5 Sample Pressure Vessel

Code: ASME VIII-1Year: 2007 Cust: Pressure Vessel Engineering

Addenda: 2009 Desc: Sample Vessel 4MAWP: 150 psi Dwg: Sample 4

MEAWP: 0 psi ID: Sample 4Max. Temp.: 120 °F

MDMT: -20 °FMDMT Press.: 150 psi

Min. Thk. (UG-16b): 0.09375 inCorrosion Allowance: 0.125 in

Hydrotest: 195 psiImpact Testing: No

Impact Exemption: UG-20(f)Radiography: None

Internal Press.: YesExternal Press.: NoVessel Weight: Yes

Weight of Attachments: NoAttachment of Internals: No

Attachment of Externals: YesCyclic or Dynamic Reactions: No

Wind Loading: NoSeismic Loading: Yes

Fluid Impact Shock Reactions: NoTemperature Gradients: No PVEcalc-Sample 4 Calulations

Differential Thermal Expansion: No Author: Brian MunnAbnormal Pressures: No Reviewer: Laurence Brundrett

Hydrotest Loads: No

[email protected]

Phone 519-880-9808

Pressure Vessel Engineering Ltd.120 Randall Drive, Suite B

Waterloo, Ontario, Canada, N2V 1C6

Pressure Vessel Engineering Ltd.ASME Calculations - CRN Assistance - Vessel Design - Finite Element Analysis

Design ConditionsASME Section VIII-1 Calculations

UG-22 Loadings Considered

Conclusion: The sample vessel has been calculated to ASME Section VIII-1 and found acceptable.

http://www.pveng.com

mailto:[email protected]

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Pressure Vessel Engineering, Ltd.Shell 1

Job No: Sample Vessel 4 Vessel Number: Vertical Vessel N u m b e r : 1 Mark Number: S1

Date Printed: 4/15/2010

Cylindrical Shell Design Information

Design Pressure: 150.00 PSI Design Temperature: 120 °FStatic Head: 4.33 PSI Long. Joint Efficiency: 70 %

Shell Material: SA-516 Gr. 70 Factor B Chart: CS-2Material Stress (hot): 20000 PSI

Shell Length: 120.0000 in. Material Stress (cold): 20000 PSICompressive Stress: 14118 PSI

Corrosion Allowance: 0.1250 in. Actual Circumferential Stress: 17550 PSIExternal Corrosion Allowance: 0.0000 in. Actual Longitudinal Stress: 8665 PSI

Outside Diameter (new): 60.0000 in.Outside Diameter (corroded): 60.0000 in. Specific Gravity: 1.00

Shell Surface Area: 157.08 Sq. Ft. Weight of Fluid: 11866.17 lb.Shell Estimated Volume: 1420.41 Gal. Total Flooded Shell Weight: 15040.15 lb.

Circ. Joint Efficiency: 70 % Shell Weight: 3173.98 lb.

Minimum Design Metal Temperature Data

Min. Temperature Curve: B Pressure at MDMT: 150.00 PSIUCS-66(b) reduction: Yes Minimum Design Metal Temperature: -20 °FUCS-68(c) reduction: No Computed Minimum Temperature: -39 °F

Design Thickness Calculations

Longitudinal Stress Calculations per Paragraph UG-27(c)(2)

t = PR

2SE + 0.4P =

154.33 * 29.62502 * 20000 * 0.70 + 0.4 * 154.33

= 0.1629 + 0.1250 ( c o r r o s i o n ) + 0.0000 (ext. corrosion) = minimum of 0.2879 i n .

Circumferential Stress Calculations per Appendix 1-1(a)(1)

t = PRo

SE + 0.4P=

154.33 * 30.000020000 * 0.70 + 0.4 * 154.33

= 0.3293 + 0.1250 ( c o r r o s i o n ) + 0.0000 (ext. corrosion) = minimum of 0.4543 i n .

External loads do not control design.

Nominal Shell Thickness Selected = 0.5000 i n .

Advanced Pressure Vessel version: 2010.1.2 ©Computer Engineering, Inc. Section VIII, Division 1, 2007 Edition, 2009 AddendaPage 1 of 28

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Pressure Vessel Engineering, Ltd.Bottom Head

Job No: Sample Vessel 4 Vessel Number: Vertical Vessel N u m b e r : 1 Mark Number: H1


ASME F&D Head Design Information

Design Pressure: 150.00 PSI Design Temperature: 120 °FStatic Head: 4.33 PSI Joint Efficiency: 85 %

Head Material: SA-516 Gr. 70 Factor B Chart: CS-2Material Stress (hot): 20000 PSI

Corrosion Allowance: 0.1250 in. Material Stress (cold): 20000 PSIExternal Corrosion Allowance: 0.0000 in. Actual Head Stress: 17172 PSI

Head Location: Bottom Straight Flange : 1.5000 in.Outside Diameter : 60.0000 in. Knuckle (r) : 3.6000 in.

Thin Out : 0.0750 in.Crown Radius (Lo) : 60.0000 in. M = ¼[ 3 + L/r ] : 1.7481

Head Surface Area: 24.32 Sq. Ft. Specific Gravity: 1.00Head Estimated Volume: 93.98 Gal. Weight of Fluid: 783.78 lb.

Head Weight: 743.28 lb. Total Flooded Head Weight: 1527.06 lb.




Design Thickness Calculations per Appendix 1-4(d)

t = PLoM

2SE + P(M - 0.2) =

154.33 * 60.0000 * 1.74812 * 20000 * 0.85 + 154.33 ( 1.7481 - 0.2 )

= 0.4728 + 0.1250 ( c o r r o s i o n ) + 0.0000 (ext. corrosion) + 0.0750(thin out) = minimum of 0.6728 i n .

Nominal Head Thickness Selected = 0.7500 i n .Minimum Thickness after forming, ts (uncorroded) = 0.6750 i n .


Pressure Vessel Engineering, Ltd.Top Head

Job No: Sample Vessel 4 Vessel Number: Vertical Vessel N u m b e r : 2 Mark Number: H2


ASME F&D Head Design Information

Design Pressure: 150.00 PSI Design Temperature: 120 °FStatic Head: 4.33 PSI Joint Efficiency: 85 %

Head Material: SA-516 Gr. 70 Factor B Chart: CS-2Material Stress (hot): 20000 PSI

Corrosion Allowance: 0.1250 in. Material Stress (cold): 20000 PSIExternal Corrosion Allowance: 0.0000 in. Actual Head Stress: 17172 PSI

Head Location: Top Straight Flange : 1.5000 in.Outside Diameter : 60.0000 in. Knuckle (r) : 3.6000 in.

Thin Out : 0.0750 in.Crown Radius (Lo) : 60.0000 in. M = ¼[ 3 + L/r ] : 1.7481

Head Surface Area: 24.32 Sq. Ft. Specific Gravity: 1.00Head Estimated Volume: 93.98 Gal. Weight of Fluid: 783.78 lb.

Head Weight: 743.28 lb. Total Flooded Head Weight: 1527.06 lb.




Design Thickness Calculations per Appendix 1-4(d)

t = PLoM

2SE + P(M - 0.2) =

154.33 * 60.0000 * 1.74812 * 20000 * 0.85 + 154.33 ( 1.7481 - 0.2 )

= 0.4728 + 0.1250 ( c o r r o s i o n ) + 0.0000 (ext. corrosion) + 0.0750(thin out) = minimum of 0.6728 i n .

Nominal Head Thickness Selected = 0.7500 i n .Minimum Thickness after forming, ts (uncorroded) = 0.6750 i n .


Pressure Vessel Engineering, Ltd.H.Cplg. 1" NPT 6000#

Job No: Sample Vessel 4 Vessel Number: Vertical VesselN u m b e r : 1 Mark Number: N3

ID Number: 3


Nozzle Design Information

Design Pressure: 150.00 PSI Design Temperature: 120 °FStatic Head: 4.33 PSI Nozzle Efficiency (E): 100 %

Nozzle Material: SA-105 Joint Efficiency (E1): 1.00Factor B Chart: CS-6

External Projection: 0.5150 in. Allowable Stress at Design Temperature (Sn): 20000 PSIInternal Projection: 0.0000 in. Allowable Stress at Ambient Temperature: 20000 PSI

Inside Corrosion Allowance: 0.1250 in. Correction Factor (F): 1.00External Corrosion Allowance: 0.0000 in. Nozzle Path: None

Nozzle ID (new): 0.8450 in. Nozzle Wall Thickness(new): 0.3120 in.Nozzle ID (corroded): 1.0950 in. Nozzle Wall Thickness(corroded): 0.1870 in.

Outer "h" Limit: 0.4675 in. Upper Weld Leg Size(Weld 41): 0.3750 in.Internal "h" Limit: 0.1550 in. Internal Weld Leg Size(Weld 43): 0.0000 in.

OD, Limit of Reinforcement: 2.5690 in. Outside Groove Weld Depth: 0.7180 in.

Minimum Design Metal Temperature

Min. Temp. Curve: A Pressure at MDMT: 150.00 PSIUCS-66(b) reduction: Yes Minimum Design Metal Temperature: -20 °FUCS-68(c) reduction: No Computed Minimum Temperature: -122 °F

Host Component: Head 2 - Top Head

Material: SA-516 Gr. 70 Head wall thickness(new): 0.7500 in.Material Stress(Sv): 20000 PSI Head wall thickness - thin out (corroded): 0.5500 in.

Nozzle Detail Information

Upper Weld Leg Size(Weld 41): 0.3750 in.

Nozzle Wall Thickness(tn): 0.3120 in.

Outside Groove Weld Depth: 0.7180 in.

Nozzle passes through the vessel, attached by a groove weld.Nozzle is adequate for UG-45 requirements.

Opening is adequately reinforced for Internal Pressure.Reinforcement calculations are not required per UG-36(c)(3)(a)See Uw-14 for exceptions.

Weld Strength Paths are adequate.


Pressure Vessel Engineering, Ltd.H.Cplg. 1" NPT 6000#


ID Number: 3


Required Head Thickness per Paragraph UG-37(a)

tr = PLoM

(2SE + P * (M - 0.2)) =

154.33 * 60.0000 * 1.0000(2 * 20000 * 1 + 154.33 * (1.0000 - 0.2))

= 0.2308 i n .

Nozzle Required Thickness Calculations

Required Nozzle Thickness for Internal Pressure per Paragraph UG-37(a)

trn = PRn

SE - 0.6P =

154.33 * 0.547520000 * 1 - 0.6 * 154.33

= 0.0042 i n .

Strength Reduction Factors

fr1 = min SnSv

, 1.0000 = min 2000020000

, 1.0000 = 1.0000 fr2 = min SnSv

, 1.0000 = min 2000020000

, 1.0000 = 1.0000

fr3 = min SnSv

, 1.0000 = min 2000020000

, 1.0000 = 1.0000

UG-45 Thickness Calculations

Nozzle Thickness for Pressure Loading (plus corrosion) per Paragraph UG-45(a)

t = PRn

SE - 0.6P + Ca + ext. Ca =

154.33 * 0.547520000 * 1.00 - 0.6 * 154.33

+ 0.1250 + 0.0000 = 0.1292 i n .

Nozzle Thickness for Internal Pressure (plus corrosion) per Paragraph UG-45(b)(1)

t = PLoM

(2SE + P * (M - 0.2)) + Ca + ext. Ca =

154.33 * 60.0000 * 1.7481(2 * 20000 * 1 + 154.33 * (1.7481 - 0.2))

+ 0.1250 + 0.0000 = 0.5273 i n .

Minimum Thickness of Standard Wall Pipe (plus corrosion) per Paragraph UG-45(b)(4)t = minimum thickness of standard wall pipe + Ca + ext. Ca = 0.2475 i n .

Nozzle Minimum Thickness per Paragraph UG-45(b)t = Smallest of UG-45(b)(1) or UG-45(b)(4) = 0.2475 i n .

Wall thickness = tn = 0.3120 is greater than or equal to UG-45 value of 0.2475


Pressure Vessel Engineering, Ltd.4" SCH 160


ID Number: 2




Nozzle Material: SA-106 Gr. B Joint Efficiency (E1): 1.00Factor B Chart: CS-2



Nozzle Pipe Size: 4 Nozzle Pipe Schedule: 160Nozzle ID (new): 3.4380 in. Nozzle Wall Thickness(new): 0.5310 in.

Nozzle ID (corroded): 3.6880 in. Nozzle Wall Thickness(corroded): 0.4060 in.Outer "h" Limit: 1.0150 in. Upper Weld Leg Size(Weld 41): 0.3750 in.

Internal "h" Limit: 0.7025 in. Internal Weld Leg Size(Weld 43): 0.0000 in.OD, Limit of Reinforcement: 7.3760 in. Outside Groove Weld Depth: 0.7500 in.


Min. Temp. Curve: B Pressure at MDMT: 150.00 PSIUCS-66(b) reduction: Yes Minimum Design Metal Temperature: -20 °FUCS-68(c) reduction: No Computed Minimum Temperature: -150 °F

Host Component: Head 1 - Bottom Head






Nozzle passes through the vessel, attached by a groove weld.Pipe Size: 4 Schedule: 160

Nozzle is adequate for UG-45 requirements.Opening is adequately reinforced for Internal Pressure.





ID Number: 2



tr = PLoM

(2SE + P * (M - 0.2)) =

154.33 * 60.0000 * 1.0000(2 * 20000 * 1 + 154.33 * (1.0000 - 0.2))

= 0.2308 i n .



trn = PRn

SE - 0.6P =

154.33 * 1.844017100 * 1 - 0.6 * 154.33

= 0.0167 i n .


fr1 = min SnSv

, 1.0000 = min 1710020000

, 1.0000 = 0.8550 fr2 = min SnSv

, 1.0000 = min 1710020000

, 1.0000 = 0.8550

fr3 = min SnSv

, 1.0000 = min 1710020000

, 1.0000 = 0.8550



t = PRn

SE - 0.6P + Ca + ext. Ca =

154.33 * 1.844017100 * 1.00 - 0.6 * 154.33

+ 0.1250 + 0.0000 = 0.1417 i n .


t = PLoM

(2SE + P * (M - 0.2)) + Ca + ext. Ca =

154.33 * 60.0000 * 1.7481(2 * 20000 * 1 + 154.33 * (1.7481 - 0.2))

+ 0.1250 + 0.0000 = 0.5273 i n .



Wall thickness = tn * 0.875(pipe) = 0.4646 is greater than or equal to UG-45 value of 0.3324




ID Number: 2


Nozzle Reinforcement Calculations

Area Required for Internal PressureA = d tr F + 2 tn tr F (1 - fr1) = (3.6880 * 0.2308 * 1.00) + (2 * 0.4060 * 0.2308 * 1.00 * (1 - 0.8550)) = 0.8784 sq. in.

Area Available - Internal PressureA1 Formula 1 = d(E1 t - F tr) - 2tn(E1 t - F tr)(1 - fr1) = 3.6880 * (1.00 * 0.5500 - 1.00 * 0.2308) - 2 * 0.4060 * (1.00 * 0.5500 - 1.00 * 0.2308) * (1 - 0.8550) = 1.1396 sq. in.A1 Formula 2 = 2(t + tn)(E1 t - F tr) - 2tn(E1 t - F tr)(1 - fr1) = 2 * (0.5500 + 0.4060)(1.00 * 0.5500 - 1.00 * 0.2308) - 2 * 0.4060 * (1.00 * 0.5500 - 1.00 * 0.2308) * (1 - 0.8550) = 0.5727 sq. in.A1 = Larger value of A1 Formula 1 a n d A1 Formula 2 = 1.1396 sq. in.

A2 Formula 1 = 5(tn - trn) fr2 t = 5(0.4060 - 0.0167) * 0.8550 * 0.5500 = 0.9153 sq. in.A2 Formula 2 = 5(tn - trn) fr2 tn = 5(0.4060 - 0.0167) * 0.8550 * 0.4060 = 0.6757 sq. in.A2 = Smaller value of A2 Formula 1 a n d A2 Formula 2 = 0.6757 sq. in.

A3 = Smaller value of the following : 5 * t * ti * fr2 = 5 * 0.5500 * 0.2810 * 0.8550 = 0.6607 sq. in.5 * ti * ti * fr2 = 5 * 0.2810 * 0.2810 * 0.8550 = 0.3376 sq. in.2 * h * ti * fr2 = 2 * 0.0000 * 0.2810 * 0.8550= 0.0000 sq. in.

= 0.0000 sq. in.

A41 = (leg)² * fr2 = (0.3750)² * 0.8550 = 0.1202 sq. in.

A43 = (leg)² * fr2 = 0 * 0.8550 = 0.0000 sq. in.

Area Available (Internal Pressure) = A1 + A2 + A3 + A41 + A43 = 1.9355 sq. in., which is greater than A (0.8784)


Pressure Vessel Engineering, Ltd.12" x 16" MWY c/w 1" x 3" Ring

Job No: Sample Vessel 4 Vessel Number: Vertical VesselN u m b e r : 3 Mark Number: M1

ID Number: M1












Reinforcing Pad Information

Reinforcing Material: SA-516 Gr. 70 Allowable Stress at Design Temperature(Sp): 20000 PSIAllowable Stress at Ambient Temperature: 20000 PSI

Reinforcing Plate Thickness(te): 0.5000 in. Repad to Vessel Weld Leg Size(Weld 42): 0.3750 in.OD, Reinforcing Plate(Dp): 21.5000 in. Repad to Nozzle Groove Weld Depth: 0.5000 in.

Host Component: Head 2 - Top Head




Internal Weld Leg Size(Weld 43): 0.3750 in.



Repad to Vessel Weld Leg Size(Weld 42): 0.3750 in.

Repad Thickness(te): 0.5000 in.


Opening is adequately reinforced for Internal Pressure.Weld Strength Paths are adequate.




ID Number: M1



tr = PLoM

(2SE + P * (M - 0.2)) =

154.33 * 60.0000 * 1.0000(2 * 20000 * 1 + 154.33 * (1.0000 - 0.2))

= 0.2308 i n .



trn = PRn

SE - 0.6P =

154.33 * 8.125017100 * 1 - 0.6 * 154.33

= 0.0737 i n .


fr1 = min SnSv

, 1.0000 = min 1710020000

, 1.0000 = 0.8550 fr2 = min SnSv

, 1.0000 = min 1710020000

, 1.0000 = 0.8550

fr3 = min SnSv

, 1.0000 = min 1710020000

, 1.0000 = 0.8550 fr4 = min SpSv

, 1.0000 = min 2000020000

, 1.0000 = 1.0000

UG-45 Thickness CalculationsThis calculation is for an access or inspection opening.


t = PRn

SE - 0.6P + Ca + ext. Ca =

154.33 * 8.125017100 * 1.00 - 0.6 * 154.33

+ 0.1250 + 0.0000 = 0.1987 i n .




ID Number: M1





A2 Formula 1 = 5(tn - trn) fr2 t = 5(0.6250 - 0.0737) * 0.8550 * 0.5500 = 1.2962 sq. in.A2 Formula 2 = 2(tn - trn) fr2 (2.5 tn + te ) = 2(0.6250 - 0.0737) * 0.8550 * (2.5 * 0.6250 + 0.5000) = 1.9444 sq. in.A2 = Smaller value of A2 Formula 1 a n d A2 Formula 2 = 1.2962 sq. in.


= 0.5344 sq. in.

A41 = (leg)² * fr3 = (0.5000)² * 0.8550 = 0.2138 sq. in.

A42 = (leg)² * fr4 = (0.3750)² * 1.0000 = 0.1406 sq. in.

A43 = (leg)² * fr2 = (0.1964)² * 0.8550 = 0.0330 sq. in.

A5 = (Dp - d - 2tn) te fr4 = (21.5000 - 16.2500 - 2 * 0.6250) * 0.5000 * 1.0000 = 2.0000 sq. in.

Area Available (Internal Pressure) = A1 + A2 + A3 + A41 + A42 + A43 + A5 = 9.3471 sq. in., which is greater than A (3.7923)




ID Number: M1


Nozzle Weld Strength Calculations

Attachment Weld Strength per Paragraph UW-16 (Corroded Condition)

Weld 41 tmin = smaller of 0.75, te, or tn = smaller of 0.75, 0.5000, or 0.6250 = 0.5000 i n .

Weld 41 Leg min. = (smaller of 0.25 or (tmin * 0.7)) + ext. CA

0.7 =

0.25000.7

= 0.3571 i n .

Weld 41, actual weld leg = 0.5000 i n .

Weld 42 tmin = smaller of 0.75, t, or te = smaller of 0.75, 0.5500, or 0.5000 = 0.5000 i n .

Weld 42 Leg min. = 0.5 * tmin + ext. CA

0.7 =

0.5 * 0.5000 + 0.00000.7

= 0.3571 i n .


Weld 43 tmin = smaller of 0.75, t, or tn = smaller of 0.75, 0.5500, or 0.6250 = 0.5500 i n .

Weld 43 Leg min. = (smaller of 0.25 or (tmin * 0.7)) + ca

0.7 =

(smaller of 0.25 or (0.5500 * 0.7)) + 0.12500.7

= 0.3750

0.7 = 0.5357 i n .


Unit Stresses per Paragraphs UG-45(c) and UW-15Nozzle wall in shear = 0.70 * Sn = 0.70 * 17100 = 11970 P S IUpper fillet, Weld 41, in shear = 0.49 * Material Stress = 0.49 * 17100 = 8379 P S IVessel groove weld, in tension = 0.74 * Material Stress = 0.74 * 17100 = 12654 P S IInner fillet, Weld 43, in shear = 0.49 * Material Stress = 0.49 * 17100 = 8379 P S IOuter fillet, Weld 42, in shear = 0.49 * Material Stress = 0.49 * 20000 = 9800 P S IRepad groove weld, in tension = 0.74 * Material Stress = 0.74 * 17100 = 12654 P S I

Strength of Connection ElementsNozzle wall in shear = ½ * * mean nozzle diameter * tn * Nozzle wall in shear unit stress = ½ * * 16.8750 * 0.6250 * 11970 = 198200 l b .Upper fillet in shear = ½ * * Nozzle OD * weld leg * upper fillet in shear unit stress = ½ * * 17.5000 * 0.5000 * 8379 = 115100 l b .Groove Weld in Tension = ½ * * Nozzle OD * groove depth * groove weld tension unit stress = ½ * * 17.5000 * 0.7500 * 12654 = 260800 l b .Inner fillet in shear = ½ * * Nozzle OD * weld leg * inner fillet in shear unit stress = ½ * * 17.5000 * 0.1964 * 8379 = 45200 l b .Outer fillet in shear = ½ * * Plate OD * weld leg * outer fillet in shear unit stress = ½ * * 21.5000 * 0.3750 * 9800 = 124000 l b .Repad groove weld = ½ * * Nozzle OD * Groove Depth * repad groove weld in tension unit stress = ½ * * 17.5000 * 0.5000 * 12654 = 173800 l b .




ID Number: M1


Load to be carried by welds, per UG-41(b)(1) and Fig. UG-41.1 sketch (a)W = [A - A1 + 2 tn fr1(E1t - Ftr)] Sv = [3.7923 - 5.1291 + 2 * 0.6250 * 0.8550 * (1.00 * 0.5500 - 1.0000 * 0.2308)] * 20000 = -19913 l b .W1-1 = (A2 + A5 + A41 + A42) * Sv = (1.2962 + 2.0000 + 0.2138 + 0.1406) * 20000 = 73000 l b .W2-2 = (A2 + A3 + A41 + A43 + 2 tn t fr1) Sv = (1.2962 + 0.5344 + 0.2138 + 0.0330 + 2 * 0.6250 * 0.5500 * 0.8550) * 20000 = 53300 l b .W3-3 = (A2 + A3 + A5 + A41 + A42 + A43 + 2 tn t fr1) * Sv = (1.2962 + 0.5344 + 2.0000 + 0.2138 + 0.1406 + 0.0330 + 2 * 0.6250 * 0.5500 * 0.8550) * 20000 = 96100 l b .

Check Strength PathsPath 1-1 = Outer fillet in shear + Nozzle wall in shear = 124000 + 198200 = 322200 l b .Path 2-2 = Upper fillet in shear + Repad groove weld + Groove weld in tension + Inner fillet in shear = 115100 + 173800 + 260800 + 45200 = 594900 l b .Path 3-3 = Outer fillet in shear + Inner fillet in shear + Groove weld in tension = 124000 + 45200 + 260800 = 430000 l b .

Plate Strength = A5 * Sp = 2.0000 * 20000 = 40000 l b .

Outer fillet weld strength(124000) is greater than plate strength(40000).




ID Number: M2












Host Component: Shell 1 - Shell 1

Material: SA-516 Gr. 70 Shell wall thickness(new): 0.5000 in.Material Stress(Sv): 20000 PSI Shell wall thickness(corroded): 0.3750 in.



Internal Weld Leg Size(Weld 43): 0.3750 in.




Opening is adequately reinforced for Internal Pressure.Weld Strength Paths are adequate.




ID Number: M2


Required Shell Thickness per Paragraph UG-37(a)

tr = PRo

SE + 0.4P =

154.33 * 30.000020000 * 1 + 0.4 * 154.33

= 0.2308 i n .



trn = PRn

SE - 0.6P =

154.33 * 8.125017100 * 1 - 0.6 * 154.33

= 0.0737 i n .


fr1 = min SnSv

, 1.0000 = min 1710020000

, 1.0000 = 0.8550 fr2 = min SnSv

, 1.0000 = min 1710020000

, 1.0000 = 0.8550

fr3 = min SnSv

, 1.0000 = min 1710020000

, 1.0000 = 0.8550

UG-45 Thickness CalculationsThis calculation is for an access or inspection opening.


t = PRn

SE - 0.6P + Ca + ext. Ca =

154.33 * 8.125017100 * 1.00 - 0.6 * 154.33

+ 0.1250 + 0.0000 = 0.1987 i n .




ID Number: M2







= 0.6413 sq. in.

A41 = (leg)² * fr2 = (0.3750)² * 0.8550 = 0.1202 sq. in.

A43 = (leg)² * fr2 = (0.1964)² * 0.8550 = 0.0330 sq. in.



Pressure Vessel Engineering, Ltd.4 In SCH 160 Pipe


ID Number: 1







Nozzle Pipe Size: 4 Nozzle Pipe Schedule: 160Nozzle ID (new): 3.4380 in. Nozzle Wall Thickness(new): 0.5310 in.

Nozzle ID (corroded): 3.6880 in. Nozzle Wall Thickness(corroded): 0.4060 in.Outer "h" Limit: 0.9375 in. Upper Weld Leg Size(Weld 41): 0.3750 in.

Internal "h" Limit: 0.7025 in. Internal Weld Leg Size(Weld 43): 0.0000 in.OD, Limit of Reinforcement: 7.3760 in. Outside Groove Weld Depth: 0.5000 in.



Host Component: Shell 1 - Shell 1

Material: SA-516 Gr. 70 Shell wall thickness(new): 0.5000 in.Material Stress(Sv): 20000 PSI Shell wall thickness(corroded): 0.3750 in.





Nozzle passes through the vessel, attached by a groove weld.Pipe Size: 4 Schedule: 160

Nozzle is adequate for UG-45 requirements.Opening is adequately reinforced for Internal Pressure.





ID Number: 1


Required Shell Thickness per Paragraph UG-37(a)

tr = PRo

SE + 0.4P =

154.33 * 30.000020000 * 1 + 0.4 * 154.33

= 0.2308 i n .



trn = PRn

SE - 0.6P =

154.33 * 1.844017100 * 1 - 0.6 * 154.33

= 0.0167 i n .


fr1 = min SnSv

, 1.0000 = min 1710020000

, 1.0000 = 0.8550 fr2 = min SnSv

, 1.0000 = min 1710020000

, 1.0000 = 0.8550

fr3 = min SnSv

, 1.0000 = min 1710020000

, 1.0000 = 0.8550



t = PRn

SE - 0.6P + Ca + ext. Ca =

154.33 * 1.844017100 * 1.00 - 0.6 * 154.33

+ 0.1250 + 0.0000 = 0.1417 i n .


t = PRo

SE + 0.4P + Ca + ext. Ca =

154.33 * 30.000020000 * 1 + 0.4 * 154.33

+ 0.1250 + 0.0000 = 0.3558 i n .



Wall thickness = tn * 0.875(pipe) = 0.4646 is greater than or equal to UG-45 value of 0.3324




ID Number: 1







= 0.0000 sq. in.

A41 = (leg)² * fr2 = (0.3750)² * 0.8550 = 0.1202 sq. in.

A43 = (leg)² * fr2 = 0 * 0.8550 = 0.0000 sq. in.



Pressure Vessel Engineering, Ltd.Leg Beams

Job No: Sample Vessel 4 Vessel Number: Vertical VesselMark Number: LEG1


Leg Information Design Temperature: 120 °F Factor B Chart: CS-2

M a t e r i a l : SA-36 Material Stress ( Hot ): 16600 PSIC o n d i t i o n : Material Stress ( Cold ): 16600 PSI

B.P. to Vessel Attachment Length ( L ): 24.5000 in. Modulus of Elasticity: 29.2 10^6 PSIDirection of Applied Force: 0 ° Yield Strength: 35120 PSI

Length of Supports: 42.5000 in. Dist. From Reference Line: 12.5000 in.Q u a n t i t y : 4 Method of Attachment: Leg In

T y p e : W-beam Molded to Head Curvature: YesD e s c r i p t i o n : W6 x 15

d1: 5.9900 in. t1: 0.2300 in.d2: 5.9900 in. t2: 0.2600 in.

Weld Attachment Length Top ( W t ) : 12.5000 in. Side ( Ws ) : 6.0000 in.Weld Leg Dimension ( W l ) : 0.2500 in. E c c e n t r i c i t y : 0.0000 in.

Base Plate Information

Design Temperature: 120 °FM a t e r i a l : SA/CSA-G40.21 Gr 38W Material Stress ( Hot ): 17100 PSI

C o n d i t i o n : Material Stress ( Cold ): 17100 PSIL e n g t h : 7.0000 in. Yield Strength: 37080 PSIW i d t h : 7.0000 in. T h i c k n e s s : 0.7500 in.

Leg to B.P. Attachment Factor: 0.7500 Bending Coefficient ( Cm ) : 1.0000Effective Length Factor ( K ): 1.5000

Anchor Bolt Information

M a t e r i a l : SA-193 Gr B7 <=2.5" Material Stress ( Hot ): 25000 PSIC o n d i t i o n : Material Stress ( Cold ): 25000 PSID i a m e t e r : 1.0000 in. Root Area: 0.5510 sq. in.Q u a n t i t y : 2 Bolt Circle Diameter: 63.7500 in.

Ultimate 28 Day Concrete Strength: 3000 PSI





Operating Pressurized Conditions - Occasional Loads - Seismic Formula 16-10

Support Leg Properties

Section Modulus, Sx = IxCx

= 28.72152.9950

= 9.5898 i n . ³

Section Modulus, Sy = IyCy

= 9.31882.9950

= 3.1115 i n . ³

Radius of gyration, rx = IxA

= 28.72154.3729

= 2.5628 i n .

Radius of gyration, ry = IyA

= 9.31884.3729

= 1.4598 i n .

Least radius of gyration, rmin = IminA

= 9.31884.3729

= 1.4598 i n .

Slenderness ratio, SRx = K L rx

= 1.5000 * 24.5000

2.5628 = 14.3398

Slenderness ratio, SRy = K L r y

= 1.5000 * 24.5000

1.4598 = 25.1747

SRmax = K L r min

= 1.5000 * 24.5000

1.4598 = 25.1747

Critical slenderness ratio, Cc = 2 ² E

Fy =

2 * ² * ( 29.2 * 10 )35120

= 128.11

F'ex = 1 2 ² E23 SRx²

= 12 * ² * ( 29.2 * 10 )

23 * 14.3398² = 731223 P S I

F'ey = 1 2 ² E23 SRy²

= 12 * ² * ( 29.2 * 10 )

23 * 25.1747² = 237251 P S I

For SRmax <= Cc, Allowable compressive stress:

Fa =

1 -

SRmax²2 Cc²

Fy

53

+ 3 SRmax

8 Cc -

SRmax³8 Cc³

=

1 -

25.1747²2 * 128.11²

* 35120

53

+ 3 * 25.17478 * 128.11

- 25.1747³

8 * 128.11³

= 19801 P S I

Allowable bending stress: Sb = 0.6 Fy = 0.6 * 35120 = 21072 P S IAllowable tension stress: St = 0.6 Fy = 0.6 * 35120 = 21072 P S I

NO Wind Analysis Information

Wind Analysis Calculations

No Wind Load Calculations were performed


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IBC 2000 Seismic Design InformationSpectral Resp. Accel. at short periods ( Ss ) : 0.750pectral Resp. Accel. at a period of 1 s ( S1 ) : 0.040 Response Modification Factor ( R ): 2.000

Seismic Use Group: I Site Class: ESeismic Design Category: D

Seismic Analysis Calculations

Seismic Center of Gravity: = 90.0000 i n .

Cs = SDS I

R =

0.6000 * 1.002.000

= 0.3000

V = W * Cs = 4660.54 * 0.08 = 1398.16 l b .Fs = V Ceh = 1398.16 * 0.70 = 979 l b .

Loadings and Stresses on Support Legs

Direction of Applied Force = 0 °

Leg Moment of Lateral Axial Bending Bending Acceptance AcceptanceOrientation Inertia Force Stress Stresses ( fbx ) Stresses ( fby ) Ratio ( Eqn1 ) Ratio ( Eqn2 )

° in.^4 lb. PSI PSI PSI0 9.3188 120 22 0 708 0.0346

90 28.7215 369 -289 708 0 0.0482 180 9.3188 120 -599 0 708 0.0639 270 28.7215 369 -289 708 0 0.0482

Direction of Worst case Force = 37 °Highest Stress Ratio = 0.0915

Loadings and Pressure on Concrete Foundation

Direction of applied force: = 0 °

L e g B e a r i n g M o m e n t M o m e n t M a x i m u m M a x i m u m Max. Concrete C o n c r e t e Orientation Pressure Mx My Pressure Px Pressure Py Pressure Pressure Ratio

° PSI in.-lb. in.-lb. PSI PSI PSI0 -2 0 1469 25.70 0.00 23.76 0.0264

90 26 4526 0 0.00 79.17 104.95 0.1166180 53 0 1469 25.70 0.00 79.19 0.0880270 26 4526 0 0.00 79.17 104.95 0.1166

Direction of Worst case Force: = 25 °Highest Stress Ratio = 0.1449





Loadings and Stresses on BasePlate and Anchor bolts

L e g M o m e n t M o m e n t Maximum Maximum M a x i m u m B a s e P l a t e A n c h o r Anchor BoltOrientation Mx My Pressure Px Pressure Py B.P. Stress Stress Ratio Bolt Stress Stress Ratio

° in.-lb. in.-lb. PSI PSI PSI PSI0 14 0 146 0 146 0.0066 330 0.0132

90 16 21 168 229 283 0.0127 400 0.0160180 47 11 506 122 521 0.0234 0 0.0000270 16 21 168 229 283 0.0127 400 0.0160

Direction of Worst case Force: = 29 °Highest Stress Ratio = 0.0303

Maximum General Longitudinal Stresses

VE = ( Cde + 0.2 * SDS * I * Cev ) = ( 1.00 + 0.2 * 0.60 * 1.00 * 0.70 ) = 1.08

SL1 = MaZ

- W VE

A +

P * D4 * t

= 64106

1040.5723 -

4660.54 * 1.0870.24

+ 154.69 * 60.0000

4 * 0.3750 = 6177 P S I

SL2 = - MaZ

- W VE

A = -

641061040.5723

- 4660.54 * 1.08

70.24 = -134 P S I

Allowable Tension Stress, Sta = S E = 20000 * 0.70 = 14000 P S IAllowable Compressive Stress, Sca = -B = -14118 = -14118 P S I

RSL1 = SL1Sta

= 6177

14000 = 0.4412

RSL2 = SL2Sca

= -134

-14118 = 0.0095

S u m m a r y

Governing external force = Seismic load

Total Force = 979 l b .

Weight = 4660.54 l b .

Base Moment = 88084 i n . - l b .

Tangent Moment = 64106 i n . - l b .

Leg Stresses

Maximum combined compressive and bending stress ratio = 0.0915

Leg BasePlate

Concrete Stress Ratio = 0.1449

Base Plate Stress Ratio = 0.0303

Host Stresses

Sl1 ratio = 0.4412

Sl2 ratio = 0.0095


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Pressure Vessel Engineering, Ltd.Vertical Vessel

Job No: Sample Vessel 4 Vessel Number: Vertical Vessel


ASME Flange Design InformationHost Description Type S i z e Material A S M E Material MAP

( i n . ) C l a s s Group (PSI)

4" SCH 160 ASME Flange 1 Slip-On 4 S A - 1 0 5 150 1.1 280.004 In SCH 160 Pipe ASME Flange 2 Slip-On 4 S A - 1 0 5 150 1.1 280.00


Pressure Vessel Engineering, Ltd.Job No: Sample Vessel 4 Vessel Number: Vertical Vessel


MDMT Report by ComponentsDesign MDMT is -20 °F

Component Material Curve Pressure MDMT

Shell 1 SA-516 Gr. 70 B 150.00 PSI -39 °F 12" x 16" MWY c/w 1" x 4" Ring SA-106 Gr. B B 150.00 PSI -147 °F 4 In SCH 160 Pipe SA-106 Gr. B B 150.00 PSI -150 °FBottom Head SA-516 Gr. 70 B 150.00 PSI -20 °F 4" SCH 160 SA-106 Gr. B B 150.00 PSI -150 °FTop Head SA-516 Gr. 70 B 150.00 PSI -20 °F H.Cplg. 1" NPT 6000# SA-105 A 150.00 PSI -122 °F 12" x 16" MWY c/w 1" x 3" Ring SA-106 Gr. B B 150.00 PSI -125 °F

Component with highest MDMT: Bottom Head.

Computed MDMT = -20 °F

The required design MDMT of -20 °F has been met or exceeded for the calculated MDMT values.

ASME Flanges Are Not Included in MDMT Calculations.


Pressure Vessel Engineering, Ltd.Vertical Vessel

Job No: Sample Vessel 4 Vessel Number: Vertical Vessel


MAWP Report by Components

Vessel Component VesselMAWP MAWP MAWP

Design Static New & Cold Hot & Corroded Hot & Corroded Component Pressure Head UG-98(a) UG-98(b) UG-98(a)Shell 1 150.00 PSI 4.33 PSI 218.15 PSI 158.46 PSI 154.13 PSI 12" x 16" MWY c/w 1" x 4" Ring 150.00 PSI 4.33 PSI 218.15 PSI 158.46 PSI 154.13 PSI 4 In SCH 160 Pipe 150.00 PSI 4.33 PSI 272.29 PSI 188.47 PSI 184.14 PSI ASME Flange Class: 150 Gr:1.1 4.33 PSI 280.67 PSI 280.00 PSI 275.67 PSIBottom Head 150.00 PSI 4.33 PSI 214.67 PSI 179.75 PSI 175.42 PSI 4" SCH 160 150.00 PSI 4.33 PSI 333.84 PSI 249.00 PSI 244.67 PSI ASME Flange Class: 150 Gr:1.1 4.33 PSI 280.67 PSI 280.00 PSI 275.67 PSITop Head 150.00 PSI 4.33 PSI 214.67 PSI 179.75 PSI 175.42 PSI H.Cplg. 1" NPT 6000# 150.00 PSI 4.33 PSI 449.79 PSI 369.40 PSI 365.07 PSI 12" x 16" MWY c/w 1" x 3" Ring 150.00 PSI 4.33 PSI 323.10 PSI 266.58 PSI 262.25 PSI

NC = Not Calculated Inc = Incomplete

Summary

Component with the lowest vessel MAWP(New & Cold) : Bottom HeadThe lowest vessel MAWP(New & Cold) : 214.67 P S I

Component with the lowest vessel MAWP(Hot & Corroded) : Shell 1The lowest vessel MAWP(Hot & Corroded) : 154.13 P S I

Pressures are exclusive of any external loads.

Flange pressures listed here do not consider external loadings




Summary Information

Dry Weight Flooded WeightShell 3173.98 lb. 15040.15 lb.Head 1486.56 lb. 3054.12 lb.Nozzle 117.01 lb. 117.01 lb.ASME Flange 26.00 lb. 26.00 lb.

_________________ _________________T o t a l s 4803.55 lb. 18237.27 lb.

Volume Shell 1420.41 Gal.Head 187.96 Gal.Nozzle 4.79 Gal.

_________________T o t a l s 1613.15 Gal.

Area Shell 157.08 Sq. Ft.Head 48.64 Sq. Ft.Nozzle 9.40 Sq. Ft.

_________________T o t a l s 215.11 Sq. Ft.




Hydrostatic Test Information Par. UG-99(b)Gauge at Top

Component Const. x STest / SDesign x Pressure = Component Hydro Test Pressure

12" x 16" MWY c/w 1" x 1.3 x 17100 / 17100 x 150.00 = 195.0012" x 16" MWY c/w 1" x 1.3 x 17100 / 17100 x 150.00 = 195.004 In SCH 160 Pipe 1.3 x 17100 / 17100 x 150.00 = 195.004" SCH 160 1.3 x 17100 / 17100 x 150.00 = 195.00Bottom Head 1.3 x 20000 / 20000 x 150.00 = 195.00H.Cplg. 1" NPT 6000# 1.3 x 20000 / 20000 x 150.00 = 195.00Shell 1 1.3 x 20000 / 20000 x 150.00 = 195.00Top Head 1.3 x 20000 / 20000 x 150.00 = 195.00

Calculated Test Pressure: 195.00 PSI

Special Notes:

This calculation assumes one chamber.

This calculation is limited by the lowest component pressure per chamber.


Table of Contents

Shell 1 1

Bottom Head 2

Top Head 3

H.Cplg. 1" NPT 6000# 4

4" SCH 160 6

12" x 16" MWY c/w 1" x 3" Ring 9

12" x 16" MWY c/w 1" x 4" Ring 14

4 In SCH 160 Pipe 17

Leg Information 20

ASME Flanges 24

MDMT Summary 25

MAWP Summary 26

Summary Information 27

Hydrostatic Test Information Par. UG-99(b) 28

Date post:	17-Jan-2016
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5 Sample Pressure Vessel

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