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7/31/2019 Tonycalcelate English

1/32

1.

2.

(YES/NO)

(kg/cm2G)

(kg/cm2G)

()()

(kg/cm2G)

()

()

3.

4.CNS

5.


2/32


3/32

Inside radius(corroded) R

Do

tm

Internal pressure P

Extermal design pressure Px

Static head pressure Phd

Design temperature tem

Corrosion allowance CA

1

Joint efficiency E()

Shell material

Shell length L

Max. allowable stress S

Modulus of elasticity @ design trmperture E

P does not exceed 0.385SE P= 45.0 < 0.385SE= 266.42

T does ot exceed 0.5R T= 40.0 < 0.5R=

Cylinders having Do/t values Do/t > Do/t=

Tr1

Tr2

Tr3

NOTE

Circumferential Shell or tube-CNS9789 5.2

Minimum required thickness ,Tt1=(P+Phd)R/(SE-0.6(P+Phd))

Minimum required thickness(min. thickness >1.6mm)

Minimum required thickness for extemal pressure(assumed)

DESIGN DATA

Outside diameter SHELL or TUBE of moninal thickness

Assume SHELL or TUBE thickness

Radiograp examination (1=FULL/2=SPOT)

CALCULATION


4/32

335.00 mm.

1756.00 mm.

40.000 mm.

45.00 kg/cm2G

30.00 kg/cm2G

0.00 kg/cm2G

110.00

0.00 mm.

1

4500

692 kg/cm2

1765268 kg/cm2

Kg/cm2 #OK#

mm. #OK#

#FROME 1#

22.67 mm.

22.67 mm.

40.00 mm.


5/32

Ps

Pt

Temp.-SS

Temp.-TS

No. Description Material St(Kg/cm2)

1 SA106-B 1202

2

3

4

5

6S

Ph

TEST


1 TUBE SIDE SA312-312 1174

2

3

4

5

6

S

Ph

TEST

NOTE

HYDOSTATIC TEST PRESSURE FOR SHEEL SIDE =1.25PS

TUBE SIDE-CNS9788 11.6.3 (2)

Sd(Kg/

117


St=Max. allowable stress at test temperature

Sd=Max. allowable stress at desgin temperature

SHELL SIDE -CNS9788 11.6.3 (2)

Sd(Kg/

120

Design pressure

SHELL SIDE

TUBE SIDE

Design Temperature

SHELL SIDE

TUBE SIDE


6/32

Kg/cm2g

13.58 Kg/cm2g

St/Sd

1

Kg/cm2g

Kg/cm2g

St/Sd

1

Kg/cm2g

Kg/cm2g

1.00

m2)

1.00

m2)


7/32

1. CNS9788 KEY

2.

DESIGN PRESSURE 16.8

DESIGN TEMPERATURE 165

MAX. OPERATING PRESSURE 12.4

MAX. OPERATING TEMPERATURE 135

HYDROSTATIC TEST PRESSURE 25.2

335

RADIOGRAPHY EXAMIATION

JOINT EFFICIENCY

CORROSION ALLOWANCE 3MIN. DESIGN METAL TEMPERATURE

IMPACT TEST

POSTWELD HEAT TREATMENT

INSULATION

FLUID

NUMBER OF PASSES

EMPTY WEIGHT

FULL OF WATER WEIGHT

VOLUME 1.27

HEATING SURFACE

LETHAL DESIGN

Material

SHELLS SA516-70

CHANNELS SA516-70

CAP --

TUBESHEETS SA516-70

CHANNEL FLANGES SA105

TUBES SA179

NOZZLE FLANGES (Shell side)

NOZZLE NECKS (Shell side)

NOZZLE FLANGES (Tube side)

NOZZLE NECKS (tube side)

MATERIAL SPECIFICATION

1

1.

DESIGN CODECNS9788SHEL

INSIDE RADIUS(corroded)R

FU


8/32

kg/cm2g 10.5 kg/cm2g

280

kg/cm2g 3.5 kg/cm2g

146

kg/cm2g 15.75 kg/cm2g

mm. 335 mm.

mm. 3 mm.

M3 0.56 M3

St(Kg/cm2) Sd(Kg/cm2) St/Sd

1230 1230 1.00

1230 1230 1.00

1230 1230 1.00

1230 1230 1.00

1670 1670 1.00

kg.

4 m2

NA

kg.

0 1.00

NO

NA

SIDE TUBE SIDE

LL FULL


9/32

R

Nominal thickness tm

Design pressure P




1


Shell material




Tr1Tr2

Tr

Td

MAWP

CONCLUSTION

mm.

mm.



Tr1

Tr2

Tr

Td

MAWP

CONCLUSTION

5.28 mm.

12.00 mm.

NOTE

#SUFFICIENT#


Minimum required thickness , Tr=Max of {Tr1,Tr2}

Design thickness , Td=Tr+CA

MAWP=(tm-CA)2SE/(R+0.2(tm-CA))-Phd

The design shell thickness of

Selecting the nomial thickness of

The design shell thickness of

Selecting the nomial thickness of

#SUFFICIENT#

Spherical Shells CNS9789 3.3

Minimum required thickness ,Tt1=(P+Phd)R/(2SE+0.4(P+Phd))

Circumferential Shell or tube CNS9789 3.2

Minimum required thickness ,Tt1=(P+Phd)R/(S*E-0.6(P+Phd))Minimum required thickness(min. thickness >1.6mm)

Minimum required thickness , Tr=Max of {Tr1,Tr2}

Design thickness , Td=Tr+CA

MAWP=(tm-CA)SE/(R+0.6(tm-CA))-Phd

DESIGN DATA

Inside radius(corroded)


CALCULATION


10/32

335.00 mm.

12.00 mm.

16.80 kg/cm2

0.00 kg/cm2

165

3.00 mm.

1

1230 Kg/cm2

Kg/cm2 #OK#

mm. #OK#

4.61 mm.4.61 mm.

4.61 mm.

7.61 mm.

20.72 Kg/cm2

Kg/cm2 #OK#

mm. #OK#

2.28 mm.

2.28 mm.

2.28 mm.

5.28 mm.

65.74 kg/cm2G


11/32

R

Nominal thickness tm

Internal pressure P




Type of head(1=Ellipsidal /2=Torispherical)

2


Shell material


Tr1Tr2

Tr

Final center line radius Rf

Original centerline radius=infinity for flat plate Re

% Extreme fiber elongation =(75*tm(1-Rf/Re))/Rf 0.223714286 >

MAWP

CONCLUSTION

The design shell thickness of mm.

Selecting the nomial thickness of mm.

Tr1

Tr2

Tr

Final center line radius Rf

Original centerline radius=infinity for flat plate Re

% Extreme fiber elongation =(75*tm(1-Rf/Re))/Rf 0.223714286 >

Design thickness shall not exceed thickness after formin

Check extreme fiber eiongation for exemption of heat treatment after formin

Torispherical CNS9789 4.2

Minimum required thickness ,Tt1=1.77(P+Phd)Di/(2SE+0.2(P+Phd))


Design thickness , Tr=Max.{Tr1,Tr2}+CA

%Reduction after forming =>Assume to be

Thickness after forming =Tr+CA/(1-%)

Thickness after forming =Tr+CA/(1-%)

Design thickness shall not exceed thickness after formin

Check extreme fiber eiongation for exemption of heat treatment after formin

MAWP=(tm-CA)2SE/(Di+0.2(tm-CA))-Phd

CALCULATION

Ellipsoidal Head CNS9789 4.3

Minimum required thickness ,Tt1=(P+Phd)Di/(2SE-0.2(P+Phd))Minimum required thickness(min. thickness >1.6mm)

Design thickness , Tr=Max.{Tr1,Tr2}+CA

%Reduction after forming =>Assume to be

DESIGN DATA

Inside radius(corroded)



12/32

MAWP

CONCLUSTION

The design shell thickness of mm.

Selecting the nomial thickness of mm.

NOTE

MAWP=(tm-CA)2SE/(1.77Di+0.2(tm-CA))-Phd


13/32

335.00 mm.

10.44 mm.

16.80 Kg/cm2G

0.00 Kg/cm2G

165.00

3.00 mm.

1

1230 Kg/cm2

2.29 mm.2.29 mm.

5.29 mm.

15.00 %

8.82 mm.

35.00 mm.

infinity mm.

0.05 #OK#

45.60 Kg/cm2G

4.04 mm.

4.04 mm.

7.04 mm.

15.00 %

7.10 mm.

35.00 mm.

infinity mm.

0.05 #OK#

#SATISFACTORY#

CNS 97888.6(7)

#SATISFACTORY#

CNS 97888.6(7)


14/32

30.79 kg/cm2G


15/32

DESIGN DATA

Shell side internal pressure(negatibe sign if vacuum) Ps

Tube side internal pressure(negatibe sign if vacuum) Pt

Shell side internal design Tem. Temp-S

Tube side internal design Tem. Temp-T

Shell outside diameter Ds(Do)Shell thickness Ts(ts)

Shell inside diameter(corroded codition) Di(G)

Inside corrosion allowance of shell Cas

Tube outside diameter Dt

Tube thickness Tt

Tube pitch Pit

Tube length L

Number of tube N

Tube patter(2=Square/1=Triangular)

Outside diameter of the tubesheet ACorrosion allowance of tubesheet Cats

Nominal thickness of tubesheet h

Assume tubesheet thickness Tass


TUBESHEET Material

Max. allowable stress at design metal temperature Sts

Elastic modulus of tubesheet at metal temperature E

SHELL Material

Elastic modulus of shell at mean metal temperature Es

TUBE Material

Elastic modulus of tube at mean metal temperature Et

CALCULATION

K=EsTs(Ds-Ts)/(EtTtN(Dt-Tt)) K

Fq=0.25+(F-0.6)(300TsEs/(KLE)(Di/Tass)3)0.25 Fq(Fg)

F=(17-100(TsDi))/15 (Max 1-Min 8) F

J=1 for shell without expansion joint J

s=coefficient of thermal expansion of the shell s

t=coefficient of thermal expansion of the tubes tTm=shell mean metal temperature Tm

tm=tube mean metal temperature tm

Differential metal growth ,dL=L(tes(Tm-70)-tet(tm-70)) dl

Pd=4JEsTs(dl/Lt)/((Ds-3Ts)(1+JKFq) Pd(Pe)

Mo=Total moment acting under operating conditions Mo

1.FACTOR

2.EQUIVALENT DIFFERENTIAL EXPANSION PRESSURE CNS9792-5.5(1

3.EQUIVALENT BOLTING PRESSURE CNS9792-5.5(2)


16/32

Mg=Total momet acting under bolting-up conditions Mg

Pbt=620Mo/(F2Di3) Pbt

Pbs=620Mg/(F2Di3) Pbs

fs=1-N(Dt/Di)2 fs

Ps'=Ps(0.4J(1.5+K(1.5+fs/(1+KFq))) Ps'

1.1 P=(Ps'-Pd)/2

1.2 P=Ps'

1.3 P=Pbs

1.4 P=(Ps'-Pd-Pbs)/2

1.5 P=(Pbs+Pd)/2

1.6 P=(Ps'-Pbs)

ft=1-N((Dt-2Tt)/Di)2 ft

Pt'=Pt(1+0.4JK(1.5+ft)/(1+JKFq) Pt'

2.1 P=(Pt'+Pbt+Pd)/2

2.2 P=Pt'+Pbt

3.1 P=Pt'-Ps'+Pbt

3.2 P=(Pt'-Ps'+Pbt+Pd)/2

3.3 P=Pbs

3.4 P=(Pbs+Pd)/2

3.5 P=Pt'-Ps'

3.6 P=(Pt'-Ps'+Pd)/2

3.7 P=PbtThe greatest absolute value of Max.P{1.1-3.7} P

= 1-0.907/(Pit/Dt)2 or 1-0.785/(Pit/Dt)2

Tcal=FDi/3(P/(nSts))0.5 Tcal(t1)

Effective design pressure for shear formular Ph

Ph/Sts

1.6(1-Dt/Pit)2

Checkif Ph/Sts


17/32

Tmin=max{Tcal(t1),(t2),Tr(tr)}+2Cats Tmin

COCLUSION

The minimum design thickness is 64.6

Ttherefore selecting nominal thickness of 80.0

NOTE


18/32

16.8 kg/cm2G

10.5 kg/cm2G

165

280

694 mm.

12 mm.

670 mm.

3 mm.

19.05 mm.

2.11 mm.

25.4 mm.

4800 mm.

207

2

830 mm.3 mm.

80 mm.

58 mm.

1670 kg/cm2

2070000 kg/cm2

2070000 kg/cm2

2070000 kg/cm2

1.106

2.524

1.000

1

0.000006513 (1/)

0.000006698 (1/)

165

280

-3.782 mm

-31.90 kg/cm2

20961804.7 kg-mm

)


19/32

10169837.3 kg-mm

43.21 kg/cm2

20.96 kg/cm2

0.8327

8.23 kg/cm2

20.07 kg/cm2

8.23 kg/cm2

20.96 kg/cm2

9.58 kg/cm2

-5.47 kg/cm2

-12.73 kg/cm2

0.898584802

4.75 kg/cm2

8.029118879 kg/cm2

47.96 kg/cm2

39.73 kg/cm2

3.914118879 kg/cm2

20.96 kg/cm2

-5.469290266 kg/cm2

-3.48 kg/cm2

-17.69146246 kg/cm2

43.21 kg/cm247.96 kg/cm2

0.5584375

50.647 mm

? kg/cm2

mm

1.23880597

20961804.71 kg-mm

58.607 mm

-5.3


20/32

64.607 mm

mm

mm

#SATISFACTORY#


21/32

E-730

Outside diameter of flange

Inside diameter of flange(corroded)

Bolt-circle diamter

Number of boltSize of bolt

Cross section area per a bolt

Outside diameter of gasket

Width of gasket used to determine the basic gasket seating

Thickness of gasket

Thickness of hub at small end

Thickness of hub at back of flange

Tub length

Corrosion allowance

Intermal design pressureFlange thickness

Max. allowable stress at design temprtature

Max. allowable stress at atm temprtature

Gasket or joint contact-surface unit seating load

Gasket factor

Allowable bolt stress at design temperatureAllowable bolt stress at atm temperature

Factor involvig K

Factor ho=(Bgo)0.5

g1 /go=

h / ho=

Factor d,d=(u/v)hogo2

Factor e,e=F/ho

Factor for intergraltype flages ,F5

Hub stress corrosion factor integral type flanges , f4

BOLT:

CALCULATION

1.FACTOR

Ratio of outside diameter of alange to inside diameter of flange ,K=A/B

Factor for intergraltype flages ,V8

DESIGN DATA


FLANGE:

Gasket :


22/32

Factor L,L=(te+1)/T+t3/d

Basic gasket seating width , bo=N/2

?

Diameter at location of gasket load reaction

Wm1=0.785G2P+2b3.14159mP

Wm2=3.14159bGy

For the operating conditions..

Total hydrostatic end force, H=0.785G2P

Hydrostatic end force on area inside of flange ,HD=0.785B2P

HT=H-HDGasket load HG=Wm1-H

R=(C-B)/2-g1

Total flange moment for the operating conditions Mo=MD+MG+MT

Longitudinal hub stress ,SH=fMo/(Lg12B)Longitudinal hub stress ,SH=fMg/(Lg12B)

Radial flange stress ,SR=(1.33te+1)Mo/(Lt2B)

Radial flange stress ,SR=(1.33te+1)Mg/(Lt2B)

4.CALCULATION OF FLAGE STRESSES (CNS9791-3.5)

Tangential flange stress ,ST=YMo/(t2B)-ZSR1

Tangential flange stress ,ST=YMg/(t2B)-ZSR2

5.CHECKED CODITIONS (CNS9791-3.6)

Total cross-sectional area of bolts at root of thread required for the operting conditions

Total cross-sectional area of bolts at root of thread required for gaster seating

Total required cross-sectional area of bolts, taken as the greater of Am1 and Am2

Cross-section area of the bolts using the root diameter of the thread

Flang design bolt load , Wg=(Am+Ab)Sa/2

Total flange moment for gasket seating , Mg=Wg(C-G)/2

Radial distance from the bolt circle to the circle on which HT acts=(R+g1+hG)/2

Radial distance from gasket load reaction to the bolt circle hG=(C-G)/2

Component of moment due to HD , MD=HDHd

Component of moment due to HG , MG=HGHg

Component of moment due to HT , MT=HTHt

3.2For gasket seating

Min required bolt load for gasket seating

3.FLANGE MOMENT (CNS9791-3.4)

Difference between total hydrostatic end force and the hydrostatic end force

3.1For intergral flange

Radial distance from BCD to point of intersection of hub and hub flange

Radial distance from the bolt circle to the circle on which HD acts=R+0.5g1

2.BOLT LOADS (CNS9791-3.3)- -

Effective gasket or joint contact surfaace seating width

b=0.5(bo)0.5 for bo>6.35mm(0.25in) or b=bo for bo


23/32

SH is mot greater then 1.5*Sf SH=

SR is not greater then Sf SR=

ST is not greater then Sf ST=

(SH+SR)/2 is not greater then Sf =

(SH+ST)/2 is not greater then Sf =

mm.

mm.

NOTE

The required for the not operting conditions t1

The required for the operting conditions t2

Design thickness of flange ,Tm=Mix.{t1,t2}+CA

The design thickness of flange is

Therefore the norminal thickness used of

#ALL CONDITIONS ARE SATISFACTORY

6.MIX. USED THICKNEES OF FLANGE


24/32

A 3217 mm

B 3000 mm

C 3176 mm

128 setDb 19.05 mm

Ar 195.00 mm2

do 3142 mm

N 12.5 mm

Tg 4 mm

go 16 mm

g1 48 mm

h 98 mm

CA 3 mm

P 4.2 Kg/cm2Gt mm

Sfb 1406 Kg/cm2

Sfa 1406 Kg/cm2

y 7.1 Kg/cm2

m 4.25

Sb 1757 Kg/cm2Sa 1757 Kg/cm2

K 1.072

T 1.887

U 30.363

Y 27.630

Z 14.342

ho 219.089 mm

3.000

0.447

V 0.146

F 0.810

f 3.940

d 11663983.8 mm3

e 0.004 1/mm

SA193-B7

SA266-4

GRAPHITE


25/32

L 0.919

bo 6.25 mm

b 6.30 mm

6.25

G 3129.50 mm

Wm1 Kg

Wm2 Kg

H 322900.61 Kg

HD 296877.42 Kg

HT 26023.19 KgHG 22112.26 Kg

R 40.000 mm

Hd 64.000 mm

Ht 55.625 mm

Hg 23.250 mm

MD 19000154.88 kg-mm

MG 514110.16 kg-mm

MT 1447539.67 kg-mm

Mo kg-mm

Am1 19636.5 mm2

Am2 24830.8 mm2

Am mm2

Ab 24960.0 mm2

437412.4 kg

Mg kg-mm

SH1 1300.330Kg/cm2

SH2 630.869 Kg/cm2

SR1 82.837 Kg/cm2

SR2 40.189 Kg/cm2

ST1 (1187.943) Kg/cm2

ST2 (548.335) Kg/cm2


26/32

1.5*Sf= Kg/cm2

Sf= Kg/cm2

Sf= Kg/cm2

Sf= Kg/cm2

Sf= Kg/cm2

t1 mm

t2 mm

mm

#SUFFICIENT#


27/32

ITEM

Nominal pipe size

Outside diameter Do

Thickness of nozzle TnThickness of STD wall pipe T(STD)

Corrosion allwannce of nozzle Can

Material of nozzle

Max. allowable stress of nozzle Sn

Joint efficiency of nozzle En

Internal design pressure P

Desing temperature degree

Location to be attached

Outside diameter of vessel

Nominal thickness of vesselCorrosion allwannce of vessel Cas

Max. allowable stress of vessel Sv

Joint efficiency of vessel Es

Required thickness of nozzle Trn=PR/(SE-0.6P) Trn

Tr1=Trn+Can Tr1

Required thickness of seamless shell or head Tr

Tr2=Tr+Cas Tr2

Min. thickness according to CNS9788 6.1.5+Cas Tr3

The greater of Min.{Tr2,Tr3} Tr4

Min. thickness of STD. wall pipe Tm1=T(STD)0.875 Tm1

Tr5=Tm1+Can Tr5

The lesser of Tr4 or Tr5 Tr6

The greater of Min.{Tr1,Tr6} Trq

Tn'=Tn0.875 Tn'

DESIGN DATA

CALCULATION

Nozzle Neck Thickness CNS9788 6.9.2

If Tn' >Trq ,The nozzle neck thickness is "adequate"


28/32

N1

2"SCH10 NPS

60.3 mm.

5.54 mm.3.91 mm.

3 mm.

SA106-B

1202 kg/cm2g

1

6 kg/cm2g

70

Shell -

219.1 mm.

6.35 mm.3 mm.

1202 kg/cm2g

1

0.12 mm.

3.12 mm.

0.52 mm.

3.52 mm.

4.60 mm.

4.60 mm.

3.42 mm.

6.42 mm.

4.60 mm.

4.60 mm.

4.85 mm.

NOZZLE

#ADEQUATE#


29/32

ITEM

Outside diameter Dn

Thickness of nozzle tn

Corrosion allwannce of nozzle Can

Material of nozzle

Max. allowable stress of nozzle Sn

Joint efficiency of nozzle En

Internal design pressure P

Material of vessel

Outside diameter of vessel Ds

Nominal thickness of vessel t

Corrosion allwannce of vessel Cas

Max. allowable stress of vessel Sv

Joint efficiency of vessel Es

Thickness required of shell ,Tr=PR/(SvEn-0.6P) Tr

Thickness required of nozzle ,Trn=PR/(SnEs-0.6P) Trn

Total area of reinforcement required A=dTrF+2TnTrF(1-fr1) A

A11=d(Est-ftr)-2tn(Est-ftr)(1-fr1) A11

A12=2(t+tn)(Est-Ftr)-2tn(Est-Ftr)(1-fr1) A12

A1=Max.{A11,A12} A1

A21=5(tn-trn)fr2t A21

A22=5(tn-trn)fr2tn A22

A2=Min.{A21,A23} A2

A5=(Dp-d-2tn)tefr3 A5

If A'=A1+A2+A3+A41+A43+A5>A,Opening is adequately A'

A'>A

(5)Cross-sectional area of various welds available as reinforcement

DESIGN DATA

FACTORCALCULATION

Reinforement required for openings in shell CNS9790 3.1

(1).Area in excess thickness in the vessel wall available for reinforcement

(2).Area in excess thickness in the nozzle wall available for reinforcement


30/32

N2

320.1 mm.

60.2 mm.

0 mm.

1103 kg/cm2g

1

45 kg/cm2g

755.5 mm.

39.75 mm.

3 mm.

1103 kg/cm2g

1

14.14 mm.

4.18 mm.

4524.83 mm2

8199.14 mm2

5120.30 mm2

8199.14 mm2

11134.79 mm2

16863.26 mm2

11134.79 mm2

0.00 mm2

19333.93 mm2

#ADEQUATELY#


31/32

Ps

Pt

Temp.-SS

Temp.-TS

SHELL

TUBESHEEL

TUBE

FLANGE

NOZZLE

STUD BOLT

CHANNEL

PIPE


1 SA516-70 1230

2

3

4

5

6

S

Ph

TEST

NOTE


St=Max. allowable stress at test temperature

Sd=Max. allowable stress at desgin temperatureSHELL SIDE -CNS9788 11.6.2 (2)

Sd(Kg/

123

Design pressure

SHELL SIDE

TUBE SIDE

Design Temperature

SHELL SIDE

TUBE SIDE


32/32

Kg/cm2g

10.5 Kg/cm2g

St/Sd

1

Kg/cm2g

Kg/cm2g

1.00

m2)

Date post:	04-Apr-2018
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