincoln Arc Welding

Foundation

Vessel Internals 385

For E60XX Welds

w frac14 Vdy9600In

Sample Problem

bull Given Horizontal vessel with a vertical baffle

P frac14 250 psig

DT frac14 500F

Material frac14 SA-516-70

Ca frac14 0125 in

JE frac14 10

E frac14 273 106 psi

a frac14 7124 10-6 in=in=FFy frac14 308 ksi

D frac14 240 in

Fb frac14 066 Fy frac14 2033 ksi

Rm frac14 120938

ts frac14 175 in

Sg frac14 08

a frac14 15 ft

DT frac14 500 70 frac14 430F

bull Find baffle thickness without stiffener

p frac14 624aSg144

frac14 52 psi

a

bratio frac14 15=20 frac14 075

from Table 5-25 Case 1

b1 frac14 016 g1 frac14 0033

bull Thickness of baffle tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

sfrac14

ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi016eth52THORN2402

20 330

s

tb frac14 153thorn 025 frac14 178

No good Use stiffeners

bull Assume a suitable baffle thickness and determinemaximum panel size

tb frac14 075 in corroded

maximum panel size frac14 4ft 4ft

bull Maximum pressure p

p frac14 13eth624THORN08144

frac14 45 psi

a

bfrac14 4

4frac14 1

See Table 5-25 Case 3

b3 frac14 0287 g3 frac14 00443

sb frac14 b3pb2n

t2

frac14 0287eth45THORN4820752

frac14 5290 psi lt 20 333 psiFigure 5-19 Sample problem

386 Pressure Vessel Design Manual

d frac14 g3

pE

b4nt3

frac14 00443

45

273 106

484

0753

frac14 0092 in lt 0375 in

Balance OK by inspection

bull Assume a layout where the maximum stiffenerspacing is 4 ft

(4) horizontal stiffeners(4) vertical stiffeners(18) panels

bull Check horizontal stiffeners

Dimensions

a1 frac14 3 ft b1 frac14 4 ft

a2 frac14 4 ft b2 frac14 4 ft

a3 frac14 4 ft b3 frac14 12 ft

a4 frac14 4 ft b4 frac14 196 ft

a5 frac14 13 ft

a6 frac14 148ft

bull Assume stiffener size 1 in 4 in

y frac14 2375 in

As frac14 tsh frac14 1eth4THORN frac14 4 in2

l frac14 32tb frac14 32eth075THORN frac14 24 in lt 48 in

AP frac14 tbl frac14 07524 frac14 18 in2

Is frac14 bh3

12frac14 1

43

12frac14 533 in4

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 533thorn 0633thorn 1846 frac14 2442 in4

Cp frac14 AsyAs thorn Ap

thorn tb2

frac14 4eth2375THORN22

thorn 0752

frac14 0807 in

Cs frac14 hthorn tb

Cp

frac14 4thorn 075 0807 frac14 3943

Check deflections

Deflections exceed allowable No good

bull Assume a larger stiffener size WT9 593

tf frac14 106 025 frac14 081

tw frac14 0625 025 frac14 0375

bull Check corroded thickness to find properties ofcorroded section This section would be equivalent toa WT9 30 Properties are

As frac14 882 in2

Is frac14 647 in4

Cs frac14 216 in

H frac14 9 in

Cp frac14 hthorn tb Cs

frac14 9thorn 075 216 frac14 759 in

Figure 5-20 Battle layout for sample problem

Item bn pn d

1 2352 104 149

2 2352 243 349

3 144 381 0767

Vessel Internals 387

y frac14 Cp tb2

frac14 7215 in

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 647thorn 0844thorn 30814 frac14 3737 in4

bull Check stresses and deflections See results in Table5-27

bull Stresses and deflections are acceptablebull Check welds

d frac14 ts thorn 2tw frac14 0375thorn 2eth0323THORN frac14 102

y frac14 7215 in

I frac14 3737 in4

n frac14 2

w frac14 Vdy11 200In

frac14 6681eth102THORN721511 200eth3737THORN2

frac14 0005thorn 0125 frac14 013 in

bull Check thermal expansion of baffle

D1 frac14 085PRm

tEfrac14 085eth250THORN120938

175eth273 106THORNfrac14 000054 in

D2 frac14 Rma DT frac14 1209387124 106430

frac14 0370 in

D3 frac14 05ba DT frac14 05240

7124 106430

frac14 0367 in

D4 frac14 D1 thorn D2 D3 frac14 000054thorn 0370 0367

frac14 00035 lt 006 in

Table 5-26Summary of Results for Stress and Deflection in Composite Stiffeners for Sample Problem

Item Orientation an bn pn M d V sp ss

1 Horiz 2352 d 104 172595 009 2690 3504 997

2 Horiz 2352 d 243 403275 021 6287 8186 2330

3 Horiz 144 d 381 237012 0045 6035 4811 1370

4 Vert d 156 450 154674 0037 5648 3141 894

5 Vert d 1776 513 228539 0072 6681 6681 1320

Figure 5-21 Details of weld attaching stiffener

388 Pressure Vessel Design Manual

Vessel Internals 389

Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 16: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

PROPERTIES OF SECTIONS

C frac14 SAY=SA

I frac14 SAY2 thorn SI C SAY

Z frac14 I=C

CALCULATIONS

bull Determine panel area AP

AP frac14 Ln dnbull Load on panel FP

FP frac14 AP p

Uniform Load

bull Uniform load on beam w

w frac14 FP=Ln

bull Moment M

M frac14 w L2

n

8

bull Bending stress fb

fb frac14 M=Z

bull Deflection d

d frac14 5 w L4

n

384 E I

Concentrated Load

bull Moment M

M frac14 ethP LnTHORN=4bull Bending stress fb

fb frac14 M=Z

bull Deflection d

d frac14 P L3

n

48 E I

TYPE 1

1

2

XX

h

dn

t

PART A Y AY AY2 I12sum

C frac14 SAY=SA

I frac14 SAY2 thorn SI C SAY

Z frac14 I=C

TYPE 2

1

32

XX

h

dn

do

t

PART A Y AY AY2 I123sum

L1

DC

DIMENSIONS OF TRAY PANELS

d1 d2 d3 d4

Vessel Internals 373

NOTES1 Design Loads Trays pans drawoff boxes or

similar intemals shall be designed using a corrodedthickness to support their own weight plus thefollowing live loadsa Fractionation trays Design live load shall be the

greater of 20 PSF (98 KgSq meter) or the weightof water 2 (50 mm) over the highest weirsetting

b Areas under downcomers Design live load shallbe the greater of 64 PSF (314 Kg Sq meter) ora head of water one half the height of thedowncomer

c Pans (accumulator and drawoff pans) Designlive load shall be the greater of 1 PSI (700 Kg Sqmeter) or the weight of water at the maximumoperating level of the pan

d Baffles With no operating liquid level shall usea design live load of 1 PSI (700 KgSq meter) onthe projected horizontal area or actual impulseforce whichever is greater

2 Maintenance Loads Tray support members (allbeams support clips etc) shall be designed fora concentrated load of 300 Lbs (135 Kg) at any pointon the installed assembly The design shall be basedon the corroded thicknesses and an allowable stressof 9 Fy For maintenance loads stresses in the trayplates need not be considered

3 Uplift resistance Typical design of uplift for traysand packing is 25 PSI (17 Millibar) For serviceswhere excessive uplift can occur a higher upliftresistance may be used Examples of higher upliftfactors are as follows

a Crude and FCC side strippers 1 PSI (70 millibar)b Vacuum tower stripping trays overflash

collector wash trays or beds 2 PSI (140Millibar)

c Collectiors and packed beds above the washsection of a vacuum Tower 1 PSI (70 Millibar)

4 Failure sequence Tray assemblies wheneverpossible shall be designed so that failure will occurin the following ordera Tray manwaysb Tray deck active areasc Minor beams and downcomersd Major beams (defined as beams 10ft (3 Meters)

or longer or beams which extend across a vesselwithout interruption regardless of length)

5 Allowable stresses Allowable unit stress shall bebased on yield strength Fy at design temperaturewith AISC factors for tension bearing shear etc

6 Allowable Deflection The calculated combineddeflection of trays and support beams due to oper-ating loads shall not exceed the lesser of 1900 of thevessel diameter (in inches) or 316 (5 mm)

RECOMMENDED TRAY SPACING amp MANWAY SIZE

COLUMN DIA

(FT)

TRAY SPACING

(IN)

MANWAY

SPACING

MIN MANWAY

SIZE

25 to 16 24 Every 10 trays 18 in

16 to 24 30 Every 8 trays 20 in

24 to 32 36 Every 6 trays 24 in

32 and larger 42 Every 4 trays 30 in

374 Pressure Vessel Design Manual

Procedure 5-10 Flow Over Weirs

Notation

b frac14 width ftH frac14 static head of liquid ftQ frac14 discharge rate cu ftsecV frac14 velocity of approach ftsecH0 frac14 head correction per Table 5-22

Calculations

Discharge Q

bull For a full-length weir (Case 1)

Q frac14 333beth15 HTHORNbull For a contracted weir (Case 2)

Q frac14 333beth15 HTHORNbull For a V-notch weir (Case 3)

Q frac14 633 H

bull For a Cippoletti weir (Case 4)

Q frac14 3367beth15 HTHORN

Notes

1 Assumes troughs are level

Case 1 Full-Width Weir

V frac14 1ndash2 ftsec at 4 H upstream

Case 2 Contracted Weir

V frac14 1ndash2 ftsec at 3 H upstream

Case 3 V-Notch Weir

V frac14 5 ftsec at 5 H upstream

Case 4 Cippoletti Weir

V frac14 1ndash2 ftsec at 4 H upstream

Table 5-21Head correction for velocity of approach

V 04 06 08 10 12 14 16 18 20

Hrsquo 0002 0005 001 0015 0023 003 004 005 0062

V 22 24 26 28 30 32 34 36 38

Hrsquo 0075 0089 0105 0122 014 015 0179 0201 0213

Vessel Internals 375

Procedure 5-11 Design of Demisters

Demister pads or mist eliminators are important inter-nals in process vessels Anytime there is a continuous twophase flow vapor and liquid there is the possibility forliquid entrainment If it is desirable to separate the liquidand vapor or prevent liquid carryover in the vapor streamthe velocity must be kept sufficiently low to allow the liquiddroplets to fall out of the vapor stream Demister pads areeffective entrainment separators which allow operation atvapor velocities that would otherwise be excessive

ldquoVapor disengagementrdquo can be accomplished withouta demister but the vessel must be made much larger toaccomplish the same degree of separation This is knownas gravity separation

Demister pads are used in a wide variety of processvessels Good performance can be achieved at velocitiesof 30 to 110 of optimum

Demister pads can be used in vertical or horizontalvessels The mesh pad orientation can be either vertical orhorizontal in a vertical or horizontal vessel

A wire mesh demister consists of a knitted wire matmounted on a light weight support grid The mesh is madeby weaving small diameter metal wire into a mesh Padsmay be made out of metal or plastics Metal type includecarbon steel stainless steel monel and others Plasticmaterials include PTFE HDPE and PP

Pressure drop is usually extremely low in the range of1 inch of water column maximum The pressure drop isnormally so low that it is ignored in design

Vapor disengagement is dependent on the velocity ofthe stream The most common equation for determining theallowable vapor velocity for two phase flows is as follows

Va frac14 K frac12ethrL rVTHORN=rV1=2

Where

Va frac14 Allowable vapor velocity FtSecK frac14 Constant or coefficientrL frac14 Density of liquid PCFrV frac14 Density of vapor PCF

Notes

1 The mesh pad shall be in one piece or sectional asrequired for insertion through the vessel manwayEach pad section shall be removable through thevessel manhole

2 Layers shall not be more than 6 inches thick3 Where more than one layer is required all joints

shall be staggered

4 One piece circular pads may be spiral in form5 Each section of mesh shall include a grid on one or

both sides The grid wire andor fastening deviceshall be the same material as the mesh pad Top andbottom grids shall be constructed of frac14 inch diam-eter rods welded to ⅛ inch by 1 inch bars Themaximum gap between mesh pad and grids shall befrac12 inch for diameters less than 84 inches and 1 inchfor larger diameters

6 Estimate grid weights as 3 PSF7 Tie down wires shall be 1=16 inch diameter wire thru

frac14 inch diameter holes on 4 inch centers Tie wiresshould not be pushed through the pad as this couldcause leak paths

8 Pressure drop across mist eliminator shall beassumed as 02 PSI for support design

9 Unless otherwise specified support rings shall be2 inches wide for pads 84 inches in diameter andless and 3 inches wide for larger diameters

10 The mist eliminator shall be a tight fit against theshell or enclosure as well as between sections Meshpads shall be⅜ inches oversize all around for a forcefit against the enclosure No gaps are allowed

11 Vessel fabricator shall provide the mesh and gridsas well as any stiffeners required

12 The Mist eliminator shall be specified as either topor bottom removable

13 ldquoKrdquo is a constant or coefficient that is a functionof the efficiency of the separation K-values rangefrom 04 to 43 but are generally in the 15 to 35range The K-value is affected by pressure type ofpad size of wire type of vessel and disengagingheight For pressure applications the K-valueshould be decreased by 01 for every 100 PSI ofpressure after 100 PSI

14 Wire diameter for the mesh pad itself vary from0003 to 0016 inches

15 The free volume of demisters range from 92 to994

16 The density of the pads ranges from 3 to 33 PCF17 The NSA (nominal surface area) is the surface area

to volume ratio Ft2 Ft3 and is an important indi-cator of performance Ratios range from 50 to 600

18 To obtain higher separation efficiencies the wirediameter is decreased and the density and thicknessare increased

19 Typical width of sections for multi-section pads is12 inches (300 mm) but may vary by manufacturer

376 Pressure Vessel Design Manual

A Horizontal element B Vertical elements

Vertical vessels

Manway

Plate-Pakunit

Meshpad

Drain tubewith seal trap

END VIEW

END VIEW

SIDE VIEW

SIDE VIEW

C Vertical element

Horizontal vessels

D Horizontal element

Figure 5-15 Typical demister configurations in vessels

Vessel Internals 377

d

E Axial entrance

H gt (23) D ndash d

H gt D2 + d(minimum 24rdquo)

H gt D2 ndash d2

H gt D2 + d

H gt D2 ndash d2

h gt d

D

D Side entrance

d

D

B Axial exit

d

D

Φ lt 45ordm

Φ lt 45ordm

C Reverse axial exit

d

A Side exit

D

Figure 5-16 Guidelines for maintaining even flow distribution in vessels with axial flow

378 Pressure Vessel Design Manual

wire mesh

Top grid

Bottom grid

Vertical 14rdquo rodsspaced 12rdquo to 18rdquocenter to center

12rdquo to 18rdquosegmentwidth

18rdquo x 1rdquo flat bars14rdquo rodsspaced 6rdquocenterto center

Manway

Support ring

Support beam

Tie wires

Figure 5-17 Typical mesh pad construction and installation

Vessel Internals 379

Table 5-22Properties of demister pads

Type NSA (1) Ft2 Ft3 Density Pcf Wire Dia in Free Area York Style No Remarks

A 48 5 0011 99 931 High Throughput

B 65 7 0011 986 531 Economy Performance

C 85 9 0011 982 431 Standard - Good All

Around

D 110 108 0011 977 421 Heavy Duty

E 140 8 0006 984 326 Super High Efficiency -

Fine Mist

F 163 0006 94 371 Liquid - Liquid Coalescer

G 450 20 00045 959

H 600 27 00045 945

Notes

1 NSA frac14 Nominal Surface Area

Table 5-23Values of K (Note 13)

Based on Pressure

Pressure (PSIa) Vacuum (In Hg)

Pressure (PSIa) K Vacuum (In Hg) K

15 035 30 035

50 034 20 032

100 032 10 028

200 031 5 023

300 03 1 017

500 028 lt1 017

1000 027

gt1000 027

Based on Disengaging Height

Disengaging Height in K Disengaging Height in K

3 012 9 032

4 015 10 035

5 019 11 038

6 022 12 04

7 025 13 042

8 029 14 043

Based on Application

Vertical Vessels Horizontal Vessels

Type K Type K

General 035 General 035

Compressor Suction Drums 025 Steam Drums 025

Steam Drums 015

380 Pressure Vessel Design Manual

Procedure 5-12 Design of Baffles [10]

Baffles are frequently used in pressure vessels eithervertical or horizontal to divide the interior volume intodifferent compartments These compartments may beused to segregate liquids or provide overflow weirs forthe separation of liquids Baffles may be stiffened orunstiffened When welded across the entire cross sectionof the vessel they must be checked that they are notunduly restricting the diametral expansion of the vesselIf the unrestrained radial expansion of the vessel exceedsthat of the baffle by more than 1=16 in (⅛ in on thediameter) then a ldquoflexiblerdquo type of connection betweenthe vessel shell and the baffle should be utilized Variousflexible attachment designs are shown within theprocedure

Baffles should always be designed in the corrodedcondition It is typical for welded baffles to be designedwith a full corrosion allowance on both sides If the baffleis bolted in then one-half the full corrosion allowancemay be applied to each side the logic being that a boltedbaffle is removable and therefore replaceable

The majority of baffles are flat and as a result are veryinefficient from a strength standpoint Deflection is thegoverning case for flat plates loaded on one side Thepreference is to have unstiffened baffles and they shouldalways be the first choice This will be acceptable forsmall baffles However for larger baffles as the bafflethickness becomes excessive stiffeners offer a moreeconomical design Therefore stiffeners are frequentlyused to stiffen the baffle to prevent the thickness of thebaffle from becoming excessive The number size andspacing of stiffeners are dependent on the baffle thicknessselected There is a continual trade-off between bafflethickness and stiffener parameters

The design of a baffle with stiffeners is an iterativeprocess The procedure for the design of the stiffeners isfirst to divide the baffle into ldquopanelrdquo sections that are rigidenough to withstand the pressure applied on one sideEach individual panel is checked as a flat plate of thedimensions of the panel The stiffeners are assumed to bestrong enough to provide the necessary edge support forthe panel

The stiffeners themselves are designed next A sectionof the baffle is assumed as acting with the stiffener and ascontributing to the overall stiffness This combinedsection is known as the composite stiffener Thecomposite section is checked for stress and deflectionBoth vertical and horizontal stiffeners can be added asrequired

If required an alternate design is assumed based ona thicker or thinner baffle and checked until a satisfactorydesign is found There is no ldquorightrdquo answer however itshould be noted that the thinner the baffle the greater thenumber of stiffeners The lightest overall weight isprobably the ldquobestrdquo design but may not be the leastexpensive due to the welding costs in attaching thestiffeners

One alternative to a flat baffle with stiffeners is to go toa curved baffle A curved baffle works best as a verticalbaffle in a vertical vessel The curved baffle takes pressurefrom either side wall If the pressure is on the concave sidethe baffle is in tension If the pressure is on the convexside the baffle is in compression

There are various tables given in this procedure for flatplate coefficients Flat plate coefficients are utilized todetermine the baffle thickness or a panel thickness Eachtable is specific for a given condition and loading

Vessel Internals 381

Notation

Ap frac14 area of baffle working with stiffener in2

As frac14 area of stiffener in2

Cp frac14 distance from centroid of composite section topanel in

Cs frac14 distance from centroid of composite section tostiffener in

E frac14 modulus of elasticity psiFb frac14 allowable bending stress psiI frac14 moment of inertia composite in4

Is frac14 moment of inertia stiffener in4

l frac14 length of baffle that works with the stiffener inM frac14 moment in-lbn frac14 number of welds attaching stiffenerP frac14 vessel internal pressure psigp frac14 maximum uniform pressure psipn frac14 uniform pressure at any elevation an psiRm frac14 vessel mean radius inSg frac14 specific gravity of contentst frac14 thickness shell intb frac14 thickness baffle ints frac14 thickness stiffener inV frac14 shear load lbw frac14 required fillet weld size ina frac14 thermal coefficient of expansion ininF

bg frac14 flat plate coefficientsDT frac14 differential temperature (design temperature

minus 70F) Fsb frac14 bending stress in baffle psiss frac14 bending stress in stiffener psi

6n frac14 radial expansion ind frac14 deflection inda frac14 maximum allowable deflection in

Baffle Dimensions

382 Pressure Vessel Design Manual

Table 5-24Flat plate coefficients

Vessel Internals 383

Unstiffened Baffle Check

bull Find load p

p frac14 624aSg144

bull Find baffle thickness tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

s

bull Find baffle deflection d

d frac14 pg1b4

Et3b

Limit deflection to the smaller of tb2 or b360 Ifdeflection is excessive then

a Increase the baffle thicknessb Add stiffenersc Go to curved baffle design

If stiffeners are added the first step is to find themaximum ldquoardquo and ldquobrdquo dimensions that will meet theallowable deflection for a given panel size This willestablish the stiffener spacing for both horizontal andvertical stiffeners The ultimate design is a balancebetween baffle thickness stiffener spacing and stiffenersize

Thermal Check of Baffle

bull Vessel radial expansion due to pressure

D1 frac14 085PRm

tE

bull Vessel radial expansion due to temperature

D2 frac14 Rma DT

bull Thermal expansion of baffle

D3 frac14 05ba DT

bull Differential expansion

D4 frac14 D1 thorn D2 D3

Stiffener Design

Divide baffle into panels to limit deflection to the lesserof tb2 or b360 Deflection is calculated based on theappropriate Cases 1 through 3

bull Check baffle for panel size a0 b0bull Check stiffener for length a or b

Recommendations for attaching stiffeners

Benefits Provides added stiffness and no corrosiontrap

Figure 5-18 Example of stiffener layout

384 Pressure Vessel Design Manual

As frac14 tsh

Ap frac14 tbl

IS frac14 tsh3

12

Cp frac14 AsyAs thorn Ap

thorn tb2

Cs frac14 ethhthorn tbTHORN Cp

I frac14 IS thorn Apt2b12

thorn AsApy2

As thorn Ap

lsquo frac14 lesser of 32tb or stiffener spacing

Stresses in BaffleStiffener

sp frac14 MCp

I

ss frac14 MCs

I

Size Welds Attaching Stiffeners

For E70XX Welds

w frac14 Vdy11 200In

Table 5-25Intermittent Welds

Percent of

Continuous Weld

Length of Intermittent Welds

and Distance Between Centers

75 3e4

66 4e6

60 3e5

57 4e7

50 2e4 3e6 4e8

44 4e9

43 3e7

40 2e5 4e10

37 3e8

33 2e6 3e9 4e12

Reprinted by permission of the James F Lincoln Arc Welding

Foundation

Vessel Internals 385

For E60XX Welds

w frac14 Vdy9600In

Sample Problem

bull Given Horizontal vessel with a vertical baffle

P frac14 250 psig

DT frac14 500F

Material frac14 SA-516-70

Ca frac14 0125 in

JE frac14 10

E frac14 273 106 psi

a frac14 7124 10-6 in=in=FFy frac14 308 ksi

D frac14 240 in

Fb frac14 066 Fy frac14 2033 ksi

Rm frac14 120938

ts frac14 175 in

Sg frac14 08

a frac14 15 ft

DT frac14 500 70 frac14 430F

bull Find baffle thickness without stiffener

p frac14 624aSg144

frac14 52 psi

a

bratio frac14 15=20 frac14 075

from Table 5-25 Case 1

b1 frac14 016 g1 frac14 0033

bull Thickness of baffle tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

sfrac14

ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi016eth52THORN2402

20 330

s

tb frac14 153thorn 025 frac14 178

No good Use stiffeners

bull Assume a suitable baffle thickness and determinemaximum panel size

tb frac14 075 in corroded

maximum panel size frac14 4ft 4ft

bull Maximum pressure p

p frac14 13eth624THORN08144

frac14 45 psi

a

bfrac14 4

4frac14 1

See Table 5-25 Case 3

b3 frac14 0287 g3 frac14 00443

sb frac14 b3pb2n

t2

frac14 0287eth45THORN4820752

frac14 5290 psi lt 20 333 psiFigure 5-19 Sample problem

386 Pressure Vessel Design Manual

d frac14 g3

pE

b4nt3

frac14 00443

45

273 106

484

0753

frac14 0092 in lt 0375 in

Balance OK by inspection

bull Assume a layout where the maximum stiffenerspacing is 4 ft

(4) horizontal stiffeners(4) vertical stiffeners(18) panels

bull Check horizontal stiffeners

Dimensions

a1 frac14 3 ft b1 frac14 4 ft

a2 frac14 4 ft b2 frac14 4 ft

a3 frac14 4 ft b3 frac14 12 ft

a4 frac14 4 ft b4 frac14 196 ft

a5 frac14 13 ft

a6 frac14 148ft

bull Assume stiffener size 1 in 4 in

y frac14 2375 in

As frac14 tsh frac14 1eth4THORN frac14 4 in2

l frac14 32tb frac14 32eth075THORN frac14 24 in lt 48 in

AP frac14 tbl frac14 07524 frac14 18 in2

Is frac14 bh3

12frac14 1

43

12frac14 533 in4

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 533thorn 0633thorn 1846 frac14 2442 in4

Cp frac14 AsyAs thorn Ap

thorn tb2

frac14 4eth2375THORN22

thorn 0752

frac14 0807 in

Cs frac14 hthorn tb

Cp

frac14 4thorn 075 0807 frac14 3943

Check deflections

Deflections exceed allowable No good

bull Assume a larger stiffener size WT9 593

tf frac14 106 025 frac14 081

tw frac14 0625 025 frac14 0375

bull Check corroded thickness to find properties ofcorroded section This section would be equivalent toa WT9 30 Properties are

As frac14 882 in2

Is frac14 647 in4

Cs frac14 216 in

H frac14 9 in

Cp frac14 hthorn tb Cs

frac14 9thorn 075 216 frac14 759 in

Figure 5-20 Battle layout for sample problem

Item bn pn d

1 2352 104 149

2 2352 243 349

3 144 381 0767

Vessel Internals 387

y frac14 Cp tb2

frac14 7215 in

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 647thorn 0844thorn 30814 frac14 3737 in4

bull Check stresses and deflections See results in Table5-27

bull Stresses and deflections are acceptablebull Check welds

d frac14 ts thorn 2tw frac14 0375thorn 2eth0323THORN frac14 102

y frac14 7215 in

I frac14 3737 in4

n frac14 2

w frac14 Vdy11 200In

frac14 6681eth102THORN721511 200eth3737THORN2

frac14 0005thorn 0125 frac14 013 in

bull Check thermal expansion of baffle

D1 frac14 085PRm

tEfrac14 085eth250THORN120938

175eth273 106THORNfrac14 000054 in

D2 frac14 Rma DT frac14 1209387124 106430

frac14 0370 in

D3 frac14 05ba DT frac14 05240

7124 106430

frac14 0367 in

D4 frac14 D1 thorn D2 D3 frac14 000054thorn 0370 0367

frac14 00035 lt 006 in

Table 5-26Summary of Results for Stress and Deflection in Composite Stiffeners for Sample Problem

Item Orientation an bn pn M d V sp ss

1 Horiz 2352 d 104 172595 009 2690 3504 997

2 Horiz 2352 d 243 403275 021 6287 8186 2330

3 Horiz 144 d 381 237012 0045 6035 4811 1370

4 Vert d 156 450 154674 0037 5648 3141 894

5 Vert d 1776 513 228539 0072 6681 6681 1320

Figure 5-21 Details of weld attaching stiffener

388 Pressure Vessel Design Manual

Vessel Internals 389

Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 17: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

NOTES1 Design Loads Trays pans drawoff boxes or

similar intemals shall be designed using a corrodedthickness to support their own weight plus thefollowing live loadsa Fractionation trays Design live load shall be the

greater of 20 PSF (98 KgSq meter) or the weightof water 2 (50 mm) over the highest weirsetting

b Areas under downcomers Design live load shallbe the greater of 64 PSF (314 Kg Sq meter) ora head of water one half the height of thedowncomer

c Pans (accumulator and drawoff pans) Designlive load shall be the greater of 1 PSI (700 Kg Sqmeter) or the weight of water at the maximumoperating level of the pan

d Baffles With no operating liquid level shall usea design live load of 1 PSI (700 KgSq meter) onthe projected horizontal area or actual impulseforce whichever is greater

2 Maintenance Loads Tray support members (allbeams support clips etc) shall be designed fora concentrated load of 300 Lbs (135 Kg) at any pointon the installed assembly The design shall be basedon the corroded thicknesses and an allowable stressof 9 Fy For maintenance loads stresses in the trayplates need not be considered

3 Uplift resistance Typical design of uplift for traysand packing is 25 PSI (17 Millibar) For serviceswhere excessive uplift can occur a higher upliftresistance may be used Examples of higher upliftfactors are as follows

a Crude and FCC side strippers 1 PSI (70 millibar)b Vacuum tower stripping trays overflash

collector wash trays or beds 2 PSI (140Millibar)

c Collectiors and packed beds above the washsection of a vacuum Tower 1 PSI (70 Millibar)

4 Failure sequence Tray assemblies wheneverpossible shall be designed so that failure will occurin the following ordera Tray manwaysb Tray deck active areasc Minor beams and downcomersd Major beams (defined as beams 10ft (3 Meters)

or longer or beams which extend across a vesselwithout interruption regardless of length)

5 Allowable stresses Allowable unit stress shall bebased on yield strength Fy at design temperaturewith AISC factors for tension bearing shear etc

6 Allowable Deflection The calculated combineddeflection of trays and support beams due to oper-ating loads shall not exceed the lesser of 1900 of thevessel diameter (in inches) or 316 (5 mm)

RECOMMENDED TRAY SPACING amp MANWAY SIZE

COLUMN DIA

(FT)

TRAY SPACING

(IN)

MANWAY

SPACING

MIN MANWAY

SIZE

25 to 16 24 Every 10 trays 18 in

16 to 24 30 Every 8 trays 20 in

24 to 32 36 Every 6 trays 24 in

32 and larger 42 Every 4 trays 30 in

374 Pressure Vessel Design Manual

Procedure 5-10 Flow Over Weirs

Notation

b frac14 width ftH frac14 static head of liquid ftQ frac14 discharge rate cu ftsecV frac14 velocity of approach ftsecH0 frac14 head correction per Table 5-22

Calculations

Discharge Q

bull For a full-length weir (Case 1)

Q frac14 333beth15 HTHORNbull For a contracted weir (Case 2)

Q frac14 333beth15 HTHORNbull For a V-notch weir (Case 3)

Q frac14 633 H

bull For a Cippoletti weir (Case 4)

Q frac14 3367beth15 HTHORN

Notes

1 Assumes troughs are level

Case 1 Full-Width Weir

V frac14 1ndash2 ftsec at 4 H upstream

Case 2 Contracted Weir

V frac14 1ndash2 ftsec at 3 H upstream

Case 3 V-Notch Weir

V frac14 5 ftsec at 5 H upstream

Case 4 Cippoletti Weir

V frac14 1ndash2 ftsec at 4 H upstream

Table 5-21Head correction for velocity of approach

V 04 06 08 10 12 14 16 18 20

Hrsquo 0002 0005 001 0015 0023 003 004 005 0062

V 22 24 26 28 30 32 34 36 38

Hrsquo 0075 0089 0105 0122 014 015 0179 0201 0213

Vessel Internals 375

Procedure 5-11 Design of Demisters

Demister pads or mist eliminators are important inter-nals in process vessels Anytime there is a continuous twophase flow vapor and liquid there is the possibility forliquid entrainment If it is desirable to separate the liquidand vapor or prevent liquid carryover in the vapor streamthe velocity must be kept sufficiently low to allow the liquiddroplets to fall out of the vapor stream Demister pads areeffective entrainment separators which allow operation atvapor velocities that would otherwise be excessive

ldquoVapor disengagementrdquo can be accomplished withouta demister but the vessel must be made much larger toaccomplish the same degree of separation This is knownas gravity separation

Demister pads are used in a wide variety of processvessels Good performance can be achieved at velocitiesof 30 to 110 of optimum

Demister pads can be used in vertical or horizontalvessels The mesh pad orientation can be either vertical orhorizontal in a vertical or horizontal vessel

A wire mesh demister consists of a knitted wire matmounted on a light weight support grid The mesh is madeby weaving small diameter metal wire into a mesh Padsmay be made out of metal or plastics Metal type includecarbon steel stainless steel monel and others Plasticmaterials include PTFE HDPE and PP

Pressure drop is usually extremely low in the range of1 inch of water column maximum The pressure drop isnormally so low that it is ignored in design

Vapor disengagement is dependent on the velocity ofthe stream The most common equation for determining theallowable vapor velocity for two phase flows is as follows

Va frac14 K frac12ethrL rVTHORN=rV1=2

Where

Va frac14 Allowable vapor velocity FtSecK frac14 Constant or coefficientrL frac14 Density of liquid PCFrV frac14 Density of vapor PCF

Notes

1 The mesh pad shall be in one piece or sectional asrequired for insertion through the vessel manwayEach pad section shall be removable through thevessel manhole

2 Layers shall not be more than 6 inches thick3 Where more than one layer is required all joints

shall be staggered

4 One piece circular pads may be spiral in form5 Each section of mesh shall include a grid on one or

both sides The grid wire andor fastening deviceshall be the same material as the mesh pad Top andbottom grids shall be constructed of frac14 inch diam-eter rods welded to ⅛ inch by 1 inch bars Themaximum gap between mesh pad and grids shall befrac12 inch for diameters less than 84 inches and 1 inchfor larger diameters

6 Estimate grid weights as 3 PSF7 Tie down wires shall be 1=16 inch diameter wire thru

frac14 inch diameter holes on 4 inch centers Tie wiresshould not be pushed through the pad as this couldcause leak paths

8 Pressure drop across mist eliminator shall beassumed as 02 PSI for support design

9 Unless otherwise specified support rings shall be2 inches wide for pads 84 inches in diameter andless and 3 inches wide for larger diameters

10 The mist eliminator shall be a tight fit against theshell or enclosure as well as between sections Meshpads shall be⅜ inches oversize all around for a forcefit against the enclosure No gaps are allowed

11 Vessel fabricator shall provide the mesh and gridsas well as any stiffeners required

12 The Mist eliminator shall be specified as either topor bottom removable

13 ldquoKrdquo is a constant or coefficient that is a functionof the efficiency of the separation K-values rangefrom 04 to 43 but are generally in the 15 to 35range The K-value is affected by pressure type ofpad size of wire type of vessel and disengagingheight For pressure applications the K-valueshould be decreased by 01 for every 100 PSI ofpressure after 100 PSI

14 Wire diameter for the mesh pad itself vary from0003 to 0016 inches

15 The free volume of demisters range from 92 to994

16 The density of the pads ranges from 3 to 33 PCF17 The NSA (nominal surface area) is the surface area

to volume ratio Ft2 Ft3 and is an important indi-cator of performance Ratios range from 50 to 600

18 To obtain higher separation efficiencies the wirediameter is decreased and the density and thicknessare increased

19 Typical width of sections for multi-section pads is12 inches (300 mm) but may vary by manufacturer

376 Pressure Vessel Design Manual

A Horizontal element B Vertical elements

Vertical vessels

Manway

Plate-Pakunit

Meshpad

Drain tubewith seal trap

END VIEW

END VIEW

SIDE VIEW

SIDE VIEW

C Vertical element

Horizontal vessels

D Horizontal element

Figure 5-15 Typical demister configurations in vessels

Vessel Internals 377

d

E Axial entrance

H gt (23) D ndash d

H gt D2 + d(minimum 24rdquo)

H gt D2 ndash d2

H gt D2 + d

H gt D2 ndash d2

h gt d

D

D Side entrance

d

D

B Axial exit

d

D

Φ lt 45ordm

Φ lt 45ordm

C Reverse axial exit

d

A Side exit

D

Figure 5-16 Guidelines for maintaining even flow distribution in vessels with axial flow

378 Pressure Vessel Design Manual

wire mesh

Top grid

Bottom grid

Vertical 14rdquo rodsspaced 12rdquo to 18rdquocenter to center

12rdquo to 18rdquosegmentwidth

18rdquo x 1rdquo flat bars14rdquo rodsspaced 6rdquocenterto center

Manway

Support ring

Support beam

Tie wires

Figure 5-17 Typical mesh pad construction and installation

Vessel Internals 379

Table 5-22Properties of demister pads

Type NSA (1) Ft2 Ft3 Density Pcf Wire Dia in Free Area York Style No Remarks

A 48 5 0011 99 931 High Throughput

B 65 7 0011 986 531 Economy Performance

C 85 9 0011 982 431 Standard - Good All

Around

D 110 108 0011 977 421 Heavy Duty

E 140 8 0006 984 326 Super High Efficiency -

Fine Mist

F 163 0006 94 371 Liquid - Liquid Coalescer

G 450 20 00045 959

H 600 27 00045 945

Notes

1 NSA frac14 Nominal Surface Area

Table 5-23Values of K (Note 13)

Based on Pressure

Pressure (PSIa) Vacuum (In Hg)

Pressure (PSIa) K Vacuum (In Hg) K

15 035 30 035

50 034 20 032

100 032 10 028

200 031 5 023

300 03 1 017

500 028 lt1 017

1000 027

gt1000 027

Based on Disengaging Height

Disengaging Height in K Disengaging Height in K

3 012 9 032

4 015 10 035

5 019 11 038

6 022 12 04

7 025 13 042

8 029 14 043

Based on Application

Vertical Vessels Horizontal Vessels

Type K Type K

General 035 General 035

Compressor Suction Drums 025 Steam Drums 025

Steam Drums 015

380 Pressure Vessel Design Manual

Procedure 5-12 Design of Baffles [10]

Baffles are frequently used in pressure vessels eithervertical or horizontal to divide the interior volume intodifferent compartments These compartments may beused to segregate liquids or provide overflow weirs forthe separation of liquids Baffles may be stiffened orunstiffened When welded across the entire cross sectionof the vessel they must be checked that they are notunduly restricting the diametral expansion of the vesselIf the unrestrained radial expansion of the vessel exceedsthat of the baffle by more than 1=16 in (⅛ in on thediameter) then a ldquoflexiblerdquo type of connection betweenthe vessel shell and the baffle should be utilized Variousflexible attachment designs are shown within theprocedure

Baffles should always be designed in the corrodedcondition It is typical for welded baffles to be designedwith a full corrosion allowance on both sides If the baffleis bolted in then one-half the full corrosion allowancemay be applied to each side the logic being that a boltedbaffle is removable and therefore replaceable

The majority of baffles are flat and as a result are veryinefficient from a strength standpoint Deflection is thegoverning case for flat plates loaded on one side Thepreference is to have unstiffened baffles and they shouldalways be the first choice This will be acceptable forsmall baffles However for larger baffles as the bafflethickness becomes excessive stiffeners offer a moreeconomical design Therefore stiffeners are frequentlyused to stiffen the baffle to prevent the thickness of thebaffle from becoming excessive The number size andspacing of stiffeners are dependent on the baffle thicknessselected There is a continual trade-off between bafflethickness and stiffener parameters

The design of a baffle with stiffeners is an iterativeprocess The procedure for the design of the stiffeners isfirst to divide the baffle into ldquopanelrdquo sections that are rigidenough to withstand the pressure applied on one sideEach individual panel is checked as a flat plate of thedimensions of the panel The stiffeners are assumed to bestrong enough to provide the necessary edge support forthe panel

The stiffeners themselves are designed next A sectionof the baffle is assumed as acting with the stiffener and ascontributing to the overall stiffness This combinedsection is known as the composite stiffener Thecomposite section is checked for stress and deflectionBoth vertical and horizontal stiffeners can be added asrequired

If required an alternate design is assumed based ona thicker or thinner baffle and checked until a satisfactorydesign is found There is no ldquorightrdquo answer however itshould be noted that the thinner the baffle the greater thenumber of stiffeners The lightest overall weight isprobably the ldquobestrdquo design but may not be the leastexpensive due to the welding costs in attaching thestiffeners

One alternative to a flat baffle with stiffeners is to go toa curved baffle A curved baffle works best as a verticalbaffle in a vertical vessel The curved baffle takes pressurefrom either side wall If the pressure is on the concave sidethe baffle is in tension If the pressure is on the convexside the baffle is in compression

There are various tables given in this procedure for flatplate coefficients Flat plate coefficients are utilized todetermine the baffle thickness or a panel thickness Eachtable is specific for a given condition and loading

Vessel Internals 381

Notation

Ap frac14 area of baffle working with stiffener in2

As frac14 area of stiffener in2

Cp frac14 distance from centroid of composite section topanel in

Cs frac14 distance from centroid of composite section tostiffener in

E frac14 modulus of elasticity psiFb frac14 allowable bending stress psiI frac14 moment of inertia composite in4

Is frac14 moment of inertia stiffener in4

l frac14 length of baffle that works with the stiffener inM frac14 moment in-lbn frac14 number of welds attaching stiffenerP frac14 vessel internal pressure psigp frac14 maximum uniform pressure psipn frac14 uniform pressure at any elevation an psiRm frac14 vessel mean radius inSg frac14 specific gravity of contentst frac14 thickness shell intb frac14 thickness baffle ints frac14 thickness stiffener inV frac14 shear load lbw frac14 required fillet weld size ina frac14 thermal coefficient of expansion ininF

bg frac14 flat plate coefficientsDT frac14 differential temperature (design temperature

minus 70F) Fsb frac14 bending stress in baffle psiss frac14 bending stress in stiffener psi

6n frac14 radial expansion ind frac14 deflection inda frac14 maximum allowable deflection in

Baffle Dimensions

382 Pressure Vessel Design Manual

Table 5-24Flat plate coefficients

Vessel Internals 383

Unstiffened Baffle Check

bull Find load p

p frac14 624aSg144

bull Find baffle thickness tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

s

bull Find baffle deflection d

d frac14 pg1b4

Et3b

Limit deflection to the smaller of tb2 or b360 Ifdeflection is excessive then

a Increase the baffle thicknessb Add stiffenersc Go to curved baffle design

If stiffeners are added the first step is to find themaximum ldquoardquo and ldquobrdquo dimensions that will meet theallowable deflection for a given panel size This willestablish the stiffener spacing for both horizontal andvertical stiffeners The ultimate design is a balancebetween baffle thickness stiffener spacing and stiffenersize

Thermal Check of Baffle

bull Vessel radial expansion due to pressure

D1 frac14 085PRm

tE

bull Vessel radial expansion due to temperature

D2 frac14 Rma DT

bull Thermal expansion of baffle

D3 frac14 05ba DT

bull Differential expansion

D4 frac14 D1 thorn D2 D3

Stiffener Design

Divide baffle into panels to limit deflection to the lesserof tb2 or b360 Deflection is calculated based on theappropriate Cases 1 through 3

bull Check baffle for panel size a0 b0bull Check stiffener for length a or b

Recommendations for attaching stiffeners

Benefits Provides added stiffness and no corrosiontrap

Figure 5-18 Example of stiffener layout

384 Pressure Vessel Design Manual

As frac14 tsh

Ap frac14 tbl

IS frac14 tsh3

12

Cp frac14 AsyAs thorn Ap

thorn tb2

Cs frac14 ethhthorn tbTHORN Cp

I frac14 IS thorn Apt2b12

thorn AsApy2

As thorn Ap

lsquo frac14 lesser of 32tb or stiffener spacing

Stresses in BaffleStiffener

sp frac14 MCp

I

ss frac14 MCs

I

Size Welds Attaching Stiffeners

For E70XX Welds

w frac14 Vdy11 200In

Table 5-25Intermittent Welds

Percent of

Continuous Weld

Length of Intermittent Welds

and Distance Between Centers

75 3e4

66 4e6

60 3e5

57 4e7

50 2e4 3e6 4e8

44 4e9

43 3e7

40 2e5 4e10

37 3e8

33 2e6 3e9 4e12

Reprinted by permission of the James F Lincoln Arc Welding

Foundation

Vessel Internals 385

For E60XX Welds

w frac14 Vdy9600In

Sample Problem

bull Given Horizontal vessel with a vertical baffle

P frac14 250 psig

DT frac14 500F

Material frac14 SA-516-70

Ca frac14 0125 in

JE frac14 10

E frac14 273 106 psi

a frac14 7124 10-6 in=in=FFy frac14 308 ksi

D frac14 240 in

Fb frac14 066 Fy frac14 2033 ksi

Rm frac14 120938

ts frac14 175 in

Sg frac14 08

a frac14 15 ft

DT frac14 500 70 frac14 430F

bull Find baffle thickness without stiffener

p frac14 624aSg144

frac14 52 psi

a

bratio frac14 15=20 frac14 075

from Table 5-25 Case 1

b1 frac14 016 g1 frac14 0033

bull Thickness of baffle tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

sfrac14

ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi016eth52THORN2402

20 330

s

tb frac14 153thorn 025 frac14 178

No good Use stiffeners

bull Assume a suitable baffle thickness and determinemaximum panel size

tb frac14 075 in corroded

maximum panel size frac14 4ft 4ft

bull Maximum pressure p

p frac14 13eth624THORN08144

frac14 45 psi

a

bfrac14 4

4frac14 1

See Table 5-25 Case 3

b3 frac14 0287 g3 frac14 00443

sb frac14 b3pb2n

t2

frac14 0287eth45THORN4820752

frac14 5290 psi lt 20 333 psiFigure 5-19 Sample problem

386 Pressure Vessel Design Manual

d frac14 g3

pE

b4nt3

frac14 00443

45

273 106

484

0753

frac14 0092 in lt 0375 in

Balance OK by inspection

bull Assume a layout where the maximum stiffenerspacing is 4 ft

(4) horizontal stiffeners(4) vertical stiffeners(18) panels

bull Check horizontal stiffeners

Dimensions

a1 frac14 3 ft b1 frac14 4 ft

a2 frac14 4 ft b2 frac14 4 ft

a3 frac14 4 ft b3 frac14 12 ft

a4 frac14 4 ft b4 frac14 196 ft

a5 frac14 13 ft

a6 frac14 148ft

bull Assume stiffener size 1 in 4 in

y frac14 2375 in

As frac14 tsh frac14 1eth4THORN frac14 4 in2

l frac14 32tb frac14 32eth075THORN frac14 24 in lt 48 in

AP frac14 tbl frac14 07524 frac14 18 in2

Is frac14 bh3

12frac14 1

43

12frac14 533 in4

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 533thorn 0633thorn 1846 frac14 2442 in4

Cp frac14 AsyAs thorn Ap

thorn tb2

frac14 4eth2375THORN22

thorn 0752

frac14 0807 in

Cs frac14 hthorn tb

Cp

frac14 4thorn 075 0807 frac14 3943

Check deflections

Deflections exceed allowable No good

bull Assume a larger stiffener size WT9 593

tf frac14 106 025 frac14 081

tw frac14 0625 025 frac14 0375

bull Check corroded thickness to find properties ofcorroded section This section would be equivalent toa WT9 30 Properties are

As frac14 882 in2

Is frac14 647 in4

Cs frac14 216 in

H frac14 9 in

Cp frac14 hthorn tb Cs

frac14 9thorn 075 216 frac14 759 in

Figure 5-20 Battle layout for sample problem

Item bn pn d

1 2352 104 149

2 2352 243 349

3 144 381 0767

Vessel Internals 387

y frac14 Cp tb2

frac14 7215 in

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 647thorn 0844thorn 30814 frac14 3737 in4

bull Check stresses and deflections See results in Table5-27

bull Stresses and deflections are acceptablebull Check welds

d frac14 ts thorn 2tw frac14 0375thorn 2eth0323THORN frac14 102

y frac14 7215 in

I frac14 3737 in4

n frac14 2

w frac14 Vdy11 200In

frac14 6681eth102THORN721511 200eth3737THORN2

frac14 0005thorn 0125 frac14 013 in

bull Check thermal expansion of baffle

D1 frac14 085PRm

tEfrac14 085eth250THORN120938

175eth273 106THORNfrac14 000054 in

D2 frac14 Rma DT frac14 1209387124 106430

frac14 0370 in

D3 frac14 05ba DT frac14 05240

7124 106430

frac14 0367 in

D4 frac14 D1 thorn D2 D3 frac14 000054thorn 0370 0367

frac14 00035 lt 006 in

Table 5-26Summary of Results for Stress and Deflection in Composite Stiffeners for Sample Problem

Item Orientation an bn pn M d V sp ss

1 Horiz 2352 d 104 172595 009 2690 3504 997

2 Horiz 2352 d 243 403275 021 6287 8186 2330

3 Horiz 144 d 381 237012 0045 6035 4811 1370

4 Vert d 156 450 154674 0037 5648 3141 894

5 Vert d 1776 513 228539 0072 6681 6681 1320

Figure 5-21 Details of weld attaching stiffener

388 Pressure Vessel Design Manual

Vessel Internals 389

Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 18: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

Procedure 5-10 Flow Over Weirs

Notation

b frac14 width ftH frac14 static head of liquid ftQ frac14 discharge rate cu ftsecV frac14 velocity of approach ftsecH0 frac14 head correction per Table 5-22

Calculations

Discharge Q

bull For a full-length weir (Case 1)

Q frac14 333beth15 HTHORNbull For a contracted weir (Case 2)

Q frac14 333beth15 HTHORNbull For a V-notch weir (Case 3)

Q frac14 633 H

bull For a Cippoletti weir (Case 4)

Q frac14 3367beth15 HTHORN

Notes

1 Assumes troughs are level

Case 1 Full-Width Weir

V frac14 1ndash2 ftsec at 4 H upstream

Case 2 Contracted Weir

V frac14 1ndash2 ftsec at 3 H upstream

Case 3 V-Notch Weir

V frac14 5 ftsec at 5 H upstream

Case 4 Cippoletti Weir

V frac14 1ndash2 ftsec at 4 H upstream

Table 5-21Head correction for velocity of approach

V 04 06 08 10 12 14 16 18 20

Hrsquo 0002 0005 001 0015 0023 003 004 005 0062

V 22 24 26 28 30 32 34 36 38

Hrsquo 0075 0089 0105 0122 014 015 0179 0201 0213

Vessel Internals 375

Procedure 5-11 Design of Demisters

Demister pads or mist eliminators are important inter-nals in process vessels Anytime there is a continuous twophase flow vapor and liquid there is the possibility forliquid entrainment If it is desirable to separate the liquidand vapor or prevent liquid carryover in the vapor streamthe velocity must be kept sufficiently low to allow the liquiddroplets to fall out of the vapor stream Demister pads areeffective entrainment separators which allow operation atvapor velocities that would otherwise be excessive

ldquoVapor disengagementrdquo can be accomplished withouta demister but the vessel must be made much larger toaccomplish the same degree of separation This is knownas gravity separation

Demister pads are used in a wide variety of processvessels Good performance can be achieved at velocitiesof 30 to 110 of optimum

Demister pads can be used in vertical or horizontalvessels The mesh pad orientation can be either vertical orhorizontal in a vertical or horizontal vessel

A wire mesh demister consists of a knitted wire matmounted on a light weight support grid The mesh is madeby weaving small diameter metal wire into a mesh Padsmay be made out of metal or plastics Metal type includecarbon steel stainless steel monel and others Plasticmaterials include PTFE HDPE and PP

Pressure drop is usually extremely low in the range of1 inch of water column maximum The pressure drop isnormally so low that it is ignored in design

Vapor disengagement is dependent on the velocity ofthe stream The most common equation for determining theallowable vapor velocity for two phase flows is as follows

Va frac14 K frac12ethrL rVTHORN=rV1=2

Where

Va frac14 Allowable vapor velocity FtSecK frac14 Constant or coefficientrL frac14 Density of liquid PCFrV frac14 Density of vapor PCF

Notes

1 The mesh pad shall be in one piece or sectional asrequired for insertion through the vessel manwayEach pad section shall be removable through thevessel manhole

2 Layers shall not be more than 6 inches thick3 Where more than one layer is required all joints

shall be staggered

4 One piece circular pads may be spiral in form5 Each section of mesh shall include a grid on one or

both sides The grid wire andor fastening deviceshall be the same material as the mesh pad Top andbottom grids shall be constructed of frac14 inch diam-eter rods welded to ⅛ inch by 1 inch bars Themaximum gap between mesh pad and grids shall befrac12 inch for diameters less than 84 inches and 1 inchfor larger diameters

6 Estimate grid weights as 3 PSF7 Tie down wires shall be 1=16 inch diameter wire thru

frac14 inch diameter holes on 4 inch centers Tie wiresshould not be pushed through the pad as this couldcause leak paths

8 Pressure drop across mist eliminator shall beassumed as 02 PSI for support design

9 Unless otherwise specified support rings shall be2 inches wide for pads 84 inches in diameter andless and 3 inches wide for larger diameters

10 The mist eliminator shall be a tight fit against theshell or enclosure as well as between sections Meshpads shall be⅜ inches oversize all around for a forcefit against the enclosure No gaps are allowed

11 Vessel fabricator shall provide the mesh and gridsas well as any stiffeners required

12 The Mist eliminator shall be specified as either topor bottom removable

13 ldquoKrdquo is a constant or coefficient that is a functionof the efficiency of the separation K-values rangefrom 04 to 43 but are generally in the 15 to 35range The K-value is affected by pressure type ofpad size of wire type of vessel and disengagingheight For pressure applications the K-valueshould be decreased by 01 for every 100 PSI ofpressure after 100 PSI

14 Wire diameter for the mesh pad itself vary from0003 to 0016 inches

15 The free volume of demisters range from 92 to994

16 The density of the pads ranges from 3 to 33 PCF17 The NSA (nominal surface area) is the surface area

to volume ratio Ft2 Ft3 and is an important indi-cator of performance Ratios range from 50 to 600

18 To obtain higher separation efficiencies the wirediameter is decreased and the density and thicknessare increased

19 Typical width of sections for multi-section pads is12 inches (300 mm) but may vary by manufacturer

376 Pressure Vessel Design Manual

A Horizontal element B Vertical elements

Vertical vessels

Manway

Plate-Pakunit

Meshpad

Drain tubewith seal trap

END VIEW

END VIEW

SIDE VIEW

SIDE VIEW

C Vertical element

Horizontal vessels

D Horizontal element

Figure 5-15 Typical demister configurations in vessels

Vessel Internals 377

d

E Axial entrance

H gt (23) D ndash d

H gt D2 + d(minimum 24rdquo)

H gt D2 ndash d2

H gt D2 + d

H gt D2 ndash d2

h gt d

D

D Side entrance

d

D

B Axial exit

d

D

Φ lt 45ordm

Φ lt 45ordm

C Reverse axial exit

d

A Side exit

D

Figure 5-16 Guidelines for maintaining even flow distribution in vessels with axial flow

378 Pressure Vessel Design Manual

wire mesh

Top grid

Bottom grid

Vertical 14rdquo rodsspaced 12rdquo to 18rdquocenter to center

12rdquo to 18rdquosegmentwidth

18rdquo x 1rdquo flat bars14rdquo rodsspaced 6rdquocenterto center

Manway

Support ring

Support beam

Tie wires

Figure 5-17 Typical mesh pad construction and installation

Vessel Internals 379

Table 5-22Properties of demister pads

Type NSA (1) Ft2 Ft3 Density Pcf Wire Dia in Free Area York Style No Remarks

A 48 5 0011 99 931 High Throughput

B 65 7 0011 986 531 Economy Performance

C 85 9 0011 982 431 Standard - Good All

Around

D 110 108 0011 977 421 Heavy Duty

E 140 8 0006 984 326 Super High Efficiency -

Fine Mist

F 163 0006 94 371 Liquid - Liquid Coalescer

G 450 20 00045 959

H 600 27 00045 945

Notes

1 NSA frac14 Nominal Surface Area

Table 5-23Values of K (Note 13)

Based on Pressure

Pressure (PSIa) Vacuum (In Hg)

Pressure (PSIa) K Vacuum (In Hg) K

15 035 30 035

50 034 20 032

100 032 10 028

200 031 5 023

300 03 1 017

500 028 lt1 017

1000 027

gt1000 027

Based on Disengaging Height

Disengaging Height in K Disengaging Height in K

3 012 9 032

4 015 10 035

5 019 11 038

6 022 12 04

7 025 13 042

8 029 14 043

Based on Application

Vertical Vessels Horizontal Vessels

Type K Type K

General 035 General 035

Compressor Suction Drums 025 Steam Drums 025

Steam Drums 015

380 Pressure Vessel Design Manual

Procedure 5-12 Design of Baffles [10]

Baffles are frequently used in pressure vessels eithervertical or horizontal to divide the interior volume intodifferent compartments These compartments may beused to segregate liquids or provide overflow weirs forthe separation of liquids Baffles may be stiffened orunstiffened When welded across the entire cross sectionof the vessel they must be checked that they are notunduly restricting the diametral expansion of the vesselIf the unrestrained radial expansion of the vessel exceedsthat of the baffle by more than 1=16 in (⅛ in on thediameter) then a ldquoflexiblerdquo type of connection betweenthe vessel shell and the baffle should be utilized Variousflexible attachment designs are shown within theprocedure

Baffles should always be designed in the corrodedcondition It is typical for welded baffles to be designedwith a full corrosion allowance on both sides If the baffleis bolted in then one-half the full corrosion allowancemay be applied to each side the logic being that a boltedbaffle is removable and therefore replaceable

The majority of baffles are flat and as a result are veryinefficient from a strength standpoint Deflection is thegoverning case for flat plates loaded on one side Thepreference is to have unstiffened baffles and they shouldalways be the first choice This will be acceptable forsmall baffles However for larger baffles as the bafflethickness becomes excessive stiffeners offer a moreeconomical design Therefore stiffeners are frequentlyused to stiffen the baffle to prevent the thickness of thebaffle from becoming excessive The number size andspacing of stiffeners are dependent on the baffle thicknessselected There is a continual trade-off between bafflethickness and stiffener parameters

The design of a baffle with stiffeners is an iterativeprocess The procedure for the design of the stiffeners isfirst to divide the baffle into ldquopanelrdquo sections that are rigidenough to withstand the pressure applied on one sideEach individual panel is checked as a flat plate of thedimensions of the panel The stiffeners are assumed to bestrong enough to provide the necessary edge support forthe panel

The stiffeners themselves are designed next A sectionof the baffle is assumed as acting with the stiffener and ascontributing to the overall stiffness This combinedsection is known as the composite stiffener Thecomposite section is checked for stress and deflectionBoth vertical and horizontal stiffeners can be added asrequired

If required an alternate design is assumed based ona thicker or thinner baffle and checked until a satisfactorydesign is found There is no ldquorightrdquo answer however itshould be noted that the thinner the baffle the greater thenumber of stiffeners The lightest overall weight isprobably the ldquobestrdquo design but may not be the leastexpensive due to the welding costs in attaching thestiffeners

One alternative to a flat baffle with stiffeners is to go toa curved baffle A curved baffle works best as a verticalbaffle in a vertical vessel The curved baffle takes pressurefrom either side wall If the pressure is on the concave sidethe baffle is in tension If the pressure is on the convexside the baffle is in compression

There are various tables given in this procedure for flatplate coefficients Flat plate coefficients are utilized todetermine the baffle thickness or a panel thickness Eachtable is specific for a given condition and loading

Vessel Internals 381

Notation

Ap frac14 area of baffle working with stiffener in2

As frac14 area of stiffener in2

Cp frac14 distance from centroid of composite section topanel in

Cs frac14 distance from centroid of composite section tostiffener in

E frac14 modulus of elasticity psiFb frac14 allowable bending stress psiI frac14 moment of inertia composite in4

Is frac14 moment of inertia stiffener in4

l frac14 length of baffle that works with the stiffener inM frac14 moment in-lbn frac14 number of welds attaching stiffenerP frac14 vessel internal pressure psigp frac14 maximum uniform pressure psipn frac14 uniform pressure at any elevation an psiRm frac14 vessel mean radius inSg frac14 specific gravity of contentst frac14 thickness shell intb frac14 thickness baffle ints frac14 thickness stiffener inV frac14 shear load lbw frac14 required fillet weld size ina frac14 thermal coefficient of expansion ininF

bg frac14 flat plate coefficientsDT frac14 differential temperature (design temperature

minus 70F) Fsb frac14 bending stress in baffle psiss frac14 bending stress in stiffener psi

6n frac14 radial expansion ind frac14 deflection inda frac14 maximum allowable deflection in

Baffle Dimensions

382 Pressure Vessel Design Manual

Table 5-24Flat plate coefficients

Vessel Internals 383

Unstiffened Baffle Check

bull Find load p

p frac14 624aSg144

bull Find baffle thickness tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

s

bull Find baffle deflection d

d frac14 pg1b4

Et3b

Limit deflection to the smaller of tb2 or b360 Ifdeflection is excessive then

a Increase the baffle thicknessb Add stiffenersc Go to curved baffle design

If stiffeners are added the first step is to find themaximum ldquoardquo and ldquobrdquo dimensions that will meet theallowable deflection for a given panel size This willestablish the stiffener spacing for both horizontal andvertical stiffeners The ultimate design is a balancebetween baffle thickness stiffener spacing and stiffenersize

Thermal Check of Baffle

bull Vessel radial expansion due to pressure

D1 frac14 085PRm

tE

bull Vessel radial expansion due to temperature

D2 frac14 Rma DT

bull Thermal expansion of baffle

D3 frac14 05ba DT

bull Differential expansion

D4 frac14 D1 thorn D2 D3

Stiffener Design

Divide baffle into panels to limit deflection to the lesserof tb2 or b360 Deflection is calculated based on theappropriate Cases 1 through 3

bull Check baffle for panel size a0 b0bull Check stiffener for length a or b

Recommendations for attaching stiffeners

Benefits Provides added stiffness and no corrosiontrap

Figure 5-18 Example of stiffener layout

384 Pressure Vessel Design Manual

As frac14 tsh

Ap frac14 tbl

IS frac14 tsh3

12

Cp frac14 AsyAs thorn Ap

thorn tb2

Cs frac14 ethhthorn tbTHORN Cp

I frac14 IS thorn Apt2b12

thorn AsApy2

As thorn Ap

lsquo frac14 lesser of 32tb or stiffener spacing

Stresses in BaffleStiffener

sp frac14 MCp

I

ss frac14 MCs

I

Size Welds Attaching Stiffeners

For E70XX Welds

w frac14 Vdy11 200In

Table 5-25Intermittent Welds

Percent of

Continuous Weld

Length of Intermittent Welds

and Distance Between Centers

75 3e4

66 4e6

60 3e5

57 4e7

50 2e4 3e6 4e8

44 4e9

43 3e7

40 2e5 4e10

37 3e8

33 2e6 3e9 4e12

Reprinted by permission of the James F Lincoln Arc Welding

Foundation

Vessel Internals 385

For E60XX Welds

w frac14 Vdy9600In

Sample Problem

bull Given Horizontal vessel with a vertical baffle

P frac14 250 psig

DT frac14 500F

Material frac14 SA-516-70

Ca frac14 0125 in

JE frac14 10

E frac14 273 106 psi

a frac14 7124 10-6 in=in=FFy frac14 308 ksi

D frac14 240 in

Fb frac14 066 Fy frac14 2033 ksi

Rm frac14 120938

ts frac14 175 in

Sg frac14 08

a frac14 15 ft

DT frac14 500 70 frac14 430F

bull Find baffle thickness without stiffener

p frac14 624aSg144

frac14 52 psi

a

bratio frac14 15=20 frac14 075

from Table 5-25 Case 1

b1 frac14 016 g1 frac14 0033

bull Thickness of baffle tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

sfrac14

ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi016eth52THORN2402

20 330

s

tb frac14 153thorn 025 frac14 178

No good Use stiffeners

bull Assume a suitable baffle thickness and determinemaximum panel size

tb frac14 075 in corroded

maximum panel size frac14 4ft 4ft

bull Maximum pressure p

p frac14 13eth624THORN08144

frac14 45 psi

a

bfrac14 4

4frac14 1

See Table 5-25 Case 3

b3 frac14 0287 g3 frac14 00443

sb frac14 b3pb2n

t2

frac14 0287eth45THORN4820752

frac14 5290 psi lt 20 333 psiFigure 5-19 Sample problem

386 Pressure Vessel Design Manual

d frac14 g3

pE

b4nt3

frac14 00443

45

273 106

484

0753

frac14 0092 in lt 0375 in

Balance OK by inspection

bull Assume a layout where the maximum stiffenerspacing is 4 ft

(4) horizontal stiffeners(4) vertical stiffeners(18) panels

bull Check horizontal stiffeners

Dimensions

a1 frac14 3 ft b1 frac14 4 ft

a2 frac14 4 ft b2 frac14 4 ft

a3 frac14 4 ft b3 frac14 12 ft

a4 frac14 4 ft b4 frac14 196 ft

a5 frac14 13 ft

a6 frac14 148ft

bull Assume stiffener size 1 in 4 in

y frac14 2375 in

As frac14 tsh frac14 1eth4THORN frac14 4 in2

l frac14 32tb frac14 32eth075THORN frac14 24 in lt 48 in

AP frac14 tbl frac14 07524 frac14 18 in2

Is frac14 bh3

12frac14 1

43

12frac14 533 in4

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 533thorn 0633thorn 1846 frac14 2442 in4

Cp frac14 AsyAs thorn Ap

thorn tb2

frac14 4eth2375THORN22

thorn 0752

frac14 0807 in

Cs frac14 hthorn tb

Cp

frac14 4thorn 075 0807 frac14 3943

Check deflections

Deflections exceed allowable No good

bull Assume a larger stiffener size WT9 593

tf frac14 106 025 frac14 081

tw frac14 0625 025 frac14 0375

bull Check corroded thickness to find properties ofcorroded section This section would be equivalent toa WT9 30 Properties are

As frac14 882 in2

Is frac14 647 in4

Cs frac14 216 in

H frac14 9 in

Cp frac14 hthorn tb Cs

frac14 9thorn 075 216 frac14 759 in

Figure 5-20 Battle layout for sample problem

Item bn pn d

1 2352 104 149

2 2352 243 349

3 144 381 0767

Vessel Internals 387

y frac14 Cp tb2

frac14 7215 in

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 647thorn 0844thorn 30814 frac14 3737 in4

bull Check stresses and deflections See results in Table5-27

bull Stresses and deflections are acceptablebull Check welds

d frac14 ts thorn 2tw frac14 0375thorn 2eth0323THORN frac14 102

y frac14 7215 in

I frac14 3737 in4

n frac14 2

w frac14 Vdy11 200In

frac14 6681eth102THORN721511 200eth3737THORN2

frac14 0005thorn 0125 frac14 013 in

bull Check thermal expansion of baffle

D1 frac14 085PRm

tEfrac14 085eth250THORN120938

175eth273 106THORNfrac14 000054 in

D2 frac14 Rma DT frac14 1209387124 106430

frac14 0370 in

D3 frac14 05ba DT frac14 05240

7124 106430

frac14 0367 in

D4 frac14 D1 thorn D2 D3 frac14 000054thorn 0370 0367

frac14 00035 lt 006 in

Table 5-26Summary of Results for Stress and Deflection in Composite Stiffeners for Sample Problem

Item Orientation an bn pn M d V sp ss

1 Horiz 2352 d 104 172595 009 2690 3504 997

2 Horiz 2352 d 243 403275 021 6287 8186 2330

3 Horiz 144 d 381 237012 0045 6035 4811 1370

4 Vert d 156 450 154674 0037 5648 3141 894

5 Vert d 1776 513 228539 0072 6681 6681 1320

Figure 5-21 Details of weld attaching stiffener

388 Pressure Vessel Design Manual

Vessel Internals 389

Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 19: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

Procedure 5-11 Design of Demisters

Demister pads or mist eliminators are important inter-nals in process vessels Anytime there is a continuous twophase flow vapor and liquid there is the possibility forliquid entrainment If it is desirable to separate the liquidand vapor or prevent liquid carryover in the vapor streamthe velocity must be kept sufficiently low to allow the liquiddroplets to fall out of the vapor stream Demister pads areeffective entrainment separators which allow operation atvapor velocities that would otherwise be excessive

ldquoVapor disengagementrdquo can be accomplished withouta demister but the vessel must be made much larger toaccomplish the same degree of separation This is knownas gravity separation

Demister pads are used in a wide variety of processvessels Good performance can be achieved at velocitiesof 30 to 110 of optimum

Demister pads can be used in vertical or horizontalvessels The mesh pad orientation can be either vertical orhorizontal in a vertical or horizontal vessel

A wire mesh demister consists of a knitted wire matmounted on a light weight support grid The mesh is madeby weaving small diameter metal wire into a mesh Padsmay be made out of metal or plastics Metal type includecarbon steel stainless steel monel and others Plasticmaterials include PTFE HDPE and PP

Pressure drop is usually extremely low in the range of1 inch of water column maximum The pressure drop isnormally so low that it is ignored in design

Vapor disengagement is dependent on the velocity ofthe stream The most common equation for determining theallowable vapor velocity for two phase flows is as follows

Va frac14 K frac12ethrL rVTHORN=rV1=2

Where

Va frac14 Allowable vapor velocity FtSecK frac14 Constant or coefficientrL frac14 Density of liquid PCFrV frac14 Density of vapor PCF

Notes

1 The mesh pad shall be in one piece or sectional asrequired for insertion through the vessel manwayEach pad section shall be removable through thevessel manhole

2 Layers shall not be more than 6 inches thick3 Where more than one layer is required all joints

shall be staggered

4 One piece circular pads may be spiral in form5 Each section of mesh shall include a grid on one or

both sides The grid wire andor fastening deviceshall be the same material as the mesh pad Top andbottom grids shall be constructed of frac14 inch diam-eter rods welded to ⅛ inch by 1 inch bars Themaximum gap between mesh pad and grids shall befrac12 inch for diameters less than 84 inches and 1 inchfor larger diameters

6 Estimate grid weights as 3 PSF7 Tie down wires shall be 1=16 inch diameter wire thru

frac14 inch diameter holes on 4 inch centers Tie wiresshould not be pushed through the pad as this couldcause leak paths

8 Pressure drop across mist eliminator shall beassumed as 02 PSI for support design

9 Unless otherwise specified support rings shall be2 inches wide for pads 84 inches in diameter andless and 3 inches wide for larger diameters

10 The mist eliminator shall be a tight fit against theshell or enclosure as well as between sections Meshpads shall be⅜ inches oversize all around for a forcefit against the enclosure No gaps are allowed

11 Vessel fabricator shall provide the mesh and gridsas well as any stiffeners required

12 The Mist eliminator shall be specified as either topor bottom removable

13 ldquoKrdquo is a constant or coefficient that is a functionof the efficiency of the separation K-values rangefrom 04 to 43 but are generally in the 15 to 35range The K-value is affected by pressure type ofpad size of wire type of vessel and disengagingheight For pressure applications the K-valueshould be decreased by 01 for every 100 PSI ofpressure after 100 PSI

14 Wire diameter for the mesh pad itself vary from0003 to 0016 inches

15 The free volume of demisters range from 92 to994

16 The density of the pads ranges from 3 to 33 PCF17 The NSA (nominal surface area) is the surface area

to volume ratio Ft2 Ft3 and is an important indi-cator of performance Ratios range from 50 to 600

18 To obtain higher separation efficiencies the wirediameter is decreased and the density and thicknessare increased

19 Typical width of sections for multi-section pads is12 inches (300 mm) but may vary by manufacturer

376 Pressure Vessel Design Manual

A Horizontal element B Vertical elements

Vertical vessels

Manway

Plate-Pakunit

Meshpad

Drain tubewith seal trap

END VIEW

END VIEW

SIDE VIEW

SIDE VIEW

C Vertical element

Horizontal vessels

D Horizontal element

Figure 5-15 Typical demister configurations in vessels

Vessel Internals 377

d

E Axial entrance

H gt (23) D ndash d

H gt D2 + d(minimum 24rdquo)

H gt D2 ndash d2

H gt D2 + d

H gt D2 ndash d2

h gt d

D

D Side entrance

d

D

B Axial exit

d

D

Φ lt 45ordm

Φ lt 45ordm

C Reverse axial exit

d

A Side exit

D

Figure 5-16 Guidelines for maintaining even flow distribution in vessels with axial flow

378 Pressure Vessel Design Manual

wire mesh

Top grid

Bottom grid

Vertical 14rdquo rodsspaced 12rdquo to 18rdquocenter to center

12rdquo to 18rdquosegmentwidth

18rdquo x 1rdquo flat bars14rdquo rodsspaced 6rdquocenterto center

Manway

Support ring

Support beam

Tie wires

Figure 5-17 Typical mesh pad construction and installation

Vessel Internals 379

Table 5-22Properties of demister pads

Type NSA (1) Ft2 Ft3 Density Pcf Wire Dia in Free Area York Style No Remarks

A 48 5 0011 99 931 High Throughput

B 65 7 0011 986 531 Economy Performance

C 85 9 0011 982 431 Standard - Good All

Around

D 110 108 0011 977 421 Heavy Duty

E 140 8 0006 984 326 Super High Efficiency -

Fine Mist

F 163 0006 94 371 Liquid - Liquid Coalescer

G 450 20 00045 959

H 600 27 00045 945

Notes

1 NSA frac14 Nominal Surface Area

Table 5-23Values of K (Note 13)

Based on Pressure

Pressure (PSIa) Vacuum (In Hg)

Pressure (PSIa) K Vacuum (In Hg) K

15 035 30 035

50 034 20 032

100 032 10 028

200 031 5 023

300 03 1 017

500 028 lt1 017

1000 027

gt1000 027

Based on Disengaging Height

Disengaging Height in K Disengaging Height in K

3 012 9 032

4 015 10 035

5 019 11 038

6 022 12 04

7 025 13 042

8 029 14 043

Based on Application

Vertical Vessels Horizontal Vessels

Type K Type K

General 035 General 035

Compressor Suction Drums 025 Steam Drums 025

Steam Drums 015

380 Pressure Vessel Design Manual

Procedure 5-12 Design of Baffles [10]

Baffles are frequently used in pressure vessels eithervertical or horizontal to divide the interior volume intodifferent compartments These compartments may beused to segregate liquids or provide overflow weirs forthe separation of liquids Baffles may be stiffened orunstiffened When welded across the entire cross sectionof the vessel they must be checked that they are notunduly restricting the diametral expansion of the vesselIf the unrestrained radial expansion of the vessel exceedsthat of the baffle by more than 1=16 in (⅛ in on thediameter) then a ldquoflexiblerdquo type of connection betweenthe vessel shell and the baffle should be utilized Variousflexible attachment designs are shown within theprocedure

Baffles should always be designed in the corrodedcondition It is typical for welded baffles to be designedwith a full corrosion allowance on both sides If the baffleis bolted in then one-half the full corrosion allowancemay be applied to each side the logic being that a boltedbaffle is removable and therefore replaceable

The majority of baffles are flat and as a result are veryinefficient from a strength standpoint Deflection is thegoverning case for flat plates loaded on one side Thepreference is to have unstiffened baffles and they shouldalways be the first choice This will be acceptable forsmall baffles However for larger baffles as the bafflethickness becomes excessive stiffeners offer a moreeconomical design Therefore stiffeners are frequentlyused to stiffen the baffle to prevent the thickness of thebaffle from becoming excessive The number size andspacing of stiffeners are dependent on the baffle thicknessselected There is a continual trade-off between bafflethickness and stiffener parameters

The design of a baffle with stiffeners is an iterativeprocess The procedure for the design of the stiffeners isfirst to divide the baffle into ldquopanelrdquo sections that are rigidenough to withstand the pressure applied on one sideEach individual panel is checked as a flat plate of thedimensions of the panel The stiffeners are assumed to bestrong enough to provide the necessary edge support forthe panel

The stiffeners themselves are designed next A sectionof the baffle is assumed as acting with the stiffener and ascontributing to the overall stiffness This combinedsection is known as the composite stiffener Thecomposite section is checked for stress and deflectionBoth vertical and horizontal stiffeners can be added asrequired

If required an alternate design is assumed based ona thicker or thinner baffle and checked until a satisfactorydesign is found There is no ldquorightrdquo answer however itshould be noted that the thinner the baffle the greater thenumber of stiffeners The lightest overall weight isprobably the ldquobestrdquo design but may not be the leastexpensive due to the welding costs in attaching thestiffeners

One alternative to a flat baffle with stiffeners is to go toa curved baffle A curved baffle works best as a verticalbaffle in a vertical vessel The curved baffle takes pressurefrom either side wall If the pressure is on the concave sidethe baffle is in tension If the pressure is on the convexside the baffle is in compression

There are various tables given in this procedure for flatplate coefficients Flat plate coefficients are utilized todetermine the baffle thickness or a panel thickness Eachtable is specific for a given condition and loading

Vessel Internals 381

Notation

Ap frac14 area of baffle working with stiffener in2

As frac14 area of stiffener in2

Cp frac14 distance from centroid of composite section topanel in

Cs frac14 distance from centroid of composite section tostiffener in

E frac14 modulus of elasticity psiFb frac14 allowable bending stress psiI frac14 moment of inertia composite in4

Is frac14 moment of inertia stiffener in4

l frac14 length of baffle that works with the stiffener inM frac14 moment in-lbn frac14 number of welds attaching stiffenerP frac14 vessel internal pressure psigp frac14 maximum uniform pressure psipn frac14 uniform pressure at any elevation an psiRm frac14 vessel mean radius inSg frac14 specific gravity of contentst frac14 thickness shell intb frac14 thickness baffle ints frac14 thickness stiffener inV frac14 shear load lbw frac14 required fillet weld size ina frac14 thermal coefficient of expansion ininF

bg frac14 flat plate coefficientsDT frac14 differential temperature (design temperature

minus 70F) Fsb frac14 bending stress in baffle psiss frac14 bending stress in stiffener psi

6n frac14 radial expansion ind frac14 deflection inda frac14 maximum allowable deflection in

Baffle Dimensions

382 Pressure Vessel Design Manual

Table 5-24Flat plate coefficients

Vessel Internals 383

Unstiffened Baffle Check

bull Find load p

p frac14 624aSg144

bull Find baffle thickness tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

s

bull Find baffle deflection d

d frac14 pg1b4

Et3b

Limit deflection to the smaller of tb2 or b360 Ifdeflection is excessive then

a Increase the baffle thicknessb Add stiffenersc Go to curved baffle design

If stiffeners are added the first step is to find themaximum ldquoardquo and ldquobrdquo dimensions that will meet theallowable deflection for a given panel size This willestablish the stiffener spacing for both horizontal andvertical stiffeners The ultimate design is a balancebetween baffle thickness stiffener spacing and stiffenersize

Thermal Check of Baffle

bull Vessel radial expansion due to pressure

D1 frac14 085PRm

tE

bull Vessel radial expansion due to temperature

D2 frac14 Rma DT

bull Thermal expansion of baffle

D3 frac14 05ba DT

bull Differential expansion

D4 frac14 D1 thorn D2 D3

Stiffener Design

Divide baffle into panels to limit deflection to the lesserof tb2 or b360 Deflection is calculated based on theappropriate Cases 1 through 3

bull Check baffle for panel size a0 b0bull Check stiffener for length a or b

Recommendations for attaching stiffeners

Benefits Provides added stiffness and no corrosiontrap

Figure 5-18 Example of stiffener layout

384 Pressure Vessel Design Manual

As frac14 tsh

Ap frac14 tbl

IS frac14 tsh3

12

Cp frac14 AsyAs thorn Ap

thorn tb2

Cs frac14 ethhthorn tbTHORN Cp

I frac14 IS thorn Apt2b12

thorn AsApy2

As thorn Ap

lsquo frac14 lesser of 32tb or stiffener spacing

Stresses in BaffleStiffener

sp frac14 MCp

I

ss frac14 MCs

I

Size Welds Attaching Stiffeners

For E70XX Welds

w frac14 Vdy11 200In

Table 5-25Intermittent Welds

Percent of

Continuous Weld

Length of Intermittent Welds

and Distance Between Centers

75 3e4

66 4e6

60 3e5

57 4e7

50 2e4 3e6 4e8

44 4e9

43 3e7

40 2e5 4e10

37 3e8

33 2e6 3e9 4e12

Reprinted by permission of the James F Lincoln Arc Welding

Foundation

Vessel Internals 385

For E60XX Welds

w frac14 Vdy9600In

Sample Problem

bull Given Horizontal vessel with a vertical baffle

P frac14 250 psig

DT frac14 500F

Material frac14 SA-516-70

Ca frac14 0125 in

JE frac14 10

E frac14 273 106 psi

a frac14 7124 10-6 in=in=FFy frac14 308 ksi

D frac14 240 in

Fb frac14 066 Fy frac14 2033 ksi

Rm frac14 120938

ts frac14 175 in

Sg frac14 08

a frac14 15 ft

DT frac14 500 70 frac14 430F

bull Find baffle thickness without stiffener

p frac14 624aSg144

frac14 52 psi

a

bratio frac14 15=20 frac14 075

from Table 5-25 Case 1

b1 frac14 016 g1 frac14 0033

bull Thickness of baffle tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

sfrac14

ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi016eth52THORN2402

20 330

s

tb frac14 153thorn 025 frac14 178

No good Use stiffeners

bull Assume a suitable baffle thickness and determinemaximum panel size

tb frac14 075 in corroded

maximum panel size frac14 4ft 4ft

bull Maximum pressure p

p frac14 13eth624THORN08144

frac14 45 psi

a

bfrac14 4

4frac14 1

See Table 5-25 Case 3

b3 frac14 0287 g3 frac14 00443

sb frac14 b3pb2n

t2

frac14 0287eth45THORN4820752

frac14 5290 psi lt 20 333 psiFigure 5-19 Sample problem

386 Pressure Vessel Design Manual

d frac14 g3

pE

b4nt3

frac14 00443

45

273 106

484

0753

frac14 0092 in lt 0375 in

Balance OK by inspection

bull Assume a layout where the maximum stiffenerspacing is 4 ft

(4) horizontal stiffeners(4) vertical stiffeners(18) panels

bull Check horizontal stiffeners

Dimensions

a1 frac14 3 ft b1 frac14 4 ft

a2 frac14 4 ft b2 frac14 4 ft

a3 frac14 4 ft b3 frac14 12 ft

a4 frac14 4 ft b4 frac14 196 ft

a5 frac14 13 ft

a6 frac14 148ft

bull Assume stiffener size 1 in 4 in

y frac14 2375 in

As frac14 tsh frac14 1eth4THORN frac14 4 in2

l frac14 32tb frac14 32eth075THORN frac14 24 in lt 48 in

AP frac14 tbl frac14 07524 frac14 18 in2

Is frac14 bh3

12frac14 1

43

12frac14 533 in4

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 533thorn 0633thorn 1846 frac14 2442 in4

Cp frac14 AsyAs thorn Ap

thorn tb2

frac14 4eth2375THORN22

thorn 0752

frac14 0807 in

Cs frac14 hthorn tb

Cp

frac14 4thorn 075 0807 frac14 3943

Check deflections

Deflections exceed allowable No good

bull Assume a larger stiffener size WT9 593

tf frac14 106 025 frac14 081

tw frac14 0625 025 frac14 0375

bull Check corroded thickness to find properties ofcorroded section This section would be equivalent toa WT9 30 Properties are

As frac14 882 in2

Is frac14 647 in4

Cs frac14 216 in

H frac14 9 in

Cp frac14 hthorn tb Cs

frac14 9thorn 075 216 frac14 759 in

Figure 5-20 Battle layout for sample problem

Item bn pn d

1 2352 104 149

2 2352 243 349

3 144 381 0767

Vessel Internals 387

y frac14 Cp tb2

frac14 7215 in

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 647thorn 0844thorn 30814 frac14 3737 in4

bull Check stresses and deflections See results in Table5-27

bull Stresses and deflections are acceptablebull Check welds

d frac14 ts thorn 2tw frac14 0375thorn 2eth0323THORN frac14 102

y frac14 7215 in

I frac14 3737 in4

n frac14 2

w frac14 Vdy11 200In

frac14 6681eth102THORN721511 200eth3737THORN2

frac14 0005thorn 0125 frac14 013 in

bull Check thermal expansion of baffle

D1 frac14 085PRm

tEfrac14 085eth250THORN120938

175eth273 106THORNfrac14 000054 in

D2 frac14 Rma DT frac14 1209387124 106430

frac14 0370 in

D3 frac14 05ba DT frac14 05240

7124 106430

frac14 0367 in

D4 frac14 D1 thorn D2 D3 frac14 000054thorn 0370 0367

frac14 00035 lt 006 in

Table 5-26Summary of Results for Stress and Deflection in Composite Stiffeners for Sample Problem

Item Orientation an bn pn M d V sp ss

1 Horiz 2352 d 104 172595 009 2690 3504 997

2 Horiz 2352 d 243 403275 021 6287 8186 2330

3 Horiz 144 d 381 237012 0045 6035 4811 1370

4 Vert d 156 450 154674 0037 5648 3141 894

5 Vert d 1776 513 228539 0072 6681 6681 1320

Figure 5-21 Details of weld attaching stiffener

388 Pressure Vessel Design Manual

Vessel Internals 389

Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 20: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

A Horizontal element B Vertical elements

Vertical vessels

Manway

Plate-Pakunit

Meshpad

Drain tubewith seal trap

END VIEW

END VIEW

SIDE VIEW

SIDE VIEW

C Vertical element

Horizontal vessels

D Horizontal element

Figure 5-15 Typical demister configurations in vessels

Vessel Internals 377

d

E Axial entrance

H gt (23) D ndash d

H gt D2 + d(minimum 24rdquo)

H gt D2 ndash d2

H gt D2 + d

H gt D2 ndash d2

h gt d

D

D Side entrance

d

D

B Axial exit

d

D

Φ lt 45ordm

Φ lt 45ordm

C Reverse axial exit

d

A Side exit

D

Figure 5-16 Guidelines for maintaining even flow distribution in vessels with axial flow

378 Pressure Vessel Design Manual

wire mesh

Top grid

Bottom grid

Vertical 14rdquo rodsspaced 12rdquo to 18rdquocenter to center

12rdquo to 18rdquosegmentwidth

18rdquo x 1rdquo flat bars14rdquo rodsspaced 6rdquocenterto center

Manway

Support ring

Support beam

Tie wires

Figure 5-17 Typical mesh pad construction and installation

Vessel Internals 379

Table 5-22Properties of demister pads

Type NSA (1) Ft2 Ft3 Density Pcf Wire Dia in Free Area York Style No Remarks

A 48 5 0011 99 931 High Throughput

B 65 7 0011 986 531 Economy Performance

C 85 9 0011 982 431 Standard - Good All

Around

D 110 108 0011 977 421 Heavy Duty

E 140 8 0006 984 326 Super High Efficiency -

Fine Mist

F 163 0006 94 371 Liquid - Liquid Coalescer

G 450 20 00045 959

H 600 27 00045 945

Notes

1 NSA frac14 Nominal Surface Area

Table 5-23Values of K (Note 13)

Based on Pressure

Pressure (PSIa) Vacuum (In Hg)

Pressure (PSIa) K Vacuum (In Hg) K

15 035 30 035

50 034 20 032

100 032 10 028

200 031 5 023

300 03 1 017

500 028 lt1 017

1000 027

gt1000 027

Based on Disengaging Height

Disengaging Height in K Disengaging Height in K

3 012 9 032

4 015 10 035

5 019 11 038

6 022 12 04

7 025 13 042

8 029 14 043

Based on Application

Vertical Vessels Horizontal Vessels

Type K Type K

General 035 General 035

Compressor Suction Drums 025 Steam Drums 025

Steam Drums 015

380 Pressure Vessel Design Manual

Procedure 5-12 Design of Baffles [10]

Baffles are frequently used in pressure vessels eithervertical or horizontal to divide the interior volume intodifferent compartments These compartments may beused to segregate liquids or provide overflow weirs forthe separation of liquids Baffles may be stiffened orunstiffened When welded across the entire cross sectionof the vessel they must be checked that they are notunduly restricting the diametral expansion of the vesselIf the unrestrained radial expansion of the vessel exceedsthat of the baffle by more than 1=16 in (⅛ in on thediameter) then a ldquoflexiblerdquo type of connection betweenthe vessel shell and the baffle should be utilized Variousflexible attachment designs are shown within theprocedure

Baffles should always be designed in the corrodedcondition It is typical for welded baffles to be designedwith a full corrosion allowance on both sides If the baffleis bolted in then one-half the full corrosion allowancemay be applied to each side the logic being that a boltedbaffle is removable and therefore replaceable

The majority of baffles are flat and as a result are veryinefficient from a strength standpoint Deflection is thegoverning case for flat plates loaded on one side Thepreference is to have unstiffened baffles and they shouldalways be the first choice This will be acceptable forsmall baffles However for larger baffles as the bafflethickness becomes excessive stiffeners offer a moreeconomical design Therefore stiffeners are frequentlyused to stiffen the baffle to prevent the thickness of thebaffle from becoming excessive The number size andspacing of stiffeners are dependent on the baffle thicknessselected There is a continual trade-off between bafflethickness and stiffener parameters

The design of a baffle with stiffeners is an iterativeprocess The procedure for the design of the stiffeners isfirst to divide the baffle into ldquopanelrdquo sections that are rigidenough to withstand the pressure applied on one sideEach individual panel is checked as a flat plate of thedimensions of the panel The stiffeners are assumed to bestrong enough to provide the necessary edge support forthe panel

The stiffeners themselves are designed next A sectionof the baffle is assumed as acting with the stiffener and ascontributing to the overall stiffness This combinedsection is known as the composite stiffener Thecomposite section is checked for stress and deflectionBoth vertical and horizontal stiffeners can be added asrequired

If required an alternate design is assumed based ona thicker or thinner baffle and checked until a satisfactorydesign is found There is no ldquorightrdquo answer however itshould be noted that the thinner the baffle the greater thenumber of stiffeners The lightest overall weight isprobably the ldquobestrdquo design but may not be the leastexpensive due to the welding costs in attaching thestiffeners

One alternative to a flat baffle with stiffeners is to go toa curved baffle A curved baffle works best as a verticalbaffle in a vertical vessel The curved baffle takes pressurefrom either side wall If the pressure is on the concave sidethe baffle is in tension If the pressure is on the convexside the baffle is in compression

There are various tables given in this procedure for flatplate coefficients Flat plate coefficients are utilized todetermine the baffle thickness or a panel thickness Eachtable is specific for a given condition and loading

Vessel Internals 381

Notation

Ap frac14 area of baffle working with stiffener in2

As frac14 area of stiffener in2

Cp frac14 distance from centroid of composite section topanel in

Cs frac14 distance from centroid of composite section tostiffener in

E frac14 modulus of elasticity psiFb frac14 allowable bending stress psiI frac14 moment of inertia composite in4

Is frac14 moment of inertia stiffener in4

l frac14 length of baffle that works with the stiffener inM frac14 moment in-lbn frac14 number of welds attaching stiffenerP frac14 vessel internal pressure psigp frac14 maximum uniform pressure psipn frac14 uniform pressure at any elevation an psiRm frac14 vessel mean radius inSg frac14 specific gravity of contentst frac14 thickness shell intb frac14 thickness baffle ints frac14 thickness stiffener inV frac14 shear load lbw frac14 required fillet weld size ina frac14 thermal coefficient of expansion ininF

bg frac14 flat plate coefficientsDT frac14 differential temperature (design temperature

minus 70F) Fsb frac14 bending stress in baffle psiss frac14 bending stress in stiffener psi

6n frac14 radial expansion ind frac14 deflection inda frac14 maximum allowable deflection in

Baffle Dimensions

382 Pressure Vessel Design Manual

Table 5-24Flat plate coefficients

Vessel Internals 383

Unstiffened Baffle Check

bull Find load p

p frac14 624aSg144

bull Find baffle thickness tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

s

bull Find baffle deflection d

d frac14 pg1b4

Et3b

Limit deflection to the smaller of tb2 or b360 Ifdeflection is excessive then

a Increase the baffle thicknessb Add stiffenersc Go to curved baffle design

If stiffeners are added the first step is to find themaximum ldquoardquo and ldquobrdquo dimensions that will meet theallowable deflection for a given panel size This willestablish the stiffener spacing for both horizontal andvertical stiffeners The ultimate design is a balancebetween baffle thickness stiffener spacing and stiffenersize

Thermal Check of Baffle

bull Vessel radial expansion due to pressure

D1 frac14 085PRm

tE

bull Vessel radial expansion due to temperature

D2 frac14 Rma DT

bull Thermal expansion of baffle

D3 frac14 05ba DT

bull Differential expansion

D4 frac14 D1 thorn D2 D3

Stiffener Design

Divide baffle into panels to limit deflection to the lesserof tb2 or b360 Deflection is calculated based on theappropriate Cases 1 through 3

bull Check baffle for panel size a0 b0bull Check stiffener for length a or b

Recommendations for attaching stiffeners

Benefits Provides added stiffness and no corrosiontrap

Figure 5-18 Example of stiffener layout

384 Pressure Vessel Design Manual

As frac14 tsh

Ap frac14 tbl

IS frac14 tsh3

12

Cp frac14 AsyAs thorn Ap

thorn tb2

Cs frac14 ethhthorn tbTHORN Cp

I frac14 IS thorn Apt2b12

thorn AsApy2

As thorn Ap

lsquo frac14 lesser of 32tb or stiffener spacing

Stresses in BaffleStiffener

sp frac14 MCp

I

ss frac14 MCs

I

Size Welds Attaching Stiffeners

For E70XX Welds

w frac14 Vdy11 200In

Table 5-25Intermittent Welds

Percent of

Continuous Weld

Length of Intermittent Welds

and Distance Between Centers

75 3e4

66 4e6

60 3e5

57 4e7

50 2e4 3e6 4e8

44 4e9

43 3e7

40 2e5 4e10

37 3e8

33 2e6 3e9 4e12

Reprinted by permission of the James F Lincoln Arc Welding

Foundation

Vessel Internals 385

For E60XX Welds

w frac14 Vdy9600In

Sample Problem

bull Given Horizontal vessel with a vertical baffle

P frac14 250 psig

DT frac14 500F

Material frac14 SA-516-70

Ca frac14 0125 in

JE frac14 10

E frac14 273 106 psi

a frac14 7124 10-6 in=in=FFy frac14 308 ksi

D frac14 240 in

Fb frac14 066 Fy frac14 2033 ksi

Rm frac14 120938

ts frac14 175 in

Sg frac14 08

a frac14 15 ft

DT frac14 500 70 frac14 430F

bull Find baffle thickness without stiffener

p frac14 624aSg144

frac14 52 psi

a

bratio frac14 15=20 frac14 075

from Table 5-25 Case 1

b1 frac14 016 g1 frac14 0033

bull Thickness of baffle tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

sfrac14

ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi016eth52THORN2402

20 330

s

tb frac14 153thorn 025 frac14 178

No good Use stiffeners

bull Assume a suitable baffle thickness and determinemaximum panel size

tb frac14 075 in corroded

maximum panel size frac14 4ft 4ft

bull Maximum pressure p

p frac14 13eth624THORN08144

frac14 45 psi

a

bfrac14 4

4frac14 1

See Table 5-25 Case 3

b3 frac14 0287 g3 frac14 00443

sb frac14 b3pb2n

t2

frac14 0287eth45THORN4820752

frac14 5290 psi lt 20 333 psiFigure 5-19 Sample problem

386 Pressure Vessel Design Manual

d frac14 g3

pE

b4nt3

frac14 00443

45

273 106

484

0753

frac14 0092 in lt 0375 in

Balance OK by inspection

bull Assume a layout where the maximum stiffenerspacing is 4 ft

(4) horizontal stiffeners(4) vertical stiffeners(18) panels

bull Check horizontal stiffeners

Dimensions

a1 frac14 3 ft b1 frac14 4 ft

a2 frac14 4 ft b2 frac14 4 ft

a3 frac14 4 ft b3 frac14 12 ft

a4 frac14 4 ft b4 frac14 196 ft

a5 frac14 13 ft

a6 frac14 148ft

bull Assume stiffener size 1 in 4 in

y frac14 2375 in

As frac14 tsh frac14 1eth4THORN frac14 4 in2

l frac14 32tb frac14 32eth075THORN frac14 24 in lt 48 in

AP frac14 tbl frac14 07524 frac14 18 in2

Is frac14 bh3

12frac14 1

43

12frac14 533 in4

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 533thorn 0633thorn 1846 frac14 2442 in4

Cp frac14 AsyAs thorn Ap

thorn tb2

frac14 4eth2375THORN22

thorn 0752

frac14 0807 in

Cs frac14 hthorn tb

Cp

frac14 4thorn 075 0807 frac14 3943

Check deflections

Deflections exceed allowable No good

bull Assume a larger stiffener size WT9 593

tf frac14 106 025 frac14 081

tw frac14 0625 025 frac14 0375

bull Check corroded thickness to find properties ofcorroded section This section would be equivalent toa WT9 30 Properties are

As frac14 882 in2

Is frac14 647 in4

Cs frac14 216 in

H frac14 9 in

Cp frac14 hthorn tb Cs

frac14 9thorn 075 216 frac14 759 in

Figure 5-20 Battle layout for sample problem

Item bn pn d

1 2352 104 149

2 2352 243 349

3 144 381 0767

Vessel Internals 387

y frac14 Cp tb2

frac14 7215 in

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 647thorn 0844thorn 30814 frac14 3737 in4

bull Check stresses and deflections See results in Table5-27

bull Stresses and deflections are acceptablebull Check welds

d frac14 ts thorn 2tw frac14 0375thorn 2eth0323THORN frac14 102

y frac14 7215 in

I frac14 3737 in4

n frac14 2

w frac14 Vdy11 200In

frac14 6681eth102THORN721511 200eth3737THORN2

frac14 0005thorn 0125 frac14 013 in

bull Check thermal expansion of baffle

D1 frac14 085PRm

tEfrac14 085eth250THORN120938

175eth273 106THORNfrac14 000054 in

D2 frac14 Rma DT frac14 1209387124 106430

frac14 0370 in

D3 frac14 05ba DT frac14 05240

7124 106430

frac14 0367 in

D4 frac14 D1 thorn D2 D3 frac14 000054thorn 0370 0367

frac14 00035 lt 006 in

Table 5-26Summary of Results for Stress and Deflection in Composite Stiffeners for Sample Problem

Item Orientation an bn pn M d V sp ss

1 Horiz 2352 d 104 172595 009 2690 3504 997

2 Horiz 2352 d 243 403275 021 6287 8186 2330

3 Horiz 144 d 381 237012 0045 6035 4811 1370

4 Vert d 156 450 154674 0037 5648 3141 894

5 Vert d 1776 513 228539 0072 6681 6681 1320

Figure 5-21 Details of weld attaching stiffener

388 Pressure Vessel Design Manual

Vessel Internals 389

Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 21: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

d

E Axial entrance

H gt (23) D ndash d

H gt D2 + d(minimum 24rdquo)

H gt D2 ndash d2

H gt D2 + d

H gt D2 ndash d2

h gt d

D

D Side entrance

d

D

B Axial exit

d

D

Φ lt 45ordm

Φ lt 45ordm

C Reverse axial exit

d

A Side exit

D

Figure 5-16 Guidelines for maintaining even flow distribution in vessels with axial flow

378 Pressure Vessel Design Manual

wire mesh

Top grid

Bottom grid

Vertical 14rdquo rodsspaced 12rdquo to 18rdquocenter to center

12rdquo to 18rdquosegmentwidth

18rdquo x 1rdquo flat bars14rdquo rodsspaced 6rdquocenterto center

Manway

Support ring

Support beam

Tie wires

Figure 5-17 Typical mesh pad construction and installation

Vessel Internals 379

Table 5-22Properties of demister pads

Type NSA (1) Ft2 Ft3 Density Pcf Wire Dia in Free Area York Style No Remarks

A 48 5 0011 99 931 High Throughput

B 65 7 0011 986 531 Economy Performance

C 85 9 0011 982 431 Standard - Good All

Around

D 110 108 0011 977 421 Heavy Duty

E 140 8 0006 984 326 Super High Efficiency -

Fine Mist

F 163 0006 94 371 Liquid - Liquid Coalescer

G 450 20 00045 959

H 600 27 00045 945

Notes

1 NSA frac14 Nominal Surface Area

Table 5-23Values of K (Note 13)

Based on Pressure

Pressure (PSIa) Vacuum (In Hg)

Pressure (PSIa) K Vacuum (In Hg) K

15 035 30 035

50 034 20 032

100 032 10 028

200 031 5 023

300 03 1 017

500 028 lt1 017

1000 027

gt1000 027

Based on Disengaging Height

Disengaging Height in K Disengaging Height in K

3 012 9 032

4 015 10 035

5 019 11 038

6 022 12 04

7 025 13 042

8 029 14 043

Based on Application

Vertical Vessels Horizontal Vessels

Type K Type K

General 035 General 035

Compressor Suction Drums 025 Steam Drums 025

Steam Drums 015

380 Pressure Vessel Design Manual

Procedure 5-12 Design of Baffles [10]

Baffles are frequently used in pressure vessels eithervertical or horizontal to divide the interior volume intodifferent compartments These compartments may beused to segregate liquids or provide overflow weirs forthe separation of liquids Baffles may be stiffened orunstiffened When welded across the entire cross sectionof the vessel they must be checked that they are notunduly restricting the diametral expansion of the vesselIf the unrestrained radial expansion of the vessel exceedsthat of the baffle by more than 1=16 in (⅛ in on thediameter) then a ldquoflexiblerdquo type of connection betweenthe vessel shell and the baffle should be utilized Variousflexible attachment designs are shown within theprocedure

Baffles should always be designed in the corrodedcondition It is typical for welded baffles to be designedwith a full corrosion allowance on both sides If the baffleis bolted in then one-half the full corrosion allowancemay be applied to each side the logic being that a boltedbaffle is removable and therefore replaceable

The majority of baffles are flat and as a result are veryinefficient from a strength standpoint Deflection is thegoverning case for flat plates loaded on one side Thepreference is to have unstiffened baffles and they shouldalways be the first choice This will be acceptable forsmall baffles However for larger baffles as the bafflethickness becomes excessive stiffeners offer a moreeconomical design Therefore stiffeners are frequentlyused to stiffen the baffle to prevent the thickness of thebaffle from becoming excessive The number size andspacing of stiffeners are dependent on the baffle thicknessselected There is a continual trade-off between bafflethickness and stiffener parameters

The design of a baffle with stiffeners is an iterativeprocess The procedure for the design of the stiffeners isfirst to divide the baffle into ldquopanelrdquo sections that are rigidenough to withstand the pressure applied on one sideEach individual panel is checked as a flat plate of thedimensions of the panel The stiffeners are assumed to bestrong enough to provide the necessary edge support forthe panel

The stiffeners themselves are designed next A sectionof the baffle is assumed as acting with the stiffener and ascontributing to the overall stiffness This combinedsection is known as the composite stiffener Thecomposite section is checked for stress and deflectionBoth vertical and horizontal stiffeners can be added asrequired

If required an alternate design is assumed based ona thicker or thinner baffle and checked until a satisfactorydesign is found There is no ldquorightrdquo answer however itshould be noted that the thinner the baffle the greater thenumber of stiffeners The lightest overall weight isprobably the ldquobestrdquo design but may not be the leastexpensive due to the welding costs in attaching thestiffeners

One alternative to a flat baffle with stiffeners is to go toa curved baffle A curved baffle works best as a verticalbaffle in a vertical vessel The curved baffle takes pressurefrom either side wall If the pressure is on the concave sidethe baffle is in tension If the pressure is on the convexside the baffle is in compression

There are various tables given in this procedure for flatplate coefficients Flat plate coefficients are utilized todetermine the baffle thickness or a panel thickness Eachtable is specific for a given condition and loading

Vessel Internals 381

Notation

Ap frac14 area of baffle working with stiffener in2

As frac14 area of stiffener in2

Cp frac14 distance from centroid of composite section topanel in

Cs frac14 distance from centroid of composite section tostiffener in

E frac14 modulus of elasticity psiFb frac14 allowable bending stress psiI frac14 moment of inertia composite in4

Is frac14 moment of inertia stiffener in4

l frac14 length of baffle that works with the stiffener inM frac14 moment in-lbn frac14 number of welds attaching stiffenerP frac14 vessel internal pressure psigp frac14 maximum uniform pressure psipn frac14 uniform pressure at any elevation an psiRm frac14 vessel mean radius inSg frac14 specific gravity of contentst frac14 thickness shell intb frac14 thickness baffle ints frac14 thickness stiffener inV frac14 shear load lbw frac14 required fillet weld size ina frac14 thermal coefficient of expansion ininF

bg frac14 flat plate coefficientsDT frac14 differential temperature (design temperature

minus 70F) Fsb frac14 bending stress in baffle psiss frac14 bending stress in stiffener psi

6n frac14 radial expansion ind frac14 deflection inda frac14 maximum allowable deflection in

Baffle Dimensions

382 Pressure Vessel Design Manual

Table 5-24Flat plate coefficients

Vessel Internals 383

Unstiffened Baffle Check

bull Find load p

p frac14 624aSg144

bull Find baffle thickness tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

s

bull Find baffle deflection d

d frac14 pg1b4

Et3b

Limit deflection to the smaller of tb2 or b360 Ifdeflection is excessive then

a Increase the baffle thicknessb Add stiffenersc Go to curved baffle design

If stiffeners are added the first step is to find themaximum ldquoardquo and ldquobrdquo dimensions that will meet theallowable deflection for a given panel size This willestablish the stiffener spacing for both horizontal andvertical stiffeners The ultimate design is a balancebetween baffle thickness stiffener spacing and stiffenersize

Thermal Check of Baffle

bull Vessel radial expansion due to pressure

D1 frac14 085PRm

tE

bull Vessel radial expansion due to temperature

D2 frac14 Rma DT

bull Thermal expansion of baffle

D3 frac14 05ba DT

bull Differential expansion

D4 frac14 D1 thorn D2 D3

Stiffener Design

Divide baffle into panels to limit deflection to the lesserof tb2 or b360 Deflection is calculated based on theappropriate Cases 1 through 3

bull Check baffle for panel size a0 b0bull Check stiffener for length a or b

Recommendations for attaching stiffeners

Benefits Provides added stiffness and no corrosiontrap

Figure 5-18 Example of stiffener layout

384 Pressure Vessel Design Manual

As frac14 tsh

Ap frac14 tbl

IS frac14 tsh3

12

Cp frac14 AsyAs thorn Ap

thorn tb2

Cs frac14 ethhthorn tbTHORN Cp

I frac14 IS thorn Apt2b12

thorn AsApy2

As thorn Ap

lsquo frac14 lesser of 32tb or stiffener spacing

Stresses in BaffleStiffener

sp frac14 MCp

I

ss frac14 MCs

I

Size Welds Attaching Stiffeners

For E70XX Welds

w frac14 Vdy11 200In

Table 5-25Intermittent Welds

Percent of

Continuous Weld

Length of Intermittent Welds

and Distance Between Centers

75 3e4

66 4e6

60 3e5

57 4e7

50 2e4 3e6 4e8

44 4e9

43 3e7

40 2e5 4e10

37 3e8

33 2e6 3e9 4e12

Reprinted by permission of the James F Lincoln Arc Welding

Foundation

Vessel Internals 385

For E60XX Welds

w frac14 Vdy9600In

Sample Problem

bull Given Horizontal vessel with a vertical baffle

P frac14 250 psig

DT frac14 500F

Material frac14 SA-516-70

Ca frac14 0125 in

JE frac14 10

E frac14 273 106 psi

a frac14 7124 10-6 in=in=FFy frac14 308 ksi

D frac14 240 in

Fb frac14 066 Fy frac14 2033 ksi

Rm frac14 120938

ts frac14 175 in

Sg frac14 08

a frac14 15 ft

DT frac14 500 70 frac14 430F

bull Find baffle thickness without stiffener

p frac14 624aSg144

frac14 52 psi

a

bratio frac14 15=20 frac14 075

from Table 5-25 Case 1

b1 frac14 016 g1 frac14 0033

bull Thickness of baffle tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

sfrac14

ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi016eth52THORN2402

20 330

s

tb frac14 153thorn 025 frac14 178

No good Use stiffeners

bull Assume a suitable baffle thickness and determinemaximum panel size

tb frac14 075 in corroded

maximum panel size frac14 4ft 4ft

bull Maximum pressure p

p frac14 13eth624THORN08144

frac14 45 psi

a

bfrac14 4

4frac14 1

See Table 5-25 Case 3

b3 frac14 0287 g3 frac14 00443

sb frac14 b3pb2n

t2

frac14 0287eth45THORN4820752

frac14 5290 psi lt 20 333 psiFigure 5-19 Sample problem

386 Pressure Vessel Design Manual

d frac14 g3

pE

b4nt3

frac14 00443

45

273 106

484

0753

frac14 0092 in lt 0375 in

Balance OK by inspection

bull Assume a layout where the maximum stiffenerspacing is 4 ft

(4) horizontal stiffeners(4) vertical stiffeners(18) panels

bull Check horizontal stiffeners

Dimensions

a1 frac14 3 ft b1 frac14 4 ft

a2 frac14 4 ft b2 frac14 4 ft

a3 frac14 4 ft b3 frac14 12 ft

a4 frac14 4 ft b4 frac14 196 ft

a5 frac14 13 ft

a6 frac14 148ft

bull Assume stiffener size 1 in 4 in

y frac14 2375 in

As frac14 tsh frac14 1eth4THORN frac14 4 in2

l frac14 32tb frac14 32eth075THORN frac14 24 in lt 48 in

AP frac14 tbl frac14 07524 frac14 18 in2

Is frac14 bh3

12frac14 1

43

12frac14 533 in4

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 533thorn 0633thorn 1846 frac14 2442 in4

Cp frac14 AsyAs thorn Ap

thorn tb2

frac14 4eth2375THORN22

thorn 0752

frac14 0807 in

Cs frac14 hthorn tb

Cp

frac14 4thorn 075 0807 frac14 3943

Check deflections

Deflections exceed allowable No good

bull Assume a larger stiffener size WT9 593

tf frac14 106 025 frac14 081

tw frac14 0625 025 frac14 0375

bull Check corroded thickness to find properties ofcorroded section This section would be equivalent toa WT9 30 Properties are

As frac14 882 in2

Is frac14 647 in4

Cs frac14 216 in

H frac14 9 in

Cp frac14 hthorn tb Cs

frac14 9thorn 075 216 frac14 759 in

Figure 5-20 Battle layout for sample problem

Item bn pn d

1 2352 104 149

2 2352 243 349

3 144 381 0767

Vessel Internals 387

y frac14 Cp tb2

frac14 7215 in

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 647thorn 0844thorn 30814 frac14 3737 in4

bull Check stresses and deflections See results in Table5-27

bull Stresses and deflections are acceptablebull Check welds

d frac14 ts thorn 2tw frac14 0375thorn 2eth0323THORN frac14 102

y frac14 7215 in

I frac14 3737 in4

n frac14 2

w frac14 Vdy11 200In

frac14 6681eth102THORN721511 200eth3737THORN2

frac14 0005thorn 0125 frac14 013 in

bull Check thermal expansion of baffle

D1 frac14 085PRm

tEfrac14 085eth250THORN120938

175eth273 106THORNfrac14 000054 in

D2 frac14 Rma DT frac14 1209387124 106430

frac14 0370 in

D3 frac14 05ba DT frac14 05240

7124 106430

frac14 0367 in

D4 frac14 D1 thorn D2 D3 frac14 000054thorn 0370 0367

frac14 00035 lt 006 in

Table 5-26Summary of Results for Stress and Deflection in Composite Stiffeners for Sample Problem

Item Orientation an bn pn M d V sp ss

1 Horiz 2352 d 104 172595 009 2690 3504 997

2 Horiz 2352 d 243 403275 021 6287 8186 2330

3 Horiz 144 d 381 237012 0045 6035 4811 1370

4 Vert d 156 450 154674 0037 5648 3141 894

5 Vert d 1776 513 228539 0072 6681 6681 1320

Figure 5-21 Details of weld attaching stiffener

388 Pressure Vessel Design Manual

Vessel Internals 389

Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 22: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

wire mesh

Top grid

Bottom grid

Vertical 14rdquo rodsspaced 12rdquo to 18rdquocenter to center

12rdquo to 18rdquosegmentwidth

18rdquo x 1rdquo flat bars14rdquo rodsspaced 6rdquocenterto center

Manway

Support ring

Support beam

Tie wires

Figure 5-17 Typical mesh pad construction and installation

Vessel Internals 379

Table 5-22Properties of demister pads

Type NSA (1) Ft2 Ft3 Density Pcf Wire Dia in Free Area York Style No Remarks

A 48 5 0011 99 931 High Throughput

B 65 7 0011 986 531 Economy Performance

C 85 9 0011 982 431 Standard - Good All

Around

D 110 108 0011 977 421 Heavy Duty

E 140 8 0006 984 326 Super High Efficiency -

Fine Mist

F 163 0006 94 371 Liquid - Liquid Coalescer

G 450 20 00045 959

H 600 27 00045 945

Notes

1 NSA frac14 Nominal Surface Area

Table 5-23Values of K (Note 13)

Based on Pressure

Pressure (PSIa) Vacuum (In Hg)

Pressure (PSIa) K Vacuum (In Hg) K

15 035 30 035

50 034 20 032

100 032 10 028

200 031 5 023

300 03 1 017

500 028 lt1 017

1000 027

gt1000 027

Based on Disengaging Height

Disengaging Height in K Disengaging Height in K

3 012 9 032

4 015 10 035

5 019 11 038

6 022 12 04

7 025 13 042

8 029 14 043

Based on Application

Vertical Vessels Horizontal Vessels

Type K Type K

General 035 General 035

Compressor Suction Drums 025 Steam Drums 025

Steam Drums 015

380 Pressure Vessel Design Manual

Procedure 5-12 Design of Baffles [10]

Baffles are frequently used in pressure vessels eithervertical or horizontal to divide the interior volume intodifferent compartments These compartments may beused to segregate liquids or provide overflow weirs forthe separation of liquids Baffles may be stiffened orunstiffened When welded across the entire cross sectionof the vessel they must be checked that they are notunduly restricting the diametral expansion of the vesselIf the unrestrained radial expansion of the vessel exceedsthat of the baffle by more than 1=16 in (⅛ in on thediameter) then a ldquoflexiblerdquo type of connection betweenthe vessel shell and the baffle should be utilized Variousflexible attachment designs are shown within theprocedure

Baffles should always be designed in the corrodedcondition It is typical for welded baffles to be designedwith a full corrosion allowance on both sides If the baffleis bolted in then one-half the full corrosion allowancemay be applied to each side the logic being that a boltedbaffle is removable and therefore replaceable

The majority of baffles are flat and as a result are veryinefficient from a strength standpoint Deflection is thegoverning case for flat plates loaded on one side Thepreference is to have unstiffened baffles and they shouldalways be the first choice This will be acceptable forsmall baffles However for larger baffles as the bafflethickness becomes excessive stiffeners offer a moreeconomical design Therefore stiffeners are frequentlyused to stiffen the baffle to prevent the thickness of thebaffle from becoming excessive The number size andspacing of stiffeners are dependent on the baffle thicknessselected There is a continual trade-off between bafflethickness and stiffener parameters

The design of a baffle with stiffeners is an iterativeprocess The procedure for the design of the stiffeners isfirst to divide the baffle into ldquopanelrdquo sections that are rigidenough to withstand the pressure applied on one sideEach individual panel is checked as a flat plate of thedimensions of the panel The stiffeners are assumed to bestrong enough to provide the necessary edge support forthe panel

The stiffeners themselves are designed next A sectionof the baffle is assumed as acting with the stiffener and ascontributing to the overall stiffness This combinedsection is known as the composite stiffener Thecomposite section is checked for stress and deflectionBoth vertical and horizontal stiffeners can be added asrequired

If required an alternate design is assumed based ona thicker or thinner baffle and checked until a satisfactorydesign is found There is no ldquorightrdquo answer however itshould be noted that the thinner the baffle the greater thenumber of stiffeners The lightest overall weight isprobably the ldquobestrdquo design but may not be the leastexpensive due to the welding costs in attaching thestiffeners

One alternative to a flat baffle with stiffeners is to go toa curved baffle A curved baffle works best as a verticalbaffle in a vertical vessel The curved baffle takes pressurefrom either side wall If the pressure is on the concave sidethe baffle is in tension If the pressure is on the convexside the baffle is in compression

There are various tables given in this procedure for flatplate coefficients Flat plate coefficients are utilized todetermine the baffle thickness or a panel thickness Eachtable is specific for a given condition and loading

Vessel Internals 381

Notation

Ap frac14 area of baffle working with stiffener in2

As frac14 area of stiffener in2

Cp frac14 distance from centroid of composite section topanel in

Cs frac14 distance from centroid of composite section tostiffener in

E frac14 modulus of elasticity psiFb frac14 allowable bending stress psiI frac14 moment of inertia composite in4

Is frac14 moment of inertia stiffener in4

l frac14 length of baffle that works with the stiffener inM frac14 moment in-lbn frac14 number of welds attaching stiffenerP frac14 vessel internal pressure psigp frac14 maximum uniform pressure psipn frac14 uniform pressure at any elevation an psiRm frac14 vessel mean radius inSg frac14 specific gravity of contentst frac14 thickness shell intb frac14 thickness baffle ints frac14 thickness stiffener inV frac14 shear load lbw frac14 required fillet weld size ina frac14 thermal coefficient of expansion ininF

bg frac14 flat plate coefficientsDT frac14 differential temperature (design temperature

minus 70F) Fsb frac14 bending stress in baffle psiss frac14 bending stress in stiffener psi

6n frac14 radial expansion ind frac14 deflection inda frac14 maximum allowable deflection in

Baffle Dimensions

382 Pressure Vessel Design Manual

Table 5-24Flat plate coefficients

Vessel Internals 383

Unstiffened Baffle Check

bull Find load p

p frac14 624aSg144

bull Find baffle thickness tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

s

bull Find baffle deflection d

d frac14 pg1b4

Et3b

Limit deflection to the smaller of tb2 or b360 Ifdeflection is excessive then

a Increase the baffle thicknessb Add stiffenersc Go to curved baffle design

If stiffeners are added the first step is to find themaximum ldquoardquo and ldquobrdquo dimensions that will meet theallowable deflection for a given panel size This willestablish the stiffener spacing for both horizontal andvertical stiffeners The ultimate design is a balancebetween baffle thickness stiffener spacing and stiffenersize

Thermal Check of Baffle

bull Vessel radial expansion due to pressure

D1 frac14 085PRm

tE

bull Vessel radial expansion due to temperature

D2 frac14 Rma DT

bull Thermal expansion of baffle

D3 frac14 05ba DT

bull Differential expansion

D4 frac14 D1 thorn D2 D3

Stiffener Design

Divide baffle into panels to limit deflection to the lesserof tb2 or b360 Deflection is calculated based on theappropriate Cases 1 through 3

bull Check baffle for panel size a0 b0bull Check stiffener for length a or b

Recommendations for attaching stiffeners

Benefits Provides added stiffness and no corrosiontrap

Figure 5-18 Example of stiffener layout

384 Pressure Vessel Design Manual

As frac14 tsh

Ap frac14 tbl

IS frac14 tsh3

12

Cp frac14 AsyAs thorn Ap

thorn tb2

Cs frac14 ethhthorn tbTHORN Cp

I frac14 IS thorn Apt2b12

thorn AsApy2

As thorn Ap

lsquo frac14 lesser of 32tb or stiffener spacing

Stresses in BaffleStiffener

sp frac14 MCp

I

ss frac14 MCs

I

Size Welds Attaching Stiffeners

For E70XX Welds

w frac14 Vdy11 200In

Table 5-25Intermittent Welds

Percent of

Continuous Weld

Length of Intermittent Welds

and Distance Between Centers

75 3e4

66 4e6

60 3e5

57 4e7

50 2e4 3e6 4e8

44 4e9

43 3e7

40 2e5 4e10

37 3e8

33 2e6 3e9 4e12

Reprinted by permission of the James F Lincoln Arc Welding

Foundation

Vessel Internals 385

For E60XX Welds

w frac14 Vdy9600In

Sample Problem

bull Given Horizontal vessel with a vertical baffle

P frac14 250 psig

DT frac14 500F

Material frac14 SA-516-70

Ca frac14 0125 in

JE frac14 10

E frac14 273 106 psi

a frac14 7124 10-6 in=in=FFy frac14 308 ksi

D frac14 240 in

Fb frac14 066 Fy frac14 2033 ksi

Rm frac14 120938

ts frac14 175 in

Sg frac14 08

a frac14 15 ft

DT frac14 500 70 frac14 430F

bull Find baffle thickness without stiffener

p frac14 624aSg144

frac14 52 psi

a

bratio frac14 15=20 frac14 075

from Table 5-25 Case 1

b1 frac14 016 g1 frac14 0033

bull Thickness of baffle tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

sfrac14

ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi016eth52THORN2402

20 330

s

tb frac14 153thorn 025 frac14 178

No good Use stiffeners

bull Assume a suitable baffle thickness and determinemaximum panel size

tb frac14 075 in corroded

maximum panel size frac14 4ft 4ft

bull Maximum pressure p

p frac14 13eth624THORN08144

frac14 45 psi

a

bfrac14 4

4frac14 1

See Table 5-25 Case 3

b3 frac14 0287 g3 frac14 00443

sb frac14 b3pb2n

t2

frac14 0287eth45THORN4820752

frac14 5290 psi lt 20 333 psiFigure 5-19 Sample problem

386 Pressure Vessel Design Manual

d frac14 g3

pE

b4nt3

frac14 00443

45

273 106

484

0753

frac14 0092 in lt 0375 in

Balance OK by inspection

bull Assume a layout where the maximum stiffenerspacing is 4 ft

(4) horizontal stiffeners(4) vertical stiffeners(18) panels

bull Check horizontal stiffeners

Dimensions

a1 frac14 3 ft b1 frac14 4 ft

a2 frac14 4 ft b2 frac14 4 ft

a3 frac14 4 ft b3 frac14 12 ft

a4 frac14 4 ft b4 frac14 196 ft

a5 frac14 13 ft

a6 frac14 148ft

bull Assume stiffener size 1 in 4 in

y frac14 2375 in

As frac14 tsh frac14 1eth4THORN frac14 4 in2

l frac14 32tb frac14 32eth075THORN frac14 24 in lt 48 in

AP frac14 tbl frac14 07524 frac14 18 in2

Is frac14 bh3

12frac14 1

43

12frac14 533 in4

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 533thorn 0633thorn 1846 frac14 2442 in4

Cp frac14 AsyAs thorn Ap

thorn tb2

frac14 4eth2375THORN22

thorn 0752

frac14 0807 in

Cs frac14 hthorn tb

Cp

frac14 4thorn 075 0807 frac14 3943

Check deflections

Deflections exceed allowable No good

bull Assume a larger stiffener size WT9 593

tf frac14 106 025 frac14 081

tw frac14 0625 025 frac14 0375

bull Check corroded thickness to find properties ofcorroded section This section would be equivalent toa WT9 30 Properties are

As frac14 882 in2

Is frac14 647 in4

Cs frac14 216 in

H frac14 9 in

Cp frac14 hthorn tb Cs

frac14 9thorn 075 216 frac14 759 in

Figure 5-20 Battle layout for sample problem

Item bn pn d

1 2352 104 149

2 2352 243 349

3 144 381 0767

Vessel Internals 387

y frac14 Cp tb2

frac14 7215 in

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 647thorn 0844thorn 30814 frac14 3737 in4

bull Check stresses and deflections See results in Table5-27

bull Stresses and deflections are acceptablebull Check welds

d frac14 ts thorn 2tw frac14 0375thorn 2eth0323THORN frac14 102

y frac14 7215 in

I frac14 3737 in4

n frac14 2

w frac14 Vdy11 200In

frac14 6681eth102THORN721511 200eth3737THORN2

frac14 0005thorn 0125 frac14 013 in

bull Check thermal expansion of baffle

D1 frac14 085PRm

tEfrac14 085eth250THORN120938

175eth273 106THORNfrac14 000054 in

D2 frac14 Rma DT frac14 1209387124 106430

frac14 0370 in

D3 frac14 05ba DT frac14 05240

7124 106430

frac14 0367 in

D4 frac14 D1 thorn D2 D3 frac14 000054thorn 0370 0367

frac14 00035 lt 006 in

Table 5-26Summary of Results for Stress and Deflection in Composite Stiffeners for Sample Problem

Item Orientation an bn pn M d V sp ss

1 Horiz 2352 d 104 172595 009 2690 3504 997

2 Horiz 2352 d 243 403275 021 6287 8186 2330

3 Horiz 144 d 381 237012 0045 6035 4811 1370

4 Vert d 156 450 154674 0037 5648 3141 894

5 Vert d 1776 513 228539 0072 6681 6681 1320

Figure 5-21 Details of weld attaching stiffener

388 Pressure Vessel Design Manual

Vessel Internals 389

Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 23: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

Table 5-22Properties of demister pads

Type NSA (1) Ft2 Ft3 Density Pcf Wire Dia in Free Area York Style No Remarks

A 48 5 0011 99 931 High Throughput

B 65 7 0011 986 531 Economy Performance

C 85 9 0011 982 431 Standard - Good All

Around

D 110 108 0011 977 421 Heavy Duty

E 140 8 0006 984 326 Super High Efficiency -

Fine Mist

F 163 0006 94 371 Liquid - Liquid Coalescer

G 450 20 00045 959

H 600 27 00045 945

Notes

1 NSA frac14 Nominal Surface Area

Table 5-23Values of K (Note 13)

Based on Pressure

Pressure (PSIa) Vacuum (In Hg)

Pressure (PSIa) K Vacuum (In Hg) K

15 035 30 035

50 034 20 032

100 032 10 028

200 031 5 023

300 03 1 017

500 028 lt1 017

1000 027

gt1000 027

Based on Disengaging Height

Disengaging Height in K Disengaging Height in K

3 012 9 032

4 015 10 035

5 019 11 038

6 022 12 04

7 025 13 042

8 029 14 043

Based on Application

Vertical Vessels Horizontal Vessels

Type K Type K

General 035 General 035

Compressor Suction Drums 025 Steam Drums 025

Steam Drums 015

380 Pressure Vessel Design Manual

Procedure 5-12 Design of Baffles [10]

Baffles are frequently used in pressure vessels eithervertical or horizontal to divide the interior volume intodifferent compartments These compartments may beused to segregate liquids or provide overflow weirs forthe separation of liquids Baffles may be stiffened orunstiffened When welded across the entire cross sectionof the vessel they must be checked that they are notunduly restricting the diametral expansion of the vesselIf the unrestrained radial expansion of the vessel exceedsthat of the baffle by more than 1=16 in (⅛ in on thediameter) then a ldquoflexiblerdquo type of connection betweenthe vessel shell and the baffle should be utilized Variousflexible attachment designs are shown within theprocedure

Baffles should always be designed in the corrodedcondition It is typical for welded baffles to be designedwith a full corrosion allowance on both sides If the baffleis bolted in then one-half the full corrosion allowancemay be applied to each side the logic being that a boltedbaffle is removable and therefore replaceable

The majority of baffles are flat and as a result are veryinefficient from a strength standpoint Deflection is thegoverning case for flat plates loaded on one side Thepreference is to have unstiffened baffles and they shouldalways be the first choice This will be acceptable forsmall baffles However for larger baffles as the bafflethickness becomes excessive stiffeners offer a moreeconomical design Therefore stiffeners are frequentlyused to stiffen the baffle to prevent the thickness of thebaffle from becoming excessive The number size andspacing of stiffeners are dependent on the baffle thicknessselected There is a continual trade-off between bafflethickness and stiffener parameters

The design of a baffle with stiffeners is an iterativeprocess The procedure for the design of the stiffeners isfirst to divide the baffle into ldquopanelrdquo sections that are rigidenough to withstand the pressure applied on one sideEach individual panel is checked as a flat plate of thedimensions of the panel The stiffeners are assumed to bestrong enough to provide the necessary edge support forthe panel

The stiffeners themselves are designed next A sectionof the baffle is assumed as acting with the stiffener and ascontributing to the overall stiffness This combinedsection is known as the composite stiffener Thecomposite section is checked for stress and deflectionBoth vertical and horizontal stiffeners can be added asrequired

If required an alternate design is assumed based ona thicker or thinner baffle and checked until a satisfactorydesign is found There is no ldquorightrdquo answer however itshould be noted that the thinner the baffle the greater thenumber of stiffeners The lightest overall weight isprobably the ldquobestrdquo design but may not be the leastexpensive due to the welding costs in attaching thestiffeners

One alternative to a flat baffle with stiffeners is to go toa curved baffle A curved baffle works best as a verticalbaffle in a vertical vessel The curved baffle takes pressurefrom either side wall If the pressure is on the concave sidethe baffle is in tension If the pressure is on the convexside the baffle is in compression

There are various tables given in this procedure for flatplate coefficients Flat plate coefficients are utilized todetermine the baffle thickness or a panel thickness Eachtable is specific for a given condition and loading

Vessel Internals 381

Notation

Ap frac14 area of baffle working with stiffener in2

As frac14 area of stiffener in2

Cp frac14 distance from centroid of composite section topanel in

Cs frac14 distance from centroid of composite section tostiffener in

E frac14 modulus of elasticity psiFb frac14 allowable bending stress psiI frac14 moment of inertia composite in4

Is frac14 moment of inertia stiffener in4

l frac14 length of baffle that works with the stiffener inM frac14 moment in-lbn frac14 number of welds attaching stiffenerP frac14 vessel internal pressure psigp frac14 maximum uniform pressure psipn frac14 uniform pressure at any elevation an psiRm frac14 vessel mean radius inSg frac14 specific gravity of contentst frac14 thickness shell intb frac14 thickness baffle ints frac14 thickness stiffener inV frac14 shear load lbw frac14 required fillet weld size ina frac14 thermal coefficient of expansion ininF

bg frac14 flat plate coefficientsDT frac14 differential temperature (design temperature

minus 70F) Fsb frac14 bending stress in baffle psiss frac14 bending stress in stiffener psi

6n frac14 radial expansion ind frac14 deflection inda frac14 maximum allowable deflection in

Baffle Dimensions

382 Pressure Vessel Design Manual

Table 5-24Flat plate coefficients

Vessel Internals 383

Unstiffened Baffle Check

bull Find load p

p frac14 624aSg144

bull Find baffle thickness tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

s

bull Find baffle deflection d

d frac14 pg1b4

Et3b

Limit deflection to the smaller of tb2 or b360 Ifdeflection is excessive then

a Increase the baffle thicknessb Add stiffenersc Go to curved baffle design

If stiffeners are added the first step is to find themaximum ldquoardquo and ldquobrdquo dimensions that will meet theallowable deflection for a given panel size This willestablish the stiffener spacing for both horizontal andvertical stiffeners The ultimate design is a balancebetween baffle thickness stiffener spacing and stiffenersize

Thermal Check of Baffle

bull Vessel radial expansion due to pressure

D1 frac14 085PRm

tE

bull Vessel radial expansion due to temperature

D2 frac14 Rma DT

bull Thermal expansion of baffle

D3 frac14 05ba DT

bull Differential expansion

D4 frac14 D1 thorn D2 D3

Stiffener Design

Divide baffle into panels to limit deflection to the lesserof tb2 or b360 Deflection is calculated based on theappropriate Cases 1 through 3

bull Check baffle for panel size a0 b0bull Check stiffener for length a or b

Recommendations for attaching stiffeners

Benefits Provides added stiffness and no corrosiontrap

Figure 5-18 Example of stiffener layout

384 Pressure Vessel Design Manual

As frac14 tsh

Ap frac14 tbl

IS frac14 tsh3

12

Cp frac14 AsyAs thorn Ap

thorn tb2

Cs frac14 ethhthorn tbTHORN Cp

I frac14 IS thorn Apt2b12

thorn AsApy2

As thorn Ap

lsquo frac14 lesser of 32tb or stiffener spacing

Stresses in BaffleStiffener

sp frac14 MCp

I

ss frac14 MCs

I

Size Welds Attaching Stiffeners

For E70XX Welds

w frac14 Vdy11 200In

Table 5-25Intermittent Welds

Percent of

Continuous Weld

Length of Intermittent Welds

and Distance Between Centers

75 3e4

66 4e6

60 3e5

57 4e7

50 2e4 3e6 4e8

44 4e9

43 3e7

40 2e5 4e10

37 3e8

33 2e6 3e9 4e12

Reprinted by permission of the James F Lincoln Arc Welding

Foundation

Vessel Internals 385

For E60XX Welds

w frac14 Vdy9600In

Sample Problem

bull Given Horizontal vessel with a vertical baffle

P frac14 250 psig

DT frac14 500F

Material frac14 SA-516-70

Ca frac14 0125 in

JE frac14 10

E frac14 273 106 psi

a frac14 7124 10-6 in=in=FFy frac14 308 ksi

D frac14 240 in

Fb frac14 066 Fy frac14 2033 ksi

Rm frac14 120938

ts frac14 175 in

Sg frac14 08

a frac14 15 ft

DT frac14 500 70 frac14 430F

bull Find baffle thickness without stiffener

p frac14 624aSg144

frac14 52 psi

a

bratio frac14 15=20 frac14 075

from Table 5-25 Case 1

b1 frac14 016 g1 frac14 0033

bull Thickness of baffle tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

sfrac14

ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi016eth52THORN2402

20 330

s

tb frac14 153thorn 025 frac14 178

No good Use stiffeners

bull Assume a suitable baffle thickness and determinemaximum panel size

tb frac14 075 in corroded

maximum panel size frac14 4ft 4ft

bull Maximum pressure p

p frac14 13eth624THORN08144

frac14 45 psi

a

bfrac14 4

4frac14 1

See Table 5-25 Case 3

b3 frac14 0287 g3 frac14 00443

sb frac14 b3pb2n

t2

frac14 0287eth45THORN4820752

frac14 5290 psi lt 20 333 psiFigure 5-19 Sample problem

386 Pressure Vessel Design Manual

d frac14 g3

pE

b4nt3

frac14 00443

45

273 106

484

0753

frac14 0092 in lt 0375 in

Balance OK by inspection

bull Assume a layout where the maximum stiffenerspacing is 4 ft

(4) horizontal stiffeners(4) vertical stiffeners(18) panels

bull Check horizontal stiffeners

Dimensions

a1 frac14 3 ft b1 frac14 4 ft

a2 frac14 4 ft b2 frac14 4 ft

a3 frac14 4 ft b3 frac14 12 ft

a4 frac14 4 ft b4 frac14 196 ft

a5 frac14 13 ft

a6 frac14 148ft

bull Assume stiffener size 1 in 4 in

y frac14 2375 in

As frac14 tsh frac14 1eth4THORN frac14 4 in2

l frac14 32tb frac14 32eth075THORN frac14 24 in lt 48 in

AP frac14 tbl frac14 07524 frac14 18 in2

Is frac14 bh3

12frac14 1

43

12frac14 533 in4

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 533thorn 0633thorn 1846 frac14 2442 in4

Cp frac14 AsyAs thorn Ap

thorn tb2

frac14 4eth2375THORN22

thorn 0752

frac14 0807 in

Cs frac14 hthorn tb

Cp

frac14 4thorn 075 0807 frac14 3943

Check deflections

Deflections exceed allowable No good

bull Assume a larger stiffener size WT9 593

tf frac14 106 025 frac14 081

tw frac14 0625 025 frac14 0375

bull Check corroded thickness to find properties ofcorroded section This section would be equivalent toa WT9 30 Properties are

As frac14 882 in2

Is frac14 647 in4

Cs frac14 216 in

H frac14 9 in

Cp frac14 hthorn tb Cs

frac14 9thorn 075 216 frac14 759 in

Figure 5-20 Battle layout for sample problem

Item bn pn d

1 2352 104 149

2 2352 243 349

3 144 381 0767

Vessel Internals 387

y frac14 Cp tb2

frac14 7215 in

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 647thorn 0844thorn 30814 frac14 3737 in4

bull Check stresses and deflections See results in Table5-27

bull Stresses and deflections are acceptablebull Check welds

d frac14 ts thorn 2tw frac14 0375thorn 2eth0323THORN frac14 102

y frac14 7215 in

I frac14 3737 in4

n frac14 2

w frac14 Vdy11 200In

frac14 6681eth102THORN721511 200eth3737THORN2

frac14 0005thorn 0125 frac14 013 in

bull Check thermal expansion of baffle

D1 frac14 085PRm

tEfrac14 085eth250THORN120938

175eth273 106THORNfrac14 000054 in

D2 frac14 Rma DT frac14 1209387124 106430

frac14 0370 in

D3 frac14 05ba DT frac14 05240

7124 106430

frac14 0367 in

D4 frac14 D1 thorn D2 D3 frac14 000054thorn 0370 0367

frac14 00035 lt 006 in

Table 5-26Summary of Results for Stress and Deflection in Composite Stiffeners for Sample Problem

Item Orientation an bn pn M d V sp ss

1 Horiz 2352 d 104 172595 009 2690 3504 997

2 Horiz 2352 d 243 403275 021 6287 8186 2330

3 Horiz 144 d 381 237012 0045 6035 4811 1370

4 Vert d 156 450 154674 0037 5648 3141 894

5 Vert d 1776 513 228539 0072 6681 6681 1320

Figure 5-21 Details of weld attaching stiffener

388 Pressure Vessel Design Manual

Vessel Internals 389

Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 24: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

Procedure 5-12 Design of Baffles [10]

Baffles are frequently used in pressure vessels eithervertical or horizontal to divide the interior volume intodifferent compartments These compartments may beused to segregate liquids or provide overflow weirs forthe separation of liquids Baffles may be stiffened orunstiffened When welded across the entire cross sectionof the vessel they must be checked that they are notunduly restricting the diametral expansion of the vesselIf the unrestrained radial expansion of the vessel exceedsthat of the baffle by more than 1=16 in (⅛ in on thediameter) then a ldquoflexiblerdquo type of connection betweenthe vessel shell and the baffle should be utilized Variousflexible attachment designs are shown within theprocedure

Baffles should always be designed in the corrodedcondition It is typical for welded baffles to be designedwith a full corrosion allowance on both sides If the baffleis bolted in then one-half the full corrosion allowancemay be applied to each side the logic being that a boltedbaffle is removable and therefore replaceable

The majority of baffles are flat and as a result are veryinefficient from a strength standpoint Deflection is thegoverning case for flat plates loaded on one side Thepreference is to have unstiffened baffles and they shouldalways be the first choice This will be acceptable forsmall baffles However for larger baffles as the bafflethickness becomes excessive stiffeners offer a moreeconomical design Therefore stiffeners are frequentlyused to stiffen the baffle to prevent the thickness of thebaffle from becoming excessive The number size andspacing of stiffeners are dependent on the baffle thicknessselected There is a continual trade-off between bafflethickness and stiffener parameters

The design of a baffle with stiffeners is an iterativeprocess The procedure for the design of the stiffeners isfirst to divide the baffle into ldquopanelrdquo sections that are rigidenough to withstand the pressure applied on one sideEach individual panel is checked as a flat plate of thedimensions of the panel The stiffeners are assumed to bestrong enough to provide the necessary edge support forthe panel

The stiffeners themselves are designed next A sectionof the baffle is assumed as acting with the stiffener and ascontributing to the overall stiffness This combinedsection is known as the composite stiffener Thecomposite section is checked for stress and deflectionBoth vertical and horizontal stiffeners can be added asrequired

If required an alternate design is assumed based ona thicker or thinner baffle and checked until a satisfactorydesign is found There is no ldquorightrdquo answer however itshould be noted that the thinner the baffle the greater thenumber of stiffeners The lightest overall weight isprobably the ldquobestrdquo design but may not be the leastexpensive due to the welding costs in attaching thestiffeners

One alternative to a flat baffle with stiffeners is to go toa curved baffle A curved baffle works best as a verticalbaffle in a vertical vessel The curved baffle takes pressurefrom either side wall If the pressure is on the concave sidethe baffle is in tension If the pressure is on the convexside the baffle is in compression

There are various tables given in this procedure for flatplate coefficients Flat plate coefficients are utilized todetermine the baffle thickness or a panel thickness Eachtable is specific for a given condition and loading

Vessel Internals 381

Notation

Ap frac14 area of baffle working with stiffener in2

As frac14 area of stiffener in2

Cp frac14 distance from centroid of composite section topanel in

Cs frac14 distance from centroid of composite section tostiffener in

E frac14 modulus of elasticity psiFb frac14 allowable bending stress psiI frac14 moment of inertia composite in4

Is frac14 moment of inertia stiffener in4

l frac14 length of baffle that works with the stiffener inM frac14 moment in-lbn frac14 number of welds attaching stiffenerP frac14 vessel internal pressure psigp frac14 maximum uniform pressure psipn frac14 uniform pressure at any elevation an psiRm frac14 vessel mean radius inSg frac14 specific gravity of contentst frac14 thickness shell intb frac14 thickness baffle ints frac14 thickness stiffener inV frac14 shear load lbw frac14 required fillet weld size ina frac14 thermal coefficient of expansion ininF

bg frac14 flat plate coefficientsDT frac14 differential temperature (design temperature

minus 70F) Fsb frac14 bending stress in baffle psiss frac14 bending stress in stiffener psi

6n frac14 radial expansion ind frac14 deflection inda frac14 maximum allowable deflection in

Baffle Dimensions

382 Pressure Vessel Design Manual

Table 5-24Flat plate coefficients

Vessel Internals 383

Unstiffened Baffle Check

bull Find load p

p frac14 624aSg144

bull Find baffle thickness tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

s

bull Find baffle deflection d

d frac14 pg1b4

Et3b

Limit deflection to the smaller of tb2 or b360 Ifdeflection is excessive then

a Increase the baffle thicknessb Add stiffenersc Go to curved baffle design

If stiffeners are added the first step is to find themaximum ldquoardquo and ldquobrdquo dimensions that will meet theallowable deflection for a given panel size This willestablish the stiffener spacing for both horizontal andvertical stiffeners The ultimate design is a balancebetween baffle thickness stiffener spacing and stiffenersize

Thermal Check of Baffle

bull Vessel radial expansion due to pressure

D1 frac14 085PRm

tE

bull Vessel radial expansion due to temperature

D2 frac14 Rma DT

bull Thermal expansion of baffle

D3 frac14 05ba DT

bull Differential expansion

D4 frac14 D1 thorn D2 D3

Stiffener Design

Divide baffle into panels to limit deflection to the lesserof tb2 or b360 Deflection is calculated based on theappropriate Cases 1 through 3

bull Check baffle for panel size a0 b0bull Check stiffener for length a or b

Recommendations for attaching stiffeners

Benefits Provides added stiffness and no corrosiontrap

Figure 5-18 Example of stiffener layout

384 Pressure Vessel Design Manual

As frac14 tsh

Ap frac14 tbl

IS frac14 tsh3

12

Cp frac14 AsyAs thorn Ap

thorn tb2

Cs frac14 ethhthorn tbTHORN Cp

I frac14 IS thorn Apt2b12

thorn AsApy2

As thorn Ap

lsquo frac14 lesser of 32tb or stiffener spacing

Stresses in BaffleStiffener

sp frac14 MCp

I

ss frac14 MCs

I

Size Welds Attaching Stiffeners

For E70XX Welds

w frac14 Vdy11 200In

Table 5-25Intermittent Welds

Percent of

Continuous Weld

Length of Intermittent Welds

and Distance Between Centers

75 3e4

66 4e6

60 3e5

57 4e7

50 2e4 3e6 4e8

44 4e9

43 3e7

40 2e5 4e10

37 3e8

33 2e6 3e9 4e12

Reprinted by permission of the James F Lincoln Arc Welding

Foundation

Vessel Internals 385

For E60XX Welds

w frac14 Vdy9600In

Sample Problem

bull Given Horizontal vessel with a vertical baffle

P frac14 250 psig

DT frac14 500F

Material frac14 SA-516-70

Ca frac14 0125 in

JE frac14 10

E frac14 273 106 psi

a frac14 7124 10-6 in=in=FFy frac14 308 ksi

D frac14 240 in

Fb frac14 066 Fy frac14 2033 ksi

Rm frac14 120938

ts frac14 175 in

Sg frac14 08

a frac14 15 ft

DT frac14 500 70 frac14 430F

bull Find baffle thickness without stiffener

p frac14 624aSg144

frac14 52 psi

a

bratio frac14 15=20 frac14 075

from Table 5-25 Case 1

b1 frac14 016 g1 frac14 0033

bull Thickness of baffle tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

sfrac14

ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi016eth52THORN2402

20 330

s

tb frac14 153thorn 025 frac14 178

No good Use stiffeners

bull Assume a suitable baffle thickness and determinemaximum panel size

tb frac14 075 in corroded

maximum panel size frac14 4ft 4ft

bull Maximum pressure p

p frac14 13eth624THORN08144

frac14 45 psi

a

bfrac14 4

4frac14 1

See Table 5-25 Case 3

b3 frac14 0287 g3 frac14 00443

sb frac14 b3pb2n

t2

frac14 0287eth45THORN4820752

frac14 5290 psi lt 20 333 psiFigure 5-19 Sample problem

386 Pressure Vessel Design Manual

d frac14 g3

pE

b4nt3

frac14 00443

45

273 106

484

0753

frac14 0092 in lt 0375 in

Balance OK by inspection

bull Assume a layout where the maximum stiffenerspacing is 4 ft

(4) horizontal stiffeners(4) vertical stiffeners(18) panels

bull Check horizontal stiffeners

Dimensions

a1 frac14 3 ft b1 frac14 4 ft

a2 frac14 4 ft b2 frac14 4 ft

a3 frac14 4 ft b3 frac14 12 ft

a4 frac14 4 ft b4 frac14 196 ft

a5 frac14 13 ft

a6 frac14 148ft

bull Assume stiffener size 1 in 4 in

y frac14 2375 in

As frac14 tsh frac14 1eth4THORN frac14 4 in2

l frac14 32tb frac14 32eth075THORN frac14 24 in lt 48 in

AP frac14 tbl frac14 07524 frac14 18 in2

Is frac14 bh3

12frac14 1

43

12frac14 533 in4

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 533thorn 0633thorn 1846 frac14 2442 in4

Cp frac14 AsyAs thorn Ap

thorn tb2

frac14 4eth2375THORN22

thorn 0752

frac14 0807 in

Cs frac14 hthorn tb

Cp

frac14 4thorn 075 0807 frac14 3943

Check deflections

Deflections exceed allowable No good

bull Assume a larger stiffener size WT9 593

tf frac14 106 025 frac14 081

tw frac14 0625 025 frac14 0375

bull Check corroded thickness to find properties ofcorroded section This section would be equivalent toa WT9 30 Properties are

As frac14 882 in2

Is frac14 647 in4

Cs frac14 216 in

H frac14 9 in

Cp frac14 hthorn tb Cs

frac14 9thorn 075 216 frac14 759 in

Figure 5-20 Battle layout for sample problem

Item bn pn d

1 2352 104 149

2 2352 243 349

3 144 381 0767

Vessel Internals 387

y frac14 Cp tb2

frac14 7215 in

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 647thorn 0844thorn 30814 frac14 3737 in4

bull Check stresses and deflections See results in Table5-27

bull Stresses and deflections are acceptablebull Check welds

d frac14 ts thorn 2tw frac14 0375thorn 2eth0323THORN frac14 102

y frac14 7215 in

I frac14 3737 in4

n frac14 2

w frac14 Vdy11 200In

frac14 6681eth102THORN721511 200eth3737THORN2

frac14 0005thorn 0125 frac14 013 in

bull Check thermal expansion of baffle

D1 frac14 085PRm

tEfrac14 085eth250THORN120938

175eth273 106THORNfrac14 000054 in

D2 frac14 Rma DT frac14 1209387124 106430

frac14 0370 in

D3 frac14 05ba DT frac14 05240

7124 106430

frac14 0367 in

D4 frac14 D1 thorn D2 D3 frac14 000054thorn 0370 0367

frac14 00035 lt 006 in

Table 5-26Summary of Results for Stress and Deflection in Composite Stiffeners for Sample Problem

Item Orientation an bn pn M d V sp ss

1 Horiz 2352 d 104 172595 009 2690 3504 997

2 Horiz 2352 d 243 403275 021 6287 8186 2330

3 Horiz 144 d 381 237012 0045 6035 4811 1370

4 Vert d 156 450 154674 0037 5648 3141 894

5 Vert d 1776 513 228539 0072 6681 6681 1320

Figure 5-21 Details of weld attaching stiffener

388 Pressure Vessel Design Manual

Vessel Internals 389

Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 25: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

Notation

Ap frac14 area of baffle working with stiffener in2

As frac14 area of stiffener in2

Cp frac14 distance from centroid of composite section topanel in

Cs frac14 distance from centroid of composite section tostiffener in

E frac14 modulus of elasticity psiFb frac14 allowable bending stress psiI frac14 moment of inertia composite in4

Is frac14 moment of inertia stiffener in4

l frac14 length of baffle that works with the stiffener inM frac14 moment in-lbn frac14 number of welds attaching stiffenerP frac14 vessel internal pressure psigp frac14 maximum uniform pressure psipn frac14 uniform pressure at any elevation an psiRm frac14 vessel mean radius inSg frac14 specific gravity of contentst frac14 thickness shell intb frac14 thickness baffle ints frac14 thickness stiffener inV frac14 shear load lbw frac14 required fillet weld size ina frac14 thermal coefficient of expansion ininF

bg frac14 flat plate coefficientsDT frac14 differential temperature (design temperature

minus 70F) Fsb frac14 bending stress in baffle psiss frac14 bending stress in stiffener psi

6n frac14 radial expansion ind frac14 deflection inda frac14 maximum allowable deflection in

Baffle Dimensions

382 Pressure Vessel Design Manual

Table 5-24Flat plate coefficients

Vessel Internals 383

Unstiffened Baffle Check

bull Find load p

p frac14 624aSg144

bull Find baffle thickness tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

s

bull Find baffle deflection d

d frac14 pg1b4

Et3b

Limit deflection to the smaller of tb2 or b360 Ifdeflection is excessive then

a Increase the baffle thicknessb Add stiffenersc Go to curved baffle design

If stiffeners are added the first step is to find themaximum ldquoardquo and ldquobrdquo dimensions that will meet theallowable deflection for a given panel size This willestablish the stiffener spacing for both horizontal andvertical stiffeners The ultimate design is a balancebetween baffle thickness stiffener spacing and stiffenersize

Thermal Check of Baffle

bull Vessel radial expansion due to pressure

D1 frac14 085PRm

tE

bull Vessel radial expansion due to temperature

D2 frac14 Rma DT

bull Thermal expansion of baffle

D3 frac14 05ba DT

bull Differential expansion

D4 frac14 D1 thorn D2 D3

Stiffener Design

Divide baffle into panels to limit deflection to the lesserof tb2 or b360 Deflection is calculated based on theappropriate Cases 1 through 3

bull Check baffle for panel size a0 b0bull Check stiffener for length a or b

Recommendations for attaching stiffeners

Benefits Provides added stiffness and no corrosiontrap

Figure 5-18 Example of stiffener layout

384 Pressure Vessel Design Manual

As frac14 tsh

Ap frac14 tbl

IS frac14 tsh3

12

Cp frac14 AsyAs thorn Ap

thorn tb2

Cs frac14 ethhthorn tbTHORN Cp

I frac14 IS thorn Apt2b12

thorn AsApy2

As thorn Ap

lsquo frac14 lesser of 32tb or stiffener spacing

Stresses in BaffleStiffener

sp frac14 MCp

I

ss frac14 MCs

I

Size Welds Attaching Stiffeners

For E70XX Welds

w frac14 Vdy11 200In

Table 5-25Intermittent Welds

Percent of

Continuous Weld

Length of Intermittent Welds

and Distance Between Centers

75 3e4

66 4e6

60 3e5

57 4e7

50 2e4 3e6 4e8

44 4e9

43 3e7

40 2e5 4e10

37 3e8

33 2e6 3e9 4e12

Reprinted by permission of the James F Lincoln Arc Welding

Foundation

Vessel Internals 385

For E60XX Welds

w frac14 Vdy9600In

Sample Problem

bull Given Horizontal vessel with a vertical baffle

P frac14 250 psig

DT frac14 500F

Material frac14 SA-516-70

Ca frac14 0125 in

JE frac14 10

E frac14 273 106 psi

a frac14 7124 10-6 in=in=FFy frac14 308 ksi

D frac14 240 in

Fb frac14 066 Fy frac14 2033 ksi

Rm frac14 120938

ts frac14 175 in

Sg frac14 08

a frac14 15 ft

DT frac14 500 70 frac14 430F

bull Find baffle thickness without stiffener

p frac14 624aSg144

frac14 52 psi

a

bratio frac14 15=20 frac14 075

from Table 5-25 Case 1

b1 frac14 016 g1 frac14 0033

bull Thickness of baffle tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

sfrac14

ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi016eth52THORN2402

20 330

s

tb frac14 153thorn 025 frac14 178

No good Use stiffeners

bull Assume a suitable baffle thickness and determinemaximum panel size

tb frac14 075 in corroded

maximum panel size frac14 4ft 4ft

bull Maximum pressure p

p frac14 13eth624THORN08144

frac14 45 psi

a

bfrac14 4

4frac14 1

See Table 5-25 Case 3

b3 frac14 0287 g3 frac14 00443

sb frac14 b3pb2n

t2

frac14 0287eth45THORN4820752

frac14 5290 psi lt 20 333 psiFigure 5-19 Sample problem

386 Pressure Vessel Design Manual

d frac14 g3

pE

b4nt3

frac14 00443

45

273 106

484

0753

frac14 0092 in lt 0375 in

Balance OK by inspection

bull Assume a layout where the maximum stiffenerspacing is 4 ft

(4) horizontal stiffeners(4) vertical stiffeners(18) panels

bull Check horizontal stiffeners

Dimensions

a1 frac14 3 ft b1 frac14 4 ft

a2 frac14 4 ft b2 frac14 4 ft

a3 frac14 4 ft b3 frac14 12 ft

a4 frac14 4 ft b4 frac14 196 ft

a5 frac14 13 ft

a6 frac14 148ft

bull Assume stiffener size 1 in 4 in

y frac14 2375 in

As frac14 tsh frac14 1eth4THORN frac14 4 in2

l frac14 32tb frac14 32eth075THORN frac14 24 in lt 48 in

AP frac14 tbl frac14 07524 frac14 18 in2

Is frac14 bh3

12frac14 1

43

12frac14 533 in4

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 533thorn 0633thorn 1846 frac14 2442 in4

Cp frac14 AsyAs thorn Ap

thorn tb2

frac14 4eth2375THORN22

thorn 0752

frac14 0807 in

Cs frac14 hthorn tb

Cp

frac14 4thorn 075 0807 frac14 3943

Check deflections

Deflections exceed allowable No good

bull Assume a larger stiffener size WT9 593

tf frac14 106 025 frac14 081

tw frac14 0625 025 frac14 0375

bull Check corroded thickness to find properties ofcorroded section This section would be equivalent toa WT9 30 Properties are

As frac14 882 in2

Is frac14 647 in4

Cs frac14 216 in

H frac14 9 in

Cp frac14 hthorn tb Cs

frac14 9thorn 075 216 frac14 759 in

Figure 5-20 Battle layout for sample problem

Item bn pn d

1 2352 104 149

2 2352 243 349

3 144 381 0767

Vessel Internals 387

y frac14 Cp tb2

frac14 7215 in

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 647thorn 0844thorn 30814 frac14 3737 in4

bull Check stresses and deflections See results in Table5-27

bull Stresses and deflections are acceptablebull Check welds

d frac14 ts thorn 2tw frac14 0375thorn 2eth0323THORN frac14 102

y frac14 7215 in

I frac14 3737 in4

n frac14 2

w frac14 Vdy11 200In

frac14 6681eth102THORN721511 200eth3737THORN2

frac14 0005thorn 0125 frac14 013 in

bull Check thermal expansion of baffle

D1 frac14 085PRm

tEfrac14 085eth250THORN120938

175eth273 106THORNfrac14 000054 in

D2 frac14 Rma DT frac14 1209387124 106430

frac14 0370 in

D3 frac14 05ba DT frac14 05240

7124 106430

frac14 0367 in

D4 frac14 D1 thorn D2 D3 frac14 000054thorn 0370 0367

frac14 00035 lt 006 in

Table 5-26Summary of Results for Stress and Deflection in Composite Stiffeners for Sample Problem

Item Orientation an bn pn M d V sp ss

1 Horiz 2352 d 104 172595 009 2690 3504 997

2 Horiz 2352 d 243 403275 021 6287 8186 2330

3 Horiz 144 d 381 237012 0045 6035 4811 1370

4 Vert d 156 450 154674 0037 5648 3141 894

5 Vert d 1776 513 228539 0072 6681 6681 1320

Figure 5-21 Details of weld attaching stiffener

388 Pressure Vessel Design Manual

Vessel Internals 389

Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 26: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

Table 5-24Flat plate coefficients

Vessel Internals 383

Unstiffened Baffle Check

bull Find load p

p frac14 624aSg144

bull Find baffle thickness tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

s

bull Find baffle deflection d

d frac14 pg1b4

Et3b

Limit deflection to the smaller of tb2 or b360 Ifdeflection is excessive then

a Increase the baffle thicknessb Add stiffenersc Go to curved baffle design

If stiffeners are added the first step is to find themaximum ldquoardquo and ldquobrdquo dimensions that will meet theallowable deflection for a given panel size This willestablish the stiffener spacing for both horizontal andvertical stiffeners The ultimate design is a balancebetween baffle thickness stiffener spacing and stiffenersize

Thermal Check of Baffle

bull Vessel radial expansion due to pressure

D1 frac14 085PRm

tE

bull Vessel radial expansion due to temperature

D2 frac14 Rma DT

bull Thermal expansion of baffle

D3 frac14 05ba DT

bull Differential expansion

D4 frac14 D1 thorn D2 D3

Stiffener Design

Divide baffle into panels to limit deflection to the lesserof tb2 or b360 Deflection is calculated based on theappropriate Cases 1 through 3

bull Check baffle for panel size a0 b0bull Check stiffener for length a or b

Recommendations for attaching stiffeners

Benefits Provides added stiffness and no corrosiontrap

Figure 5-18 Example of stiffener layout

384 Pressure Vessel Design Manual

As frac14 tsh

Ap frac14 tbl

IS frac14 tsh3

12

Cp frac14 AsyAs thorn Ap

thorn tb2

Cs frac14 ethhthorn tbTHORN Cp

I frac14 IS thorn Apt2b12

thorn AsApy2

As thorn Ap

lsquo frac14 lesser of 32tb or stiffener spacing

Stresses in BaffleStiffener

sp frac14 MCp

I

ss frac14 MCs

I

Size Welds Attaching Stiffeners

For E70XX Welds

w frac14 Vdy11 200In

Table 5-25Intermittent Welds

Percent of

Continuous Weld

Length of Intermittent Welds

and Distance Between Centers

75 3e4

66 4e6

60 3e5

57 4e7

50 2e4 3e6 4e8

44 4e9

43 3e7

40 2e5 4e10

37 3e8

33 2e6 3e9 4e12

Reprinted by permission of the James F Lincoln Arc Welding

Foundation

Vessel Internals 385

For E60XX Welds

w frac14 Vdy9600In

Sample Problem

bull Given Horizontal vessel with a vertical baffle

P frac14 250 psig

DT frac14 500F

Material frac14 SA-516-70

Ca frac14 0125 in

JE frac14 10

E frac14 273 106 psi

a frac14 7124 10-6 in=in=FFy frac14 308 ksi

D frac14 240 in

Fb frac14 066 Fy frac14 2033 ksi

Rm frac14 120938

ts frac14 175 in

Sg frac14 08

a frac14 15 ft

DT frac14 500 70 frac14 430F

bull Find baffle thickness without stiffener

p frac14 624aSg144

frac14 52 psi

a

bratio frac14 15=20 frac14 075

from Table 5-25 Case 1

b1 frac14 016 g1 frac14 0033

bull Thickness of baffle tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

sfrac14

ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi016eth52THORN2402

20 330

s

tb frac14 153thorn 025 frac14 178

No good Use stiffeners

bull Assume a suitable baffle thickness and determinemaximum panel size

tb frac14 075 in corroded

maximum panel size frac14 4ft 4ft

bull Maximum pressure p

p frac14 13eth624THORN08144

frac14 45 psi

a

bfrac14 4

4frac14 1

See Table 5-25 Case 3

b3 frac14 0287 g3 frac14 00443

sb frac14 b3pb2n

t2

frac14 0287eth45THORN4820752

frac14 5290 psi lt 20 333 psiFigure 5-19 Sample problem

386 Pressure Vessel Design Manual

d frac14 g3

pE

b4nt3

frac14 00443

45

273 106

484

0753

frac14 0092 in lt 0375 in

Balance OK by inspection

bull Assume a layout where the maximum stiffenerspacing is 4 ft

(4) horizontal stiffeners(4) vertical stiffeners(18) panels

bull Check horizontal stiffeners

Dimensions

a1 frac14 3 ft b1 frac14 4 ft

a2 frac14 4 ft b2 frac14 4 ft

a3 frac14 4 ft b3 frac14 12 ft

a4 frac14 4 ft b4 frac14 196 ft

a5 frac14 13 ft

a6 frac14 148ft

bull Assume stiffener size 1 in 4 in

y frac14 2375 in

As frac14 tsh frac14 1eth4THORN frac14 4 in2

l frac14 32tb frac14 32eth075THORN frac14 24 in lt 48 in

AP frac14 tbl frac14 07524 frac14 18 in2

Is frac14 bh3

12frac14 1

43

12frac14 533 in4

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 533thorn 0633thorn 1846 frac14 2442 in4

Cp frac14 AsyAs thorn Ap

thorn tb2

frac14 4eth2375THORN22

thorn 0752

frac14 0807 in

Cs frac14 hthorn tb

Cp

frac14 4thorn 075 0807 frac14 3943

Check deflections

Deflections exceed allowable No good

bull Assume a larger stiffener size WT9 593

tf frac14 106 025 frac14 081

tw frac14 0625 025 frac14 0375

bull Check corroded thickness to find properties ofcorroded section This section would be equivalent toa WT9 30 Properties are

As frac14 882 in2

Is frac14 647 in4

Cs frac14 216 in

H frac14 9 in

Cp frac14 hthorn tb Cs

frac14 9thorn 075 216 frac14 759 in

Figure 5-20 Battle layout for sample problem

Item bn pn d

1 2352 104 149

2 2352 243 349

3 144 381 0767

Vessel Internals 387

y frac14 Cp tb2

frac14 7215 in

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 647thorn 0844thorn 30814 frac14 3737 in4

bull Check stresses and deflections See results in Table5-27

bull Stresses and deflections are acceptablebull Check welds

d frac14 ts thorn 2tw frac14 0375thorn 2eth0323THORN frac14 102

y frac14 7215 in

I frac14 3737 in4

n frac14 2

w frac14 Vdy11 200In

frac14 6681eth102THORN721511 200eth3737THORN2

frac14 0005thorn 0125 frac14 013 in

bull Check thermal expansion of baffle

D1 frac14 085PRm

tEfrac14 085eth250THORN120938

175eth273 106THORNfrac14 000054 in

D2 frac14 Rma DT frac14 1209387124 106430

frac14 0370 in

D3 frac14 05ba DT frac14 05240

7124 106430

frac14 0367 in

D4 frac14 D1 thorn D2 D3 frac14 000054thorn 0370 0367

frac14 00035 lt 006 in

Table 5-26Summary of Results for Stress and Deflection in Composite Stiffeners for Sample Problem

Item Orientation an bn pn M d V sp ss

1 Horiz 2352 d 104 172595 009 2690 3504 997

2 Horiz 2352 d 243 403275 021 6287 8186 2330

3 Horiz 144 d 381 237012 0045 6035 4811 1370

4 Vert d 156 450 154674 0037 5648 3141 894

5 Vert d 1776 513 228539 0072 6681 6681 1320

Figure 5-21 Details of weld attaching stiffener

388 Pressure Vessel Design Manual

Vessel Internals 389

Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 27: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

Unstiffened Baffle Check

bull Find load p

p frac14 624aSg144

bull Find baffle thickness tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

s

bull Find baffle deflection d

d frac14 pg1b4

Et3b

Limit deflection to the smaller of tb2 or b360 Ifdeflection is excessive then

a Increase the baffle thicknessb Add stiffenersc Go to curved baffle design

If stiffeners are added the first step is to find themaximum ldquoardquo and ldquobrdquo dimensions that will meet theallowable deflection for a given panel size This willestablish the stiffener spacing for both horizontal andvertical stiffeners The ultimate design is a balancebetween baffle thickness stiffener spacing and stiffenersize

Thermal Check of Baffle

bull Vessel radial expansion due to pressure

D1 frac14 085PRm

tE

bull Vessel radial expansion due to temperature

D2 frac14 Rma DT

bull Thermal expansion of baffle

D3 frac14 05ba DT

bull Differential expansion

D4 frac14 D1 thorn D2 D3

Stiffener Design

Divide baffle into panels to limit deflection to the lesserof tb2 or b360 Deflection is calculated based on theappropriate Cases 1 through 3

bull Check baffle for panel size a0 b0bull Check stiffener for length a or b

Recommendations for attaching stiffeners

Benefits Provides added stiffness and no corrosiontrap

Figure 5-18 Example of stiffener layout

384 Pressure Vessel Design Manual

As frac14 tsh

Ap frac14 tbl

IS frac14 tsh3

12

Cp frac14 AsyAs thorn Ap

thorn tb2

Cs frac14 ethhthorn tbTHORN Cp

I frac14 IS thorn Apt2b12

thorn AsApy2

As thorn Ap

lsquo frac14 lesser of 32tb or stiffener spacing

Stresses in BaffleStiffener

sp frac14 MCp

I

ss frac14 MCs

I

Size Welds Attaching Stiffeners

For E70XX Welds

w frac14 Vdy11 200In

Table 5-25Intermittent Welds

Percent of

Continuous Weld

Length of Intermittent Welds

and Distance Between Centers

75 3e4

66 4e6

60 3e5

57 4e7

50 2e4 3e6 4e8

44 4e9

43 3e7

40 2e5 4e10

37 3e8

33 2e6 3e9 4e12

Reprinted by permission of the James F Lincoln Arc Welding

Foundation

Vessel Internals 385

For E60XX Welds

w frac14 Vdy9600In

Sample Problem

bull Given Horizontal vessel with a vertical baffle

P frac14 250 psig

DT frac14 500F

Material frac14 SA-516-70

Ca frac14 0125 in

JE frac14 10

E frac14 273 106 psi

a frac14 7124 10-6 in=in=FFy frac14 308 ksi

D frac14 240 in

Fb frac14 066 Fy frac14 2033 ksi

Rm frac14 120938

ts frac14 175 in

Sg frac14 08

a frac14 15 ft

DT frac14 500 70 frac14 430F

bull Find baffle thickness without stiffener

p frac14 624aSg144

frac14 52 psi

a

bratio frac14 15=20 frac14 075

from Table 5-25 Case 1

b1 frac14 016 g1 frac14 0033

bull Thickness of baffle tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

sfrac14

ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi016eth52THORN2402

20 330

s

tb frac14 153thorn 025 frac14 178

No good Use stiffeners

bull Assume a suitable baffle thickness and determinemaximum panel size

tb frac14 075 in corroded

maximum panel size frac14 4ft 4ft

bull Maximum pressure p

p frac14 13eth624THORN08144

frac14 45 psi

a

bfrac14 4

4frac14 1

See Table 5-25 Case 3

b3 frac14 0287 g3 frac14 00443

sb frac14 b3pb2n

t2

frac14 0287eth45THORN4820752

frac14 5290 psi lt 20 333 psiFigure 5-19 Sample problem

386 Pressure Vessel Design Manual

d frac14 g3

pE

b4nt3

frac14 00443

45

273 106

484

0753

frac14 0092 in lt 0375 in

Balance OK by inspection

bull Assume a layout where the maximum stiffenerspacing is 4 ft

(4) horizontal stiffeners(4) vertical stiffeners(18) panels

bull Check horizontal stiffeners

Dimensions

a1 frac14 3 ft b1 frac14 4 ft

a2 frac14 4 ft b2 frac14 4 ft

a3 frac14 4 ft b3 frac14 12 ft

a4 frac14 4 ft b4 frac14 196 ft

a5 frac14 13 ft

a6 frac14 148ft

bull Assume stiffener size 1 in 4 in

y frac14 2375 in

As frac14 tsh frac14 1eth4THORN frac14 4 in2

l frac14 32tb frac14 32eth075THORN frac14 24 in lt 48 in

AP frac14 tbl frac14 07524 frac14 18 in2

Is frac14 bh3

12frac14 1

43

12frac14 533 in4

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 533thorn 0633thorn 1846 frac14 2442 in4

Cp frac14 AsyAs thorn Ap

thorn tb2

frac14 4eth2375THORN22

thorn 0752

frac14 0807 in

Cs frac14 hthorn tb

Cp

frac14 4thorn 075 0807 frac14 3943

Check deflections

Deflections exceed allowable No good

bull Assume a larger stiffener size WT9 593

tf frac14 106 025 frac14 081

tw frac14 0625 025 frac14 0375

bull Check corroded thickness to find properties ofcorroded section This section would be equivalent toa WT9 30 Properties are

As frac14 882 in2

Is frac14 647 in4

Cs frac14 216 in

H frac14 9 in

Cp frac14 hthorn tb Cs

frac14 9thorn 075 216 frac14 759 in

Figure 5-20 Battle layout for sample problem

Item bn pn d

1 2352 104 149

2 2352 243 349

3 144 381 0767

Vessel Internals 387

y frac14 Cp tb2

frac14 7215 in

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 647thorn 0844thorn 30814 frac14 3737 in4

bull Check stresses and deflections See results in Table5-27

bull Stresses and deflections are acceptablebull Check welds

d frac14 ts thorn 2tw frac14 0375thorn 2eth0323THORN frac14 102

y frac14 7215 in

I frac14 3737 in4

n frac14 2

w frac14 Vdy11 200In

frac14 6681eth102THORN721511 200eth3737THORN2

frac14 0005thorn 0125 frac14 013 in

bull Check thermal expansion of baffle

D1 frac14 085PRm

tEfrac14 085eth250THORN120938

175eth273 106THORNfrac14 000054 in

D2 frac14 Rma DT frac14 1209387124 106430

frac14 0370 in

D3 frac14 05ba DT frac14 05240

7124 106430

frac14 0367 in

D4 frac14 D1 thorn D2 D3 frac14 000054thorn 0370 0367

frac14 00035 lt 006 in

Table 5-26Summary of Results for Stress and Deflection in Composite Stiffeners for Sample Problem

Item Orientation an bn pn M d V sp ss

1 Horiz 2352 d 104 172595 009 2690 3504 997

2 Horiz 2352 d 243 403275 021 6287 8186 2330

3 Horiz 144 d 381 237012 0045 6035 4811 1370

4 Vert d 156 450 154674 0037 5648 3141 894

5 Vert d 1776 513 228539 0072 6681 6681 1320

Figure 5-21 Details of weld attaching stiffener

388 Pressure Vessel Design Manual

Vessel Internals 389

Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 28: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

As frac14 tsh

Ap frac14 tbl

IS frac14 tsh3

12

Cp frac14 AsyAs thorn Ap

thorn tb2

Cs frac14 ethhthorn tbTHORN Cp

I frac14 IS thorn Apt2b12

thorn AsApy2

As thorn Ap

lsquo frac14 lesser of 32tb or stiffener spacing

Stresses in BaffleStiffener

sp frac14 MCp

I

ss frac14 MCs

I

Size Welds Attaching Stiffeners

For E70XX Welds

w frac14 Vdy11 200In

Table 5-25Intermittent Welds

Percent of

Continuous Weld

Length of Intermittent Welds

and Distance Between Centers

75 3e4

66 4e6

60 3e5

57 4e7

50 2e4 3e6 4e8

44 4e9

43 3e7

40 2e5 4e10

37 3e8

33 2e6 3e9 4e12

Reprinted by permission of the James F Lincoln Arc Welding

Foundation

Vessel Internals 385

For E60XX Welds

w frac14 Vdy9600In

Sample Problem

bull Given Horizontal vessel with a vertical baffle

P frac14 250 psig

DT frac14 500F

Material frac14 SA-516-70

Ca frac14 0125 in

JE frac14 10

E frac14 273 106 psi

a frac14 7124 10-6 in=in=FFy frac14 308 ksi

D frac14 240 in

Fb frac14 066 Fy frac14 2033 ksi

Rm frac14 120938

ts frac14 175 in

Sg frac14 08

a frac14 15 ft

DT frac14 500 70 frac14 430F

bull Find baffle thickness without stiffener

p frac14 624aSg144

frac14 52 psi

a

bratio frac14 15=20 frac14 075

from Table 5-25 Case 1

b1 frac14 016 g1 frac14 0033

bull Thickness of baffle tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

sfrac14

ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi016eth52THORN2402

20 330

s

tb frac14 153thorn 025 frac14 178

No good Use stiffeners

bull Assume a suitable baffle thickness and determinemaximum panel size

tb frac14 075 in corroded

maximum panel size frac14 4ft 4ft

bull Maximum pressure p

p frac14 13eth624THORN08144

frac14 45 psi

a

bfrac14 4

4frac14 1

See Table 5-25 Case 3

b3 frac14 0287 g3 frac14 00443

sb frac14 b3pb2n

t2

frac14 0287eth45THORN4820752

frac14 5290 psi lt 20 333 psiFigure 5-19 Sample problem

386 Pressure Vessel Design Manual

d frac14 g3

pE

b4nt3

frac14 00443

45

273 106

484

0753

frac14 0092 in lt 0375 in

Balance OK by inspection

bull Assume a layout where the maximum stiffenerspacing is 4 ft

(4) horizontal stiffeners(4) vertical stiffeners(18) panels

bull Check horizontal stiffeners

Dimensions

a1 frac14 3 ft b1 frac14 4 ft

a2 frac14 4 ft b2 frac14 4 ft

a3 frac14 4 ft b3 frac14 12 ft

a4 frac14 4 ft b4 frac14 196 ft

a5 frac14 13 ft

a6 frac14 148ft

bull Assume stiffener size 1 in 4 in

y frac14 2375 in

As frac14 tsh frac14 1eth4THORN frac14 4 in2

l frac14 32tb frac14 32eth075THORN frac14 24 in lt 48 in

AP frac14 tbl frac14 07524 frac14 18 in2

Is frac14 bh3

12frac14 1

43

12frac14 533 in4

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 533thorn 0633thorn 1846 frac14 2442 in4

Cp frac14 AsyAs thorn Ap

thorn tb2

frac14 4eth2375THORN22

thorn 0752

frac14 0807 in

Cs frac14 hthorn tb

Cp

frac14 4thorn 075 0807 frac14 3943

Check deflections

Deflections exceed allowable No good

bull Assume a larger stiffener size WT9 593

tf frac14 106 025 frac14 081

tw frac14 0625 025 frac14 0375

bull Check corroded thickness to find properties ofcorroded section This section would be equivalent toa WT9 30 Properties are

As frac14 882 in2

Is frac14 647 in4

Cs frac14 216 in

H frac14 9 in

Cp frac14 hthorn tb Cs

frac14 9thorn 075 216 frac14 759 in

Figure 5-20 Battle layout for sample problem

Item bn pn d

1 2352 104 149

2 2352 243 349

3 144 381 0767

Vessel Internals 387

y frac14 Cp tb2

frac14 7215 in

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 647thorn 0844thorn 30814 frac14 3737 in4

bull Check stresses and deflections See results in Table5-27

bull Stresses and deflections are acceptablebull Check welds

d frac14 ts thorn 2tw frac14 0375thorn 2eth0323THORN frac14 102

y frac14 7215 in

I frac14 3737 in4

n frac14 2

w frac14 Vdy11 200In

frac14 6681eth102THORN721511 200eth3737THORN2

frac14 0005thorn 0125 frac14 013 in

bull Check thermal expansion of baffle

D1 frac14 085PRm

tEfrac14 085eth250THORN120938

175eth273 106THORNfrac14 000054 in

D2 frac14 Rma DT frac14 1209387124 106430

frac14 0370 in

D3 frac14 05ba DT frac14 05240

7124 106430

frac14 0367 in

D4 frac14 D1 thorn D2 D3 frac14 000054thorn 0370 0367

frac14 00035 lt 006 in

Table 5-26Summary of Results for Stress and Deflection in Composite Stiffeners for Sample Problem

Item Orientation an bn pn M d V sp ss

1 Horiz 2352 d 104 172595 009 2690 3504 997

2 Horiz 2352 d 243 403275 021 6287 8186 2330

3 Horiz 144 d 381 237012 0045 6035 4811 1370

4 Vert d 156 450 154674 0037 5648 3141 894

5 Vert d 1776 513 228539 0072 6681 6681 1320

Figure 5-21 Details of weld attaching stiffener

388 Pressure Vessel Design Manual

Vessel Internals 389

Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 29: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

For E60XX Welds

w frac14 Vdy9600In

Sample Problem

bull Given Horizontal vessel with a vertical baffle

P frac14 250 psig

DT frac14 500F

Material frac14 SA-516-70

Ca frac14 0125 in

JE frac14 10

E frac14 273 106 psi

a frac14 7124 10-6 in=in=FFy frac14 308 ksi

D frac14 240 in

Fb frac14 066 Fy frac14 2033 ksi

Rm frac14 120938

ts frac14 175 in

Sg frac14 08

a frac14 15 ft

DT frac14 500 70 frac14 430F

bull Find baffle thickness without stiffener

p frac14 624aSg144

frac14 52 psi

a

bratio frac14 15=20 frac14 075

from Table 5-25 Case 1

b1 frac14 016 g1 frac14 0033

bull Thickness of baffle tb

tb frac14ffiffiffiffiffiffiffiffiffiffiffiffib1pb

2

Fb

sfrac14

ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffi016eth52THORN2402

20 330

s

tb frac14 153thorn 025 frac14 178

No good Use stiffeners

bull Assume a suitable baffle thickness and determinemaximum panel size

tb frac14 075 in corroded

maximum panel size frac14 4ft 4ft

bull Maximum pressure p

p frac14 13eth624THORN08144

frac14 45 psi

a

bfrac14 4

4frac14 1

See Table 5-25 Case 3

b3 frac14 0287 g3 frac14 00443

sb frac14 b3pb2n

t2

frac14 0287eth45THORN4820752

frac14 5290 psi lt 20 333 psiFigure 5-19 Sample problem

386 Pressure Vessel Design Manual

d frac14 g3

pE

b4nt3

frac14 00443

45

273 106

484

0753

frac14 0092 in lt 0375 in

Balance OK by inspection

bull Assume a layout where the maximum stiffenerspacing is 4 ft

(4) horizontal stiffeners(4) vertical stiffeners(18) panels

bull Check horizontal stiffeners

Dimensions

a1 frac14 3 ft b1 frac14 4 ft

a2 frac14 4 ft b2 frac14 4 ft

a3 frac14 4 ft b3 frac14 12 ft

a4 frac14 4 ft b4 frac14 196 ft

a5 frac14 13 ft

a6 frac14 148ft

bull Assume stiffener size 1 in 4 in

y frac14 2375 in

As frac14 tsh frac14 1eth4THORN frac14 4 in2

l frac14 32tb frac14 32eth075THORN frac14 24 in lt 48 in

AP frac14 tbl frac14 07524 frac14 18 in2

Is frac14 bh3

12frac14 1

43

12frac14 533 in4

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 533thorn 0633thorn 1846 frac14 2442 in4

Cp frac14 AsyAs thorn Ap

thorn tb2

frac14 4eth2375THORN22

thorn 0752

frac14 0807 in

Cs frac14 hthorn tb

Cp

frac14 4thorn 075 0807 frac14 3943

Check deflections

Deflections exceed allowable No good

bull Assume a larger stiffener size WT9 593

tf frac14 106 025 frac14 081

tw frac14 0625 025 frac14 0375

bull Check corroded thickness to find properties ofcorroded section This section would be equivalent toa WT9 30 Properties are

As frac14 882 in2

Is frac14 647 in4

Cs frac14 216 in

H frac14 9 in

Cp frac14 hthorn tb Cs

frac14 9thorn 075 216 frac14 759 in

Figure 5-20 Battle layout for sample problem

Item bn pn d

1 2352 104 149

2 2352 243 349

3 144 381 0767

Vessel Internals 387

y frac14 Cp tb2

frac14 7215 in

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 647thorn 0844thorn 30814 frac14 3737 in4

bull Check stresses and deflections See results in Table5-27

bull Stresses and deflections are acceptablebull Check welds

d frac14 ts thorn 2tw frac14 0375thorn 2eth0323THORN frac14 102

y frac14 7215 in

I frac14 3737 in4

n frac14 2

w frac14 Vdy11 200In

frac14 6681eth102THORN721511 200eth3737THORN2

frac14 0005thorn 0125 frac14 013 in

bull Check thermal expansion of baffle

D1 frac14 085PRm

tEfrac14 085eth250THORN120938

175eth273 106THORNfrac14 000054 in

D2 frac14 Rma DT frac14 1209387124 106430

frac14 0370 in

D3 frac14 05ba DT frac14 05240

7124 106430

frac14 0367 in

D4 frac14 D1 thorn D2 D3 frac14 000054thorn 0370 0367

frac14 00035 lt 006 in

Table 5-26Summary of Results for Stress and Deflection in Composite Stiffeners for Sample Problem

Item Orientation an bn pn M d V sp ss

1 Horiz 2352 d 104 172595 009 2690 3504 997

2 Horiz 2352 d 243 403275 021 6287 8186 2330

3 Horiz 144 d 381 237012 0045 6035 4811 1370

4 Vert d 156 450 154674 0037 5648 3141 894

5 Vert d 1776 513 228539 0072 6681 6681 1320

Figure 5-21 Details of weld attaching stiffener

388 Pressure Vessel Design Manual

Vessel Internals 389

Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 30: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

d frac14 g3

pE

b4nt3

frac14 00443

45

273 106

484

0753

frac14 0092 in lt 0375 in

Balance OK by inspection

bull Assume a layout where the maximum stiffenerspacing is 4 ft

(4) horizontal stiffeners(4) vertical stiffeners(18) panels

bull Check horizontal stiffeners

Dimensions

a1 frac14 3 ft b1 frac14 4 ft

a2 frac14 4 ft b2 frac14 4 ft

a3 frac14 4 ft b3 frac14 12 ft

a4 frac14 4 ft b4 frac14 196 ft

a5 frac14 13 ft

a6 frac14 148ft

bull Assume stiffener size 1 in 4 in

y frac14 2375 in

As frac14 tsh frac14 1eth4THORN frac14 4 in2

l frac14 32tb frac14 32eth075THORN frac14 24 in lt 48 in

AP frac14 tbl frac14 07524 frac14 18 in2

Is frac14 bh3

12frac14 1

43

12frac14 533 in4

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 533thorn 0633thorn 1846 frac14 2442 in4

Cp frac14 AsyAs thorn Ap

thorn tb2

frac14 4eth2375THORN22

thorn 0752

frac14 0807 in

Cs frac14 hthorn tb

Cp

frac14 4thorn 075 0807 frac14 3943

Check deflections

Deflections exceed allowable No good

bull Assume a larger stiffener size WT9 593

tf frac14 106 025 frac14 081

tw frac14 0625 025 frac14 0375

bull Check corroded thickness to find properties ofcorroded section This section would be equivalent toa WT9 30 Properties are

As frac14 882 in2

Is frac14 647 in4

Cs frac14 216 in

H frac14 9 in

Cp frac14 hthorn tb Cs

frac14 9thorn 075 216 frac14 759 in

Figure 5-20 Battle layout for sample problem

Item bn pn d

1 2352 104 149

2 2352 243 349

3 144 381 0767

Vessel Internals 387

y frac14 Cp tb2

frac14 7215 in

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 647thorn 0844thorn 30814 frac14 3737 in4

bull Check stresses and deflections See results in Table5-27

bull Stresses and deflections are acceptablebull Check welds

d frac14 ts thorn 2tw frac14 0375thorn 2eth0323THORN frac14 102

y frac14 7215 in

I frac14 3737 in4

n frac14 2

w frac14 Vdy11 200In

frac14 6681eth102THORN721511 200eth3737THORN2

frac14 0005thorn 0125 frac14 013 in

bull Check thermal expansion of baffle

D1 frac14 085PRm

tEfrac14 085eth250THORN120938

175eth273 106THORNfrac14 000054 in

D2 frac14 Rma DT frac14 1209387124 106430

frac14 0370 in

D3 frac14 05ba DT frac14 05240

7124 106430

frac14 0367 in

D4 frac14 D1 thorn D2 D3 frac14 000054thorn 0370 0367

frac14 00035 lt 006 in

Table 5-26Summary of Results for Stress and Deflection in Composite Stiffeners for Sample Problem

Item Orientation an bn pn M d V sp ss

1 Horiz 2352 d 104 172595 009 2690 3504 997

2 Horiz 2352 d 243 403275 021 6287 8186 2330

3 Horiz 144 d 381 237012 0045 6035 4811 1370

4 Vert d 156 450 154674 0037 5648 3141 894

5 Vert d 1776 513 228539 0072 6681 6681 1320

Figure 5-21 Details of weld attaching stiffener

388 Pressure Vessel Design Manual

Vessel Internals 389

Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 31: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

y frac14 Cp tb2

frac14 7215 in

I frac14 Is thorn Apt2b12

thorn AsApy2

As thorn Ap

frac14 647thorn 0844thorn 30814 frac14 3737 in4

bull Check stresses and deflections See results in Table5-27

bull Stresses and deflections are acceptablebull Check welds

d frac14 ts thorn 2tw frac14 0375thorn 2eth0323THORN frac14 102

y frac14 7215 in

I frac14 3737 in4

n frac14 2

w frac14 Vdy11 200In

frac14 6681eth102THORN721511 200eth3737THORN2

frac14 0005thorn 0125 frac14 013 in

bull Check thermal expansion of baffle

D1 frac14 085PRm

tEfrac14 085eth250THORN120938

175eth273 106THORNfrac14 000054 in

D2 frac14 Rma DT frac14 1209387124 106430

frac14 0370 in

D3 frac14 05ba DT frac14 05240

7124 106430

frac14 0367 in

D4 frac14 D1 thorn D2 D3 frac14 000054thorn 0370 0367

frac14 00035 lt 006 in

Table 5-26Summary of Results for Stress and Deflection in Composite Stiffeners for Sample Problem

Item Orientation an bn pn M d V sp ss

1 Horiz 2352 d 104 172595 009 2690 3504 997

2 Horiz 2352 d 243 403275 021 6287 8186 2330

3 Horiz 144 d 381 237012 0045 6035 4811 1370

4 Vert d 156 450 154674 0037 5648 3141 894

5 Vert d 1776 513 228539 0072 6681 6681 1320

Figure 5-21 Details of weld attaching stiffener

388 Pressure Vessel Design Manual

Vessel Internals 389

Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 32: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

Vessel Internals 389

Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

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Miscellaneous Baffle Configurations

Table 5-27Dimension A

Nozzle Size (in) A (in) Nozzle Size (in) A (in)

2 5 14 18

3 7 16 20

4 8 18 22

6 10 20 24

8 12 24 28

10 14

12 16

390 Pressure Vessel Design Manual

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 34: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

Procedure 5-13 Design of Impingement Plates

Notation

A frac14 Cross sectional area of nozzle in2

d frac14 Density of liquid PCFF frac14 Equivalent static force LbsFb frac14 Allowable bending stress PSIFy frac14 Minimum specified yield strength PSI

FU frac14 Minimum specified tensile strength PSIFW frac14 Allowable shear stress PSIfb frac14 Bending stress PSIfw frac14 Fillet weld sizeg frac14 Acceleration due to gravity 32 FtSec2

LW frac14 Length of weld inr frac14 Inside radius of nozzle inV frac14 Velocity FPSsS frac14 Shear stress per inch of weld PSI

Calculation

bull Equivalent static force F

F frac14 ethV A dTHORN=gbull Maximum bending stress at center of plate fbn frac14 w=h lt 1ethUse 1 for square plateTHORNfb frac14

53 F

1thorn 24 n2 t2THORNbull Allowable stressa Bending Fb

Lesser of 6 Fy or 3 FUb Weld in Shear FS

frac14 4 Fy

Size of weld required

bull Length of weld LWa Welded from one side only

LW frac14 2 w

b Welded both sides top and bottom

LW frac14 4 w

bull Shear per inch of weld sSsS frac14 F=LW

bull Size of weld required fWfW frac14 sS=707 FS

F r

TYP

h

h

Dimensions of baffle impingement plate

t

fw

fw

r

w

Figure 5-22 Dimensions of Baffle Impingement Plate

Vessel Internals 391

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual

Page 35: Pressure Vessel Design Manual - PVManagepvmanage.com/wp-content/uploads/2019/01/Pages-from-Pages-from-PRESSUR… · Noz Size N Noz Size N

References

[1] Ackley EJ Film Coefficient of Heat Transfer forAgitated Process Vessels Chemical EngineeringAugust 22 1960

[2] Stuhlbarg D How to Design Tank Heating CoilsPetroleum Refiner April 1959

[3] Steve EH Refine Temperature Control in an Odd-Shaped Vessel Hydrocarbon Processing July 1999

[4] Bisi F Menicatti S How to Calculate Tank HeatLosses Hydrocarbon Processing February 1967

[5] Kumana JD Kothari SP Predict Storage Tank HeatTransfer Precisely Chemical Engineering March 221982

[6] Kern DQ Process Heat Transfer McGraw-Hill1950

[7] Bondy F Lippa S Heat Transfer in AgitatedVessels Chemical Engineering April 4 1983

[8] Steam Its Generation and Use 40th ed Babcockand Wilcox Company 1992 section 3ndash12

[9] ldquoFlow of Fluids through Valves Fittings and PiperdquoCrane Company Technical Paper No 410

[10] Blodgett OW Design of Welded structures JFLincoln Arc Welding Foundation 1966 Section 53

[11] Manual of Steel Construction 8th ed AmericanInstitute of Steel Construction Inc 1988

392 Pressure Vessel Design Manual


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