odorant vessel

Codeware, Inc.

Houston, TX, USA

www.codeware.com

COMPRESS Pressure Vessel Design Calculations

Item: Split Stream DearatorVessel No: V-1234Customer: Magaladon Oil Venture

Contract: C-45490-R56Designer: John Doe

Date: April 1, 2001

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Deficiencies Summary

No deficiencies found.

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Nozzle Schedule

Nozzlemark Service Size

Materials

Nozzle Impact Norm Fine Grain Pad Impact Norm Fine Grain Flange

N1 Nozzle #1 2.07 IDx0.15 SA-240 304 No No No SA-240 304 No No No WN A182 F304 Class 150

N2 N2 0.74 IDx0.15 SA-240 304 No No No N/A N/A N/A N/A WN A182 F304 Class 150


N4 N4 2.07 IDx0.15 SA-240 304 No No No SA-516 70 No No No WN A182 F304 Class 150



N7 N7 2.07 IDx0.15 SA-240 304 No No No SA-516 70 No No No WN A182 F304 Class 150


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Nozzle Summary

Nozzlemark

OD(in)

tn

(in)Req t

n(in)

A1? A2?Shell Reinforcement

Pad Corr(in)

Aa/A

r(%)

Nom t(in)

Design t(in)

User t(in)

Width(in)

tpad(in)

N1 2.38 0.1540 0.1180 Yes Yes 0.1181* N/A 1.5000 0.1250 0.0000 Exempt

N2 1.05 0.1540 0.0989 Yes Yes 0.1181* N/A N/A N/A 0.0000 Exempt

N3 1.05 0.1540 0.0989 Yes Yes 0.1181* N/A N/A N/A 0.0000 Exempt

N4 2.38 0.1540 0.1250 Yes Yes 0.1250* N/A 2.0000 0.1250 0.0000 Exempt

N5 1.32 0.1790 0.1164 Yes Yes 0.1250 N/A N/A N/A 0.0000 Exempt


N7 2.38 0.1540 0.1250 Yes Yes 0.1250 N/A 2.0000 0.1250 0.0000 Exempt


tn: Nozzle thicknessReq tn: Nozzle thickness required per UG-45/UG-16Nom t: Vessel wall thicknessDesign t: Required vessel wall thickness due to pressure + corrosion allowance per UG-37User t: Local vessel wall thickness (near opening)Aa: Area available per UG-37, governing conditionAr: Area required per UG-37, governing conditionCorr: Corrosion allowance on nozzle wall* Head minimum thickness after forming

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Pressure Summary

Pressure Summary for Chamber bounded by Ellipsoidal Head #1 and Ellipsoidal Head #2

IdentifierP

Design( psi)

T

Design(°F)

MAWP( psi)

MAP( psi)

MDMT(°F)

MDMTExemption

Total Corrosion

Allowance(in)

ImpactTest

Ellipsoidal Head #2 50.0 158.0 98.85 98.85 -320.0 Note 1 0.000 No

Straight Flange on Ellipsoidal Head #2 50.0 158.0 98.61 98.61 -320.0 Note 2 0.000 No

Cylinder #1 50.0 158.0 104.38 104.38 -320.0 Note 2 0.000 No

Straight Flange on Ellipsoidal Head #1 50.0 158.0 104.38 104.38 -320.0 Note 2 0.000 No

Ellipsoidal Head #1 50.0 158.0 104.66 104.66 -320.0 Note 1 0.000 No

Saddle #1 50.0 158.0 98.61 N/A N/A N/A N/A N/A

Nozzle #1 (N1) 50.0 158.0 98.81 98.81 -55.0 Nozzle Note 3; Pad Note 2 0.000 No

N2 (N2) 50.0 158.0 109.59 109.59 -55.0 Note 3 0.000 No

N3 (N3) 50.0 158.0 109.59 109.59 -55.0 Note 3 0.000 No

N4 (N4) 50.0 158.0 104.66 104.66 -25.8 Nozzle Note 2; Pad Note 4 0.000 No

N5 (N5) 50.0 158.0 104.35 104.35 -55.0 Note 3 0.000 No

N6 (N6) 50.0 158.0 104.35 104.35 -55.0 Note 3 0.000 No

N7 (N7) 50.0 158.0 104.35 104.35 -25.5 Nozzle Note 2; Pad Note 5 0.000 No

N8 (N8) 50.0 158.0 104.35 104.35 -55.0 Note 3 0.000 No

Chamber design MDMT is -20.00°FChamber rated MDMT is -25.50°F @ 98.61 psiChamber MAWP was used in the MDMT determination

Chamber MAWP hot & corroded is 98.61 psi @ 158.0°F

Chamber MAP cold & new is 98.61 psi @ 70.0°F

This pressure chamber is not designed for external pressure.

Notes for MDMT Rating:

Note # Exemption Details

1. Material Rated MDMT per UHA-51(d)(1)(a) = -320 °F

2. Rated MDMT per UHA-51(d)(1)(a) = -320 °F

3.Flange rating governs:Flange rated MDMT = -320 °FBolts rated MDMT per Fig UCS-66 note (e) = -55 °F

Per UHA-51(d)(1)(a)

4. Pad impact test exemption temperature from Fig UCS-66 Curve B = -20 °FFig UCS-66.1 MDMT reduction = 5.8 °F, (coincident ratio = 0.94248) UCS-66 governing thickness = 0.125 in.

5. Pad impact test exemption temperature from Fig UCS-66 Curve B = -20 °FFig UCS-66.1 MDMT reduction = 5.5 °F, (coincident ratio = 0.9448) UCS-66 governing thickness = 0.125 in.

Design notes are available on the Settings Summary page.

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Revision History

No. Date Operator Notes

0 7/ 5/2013 User New vessel created ASME Section VIII Division 1 [Build 6258]

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Settings Summary

COMPRESS Build 6258

Units: U.S. Customary

Datum Line Location: 0.00" from right seam

Design

ASME Section VIII Division 1, 2007 Edition

Design or Rating: Get Thickness from PressureMinimum thickness: 1/16" per UG-16(b)Design for cold shut down only: NoDesign for lethal service (full radiography required): NoDesign nozzles for: Design P, find nozzle MAWP and MAPCorrosion weight loss: 100% of theoretical lossUG-23 Stress Increase: 1.20Skirt/legs stress increase: 1.0Minimum nozzle projection: 6.0000"Juncture calculations for α > 30 only: NoPreheat P-No 1 Materials > 1.25&#34 and <= 1.50" thick: NoButt welds are tapered per Figure UCS-66.3(a).

Hydro/Pneumatic Test

Shop Hydrotest Pressure: 1.3 times vesselMAWP

Test liquid specific gravity: 1.00Maximum stress during test: 90% of yield

Required Marking - UG-116

UG-116 (e) Radiography: RT1UG-116 (f) Postweld heat treatment: None

Code Cases\Interpretations

Use Code Case 2547: NoApply interpretation VIII-1-83-66: YesApply interpretation VIII-1-86-175: YesApply interpretation VIII-1-83-115: YesApply interpretation VIII-1-01-37: YesDisallow UG-20(f) exemptions: No

UG-22 Loadings

UG-22 (a) Internal or External Design Pressure : YesUG-22 (b) Weight of the vessel and normal contents under operating or test conditions: YesUG-22 (c) Superimposed static reactions from weight of attached equipment (external loads): No

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UG-22 (d)(2) Vessel supports such as lugs, rings, skirts, saddles and legs: YesUG-22 (f) Wind reactions: NoUG-22 (f) Seismic reactions: NoNote: UG-22 (b),(c) and (f) loads only considered when supports are present.

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Thickness Summary

ComponentIdentifier

Material Diameter(in)

Length(in)

Nominal t(in)

Design t(in)

JointE

Load

Ellipsoidal Head #2 SA-240 304 48.00 OD 12.06 0.1181* 0.0599 1.0000 Internal

Straight Flange on Ellipsoidal Head #2 SA-240 304 48.00 OD 2.00 0.1181 0.0600 1.0000 Internal

Cylinder #1 SA-240 304 48.00 OD 98.43 0.1250 0.0600 1.0000 Internal

Straight Flange on Ellipsoidal Head #1 SA-240 304 48.00 OD 2.00 0.1250 0.0600 1.0000 Internal

Ellipsoidal Head #1 SA-240 304 48.00 OD 12.06 0.1250* 0.0599 1.0000 Internal

Nominal t: Vessel wall nominal thickness

Design t: Required vessel thickness due to governing loading + corrosion

Joint E: Longitudinal seam joint efficiency

* Head minimum thickness after forming

Load

internal: Circumferential stress due to internal pressure governs

external: External pressure governs

Wind: Combined longitudinal stress of pressure + weight + wind governs

Seismic: Combined longitudinal stress of pressure + weight + seismic governs

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Weight Summary

ComponentWeight ( lb) Contributed by Vessel Elements

MetalNew*

Metal

Corroded*Insulation &

Supports Lining Piping+ Liquid

OperatingLiquid

TestLiquid

Ellipsoidal Head #2 100.65 100.65 0.00 0.00 0.00 0.00 644.88

Cylinder #1 536.35 536.35 0.00 0.00 0.00 0.00 6,362.96

Ellipsoidal Head #1 106.58 106.58 0.00 0.00 0.00 0.00 644.25

Saddle #1 248.00 248.00 0.00 0.00 0.00 0.00 0.00

TOTAL: 991.59 991.59 0.00 0.00 0.00 0.00 7,652.08

* Shells with attached nozzles have weight reduced by material cut out for opening.

Component

Weight ( lb) Contributed by Attachments

Body Flanges Nozzles &Flanges Packed

BedsTrays &

SupportsRings &

ClipsVerticalLoads

New Corroded New Corroded

Ellipsoidal Head #2 0.00 0.00 13.38 13.38 0.00 0.00 0.00 0.00

Cylinder #1 0.00 0.00 17.84 17.84 0.00 0.00 0.00 0.00

Ellipsoidal Head #1 0.00 0.00 8.68 8.68 0.00 0.00 0.00 0.00

TOTAL: 0.00 0.00 39.91 39.91 0.00 0.00 0.00 0.00

Vessel operating weight, Corroded: 1,031 lbVessel operating weight, New: 1,031 lbVessel empty weight, Corroded: 1,031 lbVessel empty weight, New: 1,031 lbVessel test weight, New: 8,684 lb

Vessel center of gravity location - from datum - lift condition

Vessel Lift Weight, New: 1,031 lbCenter of Gravity: 49.21"

Vessel Capacity

Vessel Capacity** (New): 917 US galVessel Capacity** (Corroded): 917 US gal**The vessel capacity does not include volume of nozzle, piping or other attachments.

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Hydrostatic Test

Shop test pressure determination for Chamber bounded by Ellipsoidal Head #1 and Ellipsoidal Head #2 basedon MAWP per UG-99(b)

Shop hydrostatic test gauge pressure is 128.194 psi at 70 °F (the chamber MAWP = 98.611 psi)

The shop test is performed with the vessel in the horizontal position.

IdentifierLocal testpressure

psi

Test liquidstatic head

psi

UG-99stressratio

UG-99pressure

factor

Stressduring test

psi

Allowabletest stress

psi

Stressexcessive?

Ellipsoidal Head #2 (1) 130.139 1.945 1 1.30 23,685 27,000 No

Straight Flange on Ellipsoidal Head #2 130.139 1.945 1 1.30 26,381 27,000 No

Cylinder #1 130.139 1.945 1 1.30 24,922 27,000 No

Straight Flange on Ellipsoidal Head #1 130.139 1.945 1 1.30 24,922 27,000 No

Ellipsoidal Head #1 130.139 1.945 1 1.30 22,371 27,000 No

N2 (N2) 128.857 0.663 1 1.30 23,451 36,915 No

N3 (N3) 129.724 1.53 1 1.30 23,609 36,690 No

N4 (N4) 128.592 0.398 1 1.30 13,595 40,500 No

N5 (N5) 130.36 2.166 1 1.30 24,899 37,752 No

N6 (N6) 128.411 0.217 1 1.30 24,526 38,385 No

N7 (N7) 128.411 0.217 1 1.30 18,869 40,500 No

N8 (N8) 128.411 0.217 1 1.30 24,526 38,385 No

Nozzle #1 (N1) 128.665 0.471 1 1.30 15,828 40,500 No

Notes:(1) Ellipsoidal Head #2 limits the UG-99 stress ratio.(2) PL stresses at nozzle openings have been estimated using the method described in PVP-Vol. 399, pages 77-82.(3) VIII-2, AD-151.1(b) used as the basis for nozzle allowable test stress.(4) The zero degree angular position is assumed to be up, and the test liquid height is assumed to the top-mostflange.

The field test condition has not been investigated for the Chamber bounded by Ellipsoidal Head #1 and EllipsoidalHead #2.

The test temperature of 70 °F is warmer than the minimum recommended temperature of 4.5 °F so the brittle fractureprovision of UG-99(h) has been met.

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Cylinder #1


Component: CylinderMaterial specification: SA-240 304 (II-D p. 90, ln. 4)Rated MDMT per UHA-51(d)(1)(a) = -320 °F

Internal design pressure: P = 50 psi @ 158°F

Static liquid head:

Pth =1.9447 psi (SG=1.0000, Hs=53.8750", Horizontal test head)

Corrosion allowance: Inner C = 0.0000" Outer C = 0.0000"

Design MDMT = -20.00°F No impact test performedRated MDMT = -320.00°F Material is not normalized

Material is not produced to Fine Grain PracticePWHT is not performed

Radiography: Longitudinal joint - Full UW-11(a) Type 1Left circumferential joint - Full UW-11(a) Type 1Right circumferential joint - Full UW-11(a) Type 1

Estimated weight: New = 536.6275 lb corr = 536.6275 lbCapacity: New = 763.0112 gal corr = 763.0112 galOD = 48.0000"Length Lc = 98.4252"t = 0.1250"

Design thickness, (at 158.00°F) Appendix 1-1

t = P*Ro/(S*E + 0.40*P) + Corrosion= 50.00*24.0000/(20000*1.00 + 0.40*50.00) + 0.0000= 0.0600"

Maximum allowable working pressure, (at 158.00°F) Appendix 1-1

P = S*E*t/(Ro - 0.40*t) - Ps= 20000*1.00*0.1250 / (24.0000 - 0.40*0.1250) - 0.0000= 104.3841 psi

Maximum allowable pressure, (at 70.00°F) Appendix 1-1

P = S*E*t/(Ro - 0.40*t)= 20000*1.00*0.1250 / (24.0000 - 0.40*0.1250)= 104.3841 psi

% Forming Strain - UHA-44(a)(2)(a)

= (50 * t / Rf) * (1 - Rf / Ro)= (50 * 0.1250 / 23.9375) * (1 - 23.9375 / ∞)= 0.2611 %

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Allowable Compressive Stress, Hot and Corroded- ScHC, (table HA-1)A = 0.125 / (Ro / t)

= 0.125 / (24.0000 / 0.1250)= 0.000651

B = 7137.3750 psi

S = 20000.0000 / 1.0000= 20000.0000 psi

ScHC = 7137.3750 psi

Allowable Compressive Stress, Hot and New- ScHN

ScHN = ScHC

= 7137.3750 psi

Allowable Compressive Stress, Cold and New- ScCN, (table HA-1)A = 0.125 / (Ro / t)

= 0.125 / (24.0000 / 0.1250)= 0.000651

B = 7490.2925 psi

S = 20000.0000 / 1.0000= 20000.0000 psi

ScCN = 7490.2925 psi

Allowable Compressive Stress, Cold and Corroded- ScCC

ScCC = ScCN

= 7490.2925 psi

Allowable Compressive Stress, Vacuum and Corroded- ScVC, (table HA-1)A = 0.125 / (Ro / t)

= 0.125 / (24.0000 / 0.1250)= 0.000651

B = 7490.2925 psi

S = 20000.0000 / 1.0000= 20000.0000 psi

ScVC = 7490.2925 psi

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Ellipsoidal Head #2

ASME Section VIII, Division 1, 2007 Edition

Component: Ellipsoidal HeadMaterial Specification: SA-240 304 (II-D p.90, ln. 4)Material Rated MDMT per UHA-51(d)(1)(a) = -320 °F

Internal design pressure: P = 50 psi @ 158 °F

Static liquid head:

Ps= 0 psi (SG=1, Hs=0" Operating head)Pth= 1.945 psi (SG=1, Hs=53.8819" Horizontal test head)

Corrosion allowance: Inner C = 0" Outer C = 0"

Design MDMT = -20°F No impact test performedRated MDMT = -320°F Material is not normalized

Material is not produced to fine grain practicePWHT is not performedDo not Optimize MDMT / Find MAWP

Radiography: Category A joints - Full UW-11(a) Type 1 Head to shell seam - Full UW-11(a) Type 1

Estimated weight*: new = 100.7 lb corr = 100.7 lbCapacity*: new = 77.3 US gal corr = 77.3 US gal* includes straight flange

Outer diameter = 48"Minimum head thickness = 0.1181"Head ratio D/2h = 2 (new)Head ratio D/2h = 2 (corroded)Straight flange length Lsf = 2"Nominal straight flange thickness tsf = 0.1181"Results Summary

The governing condition is UG-16.Minimum thickness per UG-16 = 0.0625" + 0" = 0.0625"Design thickness due to internal pressure (t) = 0.0599"Maximum allowable working pressure (MAWP) = 98.85 psiMaximum allowable pressure (MAP) = 98.85 psi

K (Corroded)

K=(1/6)*[2 + (D / (2*h))2]=(1/6)*[2 + (47.7638 / (2*11.941))2]=1

K (New)

K=(1/6)*[2 + (D / (2*h))2]=(1/6)*[2 + (47.7638 / (2*11.941))2]=1

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Design thickness for internal pressure, (Corroded at 158 °F) Appendix 1-4(c)

t = P*Do*K / (2*S*E + 2*P*(K - 0.1)) + Corrosion= 50*48*1 / (2*20,000*1 + 2*50*(1 - 0.1)) + 0= 0.0599"

The head internal pressure design thickness is 0.0599".

Maximum allowable working pressure, (Corroded at 158 °F) Appendix 1-4(c)

P = 2*S*E*t / (K*Do - 2*t*(K - 0.1)) - Ps= 2*20,000*1*0.1181 / (1*48 - 2*0.1181*(1 - 0.1)) - 0= 98.85 psi

The maximum allowable working pressure (MAWP) is 98.85 psi.

Maximum allowable pressure, (New at 70 °F) Appendix 1-4(c)

P = 2*S*E*t / (K*Do - 2*t*(K - 0.1)) - Ps= 2*20,000*1*0.1181 / (1*48 - 2*0.1181*(1 - 0.1)) - 0= 98.85 psi

The maximum allowable pressure (MAP) is 98.85 psi.

% Forming strain - UHA-44(a)(2)(b)

= (75*t / Rf)*(1 - Rf / Ro)= (75*0.1181 / 8.1789)*(1 - 8.1789 / ∞)= 1.083%

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Straight Flange on Ellipsoidal Head #2


Component: Straight FlangeMaterial specification: SA-240 304 (II-D p. 90, ln. 4)Rated MDMT per UHA-51(d)(1)(a) = -320 °F


Static liquid head:





Radiography: Longitudinal joint - Full UW-11(a) Type 1Circumferential joint - Full UW-11(a) Type 1





P = S*E*t/(Ro - 0.40*t) - Ps= 20000*1.00*0.1181 / (24.0000 - 0.40*0.1181) - 0.0000= 98.6108 psi


P = S*E*t/(Ro - 0.40*t)= 20000*1.00*0.1181 / (24.0000 - 0.40*0.1181)= 98.6108 psi


= (50 * t / Rf) * (1 - Rf / Ro)= (50 * 0.1181 / 23.9410) * (1 - 23.9410 / ∞)= 0.2466 %

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= 0.125 / (24.0000 / 0.1181)= 0.000615

B = 6979.3862 psi

S = 20000.0000 / 1.0000= 20000.0000 psi

ScHC = 6979.3862 psi


ScHN = ScHC

= 6979.3862 psi


= 0.125 / (24.0000 / 0.1181)= 0.000615

B = 7315.4189 psi

S = 20000.0000 / 1.0000= 20000.0000 psi

ScCN = 7315.4189 psi


ScCC = ScCN

= 7315.4189 psi


= 0.125 / (24.0000 / 0.1181)= 0.000615

B = 7315.4189 psi

S = 20000.0000 / 1.0000= 20000.0000 psi

ScVC = 7315.4189 psi

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Straight Flange on Ellipsoidal Head #1


Component: Straight FlangeMaterial specification: SA-240 304 (II-D p. 90, ln. 4)Rated MDMT per UHA-51(d)(1)(a) = -320 °F


Static liquid head:





Radiography: Longitudinal joint - Full UW-11(a) Type 1Circumferential joint - Full UW-11(a) Type 1





P = S*E*t/(Ro - 0.40*t) - Ps= 20000*1.00*0.1250 / (24.0000 - 0.40*0.1250) - 0.0000= 104.3841 psi


P = S*E*t/(Ro - 0.40*t)= 20000*1.00*0.1250 / (24.0000 - 0.40*0.1250)= 104.3841 psi


= (50 * t / Rf) * (1 - Rf / Ro)= (50 * 0.1250 / 23.9375) * (1 - 23.9375 / ∞)= 0.2611 %

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= 0.125 / (24.0000 / 0.1250)= 0.000651

B = 7137.3750 psi

S = 20000.0000 / 1.0000= 20000.0000 psi

ScHC = 7137.3750 psi


ScHN = ScHC

= 7137.3750 psi


= 0.125 / (24.0000 / 0.1250)= 0.000651

B = 7490.2925 psi

S = 20000.0000 / 1.0000= 20000.0000 psi

ScCN = 7490.2925 psi


ScCC = ScCN

= 7490.2925 psi


= 0.125 / (24.0000 / 0.1250)= 0.000651

B = 7490.2925 psi

S = 20000.0000 / 1.0000= 20000.0000 psi

ScVC = 7490.2925 psi

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Ellipsoidal Head #1

ASME Section VIII, Division 1, 2007 Edition

Component: Ellipsoidal HeadMaterial Specification: SA-240 304 (II-D p.90, ln. 4)Material Rated MDMT per UHA-51(d)(1)(a) = -320 °F

Internal design pressure: P = 50 psi @ 158 °F

Static liquid head:

Ps= 0 psi (SG=1, Hs=0" Operating head)Pth= 1.9447 psi (SG=1, Hs=53.875" Horizontal test head)

Corrosion allowance: Inner C = 0" Outer C = 0"

Design MDMT = -20°F No impact test performedRated MDMT = -320°F Material is not normalized

Material is not produced to fine grain practicePWHT is not performedDo not Optimize MDMT / Find MAWP

Radiography: Category A joints - Full UW-11(a) Type 1 Head to shell seam - Full UW-11(a) Type 1

Estimated weight*: new = 106.6 lb corr = 106.6 lbCapacity*: new = 77.2 US gal corr = 77.2 US gal* includes straight flange

Outer diameter = 48"Minimum head thickness = 0.125"Head ratio D/2h = 2 (new)Head ratio D/2h = 2 (corroded)Straight flange length Lsf = 2"Nominal straight flange thickness tsf = 0.125"Results Summary

The governing condition is UG-16.Minimum thickness per UG-16 = 0.0625" + 0" = 0.0625"Design thickness due to internal pressure (t) = 0.0599"Maximum allowable working pressure (MAWP) = 104.66 psiMaximum allowable pressure (MAP) = 104.66 psi

K (Corroded)

K=(1/6)*[2 + (D / (2*h))2]=(1/6)*[2 + (47.75 / (2*11.9375))2]=1

K (New)

K=(1/6)*[2 + (D / (2*h))2]=(1/6)*[2 + (47.75 / (2*11.9375))2]=1

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Design thickness for internal pressure, (Corroded at 158 °F) Appendix 1-4(c)

t = P*Do*K / (2*S*E + 2*P*(K - 0.1)) + Corrosion= 50*48*1 / (2*20,000*1 + 2*50*(1 - 0.1)) + 0= 0.0599"

The head internal pressure design thickness is 0.0599".

Maximum allowable working pressure, (Corroded at 158 °F) Appendix 1-4(c)

P = 2*S*E*t / (K*Do - 2*t*(K - 0.1)) - Ps= 2*20,000*1*0.125 / (1*48 - 2*0.125*(1 - 0.1)) - 0= 104.66 psi

The maximum allowable working pressure (MAWP) is 104.66 psi.

Maximum allowable pressure, (New at 70 °F) Appendix 1-4(c)

P = 2*S*E*t / (K*Do - 2*t*(K - 0.1)) - Ps= 2*20,000*1*0.125 / (1*48 - 2*0.125*(1 - 0.1)) - 0= 104.66 psi

The maximum allowable pressure (MAP) is 104.66 psi.

% Forming strain - UHA-44(a)(2)(b)

= (75*t / Rf)*(1 - Rf / Ro)= (75*0.125 / 8.18)*(1 - 8.18 / ∞)= 1.1461%

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N2 (N2)


tw(lower) = 0.1181 inLeg41 = 0.2362 in

Note: round inside edges per UG-76(c)

Located on: Ellipsoidal Head #2Liquid static head included: 0 psiNozzle material specification: SA-240 304 (II-D p. 90, ln. 4)Nozzle longitudinal joint efficiency: 1Flange description: 0.75 inch Class 150 WN A182 F304Bolt Material: SA-193 B7 Bolt <= 2 1/2 (II-D p. 348, ln. 33)Flange rated MDMT: -55°F(Per UHA-51(d)(1)(a))(Flange rated MDMT = -320 °FBolts rated MDMT per Fig UCS-66 note (e) = -55 °F)Liquid static head on flange: 0 psiASME B16.5 flange rating MAWP: 248.9 psi @ 158°FASME B16.5 flange rating MAP: 275 psi @ 70°FASME B16.5 flange hydro test: 425 psi @ 70°FNozzle orientation: 0°Calculated as hillside: yesLocal vessel minimum thickness: 0.1181 inEnd of nozzle to datum line: 117.25 inNozzle inside diameter, new: 0.742 inNozzle nominal wall thickness: 0.154 inNozzle corrosion allowance: 0 inOpening chord length: 0.7727 inProjection available outside vessel, Lpr: 5.7334 inProjection available outside vessel to flange face, Lf: 6.2334 inDistance to head center, R: 12 in

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Reinforcement Calculations for Internal Pressure

The vessel wall thickness governs the MAWP of this nozzle.

UG-37 Area Calculation Summary(in2)

For P = 109.59 psi @ 158 °F

UG-45 NozzleWall

ThicknessSummary (in)The nozzle passes

UG-45

Arequired

Aavailable A1 A2 A3 A5

Awelds treq tmin

This nozzle is exempt from areacalculations per UG-36(c)(3)(a) 0.0989 0.154

Weld Failure Path Analysis Summary

The nozzle is exempt from weld strengthcalculations per UW-15(b)(2)

UW-16 Weld Sizing Summary

Weld description Required weldthroat size (in)

Actual weldthroat size (in) Status

Nozzle to shell fillet (Leg41) 0.0827 0.1654 weld size is adequate

Calculations for internal pressure 109.59 psi @ 158 °F

Nozzle rated MDMT per UHA-51(d)(1)(a) = -320 °F.

Limits of reinforcement per UG-40

Parallel to the vessel wall: d = 0.7727 inNormal to the vessel wall outside: 2.5*(t - C) = 0.2953 in

Nozzle required thickness per UG-27(c)(1)

trn = P*Rn/(Sn*E - 0.6*P)= 109.5913*0.371/(20,000*1 - 0.6*109.5913)= 0.002 in

Required thickness tr from UG-37(a)(c)

tr = P*K1*Do/(2*S*E + 0.8*P)= 109.5913*0.9*48/(2*20,000*1 + 0.8*109.5913)= 0.1181 in

This opening does not require reinforcement per UG-36(c)(3)(a)

UW-16(c) Weld Check

23/68

Fillet weld: tmin = lesser of 0.75 or tn or t = 0.1181 intc(min) = lesser of 0.25 or 0.7*tmin = 0.0827 intc(actual) = 0.7*Leg = 0.7*0.2362 = 0.1654 in

The fillet weld size is satisfactory.

Weld strength calculations are not required for this detail which conforms to Fig. UW-16.1, sketch (c-e).

UG-45 Nozzle Neck Thickness Check

Interpretation VIII-1-83-66 has been applied.

Wall thickness per UG-45(a): tr1 = 0.002 in (E =1)Wall thickness per UG-45(b)(1): tr2 = 0.1309 inWall thickness per UG-16(b): tr3 = 0.0625 inStandard wall pipe per UG-45(b)(4): tr4 = 0.0989 inThe greater of tr2 or tr3: tr5 = 0.1309 inThe lesser of tr4 or tr5: tr6 = 0.0989 in

Required per UG-45 is the larger of tr1 or tr6 = 0.0989 in

Available nozzle wall thickness new, tn = 0.154 in

The nozzle neck thickness is adequate.

% Forming strain - UHA-44(a)(2)(a)

= (50*t / Rf)*(1 - Rf / Ro)= (50*0.154 / 0.448)*(1 - 0.448 / ∞)= 17.1875%

24/68

Reinforcement Calculations for MAP

The vessel wall thickness governs the MAP of this nozzle.


For P = 109.59 psi @ 70 °F

UG-45 NozzleWall


UG-45

Arequired


Awelds treq tmin













trn = P*Rn/(Sn*E - 0.6*P)= 109.5913*0.371/(20,000*1 - 0.6*109.5913)= 0.002 in


tr = P*K1*Do/(2*S*E + 0.8*P)= 109.5913*0.9*48/(2*20,000*1 + 0.8*109.5913)= 0.1181 in


25/68

UW-16(c) Weld Check










26/68

N3 (N3)


tw(lower) = 0.1181 inLeg41 = 0.2362 in


Located on: Ellipsoidal Head #2Liquid static head included: 0 psiNozzle material specification: SA-240 304 (II-D p. 90, ln. 4)Nozzle longitudinal joint efficiency: 1Flange description: 0.75 inch Class 150 WN A182 F304Bolt Material: SA-193 B7 Bolt <= 2 1/2 (II-D p. 348, ln. 33)Flange rated MDMT: -55°F(Per UHA-51(d)(1)(a))(Flange rated MDMT = -320 °FBolts rated MDMT per Fig UCS-66 note (e) = -55 °F)Liquid static head on flange: 0 psiASME B16.5 flange rating MAWP: 248.9 psi @ 158°FASME B16.5 flange rating MAP: 275 psi @ 70°FASME B16.5 flange hydro test: 425 psi @ 70°FNozzle orientation: 180°Calculated as hillside: yesLocal vessel minimum thickness: 0.1181 inEnd of nozzle to datum line: 117.25 inNozzle inside diameter, new: 0.742 inNozzle nominal wall thickness: 0.154 inNozzle corrosion allowance: 0 inOpening chord length: 0.7727 inProjection available outside vessel, Lpr: 5.7334 inProjection available outside vessel to flange face, Lf: 6.2334 inDistance to head center, R: 12 in

27/68




For P = 109.59 psi @ 158 °F

UG-45 NozzleWall


UG-45

Arequired


Awelds treq tmin













trn = P*Rn/(Sn*E - 0.6*P)= 109.5913*0.371/(20,000*1 - 0.6*109.5913)= 0.002 in


tr = P*K1*Do/(2*S*E + 0.8*P)= 109.5913*0.9*48/(2*20,000*1 + 0.8*109.5913)= 0.1181 in


UW-16(c) Weld Check

28/68











= (50*t / Rf)*(1 - Rf / Ro)= (50*0.154 / 0.448)*(1 - 0.448 / ∞)= 17.1875%

29/68




For P = 109.59 psi @ 70 °F

UG-45 NozzleWall


UG-45

Arequired


Awelds treq tmin













trn = P*Rn/(Sn*E - 0.6*P)= 109.5913*0.371/(20,000*1 - 0.6*109.5913)= 0.002 in


tr = P*K1*Do/(2*S*E + 0.8*P)= 109.5913*0.9*48/(2*20,000*1 + 0.8*109.5913)= 0.1181 in


30/68

UW-16(c) Weld Check










31/68

N4 (N4)


tw(lower) = 0.125 inLeg41 = 0.2362 intw(upper) = 0 inLeg42 = 0.0893 inDp = 6.9889 inte = 0.125 in


Located on: Ellipsoidal Head #1Liquid static head included: 0 psiNozzle material specification: SA-240 304 (II-D p. 90, ln. 4)Nozzle longitudinal joint efficiency: 1Pad material specification: SA-516 70 (II-D p. 18, ln. 22)Pad diameter: 6.9889 inFlange description: 2 inch Class 150 WN A182 F304Bolt Material: SA-193 B7 Bolt <= 2 1/2 (II-D p. 348, ln. 33)Flange rated MDMT: -55°F(Per UHA-51(d)(1)(a))(Flange rated MDMT = -320 °FBolts rated MDMT per Fig UCS-66 note (e) = -55 °F)Liquid static head on flange: 0 psiASME B16.5 flange rating MAWP: 248.9 psi @ 158°FASME B16.5 flange rating MAP: 275 psi @ 70°FASME B16.5 flange hydro test: 425 psi @ 70°FNozzle orientation: 0°Calculated as hillside: yesLocal vessel minimum thickness: 0.125 inEnd of nozzle to datum line: -15.529 inNozzle inside diameter, new: 2.067 inNozzle nominal wall thickness: 0.154 inNozzle corrosion allowance: 0 inOpening chord length: 2.6094 inProjection available outside vessel, Lpr: 5.2888 inProjection available outside vessel to flange face, Lf: 6.0388 inDistance to head center, R: 20 inPad is split: no

32/68




For P = 104.66 psi @ 158 °F

UG-45Nozzle WallThicknessSummary

(in)The nozzle

passes UG-45

Arequired


Awelds treq tmin







Nozzle to pad fillet (Leg41) 0.0875 0.1654 weld size is adequate

Pad to shell fillet (Leg42) 0.0625 0.0625 weld size is adequate


Nozzle rated MDMT per UHA-51(d)(1)(a) = -320 °F.Pad impact test exemption temperature from Fig UCS-66 Curve B = -20 °FFig UCS-66.1 MDMT reduction = 5.8 °F, (coincident ratio = 0.94248).

Pad UCS-66 governing thickness: 0.125 inPad rated MDMT: -25.8 °F




trn = P*Rn/(Sn*E - 0.6*P)= 104.657*1.0335/(20,000*1 - 0.6*104.657)= 0.0054 in

Required thickness tr from UG-37(a)

tr = P*Do*K / (2*S*E + 2*P*(K - 0.1))

33/68

= 104.66*48*1 / (2*20,000*1 + 2*104.66*(1 - 0.1))= 0.125"


UW-16(c)(2) Weld Check

Inner fillet: tmin = lesser of 0.75 or tn or te = 0.125 intw(min) = 0.7*tmin = 0.0875 intw(actual) = 0.7*Leg = 0.7*0.2362 = 0.1654 in

Outer fillet: tmin = lesser of 0.75 or te or t = 0.125 intw(min) = 0.5*tmin = 0.0625 intw(actual) = 0.7*Leg = 0.7*0.0893 = 0.0625 in








= (50*t / Rf)*(1 - Rf / Ro)= (50*0.154 / 1.1105)*(1 - 1.1105 / ∞)= 6.9338%

34/68




For P = 104.66 psi @ 70 °F


(in)The nozzle

passes UG-45

Arequired


Awelds treq tmin














trn = P*Rn/(Sn*E - 0.6*P)= 104.657*1.0335/(20,000*1 - 0.6*104.657)= 0.0054 in


tr = P*Do*K / (2*S*E + 2*P*(K - 0.1))= 104.66*48*1 / (2*20,000*1 + 2*104.66*(1 - 0.1))= 0.125"

35/68











36/68

N5 (N5)


tw(lower) = 0.125 inLeg41 = 0.2362 in


Located on: Cylinder #1Liquid static head included: 0 psiNozzle material specification: SA-240 304 (II-D p. 90, ln. 4)Nozzle longitudinal joint efficiency: 1Flange description: 1 inch Class 150 WN A182 F304Bolt Material: SA-193 B7 Bolt <= 2 1/2 (II-D p. 348, ln. 33)Flange rated MDMT: -55°F(Per UHA-51(d)(1)(a))(Flange rated MDMT = -320 °FBolts rated MDMT per Fig UCS-66 note (e) = -55 °F)Liquid static head on flange: 0 psiASME B16.5 flange rating MAWP: 248.9 psi @ 158°FASME B16.5 flange rating MAP: 275 psi @ 70°FASME B16.5 flange hydro test: 425 psi @ 70°FNozzle orientation: 180°Local vessel minimum thickness: 0.125 inNozzle center line offset to datum line: 35 inEnd of nozzle to shell center: 30 inNozzle inside diameter, new: 0.957 inNozzle nominal wall thickness: 0.179 inNozzle corrosion allowance: 0 inProjection available outside vessel, Lpr: 5.44 inProjection available outside vessel to flange face, Lf: 6 in

37/68




For P = 104.35 psi @ 158 °F

UG-45 NozzleWall


UG-45

Arequired


Awelds treq tmin













trn = P*Rn/(Sn*E - 0.6*P)= 104.3533*0.4785/(20,000*1 - 0.6*104.3533)= 0.0025 in


tr = P*Ro/(S*E + 0.4*P)= 104.3533*24/(20,000*1 + 0.4*104.3533)= 0.125 in


UW-16(c) Weld Check

38/68










= (50*t / Rf)*(1 - Rf / Ro)= (50*0.179 / 0.568)*(1 - 0.568 / ∞)= 15.757%

39/68




For P = 104.35 psi @ 70 °F

UG-45 NozzleWall


UG-45

Arequired


Awelds treq tmin













trn = P*Rn/(Sn*E - 0.6*P)= 104.3533*0.4785/(20,000*1 - 0.6*104.3533)= 0.0025 in


tr = P*Ro/(S*E + 0.4*P)= 104.3533*24/(20,000*1 + 0.4*104.3533)= 0.125 in


40/68

UW-16(c) Weld Check









41/68

N6 (N6)


tw(lower) = 0.125 inLeg41 = 0.2362 in


Located on: Cylinder #1Liquid static head included: 0 psiNozzle material specification: SA-240 304 (II-D p. 90, ln. 4)Nozzle longitudinal joint efficiency: 1Flange description: 0.75 inch Class 150 WN A182 F304Bolt Material: SA-193 B7 Bolt <= 2 1/2 (II-D p. 348, ln. 33)Flange rated MDMT: -55°F(Per UHA-51(d)(1)(a))(Flange rated MDMT = -320 °FBolts rated MDMT per Fig UCS-66 note (e) = -55 °F)Liquid static head on flange: 0 psiASME B16.5 flange rating MAWP: 248.9 psi @ 158°FASME B16.5 flange rating MAP: 275 psi @ 70°FASME B16.5 flange hydro test: 425 psi @ 70°FNozzle orientation: 0°Local vessel minimum thickness: 0.125 inNozzle center line offset to datum line: 30 inEnd of nozzle to shell center: 30 inNozzle inside diameter, new: 0.742 inNozzle nominal wall thickness: 0.154 inNozzle corrosion allowance: 0 inProjection available outside vessel, Lpr: 5.5 inProjection available outside vessel to flange face, Lf: 6 in

42/68




For P = 104.35 psi @ 158 °F

UG-45 NozzleWall


UG-45

Arequired


Awelds treq tmin













trn = P*Rn/(Sn*E - 0.6*P)= 104.3533*0.371/(20,000*1 - 0.6*104.3533)= 0.0019 in


tr = P*Ro/(S*E + 0.4*P)= 104.3533*24/(20,000*1 + 0.4*104.3533)= 0.125 in


UW-16(c) Weld Check

43/68










= (50*t / Rf)*(1 - Rf / Ro)= (50*0.154 / 0.448)*(1 - 0.448 / ∞)= 17.1875%

44/68




For P = 104.35 psi @ 70 °F

UG-45 NozzleWall


UG-45

Arequired


Awelds treq tmin













trn = P*Rn/(Sn*E - 0.6*P)= 104.3533*0.371/(20,000*1 - 0.6*104.3533)= 0.0019 in


tr = P*Ro/(S*E + 0.4*P)= 104.3533*24/(20,000*1 + 0.4*104.3533)= 0.125 in


45/68

UW-16(c) Weld Check









46/68

N7 (N7)


tw(lower) = 0.125 inLeg41 = 0.2362 intw(upper) = 0 inLeg42 = 0.0893 inDp = 6.375 inte = 0.125 in


Located on: Cylinder #1Liquid static head included: 0 psiNozzle material specification: SA-240 304 (II-D p. 90, ln. 4)Nozzle longitudinal joint efficiency: 1Pad material specification: SA-516 70 (II-D p. 18, ln. 22)Pad diameter: 6.375 inFlange description: 2 inch Class 150 WN A182 F304Bolt Material: SA-193 B7 Bolt <= 2 1/2 (II-D p. 348, ln. 33)Flange rated MDMT: -55°F(Per UHA-51(d)(1)(a))(Flange rated MDMT = -320 °FBolts rated MDMT per Fig UCS-66 note (e) = -55 °F)Liquid static head on flange: 0 psiASME B16.5 flange rating MAWP: 248.9 psi @ 158°FASME B16.5 flange rating MAP: 275 psi @ 70°FASME B16.5 flange hydro test: 425 psi @ 70°FNozzle orientation: 0°Local vessel minimum thickness: 0.125 inNozzle center line offset to datum line: 53 inEnd of nozzle to shell center: 30 inNozzle inside diameter, new: 2.067 inNozzle nominal wall thickness: 0.154 inNozzle corrosion allowance: 0 inProjection available outside vessel, Lpr: 5.25 inProjection available outside vessel to flange face, Lf: 6 inPad is split: no

47/68




For P = 104.35 psi @ 158 °F


(in)The nozzle

passes UG-45

Arequired


Awelds treq tmin










Nozzle rated MDMT per UHA-51(d)(1)(a) = -320 °F.Pad impact test exemption temperature from Fig UCS-66 Curve B = -20 °FFig UCS-66.1 MDMT reduction = 5.5 °F, (coincident ratio = 0.9448).

Pad UCS-66 governing thickness: 0.125 inPad rated MDMT: -25.5 °F




trn = P*Rn/(Sn*E - 0.6*P)= 104.3533*1.0335/(20,000*1 - 0.6*104.3533)= 0.0054 in


tr = P*Ro/(S*E + 0.4*P)

48/68

= 104.3533*24/(20,000*1 + 0.4*104.3533)= 0.125 in











= (50*t / Rf)*(1 - Rf / Ro)= (50*0.154 / 1.1105)*(1 - 1.1105 / ∞)= 6.9338%

49/68




For P = 104.35 psi @ 70 °F


(in)The nozzle

passes UG-45

Arequired


Awelds treq tmin














trn = P*Rn/(Sn*E - 0.6*P)= 104.3533*1.0335/(20,000*1 - 0.6*104.3533)= 0.0054 in


tr = P*Ro/(S*E + 0.4*P)= 104.3533*24/(20,000*1 + 0.4*104.3533)= 0.125 in

50/68










51/68

N8 (N8)


tw(lower) = 0.125 inLeg41 = 0.2362 in


Located on: Cylinder #1Liquid static head included: 0 psiNozzle material specification: SA-240 304 (II-D p. 90, ln. 4)Nozzle longitudinal joint efficiency: 1Flange description: 0.75 inch Class 300 WN A182 F304Bolt Material: SA-193 B7 Bolt <= 2 1/2 (II-D p. 348, ln. 33)Flange rated MDMT: -55°F(Per UHA-51(d)(1)(a))(Flange rated MDMT = -320 °FBolts rated MDMT per Fig UCS-66 note (e) = -55 °F)Liquid static head on flange: 0 psiASME B16.5 flange rating MAWP: 650.4 psi @ 158°FASME B16.5 flange rating MAP: 720 psi @ 70°FASME B16.5 flange hydro test: 1100 psi @ 70°FNozzle orientation: 0°Local vessel minimum thickness: 0.125 inNozzle center line offset to datum line: 80 inEnd of nozzle to shell center: 30 inNozzle inside diameter, new: 0.742 inNozzle nominal wall thickness: 0.154 inNozzle corrosion allowance: 0 inProjection available outside vessel, Lpr: 5.38 inProjection available outside vessel to flange face, Lf: 6 in

52/68




For P = 104.35 psi @ 158 °F

UG-45 NozzleWall


UG-45

Arequired


Awelds treq tmin













trn = P*Rn/(Sn*E - 0.6*P)= 104.3533*0.371/(20,000*1 - 0.6*104.3533)= 0.0019 in


tr = P*Ro/(S*E + 0.4*P)= 104.3533*24/(20,000*1 + 0.4*104.3533)= 0.125 in


UW-16(c) Weld Check

53/68










= (50*t / Rf)*(1 - Rf / Ro)= (50*0.154 / 0.448)*(1 - 0.448 / ∞)= 17.1875%

54/68




For P = 104.35 psi @ 70 °F

UG-45 NozzleWall


UG-45

Arequired


Awelds treq tmin













trn = P*Rn/(Sn*E - 0.6*P)= 104.3533*0.371/(20,000*1 - 0.6*104.3533)= 0.0019 in


tr = P*Ro/(S*E + 0.4*P)= 104.3533*24/(20,000*1 + 0.4*104.3533)= 0.125 in


55/68

UW-16(c) Weld Check









56/68

Nozzle #1 (N1)


tw(lower) = 0.1181 inLeg41 = 0.2362 intw(upper) = 0.125 inLeg42 = 0.125 inDp = 5.7345 inte = 0.125 in


Located on: Ellipsoidal Head #2Liquid static head included: 0 psiNozzle material specification: SA-240 304 (II-D p. 90, ln. 4)Nozzle longitudinal joint efficiency: 1Pad material specification: SA-240 304 (II-D p. 90, ln. 4)Pad diameter: 5.7345 inFlange description: 2 inch Class 150 WN A182 F304Bolt Material: SA-193 B7 Bolt <= 2 1/2 (II-D p. 348, ln. 33)Flange rated MDMT: -55°F(Per UHA-51(d)(1)(a))(Flange rated MDMT = -320 °FBolts rated MDMT per Fig UCS-66 note (e) = -55 °F)Liquid static head on flange: 0 psiASME B16.5 flange rating MAWP: 248.9 psi @ 158°FASME B16.5 flange rating MAP: 275 psi @ 70°FASME B16.5 flange hydro test: 425 psi @ 70°FNozzle orientation: 0°Calculated as hillside: yesLocal vessel minimum thickness: 0.1181 inEnd of nozzle to datum line: 115.078 inNozzle inside diameter, new: 2.067 inNozzle nominal wall thickness: 0.154 inNozzle corrosion allowance: 0 inOpening chord length: 2.3837 inProjection available outside vessel, Lpr: 5.2971 inProjection available outside vessel to flange face, Lf: 6.0471 inDistance to head center, R: 18 inPad is split: no

57/68




For P = 98.81 psi @ 158 °F


(in)The nozzle

passes UG-45

Arequired


Awelds treq tmin





Weld description Required weldsize (in)

Actual weldsize (in) Status



Nozzle to pad groove (Upper) 0.0875 0.125 weld size is adequate


Nozzle rated MDMT per UHA-51(d)(1)(a) = -320 °F.Pad rated MDMT per UHA-51(d)(1)(a) = -320 °F.




trn = P*Rn/(Sn*E - 0.6*P)= 98.8117*1.0335/(20,000*1 - 0.6*98.8117)= 0.0051 in


tr = P*Do*K / (2*S*E + 2*P*(K - 0.1))= 98.81*48*1 / (2*20,000*1 + 2*98.81*(1 - 0.1))= 0.118"

58/68



Inner fillet: tmin = lesser of 0.75 or tn or te = 0.125 intc(min) = lesser of 0.25 or 0.7*tmin = 0.0875 intc(actual) = 0.7*Leg = 0.7*0.2362 = 0.1654 in









= (50*t / Rf)*(1 - Rf / Ro)= (50*0.154 / 1.1105)*(1 - 1.1105 / ∞)= 6.9338%

59/68




For P = 98.81 psi @ 70 °F


(in)The nozzle

passes UG-45

Arequired


Awelds treq tmin





Weld description Required weldsize (in)

Actual weldsize (in) Status



Nozzle to pad groove (Upper) 0.0875 0.125 weld size is adequate


Nozzle rated MDMT per UHA-51(d)(1)(a) = -320 °F.Pad rated MDMT per UHA-51(d)(1)(a) = -320 °F.




trn = P*Rn/(Sn*E - 0.6*P)= 98.8117*1.0335/(20,000*1 - 0.6*98.8117)= 0.0051 in


tr = P*Do*K / (2*S*E + 2*P*(K - 0.1))= 98.81*48*1 / (2*20,000*1 + 2*98.81*(1 - 0.1))

60/68

= 0.118"



Inner fillet: tmin = lesser of 0.75 or tn or te = 0.125 intc(min) = lesser of 0.25 or 0.7*tmin = 0.0875 intc(actual) = 0.7*Leg = 0.7*0.2362 = 0.1654 in








61/68

Saddle #1

Saddle material: A 36Saddle construction is: Centered webSaddle allowable stress: Ss = 20,000 psiSaddle yield stress: Sy = 38,000 psiSaddle distance to datum: 10 inTangent to tangent length: L = 102.4252 inSaddle separation: Ls = 78.4252 inVessel radius: R = 24 inTangent distance left: Al = 12 inTangent distance right: Ar = 12 inSaddle height: Hs = 36 inSaddle contact angle: θ = 120 °Web plate thickness: ts = 0.25 inBase plate length: E = 42 inBase plate width: F = 9 inBase plate thickness: tb = 0.375 inNumber of stiffener ribs: n = 3Largest stiffener rib spacing: di = 20.375 inStiffener rib thickness: tw = 0.25 inSaddle width: B = 8 in

Anchor bolt size & type: 1 inch series 8threaded

Anchor bolt material:Anchor bolt allowable shear: 15,000 psiAnchor bolt corrosion allowance: 0 inAnchor bolts per saddle: 2Base coefficient of friction: µ = 0.45

Weight on left saddle: operating corr =391 lb, test new =4,218 lbWeight on right saddle: operating corr =392 lb, test new =4,218 lbWeight of saddle pair =248 lb

62/68

Notes:(1) Saddle calculations are based on the method presented in "Stresses in Large Cylindrical Pressure Vessels onTwo Saddle Supports" by L.P. Zick.

Load Vesselcondition

Bending + pressurebetween saddles

(psi)

Bending + pressure atthe saddle

(psi)

S1(+)

allow(+)

S1(-)

allow(-)

S2(+)

allow(+)

S2(-)

allow(-)

Weight Operating 9,438 20,000 21 7,137 9,419 20,000 2 7,137

Weight Test 12,652 30,000 224 7,490 12,448 30,000 19 7,490

Load Vesselcondition

Tangentialshear (psi)

Circumferentialstress (psi)

Stressover

saddle(psi)

Splitting(psi)

S3 allow S4(horns)

allow(+/-) S5 allow S6 allow

Weight Operating 122 16,000 -1,002 30,000 808 13,200 40 13,333

Weight Test 1,313 24,000 -10,782 30,000 8,691 27,000 429 34,200

Load Case 1: Weight ,Operating

Longitudinal stress between saddles (Weight ,Operating, right saddle loading and geometry govern)

S1 = +- 3*K1*Q*(L/12) / (π*R2*t)= 3*0.4666*392*(102.4252/12) / (π*23.93752*0.125)= 21 psi

Sp = P*R/(2*t)= 98.61*23.875/(2*0.125)= 9,417 psi

Maximum tensile stress S1t = S1 + Sp = 9,438 psiMaximum compressive stress (shut down) S1c = S1 = 21 psi

Tensile stress is acceptable (<=1*S*E = 20,000 psi)Compressive stress is acceptable (<=1*Sc = 7,137 psi)

Longitudinal stress at the right saddle (Weight ,Operating)

Le = 2*(Left head depth)/3 + L + 2*(Right head depth)/3= 2*12.0591/3 + 102.4252 + 2*12.0625/3= 118.5062 in

w = Wt/Le = 783/118.5062 = 6.61 lb/in

Bending moment at the right saddle:

63/68

Mq = w*(2*H*Ar/3 + Ar2/2 - (R2 - H2)/4)

= 6.61*(2*12.0625*12/3 + 122/2 - (242 - 12.06252)/4)= 402.2 lb-in

S2 = +- Mq*K1'/ (π*R2*t)= 402.2*1/ (π*23.93752*0.125)= 2 psi

Sp = P*R/(2*t)= 98.61*23.875/(2*0.125)= 9,417 psi


Tensile stress is acceptable (<=1*S = 20,000 psi)Compressive stress is acceptable (<=1*Sc = 7,137 psi)

Tangential shear stress in the shell (left saddle, Weight ,Operating)

S3 = K2.3*Q/(R*(t))= 0.8799*391/(23.9375*(0.125))= 115 psi

Tangential shear stress is acceptable (<= 0.8*S = 16,000 psi)

Tangential shear stress in the left head (Weight ,Operating)

S3 = K2.3*Q/(R*th)= 0.8799*391/(23.9375*0.1181)= 122 psi

Tangential shear stress is acceptable (<= 0.8*S = 16,000 psi)

Additional stress in the head used as a stiffener

S3h = K2.4*Q/(R*th)= 0.4011*391/(23.9375*0.1181)= 55 psi

Sp = P*(K*Di + 0.2*th)/(2*th)= 98.61*(1*47.7638 + 0.2*0.1181)/(2*0.1181)= 19,951 psi

Total stress in the head = S3h + Sp = 20,006 psi

Stress in the head is acceptable (<= 1.25*Sh = 25,000 psi)

Circumferential stress at the right saddle horns (Weight ,Operating)

S4 = -Q/(4*t*(b+1.56*Sqr(Ro*t))) - 12*K3*Q*R/(L*t2)= -392/(4*0.125*(8+1.56*Sqr(24*0.125))) - 12*0.0132*392*23.9375/(102.4252*0.1252)= -1,002 psi

Circumferential stress at saddle horns is acceptable (<=1.5*Sa = 30,000 psi)

Ring compression in shell over right saddle (Weight ,Operating)

64/68

S5 = K5*Q/((t)*(ts + 1.56*Sqr(Ro*tc)))= 0.7603*392/((0.125)*(0.25 + 1.56*Sqr(24*0.125)))= 808 psi

Ring compression in shell is acceptable (<= 0.5*Sy = 13,200 psi)

Saddle splitting load (right, Weight ,Operating)

Area resisting splitting force = Web area + wear plate area

Ae = Heff*ts + tp*Wp= 8*0.25 + 0*0= 2 in2

S6 = K8*Q / Ae= 0.2035*392 / 2= 40 psi

Stress in saddle is acceptable (<= (2/3)*Ss = 13,333 psi)

Load Case 2: Weight ,Test

Longitudinal stress between saddles (Weight ,Test, right saddle loading and geometry govern)

S1 = +- 3*K1*Q*(L/12) / (π*R2*t)= 3*0.4666*4,218*(102.4252/12) / (π*23.93752*0.125)= 224 psi

Sp = P*R/(2*t)= 130.14*23.875/(2*0.125)= 12,428 psi


Tensile stress is acceptable (<= 0.9*Sy = 30,000 psi)Compressive stress is acceptable (<=1*Sc = 7,490 psi)

Longitudinal stress at the right saddle (Weight ,Test)

Le = 2*(Left head depth)/3 + L + 2*(Right head depth)/3= 2*12.0591/3 + 102.4252 + 2*12.0625/3= 118.5062 in

w = Wt/Le = 8,436/118.5062 = 71.19 lb/in

Bending moment at the right saddle:

Mq = w*(2*H*Ar/3 + Ar2/2 - (R2 - H2)/4)

= 71.19*(2*12.0625*12/3 + 122/2 - (242 - 12.06252)/4)= 4,333.5 lb-in

S2 = +- Mq*K1'/ (π*R2*t)= 4,333.5*1/ (π*23.93752*0.125)= 19 psi

65/68

Sp = P*R/(2*t)= 130.14*23.875/(2*0.125)= 12,428 psi


Tensile stress is acceptable (<= 0.9*Sy = 30,000 psi)Compressive stress is acceptable (<=1*Sc = 7,490 psi)

Tangential shear stress in the shell (left saddle, Weight ,Test)

S3 = K2.3*Q/(R*(t))= 0.8799*4,218/(23.9375*(0.125))= 1,240 psi

Tangential shear stress is acceptable (<= 0.8*(0.9*Sy) = 24,000 psi)

Tangential shear stress in the left head (Weight ,Test)

S3 = K2.3*Q/(R*th)= 0.8799*4,218/(23.9375*0.1181)= 1,313 psi

Tangential shear stress is acceptable (<= 0.8*(0.9*Sy) = 24,000 psi)

Additional stress in the head used as a stiffener

S3h = K2.4*Q/(R*th)= 0.4011*4,218/(23.9375*0.1181)= 598 psi

Sp = P*(K*Di + 0.2*th)/(2*th)= 130.14*(1*47.7638 + 0.2*0.1181)/(2*0.1181)= 26,329 psi

Total stress in the head = S3h + Sp = 26,928 psi

Stress in the head is acceptable (<= 0.9*Sy = 30,000 psi)

Circumferential stress at the right saddle horns (Weight ,Test)

S4 = -Q/(4*t*(b+1.56*Sqr(Ro*t))) - 12*K3*Q*R/(L*t2)= -4,218/(4*0.125*(8+1.56*Sqr(24*0.125))) - 12*0.0132*4,218*23.9375/(102.4252*0.1252)= -10,782 psi

Circumferential stress at saddle horns is acceptable (<= 0.9*Sy = 30,000 psi)

Ring compression in shell over right saddle (Weight ,Test)

S5 = K5*Q/((t)*(ts + 1.56*Sqr(Ro*tc)))= 0.7603*4,218/((0.125)*(0.25 + 1.56*Sqr(24*0.125)))= 8,691 psi

Ring compression in shell is acceptable (<= 0.9*Sy = 27,000 psi)

Saddle splitting load (right, Weight ,Test)

66/68

Area resisting splitting force = Web area + wear plate area

Ae = Heff*ts + tp*Wp= 8*0.25 + 0*0= 2 in2

S6 = K8*Q / Ae= 0.2035*4,218 / 2= 429 psi

Stress in saddle is acceptable (<= 0.9*Sy = 34,200 psi)

Shear stress in anchor bolting, one end slotted

Maximum seismic or wind base shear = 0 lbf

Thermal expansion base shear = W*µ = 516 * 0.45= 232.2 lbf

Corroded root area for a 1 inch series 8 threaded bolt = 0.551 in2 ( 2 per saddle )

Bolt shear stress = 232.2/(0.551*2) = 211 psi

Anchor bolt stress is acceptable (<= 15,000 psi)

Web plate buckling check (Escoe pg 251)

Allowable compressive stress Sc is the lesser of 20,000 or 5,051 psi: (5,051)

Sc = Ki*π2*E/(12*(1 - 0.32)*(di/tw)2)= 1.28*π2*29E+06/(12*(1 - 0.32)*(20.375/0.25)2)= 5,051 psi

Allowable compressive load on the saddle

be = di*ts/(di*ts + 2*tw*(b - 1))= 20.375*0.25/(20.375*0.25 + 2*0.25*(8 - 1))= 0.5927

Fb = n*(As + 2*be*tw)*Sc= 3*(1.9375 + 2*0.5927*0.25)*5,051= 33,849.15 lbf

Saddle loading of 4,342 lbf is <= Fb; satisfactory.

Primary bending + axial stress in the saddle due to end loads (assumes one saddle slotted)σb = V * (Hs - xo)* y / I + Q / A= 0 * (36 - 19.8478)* 4 / 32.01 + 392 / 16.2048= 24 psi

The primary bending + axial stress in the saddle <= 20,000 psi; satisfactory.

Secondary bending + axial stress in the saddle due to end loads (includes thermal expansion, assumes onesaddle slotted)σb = V * (Hs - xo)* y / I + Q / A= 232.2 * (36 - 19.8478)* 4 / 32.01 + 392 / 16.2048= 493 psi

67/68

The secondary bending + axial stress in the saddle < 2*Sy= 76,000 psi; satisfactory.

Saddle base plate thickness check (Roark sixth edition, Table 26, case 7a)

where a = 20.375, b = 4.375 in

tb = (β1*q*b2/(1.5*Sa))0.5

= (3*11*4.3752/(1.5*20,000))0.5

= 0.1483 in

The base plate thickness of 0.375 in is adequate.

Foundation bearing check

Sf = Qmax / (F*E)= 4,342 / (9*42)= 11 psi

Concrete bearing stress < 1,658 psi ; satisfactory.

68/68

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