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Cover Page Deficiencies Summary Nozzle Schedule Nozzle Summary Pressure Summary Revision History Settings Summary Thickness Summary Weight Summary Hydrostatic Test Vacuum Summary Cylinder #1 Top Head Straight Flange on Top Head Straight Flange on Bottom Head Bottom Head Nozzle #1 (N1) Nozzle #2 (N2) Nozzle #3 (N3) Nozzle #4 (N4) Legs

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Cover Page

Cover Page

Custom Engineering

2800 McClelland Ave Erie, PA 16510

COMPRESS Pressure Vessel Design Calculations

Item: Pressure Vessel Vessel No: Customer: Customer #2 Contract: WO# 7220

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Cover Page

Designer: Date: Location: Purchaser: Vessel Name:

George Clark 1/14/04 New Castle Concast America, Inc. Comp2

You can edit this page by selecting Cover Page settings... in the report menu.

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Deficiencies Summary

Deficiencies Summary Warnings Summary Warnings for Nozzle #2 (N2) A full penetration groove weld would qualify this nozzle as integral reinforcment likely reducing the reinforcement required. (warning) Warnings for Nozzle #3 (N3) A full penetration groove weld would qualify this nozzle as integral reinforcment likely reducing the reinforcement required. (warning)

ASME B16.5 / B16.47 Flange Warnings Summary ASME B16.5 / 16.47 Flanges with Warnings

Flange Applicable Warnings

Nozzle #1 (N1) 1 Nozzle #2 (N2) 1 Nozzle #3 (N3) 1 Nozzle #4 (N4) 1 ASME B16.5 / 16.47 Flange Warnings

No. Warning

1

For Class 150 flanges, ASME B16.5 para. 5.4.2 recommends gaskets to be in accordance with Fig. E1, Group No. I.

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Nozzle Schedule

Nozzle Schedule

Materials Nozzle Service mark Size Nozzle Impact Norm Fine Grain Pad Impact Norm Fine Grain Flange

N1

Nozzle #1 Nozzle #2 Nozzle #3 Nozzle #4

1.500" Sch 40 (Std) 1.500" Sch 40 (Std) 1.500" Sch 40 (Std) 6" Sch 40 (Std)

SA-106 B Smls No pipe SA-106 B Smls No pipe SA-106 B Smls No pipe SA-106 B Smls No pipe

No

No

N/A N/A

N/A

N/A

WN A105 150# WN A105 150# WN A105 150# WN A105 150#

N2

No

No

N/A N/A

N/A

N/A

N3

No

No

N/A N/A

N/A

N/A

N4

No

No

N/A N/A

N/A

N/A

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Nozzle Summary

Nozzle Summary

Reinforcement Pad Corr A1? A2? Nom t Design t User t Width tpad (in) (in) (in) (in) (in) (in) Shell N/A N/A N/A N/A N/A N/A N/A N/A

Nozzle OD mark (in)

tn (in)

Req tn (in)

Aa/Ar (%)

N1 N2 N3 N4

1.90 0.1450 0.1450 Yes Yes 0.1875 N/A 1.90 0.1450 0.1450 Yes Yes 0.1875 N/A 1.90 0.1450 0.1450 Yes Yes 0.1875 N/A 6.63 0.2800 0.1279 Yes Yes 0.1875 0.1500

0.0000 Exempt 0.0000 Exempt 0.0000 Exempt 0.0000 100.0

tn: Req tn:

Nozzle thickness Nozzle thickness required per UG-45/UG-16

Nom t: Vessel wall thickness Design t: Required vessel wall thickness due to pressure + corrosion allowance per UG-37 User t: Local vessel wall thickness (near opening) Aa: Area available per UG-37, governing condition Ar: Corr: Area required per UG-37, governing condition Corrosion allowance on nozzle wall

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Pressure Summary

Pressure Summary Pressure Summary for Chamber bounded by Bottom Head and Top Head

P T MAWP Design Design ( psi) (°F) ( psi) 100.0 150.0 178.28 MAP ( psi) MDMT Rating Te MAEP external MDMT ( psi) Exemption (°F) (°F) 150.0 -55.0 Note 1 Total Corrosion Allowance (in) 0.000 Impact Test No

Identifier

Top Head Straight Flange on Top Head Cylinder #1 Straight Flange on Bottom Head Bottom Head Legs Nozzle #1 (N1) Nozzle #2 (N2) Nozzle #3 (N3) Nozzle #4 (N4)

178.28 61.33

100.0

150.0

177.35

177.35 33.07

150.0

-55.0

Note 2

0.000

No

100.0

150.0

146.44

146.44 33.33

150.0

-55.0

Note 3

0.000

No

100.0

150.0

177.35

177.35 33.07

150.0

-55.0

Note 2

0.000

No

100.0 100.0 100.0

150.0 150.0 150.0

178.28 100.00 209.14

178.28 61.33 N/A N/A

150.0 N/A 150.0

-55.0 N/A -55.0

Note 4 N/A Note 5

0.000 N/A 0.000

No N/A No

209.14 33.33

100.0

150.0

209.14

209.14 33.33

150.0

-55.0

Note 5

0.000

No

100.0

150.0

209.14

209.14 33.33

150.0

-55.0

Note 5

0.000

No

100.0

150.0

124.70

124.70 18.93

150.0

-55.0

Note 6

0.000

No

Chamber design MDMT is -20.00°F Chamber rated MDMT is -55.00°F @ 100.00 psi Chamber MAWP hot & corroded is 100.00 psi @ 150.0°F Chamber MAP cold & new is 124.70 psi @ 70.0°F Chamber MAEP is 18.93 psi @ 150.0°F

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Pressure Summary

Vacuum rings did not govern the external pressure rating. Notes for MDMT Rating:

Note # Exemption 1. Straight Flange governs MDMT Material impact test exemption temperature from Fig UCS-66 Curve B = -20 °F Fig UCS-66.1 MDMT reduction = 65.5 °F, (coincident ratio = 0.4801537) Rated MDMT is governed by UCS-66(b)(2) Material impact test exemption temperature from Fig UCS-66 Curve B = -20 °F Fig UCS-66.1 MDMT reduction = 48.7 °F, (coincident ratio = 0.5470086) Rated MDMT is governed by UCS-66(b)(2) Straight Flange governs MDMT Flange rating governs: Nozzle impact test exemption temperature from Fig UCS-66 Curve B = -20 °F Fig UCS-66.1 MDMT reduction = 65.7 °F, (coincident ratio = 0.47904) Rated MDMT is governed by UCS-66(b)(2) UCS-66(b)(1)(b) Details

2.

UCS-66 governing thickness = 0.187 in

3.

UCS-66 governing thickness = 0.1875 in

4. 5.

6.

UCS-66 governing thickness = 0.1875 in.

Design notes are available on the Settings Summary page.

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Revision History

Revision History

No. Date Operator Notes

0

3/12/2004 george

New vessel created with Vessel Wizard, ASME Division 1 [Build 6229]

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Settings Summary

Settings Summary COMPRESS Build 6242 Units: English Datum Line Location: 0.00" from bottom seam Design ASME Section VIII Division 1, 2001 Edition, A03 Addenda Design or Rating: Minimum thickness: Design for cold shut down only: Design for lethal service (full radiography required): Design nozzles for: Corrosion weight loss: UG-23 Stress Increase: Skirt/legs stress increase: Minimum nozzle projection: Get Thickness from Pressure 1/16" per UG-16(b) No No Design P, find nozzle MAWP and MAP 100% of theoretical loss 1.20 1.3 4.0000"

Yes Juncture calculations for > 30 only: Preheat P-No 1 Materials > 1.25" and <= 1.50" thick: No Butt welds are tapered per Figure UCS-66.3(a). Hydro/Pneumatic Test Shop Hydrotest Pressure: 1.3 times vessel MAWP Test liquid specific gravity: 1.00 Maximum stress during test: 90% of yield Code Interpretations Apply interpretation VIII-1-83-66: Yes Apply interpretation VIII-1-86-175: Yes Apply interpretation VIII-1-83-115: Yes

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Settings Summary

Apply interpretation VIII-1-01-37: Yes Disallow UG-20(f) exemptions: No UG-22 Loadings UG-22 (a) Internal or External Design Pressure : Yes UG-22 (b) Weight of the vessel and normal contents under operating or test conditions: Yes UG-22 (c) Superimposed static reactions from weight of attached equipment (external loads): No UG-22 (d)(2) Vessel supports such as lugs, rings, skirts, saddles and legs: Yes UG-22 (f) Wind reactions: No UG-22 (f) Seismic reactions: No Note: UG-22 (b),(c) and (f) loads only considered when supports are present.

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Thickness Summary

Thickness Summary

Component Identifier Top Head Straight Flange on Top Head Cylinder #1 Diameter Length Nominal t Design t Joint (in) (in) (in) (in) E 0.1870* 0.1870 0.1875 0.1870 0.1870* 0.1054 0.1368 0.1368 0.1368 0.1054

Material

Load

SA-516 70 36.00 OD 9.09 SA-516 70 36.00 OD 2.00 SA-516 70 36.00 OD 44.00

0.8500 Internal 0.8500 External 0.7000 External 0.8500 External 0.8500 Internal

Straight Flange on Bottom Head SA-516 70 36.00 OD 2.00 Bottom Head SA-516 70 36.00 OD 9.09

Nominal t: Vessel wall nominal thickness Design t: Joint E: * Load internal: external: Wind: Seismic: Circumferential stress due to internal pressure governs External pressure governs Combined longitudinal stress of pressure + weight + wind governs Combined longitudinal stress of pressure + weight + seismic governs Required vessel thickness due to governing loading + corrosion Longitudinal seam joint efficiency Head minimum thickness after forming

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Weight Summary

Weight Summary Weight ( lb) Contributed by Vessel Elements Component Metal Metal Insulation & Piping Operating Test Lining New* Corroded* Supports + Liquid Liquid Liquid Top Head Cylinder #1 90.30 90.30 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 285.62 1,586.39 285.62 0.00 2,157.63

260.40 260.40 90.30 37.36

Bottom Head 90.30 Legs TOTAL: 37.36

478.36 478.36

* Shells with attached nozzles have weight reduced by material cut out for opening. Weight ( lb) Contributed by Attachments Component Body Flanges Nozzles & Flanges Packed Ladders & Trays & Beds Platforms Supports 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 Rings & Clips 0.00 0.00 0.00 0.00 0.00 Vertical Loads 0.00 0.00 0.00 0.00 0.00

New Corroded New Corroded Top Head Cylinder #1 0.00 0.00 0.00 0.00 0.00 0.00

43.00 43.00 0.00 0.00 0.00 0.00

Bottom Head 0.00 0.00 Legs TOTAL: 0.00 0.00 0.00 0.00

43.00 43.00

Vessel operating weight, Corroded: 521 lb Vessel operating weight, New: 521 lb Vessel empty weight, Corroded: 521 lb Vessel empty weight, New: 521 lb Vessel test weight, New: 2,679 lb Vessel center of gravity location (from datum) Vessel Lift Weight, New: 521 lb Center of Gravity: 20.19"

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Weight Summary

Vessel Capacity Vessel Capacity** (New): 258 US gal Vessel Capacity** (Corroded): 258 US gal **The vessel capacity does not include volume of nozzle, piping or other attachments.

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Hydrostatic Test

Hydrostatic Test

Shop test pressure determination for Chamber bounded by Bottom Head and Top Head based on MAWP per UG-99(b) Shop hydrostatic test gauge pressure is 130.000 psi at 70.00 °F (the chamber MAWP = 100.000 psi) The shop test is performed with the vessel in the horizontal position.

Identifier

Top Head (1)

Stress Allowable Local test Test liquid UG-99 UG-99 Stress pressure static head stress pressure during test test stress excessive? psi psi psi ratio factor psi

131.509 1.509 1.509 1.509 1.509 1.509 0.217 0.284 0.284 0.217 1.0000 1.0000 1.0000 1.0000 1.0000 1.0000 1.0000 1.0000 1.0000 1.30 1.30 1.30 1.30 1.30 1.30 1.30 1.30 1.30 11,274 12,593 12,559 12,593 11,274 17,887 17,896 17,896 27,307 34,200 34,200 34,200 34,200 34,200 47,250 47,250 47,250 47,250 No No No No No No No No No

Straight Flange on Top 131.509 Head Cylinder #1 Straight Flange on Bottom Head Bottom Head Nozzle #1 (N1) Nozzle #2 (N2) Nozzle #3 (N3) Nozzle #4 (N4) 131.509 131.509 131.509 130.217 130.284 130.284 130.217

Notes: (1) Top Head 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 topmost flange. The field test condition has not been investigated for the Chamber bounded by Bottom Head and Top Head. The test temperature of 70.00 °F is warmer than the minimum recommended temperature of -25.00 °F so the brittle fracture provision of UG-99(h) has been met.

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Hydrostatic Test

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Vacuum Summary

Vacuum Summary

Elevation Length Le above Datum (in) (in) 55.09 48.97 46.00 44.00 44.00 0.00 0.00 -2.00 N/A N/A 53.94 53.94 53.94 53.94 53.94 53.94 N/A N/A

Component Top Head Straight Flange on Top Head Top Straight Flange on Top Head Bottom Cylinder #1 Top Cylinder #1 Bottom Straight Flange on Bottom Head Top

Line of Support 1/3 depth of Top Head -

Straight Flange on Bottom Head Bottom Bottom Head

1/3 depth of Bottom Head -4.97 -11.09

Note For main components, the listed value of 'Le' is the largest unsupported length for the component.

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Cylinder #1

Cylinder #1 ASME Section VIII Division 1, 2001 Edition, A03 Addenda Component: Cylinder Material specification: SA-516 70 (ASME II-D p. 14, ln. 31) Material impact test exemption temperature from Fig UCS-66 Curve B = -20 °F Fig UCS-66.1 MDMT reduction = 48.7 °F, (coincident ratio = 0.5470086) Rated MDMT is governed by UCS-66(b)(2) UCS-66 governing thickness = 0.1875 in Internal design pressure: P = 100 psi @ 150°F External design pressure: Pe = 15 psi @ 150°F Static liquid head: Pth=1.5093 psi(SG=1.0000, Hs=41.8125", Horizontal test head) Corrosion allowance: Design MDMT = -20.00°F Rated MDMT = -55.00°F Inner C = 0.0000" Outer C = 0.0000" No impact test performed Material is not normalized Material is not produced to Fine Grain Practice PWHT is not performed

Radiography:

Longitudinal joint None UW-11(c) Type 1 Top circumferential joint None UW-11(c) Type 1 Bottom circumferential joint - None UW-11(c) Type 1 corr = 262.6787 lb corr = 189.8630 gal

Estimated weight: New = 262.6787 lb Capacity: New = 189.8630 gal OD = 36.0000" Length Lc = 44.0000" t = 0.1875"

Design thickness, (at 150.00°F) Appendix 1-1 t = = P*Ro/(S*E + 0.40*P) + Corrosion 100.0000*18.0000/(20000.0000*0.70 + 0.40*100.0000) + 0.0000

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Cylinder #1

=

0.1283"

Maximum allowable working pressure, (at 150.00°F) Appendix 1-1 P = = = S*E*t/(Ro - 0.40*t) - Ps 20000.0000*0.70*0.1875 / (18.0000 - 0.40*0.1875) - 0.0000 146.4435 psi

Maximum allowable pressure, (at 70.00°F) Appendix 1-1 P = = = S*E*t/(Ro - 0.40*t) 20000.0000*0.70*0.1875 / (18.0000 - 0.40*0.1875) 146.4435 psi

External Pressure, (Corroded & at 150.00°F) UG-28(c) L/Do = 53.9377/36.0000 = 1.4983 Do/t = 36.0000/0.136839 = 263.0834 From table G: A = 0.000206 From table CS-2: B = 2959.6812 Pa = 4*B/(3*(Do/t)) = 4*2959.6812/(3*(36.0000/0.136839)) = 15.0000 psi Design thickness for external pressure Pa = 15.0000 psi = t + Corrosion = 0.136839 + 0.0000 = 0.1368" Maximum Allowable External Pressure, (Corroded & at 150.00°F) UG-28(c) L/Do = 53.9377/36.0000 = 1.4983 Do/t = 36.0000/0.1875 = 192.0000 From table G: A = 0.000334 From table CS-2: B = 4799.8105 Pa = 4*B/(3*(Do/t)) = 4*4799.8105/(3*(36.0000/0.1875))

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Cylinder #1

= 33.3320 psi % Extreme fiber elongation - UCS-79(d) = (50 * t / Rf) * (1 - Rf / Ro) = (50 * 0.1875 / 17.9063) * (1 - 17.9063 / ) = 0.5236 % External Pressure + Weight Check (Bergman, ASME paper 54-A-104) Pv = W / (2**Rm) + M / (*Rm2) = 390.01 / (2**17.9063) + 1003.47 / (*17.90632) = 4.4627 lb/in = Pv / (Pe*Do) = 4.462692 / (15.0000*36.0000) = 0.0083 n m =5 = 1.23 / (L/Do)2 = 1.23 / (53.937668/36.0000)2 = 0.5479 Ratio Pe = (n2 - 1 + m + m*) / (n2 - 1 + m) = (52 - 1 + 0.547931 + 0.547931*0.008264) / (52 - 1 + 0.547931) = 1.0002 Ratio Pe * Pe MAEP design cylinder thickness is satisfactory. External Pressure + Weight Check at Bottom Seam (Bergman, ASME paper 54-A-104) Pv = W / (2**Rm) + M / (*Rm2) = 390.01 / (2**17.9063) + 0.00 / (*17.90632) = 3.4665 lb/in = Pv / (Pe*Do) = 3.466493 / (15.0000*36.0000) = 0.0064 n =5

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Cylinder #1

m

= 1.23 / (L/Do)2 = 1.23 / (53.937668/36.0000)2 = 0.5479

Ratio Pe = (n2 - 1 + m + m*) / (n2 - 1 + m) = (52 - 1 + 0.547931 + 0.547931*0.006419) / (52 - 1 + 0.547931) = 1.0001 Ratio Pe * Pe MAEP design cylinder thickness is satisfactory. Design thickness = 0.1368" The governing condition is due to external pressure. The cylinder thickness of 0.1875" is adequate. Thickness Required Due to Pressure + External Loads

Allowable Stress Before UG-23 Stress Increase ( psi) St Operating, Hot & 100.00 Corroded Operating, Hot & 100.00 New Hot Shut Down, Corroded Hot Shut Down, New Empty, Corroded Empty, Sc top 20000.00 13265.59 150.00 0.0000 Bottom top 20000.00 13265.59 150.00 0.0000 Bottom top 0.00 20000.00 13265.59 150.00 0.0000 Bottom top 0.00 20000.00 13265.59 150.00 0.0000 Bottom top 0.00 20000.00 13265.59 0.00 0.0000 Bottom top Weight 0.0003 Weight 0.0002 0.0003 0.0003 Weight 0.0003 Weight 0.0002 0.0003 0.0003 Weight 0.0003 Weight 0.0002 0.0003 0.0003 Weight 0.0443 Weight 0.0002 0.0443 0.0003 Weight 0.0443 Weight 0.0444 0.0443 0.0443 Req'd Req'd Thk Thk Due to Due to Compression Tension (in) (in) 0.0443

Condition

Pressure P ( psi)

Temperature Corrosion Location (°F) C (in)

Load

Weight 0.0444

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Cylinder #1

New

0.00

20000.00 13265.59 0.00

0.0000

Bottom top

Weight 0.0003 Weight 0.0103 Weight 0.0103

0.0003 0.0104 0.0103

Vacuum Hot Shut Down, Corroded, Weight & Eccentric Moments Only

-15.00

20000.00 13265.59 150.00

0.0000 Bottom

top 0.00 20000.00 13265.59 150.00 0.0000 Bottom

Weight 0.0000

0.0001

Weight 0.0000

0.0000

Allowable Compressive Stress, Hot and Corroded- ScHC, (table CS-2) A = 0.125 / (Ro / t) = 0.125 / (18.0000 / 0.1875) = 0.001302 = 13265.5928 psi = 20000.0000 / 1.0000 = 20000.0000 psi

B S

ScHC = 13265.5928 psi Allowable Compressive Stress, Hot and New- ScHN ScHN = ScHC = 13265.5928 psi Allowable Compressive Stress, Cold and New- ScCN, (table CS-2) A = 0.125 / (Ro / t) = 0.125 / (18.0000 / 0.1875) = 0.001302 = 13265.5928 psi = 20000.0000 / 1.0000 = 20000.0000 psi

B S

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Cylinder #1

ScCN = 13265.5928 psi Allowable Compressive Stress, Cold and Corroded- ScCC ScCC = ScCN = 13265.5928 psi Allowable Compressive Stress, Vacuum and Corroded- ScVC, (table CS-2) A = 0.125 / (Ro / t) = 0.125 / (18.0000 / 0.1875) = 0.001302 = 13265.5928 psi = 20000.0000 / 1.0000 = 20000.0000 psi

B S

ScVC = 13265.5928 psi Operating, Hot & Corroded, Above Support Point tp = P*R/(2*St*Ks*Ec + 0.40*|P|) = 100.0000*17.8125/(2*20000.0000*1.0000*1.00 + 0.40*|100.0000|) = 0.0445" tm = M/(*Rm2*St*Ks*Ec) = 1003.47/(*17.90632*20000.0000*1.0000*1.00) = 0.0000" tw = W/(2**Rm*St*Ks*Ec) = 390.01/(2**17.9063*20000.0000*1.0000*1.00) = 0.0002" tt = tp + tm - tw = 0.044487 + 0.000050 - (0.000173) = 0.0444" tc = |tmc + twc - tpc| = |0.000050 + (0.000173) - (0.044487)|

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(Pressure)

(bending)

(Weight)

(total required, tensile)

(total, net tensile)

Cylinder #1

= 0.0443" Maximum allowable working pressure, Longitudinal Stress P = 2*St*Ks*Ec*(t-tm+tw) / (R - 0.40*(t-tm+tw)) 2*20000.0000*1.0000*1.00*(0.1875-0.000050+(0.000173)) / (17.8125 - 0.40*(0.18750.000050+(0.000173))) = 423.1127 psi = Operating, Hot & New, Above Support Point tp = P*R/(2*St*Ks*Ec + 0.40*|P|) = 100.0000*17.8125/(2*20000.0000*1.0000*1.00 + 0.40*|100.0000|) = 0.0445" tm = M/(*Rm2*St*Ks*Ec) = 1003.47/(*17.90632*20000.0000*1.0000*1.00) = 0.0000" tw = W/(2**Rm*St*Ks*Ec) = 390.01/(2**17.9063*20000.0000*1.0000*1.00) = 0.0002" tt = tp + tm - tw = 0.044487 + 0.000050 - (0.000173) = 0.0444" tc = |tmc + twc - tpc| = |0.000050 + (0.000173) - (0.044487)| = 0.0443" Maximum allowable working pressure, Longitudinal Stress P = 2*St*Ks*Ec*(t-tm+tw) / (R - 0.40*(t-tm+tw)) 2*20000.0000*1.0000*1.00*(0.1875-0.000050+(0.000173)) / (17.8125 - 0.40*(0.18750.000050+(0.000173))) = 423.1127 psi = (total, net tensile) (total required, tensile) (Weight) (bending) (Pressure)

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Cylinder #1

Hot Shut Down, Corroded, Above Support Point tp = 0.0000" tm = M/(*Rm2*Sc*Ks) = 1003.47/(*17.90632*13265.5928*1.0000) = 0.0001" tw = W/(2**Rm*Sc*Ks) = 390.01/(2**17.9063*13265.5928*1.0000) = 0.0003" tt = |tp + tm - tw| = |0.000000 + 0.000075 - (0.000261)| = 0.0002" tc = tmc + twc - tpc = 0.000075 + (0.000261) - (0.000000) = 0.0003" Hot Shut Down, New, Above Support Point tp = 0.0000" tm = M/(*Rm2*Sc*Ks) = 1003.47/(*17.90632*13265.5928*1.0000) = 0.0001" tw = W/(2**Rm*Sc*Ks) = 390.01/(2**17.9063*13265.5928*1.0000) = 0.0003" tt = |tp + tm - tw| = |0.000000 + 0.000075 - (0.000261)| = 0.0002" tc = tmc + twc - tpc = 0.000075 + (0.000261) - (0.000000) = 0.0003" Empty, Corroded, Above Support Point

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(Pressure) (bending)

(Weight)

(total, net compressive)

(total required, compressive)

(Pressure) (bending)

(Weight)

(total, net compressive)

(total required, compressive)

Cylinder #1

tp = 0.0000" tm = M/(*Rm2*Sc*Ks) = 1003.47/(*17.90632*13265.5928*1.0000) = 0.0001" tw = W/(2**Rm*Sc*Ks) = 390.01/(2**17.9063*13265.5928*1.0000) = 0.0003" tt = |tp + tm - tw| = |0.000000 + 0.000075 - (0.000261)| = 0.0002" tc = tmc + twc - tpc = 0.000075 + (0.000261) - (0.000000) = 0.0003" Empty, New, Above Support Point tp = 0.0000" tm = M/(*Rm2*Sc*Ks) = 1003.47/(*17.90632*13265.5928*1.0000) = 0.0001" tw = W/(2**Rm*Sc*Ks) = 390.01/(2**17.9063*13265.5928*1.0000) = 0.0003" tt = |tp + tm - tw| = |0.000000 + 0.000075 - (0.000261)| = 0.0002" tc = tmc + twc - tpc = 0.000075 + (0.000261) - (0.000000) = 0.0003" Vacuum, Above Support Point

(Pressure) (bending)

(Weight)

(total, net compressive)

(total required, compressive)

(Pressure) (bending)

(Weight)

(total, net compressive)

(total required, compressive)

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Cylinder #1

tp = P*R/(2*Sc*Ks + 0.40*|P|) = -15.0000*17.8125/(2*13265.5928*1.0000 + 0.40*|15.0000|) = -0.0101" tm = M/(*Rm2*Sc*Ks) = 1003.47/(*17.90632*13265.5928*1.0000) = 0.0001" tw = W/(2**Rm*Sc*Ks) = 390.01/(2**17.9063*13265.5928*1.0000) = 0.0003" tt = |tp + tm - tw| = |-0.010068 + 0.000075 - (0.000261)| = 0.0103" tc = tmc + twc - tpc = 0.000075 + (0.000261) - (-0.010068) = 0.0104"

(Pressure)

(bending)

(Weight)

(total, net compressive)

(total required, compressive)

Hot Shut Down, Corroded, Weight & Eccentric Moments Only, Above Support Point tp = 0.0000" tm = M/(*Rm2*St*Ks*Ec) = 1003.47/(*17.90632*20000.0000*1.0000*1.00) = 0.0000" tw = W/(2**Rm*St*Ks*Ec) = 0.00/(2**17.9063*20000.0000*1.0000*1.00) = 0.0000" tt = t p + tm - t w = 0.000000 + 0.000050 - (0.000000) = 0.0000" tmc = M/(*Rm2*Sc*Ks) = 1003.47/(*17.90632*13265.5928*1.0000) = 0.0001" tc = tmc + twc - tpc (total required, compressive) (bending) (total required, tensile) (Weight) (Pressure) (bending)

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Cylinder #1

= 0.000075 + (0.000000) - (0.000000) = 0.0001" Operating, Hot & Corroded, Below Support Point tp = P*R/(2*St*Ks*Ec + 0.40*|P|) = 100.0000*17.8125/(2*20000.0000*1.0000*1.00 + 0.40*|100.0000|) = 0.0445" tm = M/(*Rm2*St*Ks*Ec) = 0.00/(*17.90632*20000.0000*1.0000*1.00) = 0.0000" tw = W/(2**Rm*St*Ks*Ec) = 390.01/(2**17.9063*20000.0000*1.0000*1.00) = 0.0002" tt = tp + tm - tw = 0.044487 + 0.000000 - (0.000173) = 0.0443" tc = |tmc + twc - tpc| = |0.000000 + (0.000173) - (0.044487)| = 0.0443" Maximum allowable working pressure, Longitudinal Stress P = 2*St*Ks*Ec*(t-tm+tw) / (R - 0.40*(t-tm+tw)) 2*20000.0000*1.0000*1.00*(0.1875-0.000000+(0.000173)) / (17.8125 - 0.40*(0.18750.000000+(0.000173))) = 423.2255 psi = Operating, Hot & New, Below Support Point tp = P*R/(2*St*Ks*Ec + 0.40*|P|) = 100.0000*17.8125/(2*20000.0000*1.0000*1.00 + 0.40*|100.0000|) = 0.0445" (Pressure) (total, net tensile) (total required, tensile) (Weight) (bending) (Pressure)

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Cylinder #1

tm = M/(*Rm2*St*Ks*Ec) = 0.00/(*17.90632*20000.0000*1.0000*1.00) = 0.0000" tw = W/(2**Rm*St*Ks*Ec) = 390.01/(2**17.9063*20000.0000*1.0000*1.00) = 0.0002" tt = tp + tm - tw = 0.044487 + 0.000000 - (0.000173) = 0.0443" tc = |tmc + twc - tpc| = |0.000000 + (0.000173) - (0.044487)| = 0.0443" Maximum allowable working pressure, Longitudinal Stress P = 2*St*Ks*Ec*(t-tm+tw) / (R - 0.40*(t-tm+tw))

(bending)

(Weight)

(total required, tensile)

(total, net tensile)

2*20000.0000*1.0000*1.00*(0.1875-0.000000+(0.000173)) / (17.8125 - 0.40*(0.18750.000000+(0.000173))) = 423.2255 psi = Hot Shut Down, Corroded, Below Support Point tp = 0.0000" tm = M/(*Rm2*Sc*Ks) = 0.00/(*17.90632*13265.5928*1.0000) = 0.0000" tw = W/(2**Rm*Sc*Ks) = 390.01/(2**17.9063*13265.5928*1.0000) = 0.0003" tt = |tp + tm - tw| = |0.000000 + 0.000000 - (0.000261)| = 0.0003" tc = tmc + twc - tpc (total required, compressive) (total, net compressive) (Weight) (Pressure) (bending)

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Cylinder #1

= 0.000000 + (0.000261) - (0.000000) = 0.0003" Hot Shut Down, New, Below Support Point tp = 0.0000" tm = M/(*Rm2*Sc*Ks) = 0.00/(*17.90632*13265.5928*1.0000) = 0.0000" tw = W/(2**Rm*Sc*Ks) = 390.01/(2**17.9063*13265.5928*1.0000) = 0.0003" tt = |tp + tm - tw| = |0.000000 + 0.000000 - (0.000261)| = 0.0003" tc = tmc + twc - tpc = 0.000000 + (0.000261) - (0.000000) = 0.0003" Empty, Corroded, Below Support Point tp = 0.0000" tm = M/(*Rm2*Sc*Ks) = 0.00/(*17.90632*13265.5928*1.0000) = 0.0000" tw = W/(2**Rm*Sc*Ks) = 390.01/(2**17.9063*13265.5928*1.0000) = 0.0003" tt = |tp + tm - tw| = |0.000000 + 0.000000 - (0.000261)| = 0.0003" tc = tmc + twc - tpc (total required, compressive) (total, net compressive) (Weight) (Pressure) (bending) (total required, compressive) (total, net compressive) (Weight) (Pressure) (bending)

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Cylinder #1

= 0.000000 + (0.000261) - (0.000000) = 0.0003" Empty, New, Below Support Point tp = 0.0000" tm = M/(*Rm2*Sc*Ks) = 0.00/(*17.90632*13265.5928*1.0000) = 0.0000" tw = W/(2**Rm*Sc*Ks) = 390.01/(2**17.9063*13265.5928*1.0000) = 0.0003" tt = |tp + tm - tw| = |0.000000 + 0.000000 - (0.000261)| = 0.0003" tc = tmc + twc - tpc = 0.000000 + (0.000261) - (0.000000) = 0.0003" Vacuum, Below Support Point tp = P*R/(2*Sc*Ks + 0.40*|P|) = -15.0000*17.8125/(2*13265.5928*1.0000 + 0.40*|15.0000|) = -0.0101" tm = M/(*Rm2*Sc*Ks) = 0.00/(*17.90632*13265.5928*1.0000) = 0.0000" tw = W/(2**Rm*Sc*Ks) = 390.01/(2**17.9063*13265.5928*1.0000) = 0.0003" tt = |tp + tm - tw| = |-0.010068 + 0.000000 - (0.000261)| (total, net compressive) (Weight) (bending) (Pressure) (total required, compressive) (total, net compressive) (Weight) (Pressure) (bending)

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Cylinder #1

= 0.0103" tc = tmc + twc - tpc = 0.000000 + (0.000261) - (-0.010068) = 0.0103" Hot Shut Down, Corroded, Weight & Eccentric Moments Only, Below Support Point tp = 0.0000" tm = M/(*Rm2*St*Ks*Ec) = 0.00/(*17.90632*20000.0000*1.0000*1.00) = 0.0000" tw = W/(2**Rm*St*Ks*Ec) = 0.00/(2**17.9063*20000.0000*1.0000*1.00) = 0.0000" tt = tp + tm - tw = 0.000000 + 0.000000 - (0.000000) = 0.0000" tc = tmc + twc - tpc = 0.000000 + (0.000000) - (0.000000) = 0.0000" (total required, compressive) (total required, tensile) (Weight) (Pressure) (bending) (total required, compressive)

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Top Head

Top Head ASME Section VIII, Division 1, 2001 Edition, A03 Addenda Component: Material Specification: Straight Flange governs MDMT Internal design pressure: P = 100 psi @ 150 °F External design pressure: Pe = 15 psi @ 150 °F Static liquid head: Ps= 0 psi (SG=1, Hs=0" Operating head) Pth= 1.5093 psi (SG=1, Hs=41.813" Horizontal test head) Corrosion allowance: Design MDMT = -20°F Rated MDMT = -55°F Inner C = 0" Outer C = 0" Ellipsoidal Head SA-516 70 (ASME II-D p.14, ln. 31)

No impact test performed Material is not normalized Material is not produced to fine grain practice PWHT is not performed Do not Optimize MDMT / Find MAWP Seamless No RT None UW-11(c) Type 1 corr = 90.3 lb corr = 34.3 US gal

Radiography:

Category A joints Head to shell seam -

Estimated weight*: new = 90.3 lb Capacity*: new = 34.3 US gal * includes straight flange Outer diameter Minimum head thickness Head ratio D/2h Head ratio D/2h Straight flange length Lsf Nominal straight flange thickness tsf Insulation thk*: 0" = = = = = = 36" 0.187" 2 (new) 2 (corroded) 2" 0.187"

density: 0 lb/ft3

weight: 0 lb

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Top Head

Insulation support ring 0" spacing: Lining/ref thk*: 0" * includes straight flange if applicable Results Summary

individual weight: 0 lb total weight: 0 lb density: 0 lb/ft3 weight: 0 lb

The governing condition is internal pressure. Minimum thickness per UG-16 Design thickness due to internal pressure (t) Design thickness due to external pressure (te) Maximum allowable working pressure (MAWP) Maximum allowable pressure (MAP) Maximum allowable external pressure (MAEP)

= = = = = =

0.0625" + 0" = 0.0625" 0.1054" 0.0927" 178.278 psi 178.278 psi 61.3292 psi

K (Corroded) K = = = (1/6)*[2 + (D / (2*h))2] (1/6)*[2 + (35.626 / (2*8.9065))2] 1

K (New) K = = = (1/6)*[2 + (D / (2*h))2] (1/6)*[2 + (35.626 / (2*8.9065))2] 1

Design thickness for internal pressure, (Corroded at 150 °F) Appendix 1-4(c) t = = = P*Do*K / (2*S*E + 2*P*(K - 0.1)) + Corrosion 100*36*1 / (2*20000*0.85 + 2*100*(1 - 0.1)) + 0 0.1053"

The head internal pressure design thickness is 0.1054". Maximum allowable working pressure, (Corroded at 150 °F) Appendix 1-4(c) P = = 2*S*E*t / (K*Do - 2*t*(K - 0.1)) - Ps 2*20000*0.85*0.187 / (1*36 - 2*0.187*(1 - 0.1)) - 0

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Top Head

=

178.278 psi

The maximum allowable working pressure (MAWP) is 178.278 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*20000*0.85*0.187 / (1*36 - 2*0.187*(1 - 0.1)) - 0 178.278 psi

The maximum allowable pressure (MAP) is 178.278 psi. Design thickness for external pressure, (Corroded at 150 °F) UG-33(d) Equivalent outside spherical radius (Ro) Ko*Do Ro = = 0.8907 * 36 = 32.0669 in A = = = 0.125 / (Ro/t) 0.125 / (32.0669/0.092617) 0.000361

From Table CS-2: B=5,193.4531 psi Pa = = = = B/(Ro/t) 5,193.453/(32.0669/0.092617) 15 psi 0.0926" + Corrosion = 0.0926" + 0" = 0.0926"

t

Check the external pressure per UG-33(a)(1) Appendix 1-4(c) t = = = 1.67*Pe*Do*K / (2*S*E + 2*1.67*Pe*(K - 0.1)) + Corrosion 1.67*15*36*1 / (2*20000*1 + 2*1.67*15*(1 - 0.1)) + 0 0.0225"

The head external pressure design thickness (te) is 0.092617". Maximum Allowable External Pressure, (Corroded at 150 °F) UG-33(d)

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Top Head

Equivalent outside spherical radius (Ro) Ko*Do Ro = = 0.8907 * 36 = 32.0669 in A = = = 0.125 / (Ro/t) 0.125 / (32.0669/0.187) 0.000729

From Table CS-2: B=10,516.7607 psi Pa = = = B/(Ro/t) 10,516.76/(32.0669/0.187) 61.3292 psi

Check the Maximum External Pressure, UG-33(a)(1) Appendix 1-4(c) P = = = 2*S*E*t / ((K*Do - 2*t*(K - 0.1))*1.67) - Ps2 2*20000*1*0.187 / ((1*36 - 2*0.187*(1 - 0.1))*1.67) - 0 125.5921 psi

The maximum allowable external pressure (MAEP) is 61.3292 psi. % Extreme fiber elongation - UCS-79(d) = = = (75*t / Rf)*(1 - Rf / Ro) (75*0.187 / 6.1499)*(1 - 6.1499 / ) 2.2805%

The extreme fiber elongation does not exceed 5%.

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Straight Flange on Top Head

Straight Flange on Top Head ASME Section VIII Division 1, 2001 Edition, A03 Addenda Component: Straight Flange Material specification: SA-516 70 (ASME II-D p. 14, ln. 31) Material impact test exemption temperature from Fig UCS-66 Curve B = -20 °F Fig UCS-66.1 MDMT reduction = 65.5 °F, (coincident ratio = 0.4801537) Rated MDMT is governed by UCS-66(b)(2) UCS-66 governing thickness = 0.187 in Internal design pressure: P = 100 psi @ 150°F External design pressure: Pe = 15 psi @ 150°F Static liquid head: Pth=1.5093 psi(SG=1.0000, Hs=41.8130", Horizontal test head) Corrosion allowance: Design MDMT = -20.00°F Rated MDMT = -55.00°F Inner C = 0.0000" Outer C = 0.0000" No impact test performed Material is not normalized Material is not produced to Fine Grain Practice PWHT is not performed Seamless No RT None UW-11(c) Type 1

Radiography:

Longitudinal joint Circumferential joint -

Estimated weight: New = 11.9083 lb Capacity: New = 8.6306 gal OD = 36.0000" Length Lc = 2.0000" t = 0.1870"

corr = 11.9083 lb corr = 8.6306 gal

Design thickness, (at 150.00°F) Appendix 1-1 t = = = P*Ro/(S*E + 0.40*P) + Corrosion 100.0000*18.0000/(20000.0000*0.85 + 0.40*100.0000) + 0.0000 0.1057"

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Straight Flange on Top Head

Maximum allowable working pressure, (at 150.00°F) Appendix 1-1 P = = = S*E*t/(Ro - 0.40*t) - Ps 20000.0000*0.85*0.1870 / (18.0000 - 0.40*0.1870) - 0.0000 177.3481 psi

Maximum allowable pressure, (at 70.00°F) Appendix 1-1 P = = = S*E*t/(Ro - 0.40*t) 20000.0000*0.85*0.1870 / (18.0000 - 0.40*0.1870) 177.3481 psi

External Pressure, (Corroded & at 150.00°F) UG-28(c) L/Do = 53.9377/36.0000 = 1.4983 Do/t = 36.0000/0.136839 = 263.0834 From table G: A = 0.000206 From table CS-2: B = 2959.6812 Pa = 4*B/(3*(Do/t)) = 4*2959.6812/(3*(36.0000/0.136839)) = 15.0000 psi Design thickness for external pressure Pa = 15.0000 psi = t + Corrosion = 0.136839 + 0.0000 = 0.1368" Maximum Allowable External Pressure, (Corroded & at 150.00°F) UG-28(c) L/Do = 53.9377/36.0000 = 1.4983 Do/t = 36.0000/0.1870 = 192.5134 From table G: A = 0.000332 From table CS-2: B = 4775.1362 Pa = 4*B/(3*(Do/t)) = 4*4775.1362/(3*(36.0000/0.1870))

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Straight Flange on Top Head

= 33.0722 psi % Extreme fiber elongation - UCS-79(d) = (50 * t / Rf) * (1 - Rf / Ro) = (50 * 0.1870 / 17.9065) * (1 - 17.9065 / ) = 0.5222 % Design thickness = 0.1368" The governing condition is due to external pressure. The cylinder thickness of 0.1870" is adequate. Thickness Required Due to Pressure + External Loads

Allowable Stress Before UG-23 Stress Increase Pressure ( psi) P ( psi) St Operating, Hot & Corroded Operating, Hot & New Hot Shut Down, Corroded Hot Shut Down, New Empty, Corroded Empty, New Vacuum Sc Req'd Thk Due to Tension (in)

Condition

Temperature (°F)

Corrosion C (in)

Load

Req'd Thk Due to Compression (in)

100.00

20000.00 13255.46 150.00

0.0000

Weight 0.0635

0.0635

100.00

20000.00 13255.46 150.00

0.0000

Weight 0.0635

0.0635

0.00

20000.00 13255.46 150.00

0.0000

Weight 0.0001

0.0001

0.00

20000.00 13255.46 150.00

0.0000

Weight 0.0001

0.0001

0.00 0.00 -15.00

20000.00 13255.46 0.00 20000.00 13255.46 0.00 20000.00 13255.46 150.00

0.0000 0.0000 0.0000

Weight 0.0001 Weight 0.0001 Weight 0.0101

0.0001 0.0001 0.0101

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Straight Flange on Top Head

Hot Shut Down, Corroded, Weight & Eccentric Moments Only

0.00

20000.00 13255.46 150.00

0.0000

Weight 0.0001

0.0001

Allowable Compressive Stress, Hot and Corroded- ScHC, (table CS-2) A = 0.125 / (Ro / t) = 0.125 / (18.0000 / 0.1870) = 0.001299 = 13255.4551 psi = 20000.0000 / 1.0000 = 20000.0000 psi

B S

ScHC = 13255.4551 psi Allowable Compressive Stress, Hot and New- ScHN ScHN = ScHC = 13255.4551 psi Allowable Compressive Stress, Cold and New- ScCN, (table CS-2) A = 0.125 / (Ro / t) = 0.125 / (18.0000 / 0.1870) = 0.001299 = 13255.4551 psi = 20000.0000 / 1.0000 = 20000.0000 psi

B S

ScCN = 13255.4551 psi

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Straight Flange on Top Head

Allowable Compressive Stress, Cold and Corroded- ScCC ScCC = ScCN = 13255.4551 psi Allowable Compressive Stress, Vacuum and Corroded- ScVC, (table CS-2) A = 0.125 / (Ro / t) = 0.125 / (18.0000 / 0.1870) = 0.001299 = 13255.4551 psi = 20000.0000 / 1.0000 = 20000.0000 psi

B S

ScVC = 13255.4551 psi Operating, Hot & Corroded, Bottom Seam tp = P*R/(2*St*Ks*Ec + 0.40*|P|) = 100.0000*17.8130/(2*20000.0000*1.0000*0.70 + 0.40*|100.0000|) = 0.0635" tm = M/(*Rm2*St*Ks*Ec) = 0.00/(*17.90652*20000.0000*1.0000*0.70) = 0.0000" tw = W/(2**Rm*St*Ks*Ec) = 90.30/(2**17.9065*20000.0000*1.0000*0.70) = 0.0001" tt = tp + tm - tw = 0.063527 + 0.000000 - (0.000057) = 0.0635" tc = |tmc + twc - tpc| = |0.000000 + (0.000057) - (0.063527)| = 0.0635" (total, net tensile) (total required, tensile) (Weight) (bending) (Pressure)

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Straight Flange on Top Head

Maximum allowable working pressure, Longitudinal Stress P = 2*St*Ks*Ec*(t-tm+tw) / (R - 0.40*(t-tm+tw)) 2*20000.0000*1.0000*0.70*(0.1870-0.000000+(0.000057)) / (17.8130 - 0.40*(0.18700.000000+(0.000057))) = 295.2730 psi = Operating, Hot & New, Bottom Seam tp = P*R/(2*St*Ks*Ec + 0.40*|P|) = 100.0000*17.8130/(2*20000.0000*1.0000*0.70 + 0.40*|100.0000|) = 0.0635" tm = M/(*Rm2*St*Ks*Ec) = 0.00/(*17.90652*20000.0000*1.0000*0.70) = 0.0000" tw = W/(2**Rm*St*Ks*Ec) = 90.30/(2**17.9065*20000.0000*1.0000*0.70) = 0.0001" tt = tp + tm - tw = 0.063527 + 0.000000 - (0.000057) = 0.0635" tc = |tmc + twc - tpc| = |0.000000 + (0.000057) - (0.063527)| = 0.0635" Maximum allowable working pressure, Longitudinal Stress P = 2*St*Ks*Ec*(t-tm+tw) / (R - 0.40*(t-tm+tw)) 2*20000.0000*1.0000*0.70*(0.1870-0.000000+(0.000057)) / (17.8130 - 0.40*(0.18700.000000+(0.000057))) = 295.2730 psi = Hot Shut Down, Corroded, Bottom Seam (total, net tensile) (total required, tensile) (Weight) (bending) (Pressure)

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Straight Flange on Top Head

tp = 0.0000" tm = M/(*Rm2*Sc*Ks) = 0.00/(*17.90652*13255.4551*1.0000) = 0.0000" tw = W/(2**Rm*Sc*Ks) = 90.30/(2**17.9065*13255.4551*1.0000) = 0.0001" tt = |tp + tm - tw| = |0.000000 + 0.000000 - (0.000061)| = 0.0001" tc = tmc + twc - tpc = 0.000000 + (0.000061) - (0.000000) = 0.0001" Hot Shut Down, New, Bottom Seam tp = 0.0000" tm = M/(*Rm2*Sc*Ks) = 0.00/(*17.90652*13255.4551*1.0000) = 0.0000" tw = W/(2**Rm*Sc*Ks) = 90.30/(2**17.9065*13255.4551*1.0000) = 0.0001" tt = |tp + tm - tw| = |0.000000 + 0.000000 - (0.000061)| = 0.0001" tc = tmc + twc - tpc = 0.000000 + (0.000061) - (0.000000) = 0.0001" Empty, Corroded, Bottom Seam

(Pressure) (bending)

(Weight)

(total, net compressive)

(total required, compressive)

(Pressure) (bending)

(Weight)

(total, net compressive)

(total required, compressive)

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Straight Flange on Top Head

tp = 0.0000" tm = M/(*Rm2*Sc*Ks) = 0.00/(*17.90652*13255.4551*1.0000) = 0.0000" tw = W/(2**Rm*Sc*Ks) = 90.30/(2**17.9065*13255.4551*1.0000) = 0.0001" tt = |tp + tm - tw| = |0.000000 + 0.000000 - (0.000061)| = 0.0001" tc = tmc + twc - tpc = 0.000000 + (0.000061) - (0.000000) = 0.0001" Empty, New, Bottom Seam tp = 0.0000" tm = M/(*Rm2*Sc*Ks) = 0.00/(*17.90652*13255.4551*1.0000) = 0.0000" tw = W/(2**Rm*Sc*Ks) = 90.30/(2**17.9065*13255.4551*1.0000) = 0.0001" tt = |tp + tm - tw| = |0.000000 + 0.000000 - (0.000061)| = 0.0001" tc = tmc + twc - tpc = 0.000000 + (0.000061) - (0.000000) = 0.0001" Vacuum, Bottom Seam

(Pressure) (bending)

(Weight)

(total, net compressive)

(total required, compressive)

(Pressure) (bending)

(Weight)

(total, net compressive)

(total required, compressive)

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Straight Flange on Top Head

tp = P*R/(2*Sc*Ks + 0.40*|P|) = -15.0000*17.8130/(2*13255.4551*1.0000 + 0.40*|15.0000|) = -0.0101" tm = M/(*Rm2*Sc*Ks) = 0.00/(*17.90652*13255.4551*1.0000) = 0.0000" tw = W/(2**Rm*Sc*Ks) = 90.30/(2**17.9065*13255.4551*1.0000) = 0.0001" tt = |tp + tm - tw| = |-0.010076 + 0.000000 - (0.000061)| = 0.0101" tc = tmc + twc - tpc = 0.000000 + (0.000061) - (-0.010076) = 0.0101"

(Pressure)

(bending)

(Weight)

(total, net compressive)

(total required, compressive)

Hot Shut Down, Corroded, Weight & Eccentric Moments Only, Bottom Seam tp = 0.0000" tm = M/(*Rm2*Sc*Ks) = 0.00/(*17.90652*13255.4551*1.0000) = 0.0000" tw = W/(2**Rm*Sc*Ks) = 90.30/(2**17.9065*13255.4551*1.0000) = 0.0001" tt = |tp + tm - tw| = |0.000000 + 0.000000 - (0.000061)| = 0.0001" tc = tmc + twc - tpc = 0.000000 + (0.000061) - (0.000000) = 0.0001" (total required, compressive) (total, net compressive) (Weight) (Pressure) (bending)

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Straight Flange on Bottom Head

Straight Flange on Bottom Head ASME Section VIII Division 1, 2001 Edition, A03 Addenda Component: Straight Flange Material specification: SA-516 70 (ASME II-D p. 14, ln. 31) Material impact test exemption temperature from Fig UCS-66 Curve B = -20 °F Fig UCS-66.1 MDMT reduction = 65.5 °F, (coincident ratio = 0.4801537) Rated MDMT is governed by UCS-66(b)(2) UCS-66 governing thickness = 0.187 in Internal design pressure: P = 100 psi @ 150°F External design pressure: Pe = 15 psi @ 150°F Static liquid head: Pth=1.5093 psi(SG=1.0000, Hs=41.8130", Horizontal test head) Corrosion allowance: Design MDMT = -20.00°F Rated MDMT = -55.00°F Inner C = 0.0000" Outer C = 0.0000" No impact test performed Material is not normalized Material is not produced to Fine Grain Practice PWHT is not performed Seamless No RT None UW-11(c) Type 1

Radiography:

Longitudinal joint Circumferential joint -

Estimated weight: New = 11.9083 lb Capacity: New = 8.6306 gal OD = 36.0000" Length Lc = 2.0000" t = 0.1870"

corr = 11.9083 lb corr = 8.6306 gal

Design thickness, (at 150.00°F) Appendix 1-1 t = = = P*Ro/(S*E + 0.40*P) + Corrosion 100.0000*18.0000/(20000.0000*0.85 + 0.40*100.0000) + 0.0000 0.1057"

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Straight Flange on Bottom Head

Maximum allowable working pressure, (at 150.00°F) Appendix 1-1 P = = = S*E*t/(Ro - 0.40*t) - Ps 20000.0000*0.85*0.1870 / (18.0000 - 0.40*0.1870) - 0.0000 177.3481 psi

Maximum allowable pressure, (at 70.00°F) Appendix 1-1 P = = = S*E*t/(Ro - 0.40*t) 20000.0000*0.85*0.1870 / (18.0000 - 0.40*0.1870) 177.3481 psi

External Pressure, (Corroded & at 150.00°F) UG-28(c) L/Do = 53.9377/36.0000 = 1.4983 Do/t = 36.0000/0.136839 = 263.0834 From table G: A = 0.000206 From table CS-2: B = 2959.6812 Pa = 4*B/(3*(Do/t)) = 4*2959.6812/(3*(36.0000/0.136839)) = 15.0000 psi Design thickness for external pressure Pa = 15.0000 psi = t + Corrosion = 0.136839 + 0.0000 = 0.1368" Maximum Allowable External Pressure, (Corroded & at 150.00°F) UG-28(c) L/Do = 53.9377/36.0000 = 1.4983 Do/t = 36.0000/0.1870 = 192.5134 From table G: A = 0.000332 From table CS-2: B = 4775.1362 Pa = 4*B/(3*(Do/t)) = 4*4775.1362/(3*(36.0000/0.1870))

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Straight Flange on Bottom Head

= 33.0722 psi % Extreme fiber elongation - UCS-79(d) = (50 * t / Rf) * (1 - Rf / Ro) = (50 * 0.1870 / 17.9065) * (1 - 17.9065 / ) = 0.5222 % Design thickness = 0.1368" The governing condition is due to external pressure. The cylinder thickness of 0.1870" is adequate. Thickness Required Due to Pressure + External Loads

Allowable Stress Before UG-23 Stress Increase Pressure ( psi) P ( psi) St Operating, Hot & Corroded Operating, Hot & New Hot Shut Down, Corroded Hot Shut Down, New Empty, Corroded Empty, New Vacuum Sc Req'd Thk Due to Tension (in)

Condition

Temperature (°F)

Corrosion C (in)

Load

Req'd Thk Due to Compression (in)

100.00

20000.00 13255.46 150.00

0.0000

Weight 0.0636

0.0636

100.00

20000.00 13255.46 150.00

0.0000

Weight 0.0636

0.0636

0.00

20000.00 13255.46 150.00

0.0000

Weight 0.0001

0.0001

0.00

20000.00 13255.46 150.00

0.0000

Weight 0.0001

0.0001

0.00 0.00 -15.00

20000.00 13255.46 0.00 20000.00 13255.46 0.00 20000.00 13255.46 150.00

0.0000 0.0000 0.0000

Weight 0.0001 Weight 0.0001 Weight 0.0100

0.0001 0.0001 0.0100

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Straight Flange on Bottom Head

Hot Shut Down, Corroded, Weight & Eccentric Moments Only

0.00

20000.00 13255.46 150.00

0.0000

Weight 0.0001

0.0001

Allowable Compressive Stress, Hot and Corroded- ScHC, (table CS-2) A = 0.125 / (Ro / t) = 0.125 / (18.0000 / 0.1870) = 0.001299 = 13255.4551 psi = 20000.0000 / 1.0000 = 20000.0000 psi

B S

ScHC = 13255.4551 psi Allowable Compressive Stress, Hot and New- ScHN ScHN = ScHC = 13255.4551 psi Allowable Compressive Stress, Cold and New- ScCN, (table CS-2) A = 0.125 / (Ro / t) = 0.125 / (18.0000 / 0.1870) = 0.001299 = 13255.4551 psi = 20000.0000 / 1.0000 = 20000.0000 psi

B S

ScCN = 13255.4551 psi

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Straight Flange on Bottom Head

Allowable Compressive Stress, Cold and Corroded- ScCC ScCC = ScCN = 13255.4551 psi Allowable Compressive Stress, Vacuum and Corroded- ScVC, (table CS-2) A = 0.125 / (Ro / t) = 0.125 / (18.0000 / 0.1870) = 0.001299 = 13255.4551 psi = 20000.0000 / 1.0000 = 20000.0000 psi

B S

ScVC = 13255.4551 psi Operating, Hot & Corroded, Top Seam tp = P*R/(2*St*Ks*Ec + 0.40*|P|) = 100.0000*17.8130/(2*20000.0000*1.0000*0.70 + 0.40*|100.0000|) = 0.0635" tm = M/(*Rm2*St*Ks*Ec) = 0.00/(*17.90652*20000.0000*1.0000*0.70) = 0.0000" tw = W/(2**Rm*St*Ks*Ec) = -90.30/(2**17.9065*20000.0000*1.0000*0.70) = -0.0001" tt = tp + tm - tw = 0.063527 + 0.000000 - (-0.000057) = 0.0636" tc = |tmc + twc - tpc| = |0.000000 + (-0.000057) - (0.063527)| = 0.0636" (total, net tensile) (total required, tensile) (Weight) (bending) (Pressure)

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Straight Flange on Bottom Head

Maximum allowable working pressure, Longitudinal Stress P = 2*St*Ks*Ec*(t-tm+tw) / (R - 0.40*(t-tm+tw)) 2*20000.0000*1.0000*0.70*(0.1870-0.000000+(-0.000057)) / (17.8130 - 0.40*(0.1870-0.000000+(0.000057))) = 295.0913 psi = Operating, Hot & New, Top Seam tp = P*R/(2*St*Ks*Ec + 0.40*|P|) = 100.0000*17.8130/(2*20000.0000*1.0000*0.70 + 0.40*|100.0000|) = 0.0635" tm = M/(*Rm2*St*Ks*Ec) = 0.00/(*17.90652*20000.0000*1.0000*0.70) = 0.0000" tw = W/(2**Rm*St*Ks*Ec) = -90.30/(2**17.9065*20000.0000*1.0000*0.70) = -0.0001" tt = tp + tm - tw = 0.063527 + 0.000000 - (-0.000057) = 0.0636" tc = |tmc + twc - tpc| = |0.000000 + (-0.000057) - (0.063527)| = 0.0636" Maximum allowable working pressure, Longitudinal Stress P = 2*St*Ks*Ec*(t-tm+tw) / (R - 0.40*(t-tm+tw)) 2*20000.0000*1.0000*0.70*(0.1870-0.000000+(-0.000057)) / (17.8130 - 0.40*(0.1870-0.000000+(0.000057))) = 295.0913 psi = Hot Shut Down, Corroded, Top Seam (total, net tensile) (total required, tensile) (Weight) (bending) (Pressure)

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Straight Flange on Bottom Head

tp = 0.0000" tm = M/(*Rm2*St*Ks*Ec) = 0.00/(*17.90652*20000.0000*1.0000*0.70) = 0.0000" tw = W/(2**Rm*St*Ks*Ec) = -90.30/(2**17.9065*20000.0000*1.0000*0.70) = -0.0001" tt = tp + tm - tw = 0.000000 + 0.000000 - (-0.000057) = 0.0001" tc = |tmc + twc - tpc| = |0.000000 + (-0.000057) - (0.000000)| = 0.0001" Hot Shut Down, New, Top Seam tp = 0.0000" tm = M/(*Rm2*St*Ks*Ec) = 0.00/(*17.90652*20000.0000*1.0000*0.70) = 0.0000" tw = W/(2**Rm*St*Ks*Ec) = -90.30/(2**17.9065*20000.0000*1.0000*0.70) = -0.0001" tt = tp + tm - tw = 0.000000 + 0.000000 - (-0.000057) = 0.0001" tc = |tmc + twc - tpc| = |0.000000 + (-0.000057) - (0.000000)| = 0.0001" Empty, Corroded, Top Seam

(Pressure) (bending)

(Weight)

(total required, tensile)

(total, net tensile)

(Pressure) (bending)

(Weight)

(total required, tensile)

(total, net tensile)

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Straight Flange on Bottom Head

tp = 0.0000" tm = M/(*Rm2*St*Ks*Ec) = 0.00/(*17.90652*20000.0000*1.0000*0.70) = 0.0000" tw = W/(2**Rm*St*Ks*Ec) = -90.30/(2**17.9065*20000.0000*1.0000*0.70) = -0.0001" tt = tp + tm - tw = 0.000000 + 0.000000 - (-0.000057) = 0.0001" tc = |tmc + twc - tpc| = |0.000000 + (-0.000057) - (0.000000)| = 0.0001" Empty, New, Top Seam tp = 0.0000" tm = M/(*Rm2*St*Ks*Ec) = 0.00/(*17.90652*20000.0000*1.0000*0.70) = 0.0000" tw = W/(2**Rm*St*Ks*Ec) = -90.30/(2**17.9065*20000.0000*1.0000*0.70) = -0.0001" tt = tp + tm - tw = 0.000000 + 0.000000 - (-0.000057) = 0.0001" tc = |tmc + twc - tpc| = |0.000000 + (-0.000057) - (0.000000)| = 0.0001" Vacuum, Top Seam

(Pressure) (bending)

(Weight)

(total required, tensile)

(total, net tensile)

(Pressure) (bending)

(Weight)

(total required, tensile)

(total, net tensile)

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Straight Flange on Bottom Head

tp = P*R/(2*Sc*Ks + 0.40*|P|) = -15.0000*17.8130/(2*13255.4551*1.0000 + 0.40*|15.0000|) = -0.0101" tm = M/(*Rm2*Sc*Ks) = 0.00/(*17.90652*13255.4551*1.0000) = 0.0000" tw = W/(2**Rm*Sc*Ks) = -90.30/(2**17.9065*13255.4551*1.0000) = -0.0001" tt = |tp + tm - tw| = |-0.010076 + 0.000000 - (-0.000061)| = 0.0100" tc = tmc + twc - tpc = 0.000000 + (-0.000061) - (-0.010076) = 0.0100"

(Pressure)

(bending)

(Weight)

(total, net compressive)

(total required, compressive)

Hot Shut Down, Corroded, Weight & Eccentric Moments Only, Top Seam tp = 0.0000" tm = M/(*Rm2*St*Ks*Ec) = 0.00/(*17.90652*20000.0000*1.0000*0.70) = 0.0000" tw = W/(2**Rm*St*Ks*Ec) = -90.30/(2**17.9065*20000.0000*1.0000*0.70) = -0.0001" tt = tp + tm - tw = 0.000000 + 0.000000 - (-0.000057) = 0.0001" tc = |tmc + twc - tpc| = |0.000000 + (-0.000057) - (0.000000)| = 0.0001" (total, net tensile) (total required, tensile) (Weight) (Pressure) (bending)

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Bottom Head

Bottom Head ASME Section VIII, Division 1, 2001 Edition, A03 Addenda Component: Material Specification: Straight Flange governs MDMT Internal design pressure: P = 100 psi @ 150 °F External design pressure: Pe = 15 psi @ 150 °F Static liquid head: Ps= 0 psi (SG=1, Hs=0" Operating head) Pth= 1.5093 psi (SG=1, Hs=41.813" Horizontal test head) Corrosion allowance: Design MDMT = -20°F Rated MDMT = -55°F Inner C = 0" Outer C = 0" Ellipsoidal Head SA-516 70 (ASME II-D p.14, ln. 31)

No impact test performed Material is not normalized Material is not produced to fine grain practice PWHT is not performed Do not Optimize MDMT / Find MAWP Seamless No RT None UW-11(c) Type 1 corr = 90.3 lb corr = 34.3 US gal

Radiography:

Category A joints Head to shell seam -

Estimated weight*: new = 90.3 lb Capacity*: new = 34.3 US gal * includes straight flange Outer diameter Minimum head thickness Head ratio D/2h Head ratio D/2h Straight flange length Lsf Nominal straight flange thickness tsf Insulation thk*: 0" = = = = = = 36" 0.187" 2 (new) 2 (corroded) 2" 0.187"

density: 0 lb/ft3

weight: 0 lb

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Bottom Head

Insulation support ring 0" spacing: Lining/ref thk*: 0" * includes straight flange if applicable Results Summary

individual weight: 0 lb total weight: 0 lb density: 0 lb/ft3 weight: 0 lb

The governing condition is internal pressure. Minimum thickness per UG-16 Design thickness due to internal pressure (t) Design thickness due to external pressure (te) Maximum allowable working pressure (MAWP) Maximum allowable pressure (MAP) Maximum allowable external pressure (MAEP)

= = = = = =

0.0625" + 0" = 0.0625" 0.1054" 0.0927" 178.278 psi 178.278 psi 61.3292 psi

K (Corroded) K = = = (1/6)*[2 + (D / (2*h))2] (1/6)*[2 + (35.626 / (2*8.9065))2] 1

K (New) K = = = (1/6)*[2 + (D / (2*h))2] (1/6)*[2 + (35.626 / (2*8.9065))2] 1

Design thickness for internal pressure, (Corroded at 150 °F) Appendix 1-4(c) t = = = P*Do*K / (2*S*E + 2*P*(K - 0.1)) + Corrosion 100*36*1 / (2*20000*0.85 + 2*100*(1 - 0.1)) + 0 0.1053"

The head internal pressure design thickness is 0.1054". Maximum allowable working pressure, (Corroded at 150 °F) Appendix 1-4(c) P = = 2*S*E*t / (K*Do - 2*t*(K - 0.1)) - Ps 2*20000*0.85*0.187 / (1*36 - 2*0.187*(1 - 0.1)) - 0

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Bottom Head

=

178.278 psi

The maximum allowable working pressure (MAWP) is 178.278 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*20000*0.85*0.187 / (1*36 - 2*0.187*(1 - 0.1)) - 0 178.278 psi

The maximum allowable pressure (MAP) is 178.278 psi. Design thickness for external pressure, (Corroded at 150 °F) UG-33(d) Equivalent outside spherical radius (Ro) Ko*Do Ro = = 0.8907 * 36 = 32.0669 in A = = = 0.125 / (Ro/t) 0.125 / (32.0669/0.092617) 0.000361

From Table CS-2: B=5,193.4531 psi Pa = = = = B/(Ro/t) 5,193.453/(32.0669/0.092617) 15 psi 0.0926" + Corrosion = 0.0926" + 0" = 0.0926"

t

Check the external pressure per UG-33(a)(1) Appendix 1-4(c) t = = = 1.67*Pe*Do*K / (2*S*E + 2*1.67*Pe*(K - 0.1)) + Corrosion 1.67*15*36*1 / (2*20000*1 + 2*1.67*15*(1 - 0.1)) + 0 0.0225"

The head external pressure design thickness (te) is 0.092617". Maximum Allowable External Pressure, (Corroded at 150 °F) UG-33(d)

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Bottom Head

Equivalent outside spherical radius (Ro) Ko*Do Ro = = 0.8907 * 36 = 32.0669 in A = = = 0.125 / (Ro/t) 0.125 / (32.0669/0.187) 0.000729

From Table CS-2: B=10,516.7607 psi Pa = = = B/(Ro/t) 10,516.76/(32.0669/0.187) 61.3292 psi

Check the Maximum External Pressure, UG-33(a)(1) Appendix 1-4(c) P = = = 2*S*E*t / ((K*Do - 2*t*(K - 0.1))*1.67) - Ps2 2*20000*1*0.187 / ((1*36 - 2*0.187*(1 - 0.1))*1.67) - 0 125.5921 psi

The maximum allowable external pressure (MAEP) is 61.3292 psi. % Extreme fiber elongation - UCS-79(d) = = = (75*t / Rf)*(1 - Rf / Ro) (75*0.187 / 6.1499)*(1 - 6.1499 / ) 2.2805%

The extreme fiber elongation does not exceed 5%.

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Nozzle #1 (N1)

Nozzle #1 (N1)

ASME Section VIII Division 1, 2001 Edition, A03 Addenda

tw(lower) = 0.1250 in Leg41 = 0.1870 in

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

Located on: Cylinder #1 Liquid static head included: 0 psi Nozzle material specification: SA-106 B Smls pipe (ASME II-D p. 10, ln. 15) Nozzle longitudinal joint efficiency: 1.00 Nozzle description: 1.500" Sch 40 (Std) Flange description: 1.5 inch 150# WN A105 Bolt Material: SA-193 B7 Bolt <= 2 1/2 Flange rated MDMT: -55.00 °F (UCS-66(b)(1)(b)) Liquid static head on flange: 0 psi ASME B16.5 flange rating MAWP: 272.50 psi @ 150.00°F ASME B16.5 flange rating MAP: 285.00 psi @ 70.00°F ASME B16.5 flange hydro test: 450.00 psi @ 70.00°F Nozzle orientation: 0 ° Local vessel minimum thickness: 0.1875 in Nozzle center line offset to datum line: 36.0000 in End of nozzle to shell center: 22.0000 in Nozzle inside diameter, new: 1.6100 in Nozzle nominal wall thickness: 0.1450 in Nozzle corrosion allowance: 0.0000 in Projection available outside vessel, Lpr: 4.0000 in

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Nozzle #1 (N1)

Reinforcement Calculations for Internal Pressure The vessel wall thickness governs the MAWP of this nozzle. UG-37 Area Calculation Summary (in2)

For P = 209.14 psi @ 150.00 °F A required A available A1 A2 A3 A5 A welds

UG-45 Nozzle Wall Thickness Summary (in)

The nozzle passes UG-45 treq tmin

This nozzle is exempt from area calculations per UG-36(c)(3)(a) 0.1269 Weld Failure Path Analysis Summary The nozzle is exempt from weld strength calculations per UW-15(b)(2) UW-16 Weld Sizing Summary

Weld description Nozzle to shell fillet (Leg41) Required weld Actual weld Status throat size (in) throat size (in)

0.1269

0.1015

0.1309 0.1250

weld size is adequate weld size is adequate

Nozzle to shell groove (Lower) 0.1015

Calculations for internal pressure 209.14 psi @ 150.00 °F Fig UCS-66.2 general note (1) applies. Nozzle is impact test exempt per UCS-66(d)(NPS 4 or smaller pipe). Nozzle UCS-66 governing thk: 0.1269 in Nozzle rated MDMT: -155.00 °F Limits of reinforcement per UG-40 Parallel to the vessel wall: d = 1.6100 in Normal to the vessel wall outside: 2.5*(tn - Cn) + te = 0.3625 in Nozzle required thickness per UG-27(c)(1) trn = P*Rn/(Sn*E - 0.6*P)

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Nozzle #1 (N1)

= 209.1423*0.805/(17,100.00*1 - 0.6*209.1423) = 0.0099 in Required thickness tr from UG-37(a) tr = P*Ro/(S*E + 0.4*P) = 209.1423*18/(20,000.00*1 + 0.4*209.1423) = 0.1874 in This opening does not require reinforcement per UG-36(c)(3)(a)

Area calculations for weld failure path analysis Allowable stresses: Sn = 17,100.00, Sv = 20,000.00 psi fr1 = lesser of 1 or Sn/Sv = 0.855 fr2 = lesser of 1 or Sn/Sv = 0.855 A = d*tr*F + 2*tn*tr*F*(1 - fr1) = 1.61*0.18744*1 + 2*0.145*0.18744*1*(1 - 0.855) = 0.3097 in2 A1 = larger of the following= 0.0001 in2 = d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 1.61*(1*0.1875 - 1*0.18744) - 2*0.145*(1*0.1875 - 1*0.18744)*(1 - 0.855) = 0.0001 in2 = 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 2*(0.1875 + 0.145)*(1*0.1875 - 1*0.18744) - 2*0.145*(1*0.1875 - 1*0.18744)*(1 - 0.855) = 0.0000 in2 A2 = smaller of the following= 0.0837 in2 = 5*(tn - trn)*fr2*t = 5*(0.145 - 0.0099)*0.855*0.1875 = 0.1083 in2 = 5*(tn - trn)*fr2*tn = 5*(0.145 - 0.0099)*0.855*0.145 = 0.0837 in2

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Nozzle #1 (N1)

A41 = Leg2*fr2 = 0.1872*0.855 =0.0299 in2 UW-16(d) Weld Check tmin = lesser of 0.75 or tn or t = 0.1450 in t1(min) or t2(min) = lesser of 0.25 or 0.7*tmin = 0.1015 in t1(actual) = 0.7*Leg = 0.7*0.187 = 0.1309 in The weld size t1 is satisfactory. t2(actual) = 0.125 in The weld size t2 is satisfactory. t1 + t2 = 0.2559 >= 1.25*tmin The combined weld sizes for t1 and t2 are satisfactory. UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a): Wall thickness per UG-45(b)(1): Wall thickness per UG-16(b): tr1 = 0.0099 in (E =1) tr2 = 0.1874 in tr3 = 0.0625 in

Standard wall pipe per UG-45(b)(4): tr4 = 0.1269 in The greater of tr2 or tr3: tr5 = 0.1874 in The lesser of tr4 or tr5: tr6 = 0.1269 in

Required per UG-45 is the larger of tr1 or tr6 = 0.1269 in Available nozzle wall thickness new, tn = 0.8750*0.1450 = 0.1269 in The nozzle neck thickness is adequate. Reinforcement Calculations for MAP The vessel wall thickness governs the MAP of this nozzle. UG-37 Area Calculation Summary (in2)

For P = 209.14 psi @ 70.00 °F

UG-45 Nozzle Wall Thickness Summary (in)

The nozzle passes UG-45

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Nozzle #1 (N1)

A required

A available

A1

A2

A3

A5

A welds

treq

tmin

This nozzle is exempt from area calculations per UG-36(c)(3)(a) 0.1269 Weld Failure Path Analysis Summary The nozzle is exempt from weld strength calculations per UW-15(b)(2) UW-16 Weld Sizing Summary

Weld description Nozzle to shell fillet (Leg41) Required weld Actual weld Status throat size (in) throat size (in)

0.1269

0.1015

0.1309 0.1250

weld size is adequate weld size is adequate

Nozzle to shell groove (Lower) 0.1015

Calculations for internal pressure 209.14 psi @ 70.00 °F Limits of reinforcement per UG-40 Parallel to the vessel wall: d = 1.6100 in Normal to the vessel wall outside: 2.5*(tn - Cn) + te = 0.3625 in Nozzle required thickness per UG-27(c)(1) trn = P*Rn/(Sn*E - 0.6*P) = 209.1423*0.805/(17,100.00*1 - 0.6*209.1423) = 0.0099 in Required thickness tr from UG-37(a) tr = P*Ro/(S*E + 0.4*P) = 209.1423*18/(20,000.00*1 + 0.4*209.1423) = 0.1874 in This opening does not require reinforcement per UG-36(c)(3)(a)

Area calculations for weld failure path analysis

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Nozzle #1 (N1)

Allowable stresses: Sn = 17,100.00, Sv = 20,000.00 psi fr1 = lesser of 1 or Sn/Sv = 0.855 fr2 = lesser of 1 or Sn/Sv = 0.855 A = d*tr*F + 2*tn*tr*F*(1 - fr1) = 1.61*0.18744*1 + 2*0.145*0.18744*1*(1 - 0.855) = 0.3097 in2 A1 = larger of the following= 0.0001 in2 = d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 1.61*(1*0.1875 - 1*0.18744) - 2*0.145*(1*0.1875 - 1*0.18744)*(1 - 0.855) = 0.0001 in2 = 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 2*(0.1875 + 0.145)*(1*0.1875 - 1*0.18744) - 2*0.145*(1*0.1875 - 1*0.18744)*(1 - 0.855) = 0.0000 in2 A2 = smaller of the following= 0.0837 in2 = 5*(tn - trn)*fr2*t = 5*(0.145 - 0.0099)*0.855*0.1875 = 0.1083 in2 = 5*(tn - trn)*fr2*tn = 5*(0.145 - 0.0099)*0.855*0.145 = 0.0837 in2 A41 = Leg2*fr2 = 0.1872*0.855 =0.0299 in2 UW-16(d) Weld Check tmin = lesser of 0.75 or tn or t = 0.1450 in t1(min) or t2(min) = lesser of 0.25 or 0.7*tmin = 0.1015 in t1(actual) = 0.7*Leg = 0.7*0.187 = 0.1309 in The weld size t1 is satisfactory. t2(actual) = 0.125 in The weld size t2 is satisfactory.

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Nozzle #1 (N1)

t1 + t2 = 0.2559 >= 1.25*tmin The combined weld sizes for t1 and t2 are satisfactory. UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a): Wall thickness per UG-45(b)(1): Wall thickness per UG-16(b): tr1 = 0.0099 in (E =1) tr2 = 0.1874 in tr3 = 0.0625 in

Standard wall pipe per UG-45(b)(4): tr4 = 0.1269 in The greater of tr2 or tr3: tr5 = 0.1874 in The lesser of tr4 or tr5: tr6 = 0.1269 in

Required per UG-45 is the larger of tr1 or tr6 = 0.1269 in Available nozzle wall thickness new, tn = 0.8750*0.1450 = 0.1269 in The nozzle neck thickness is adequate. Reinforcement Calculations for External Pressure UG-37 Area Calculation Summary (in2)

For Pe = 33.33 psi @ 150.00 °F A required A available A1 A2 A3 A5 A welds

UG-45 Nozzle Wall Thickness Summary (in)

The nozzle passes UG-45 treq tmin

This nozzle is exempt from area calculations per UG-36(c)(3)(a) 0.0625 Weld Failure Path Analysis Summary Weld strength calculations are not required for external pressure UW-16 Weld Sizing Summary

Weld description Nozzle to shell fillet (Leg41) Required weld Actual weld Status throat size (in) throat size (in)

0.1269

0.1015

0.1309

weld size is adequate

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Nozzle #1 (N1)

Nozzle to shell groove (Lower) 0.1015

0.1250

weld size is adequate

Calculations for external pressure 33.33 psi @ 150.00 °F Limits of reinforcement per UG-40 Parallel to the vessel wall: d = 1.6100 in Normal to the vessel wall outside: 2.5*(tn - Cn) + te = 0.3625 in Nozzle required thickness per UG-28 trn = 0.0114 in From UG-37(d)(1) required thickness tr = 0.1875 in This opening does not require reinforcement per UG-36(c)(3)(a) UW-16(d) Weld Check tmin = lesser of 0.75 or tn or t = 0.1450 in t1(min) or t2(min) = lesser of 0.25 or 0.7*tmin = 0.1015 in t1(actual) = 0.7*Leg = 0.7*0.187 = 0.1309 in The weld size t1 is satisfactory. t2(actual) = 0.125 in The weld size t2 is satisfactory. t1 + t2 = 0.2559 >= 1.25*tmin The combined weld sizes for t1 and t2 are satisfactory. UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a): Wall thickness per UG-45(b)(2): Wall thickness per UG-16(b): tr1 = 0.0114 in tr2 = 0.0300 in tr3 = 0.0625 in

Standard wall pipe per UG-45(b)(4): tr4 = 0.1269 in The greater of tr2 or tr3: tr5 = 0.0625 in The lesser of tr4 or tr5: tr6 = 0.0625 in

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Nozzle #1 (N1)

Required per UG-45 is the larger of tr1 or tr6 = 0.0625 in Available nozzle wall thickness new, tn = 0.8750*0.1450 = 0.1269 in The nozzle neck thickness is adequate. External Pressure, (Corroded & at 150.00°F) UG-28(c) L/Do = 4.0251/1.9000 = 2.1185 Do/t = 1.9000/0.011395 = 166.7393 From table G: A = 0.000290 From table CS-2: B = 4168.5352 Pa = 4*B/(3*(Do/t)) = 4*4168.5352/(3*(1.9000/0.011395)) = 33.3338 psi Design thickness for external pressure Pa = 33.3338 psi = t + Corrosion = 0.011395 + 0.0000 = 0.0114"

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Nozzle #2 (N2)

Nozzle #2 (N2)

ASME Section VIII Division 1, 2001 Edition, A03 Addenda

tw(lower) = 0.1250 in Leg41 = 0.1870 in

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

Located on: Cylinder #1 Liquid static head included: 0 psi Nozzle material specification: SA-106 B Smls pipe (ASME II-D p. 10, ln. 15) Nozzle longitudinal joint efficiency: 1.00 Nozzle description: 1.500" Sch 40 (Std) Flange description: 1.5 inch 150# WN A105 Bolt Material: SA-193 B7 Bolt <= 2 1/2 Flange rated MDMT: -55.00 °F (UCS-66(b)(1)(b)) Liquid static head on flange: 0 psi ASME B16.5 flange rating MAWP: 272.50 psi @ 150.00°F ASME B16.5 flange rating MAP: 285.00 psi @ 70.00°F ASME B16.5 flange hydro test: 450.00 psi @ 70.00°F Nozzle orientation: 0 ° Local vessel minimum thickness: 0.1875 in Nozzle center line offset to datum line: 36.0000 in End of nozzle to shell center: 22.0000 in Offset from center, Lo: 8.0000 in Nozzle inside diameter, new: 1.6100 in Nozzle nominal wall thickness: 0.1450 in Nozzle corrosion allowance: 0.0000 in Opening chord length: 1.8014 in Projection available outside vessel, Lpr: 5.4381 in

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Nozzle #2 (N2)

Reinforcement Calculations for Internal Pressure The vessel wall thickness governs the MAWP of this nozzle. UG-37 Area Calculation Summary (in2)

For P = 209.14 psi @ 150.00 °F A required A available A1 A2 A3 A5 A welds

UG-45 Nozzle Wall Thickness Summary (in)

The nozzle passes UG-45 treq tmin

This nozzle is exempt from area calculations per UG-36(c)(3)(a) 0.1269 Weld Failure Path Analysis Summary The nozzle is exempt from weld strength calculations per UW-15(b)(2) UW-16 Weld Sizing Summary

Weld description Nozzle to shell fillet (Leg41) Required weld Actual weld Status throat size (in) throat size (in)

0.1269

0.1015

0.1309 0.1250

weld size is adequate weld size is adequate

Nozzle to shell groove (Lower) 0.1015

Calculations for internal pressure 209.14 psi @ 150.00 °F Fig UCS-66.2 general note (1) applies. Nozzle is impact test exempt per UCS-66(d)(NPS 4 or smaller pipe). Nozzle UCS-66 governing thk: 0.1269 in Nozzle rated MDMT: -155.00 °F Limits of reinforcement per UG-40 Parallel to the vessel wall: d = 1.8014 in Normal to the vessel wall outside: 2.5*(tn - Cn) + te = 0.3625 in Nozzle required thickness per UG-27(c)(1)

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Nozzle #2 (N2)

trn = P*Rn/(Sn*E - 0.6*P) = 209.1423*0.805/(17,100.00*1 - 0.6*209.1423) = 0.0099 in Required thickness tr from UG-37(a) tr = P*Ro/(S*E + 0.4*P) = 209.1423*18/(20,000.00*1 + 0.4*209.1423) = 0.1874 in This opening does not require reinforcement per UG-36(c)(3)(a)

Area calculations for weld failure path analysis Allowable stresses: Sn = 17,100.00, Sv = 20,000.00 psi fr1 = lesser of 1 or Sn/Sv = 0.855 fr2 = lesser of 1 or Sn/Sv = 0.855 A = d*tr*F + 2*tn*tr*F*(1 - fr1) = 1.8014*0.18744*1 + 2*0.145*0.18744*1*(1 - 0.855) = 0.3455 in2 A1 = larger of the following= 0.0001 in2 = d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 1.8014*(1*0.1875 - 1*0.18744) - 2*0.145*(1*0.1875 - 1*0.18744)*(1 - 0.855) = 0.0001 in2 = 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 2*(0.1875 + 0.145)*(1*0.1875 - 1*0.18744) - 2*0.145*(1*0.1875 - 1*0.18744)*(1 - 0.855) = 0.0000 in2 A2 = smaller of the following= 0.0837 in2 = 5*(tn - trn)*fr2*t = 5*(0.145 - 0.0099)*0.855*0.1875 = 0.1083 in2 = 5*(tn - trn)*fr2*tn

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Nozzle #2 (N2)

= 5*(0.145 - 0.0099)*0.855*0.145 = 0.0837 in2 A41 = Leg2*fr2 = 0.1872*0.855 =0.0299 in2 UW-16(d) Weld Check tmin = lesser of 0.75 or tn or t = 0.1450 in t1(min) or t2(min) = lesser of 0.25 or 0.7*tmin = 0.1015 in t1(actual) = 0.7*Leg = 0.7*0.187 = 0.1309 in The weld size t1 is satisfactory. t2(actual) = 0.125 in The weld size t2 is satisfactory. t1 + t2 = 0.2559 >= 1.25*tmin The combined weld sizes for t1 and t2 are satisfactory. UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a): Wall thickness per UG-45(b)(1): Wall thickness per UG-16(b): tr1 = 0.0099 in (E =1) tr2 = 0.1874 in tr3 = 0.0625 in

Standard wall pipe per UG-45(b)(4): tr4 = 0.1269 in The greater of tr2 or tr3: tr5 = 0.1874 in The lesser of tr4 or tr5: tr6 = 0.1269 in

Required per UG-45 is the larger of tr1 or tr6 = 0.1269 in Available nozzle wall thickness new, tn = 0.8750*0.1450 = 0.1269 in The nozzle neck thickness is adequate. Reinforcement Calculations for MAP The vessel wall thickness governs the MAP of this nozzle.

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Nozzle #2 (N2)

UG-37 Area Calculation Summary (in2)

For P = 209.14 psi @ 70.00 °F A required A available A1 A2 A3 A5 A welds

UG-45 Nozzle Wall Thickness Summary (in)

The nozzle passes UG-45 treq tmin

This nozzle is exempt from area calculations per UG-36(c)(3)(a) 0.1269 Weld Failure Path Analysis Summary The nozzle is exempt from weld strength calculations per UW-15(b)(2) UW-16 Weld Sizing Summary

Weld description Nozzle to shell fillet (Leg41) Required weld Actual weld Status throat size (in) throat size (in)

0.1269

0.1015

0.1309 0.1250

weld size is adequate weld size is adequate

Nozzle to shell groove (Lower) 0.1015

Calculations for internal pressure 209.14 psi @ 70.00 °F Limits of reinforcement per UG-40 Parallel to the vessel wall: d = 1.8014 in Normal to the vessel wall outside: 2.5*(tn - Cn) + te = 0.3625 in Nozzle required thickness per UG-27(c)(1) trn = P*Rn/(Sn*E - 0.6*P) = 209.1423*0.805/(17,100.00*1 - 0.6*209.1423) = 0.0099 in Required thickness tr from UG-37(a) tr = P*Ro/(S*E + 0.4*P) = 209.1423*18/(20,000.00*1 + 0.4*209.1423) = 0.1874 in This opening does not require reinforcement per UG-36(c)(3)(a)

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Nozzle #2 (N2)

Area calculations for weld failure path analysis Allowable stresses: Sn = 17,100.00, Sv = 20,000.00 psi fr1 = lesser of 1 or Sn/Sv = 0.855 fr2 = lesser of 1 or Sn/Sv = 0.855 A = d*tr*F + 2*tn*tr*F*(1 - fr1) = 1.8014*0.18744*1 + 2*0.145*0.18744*1*(1 - 0.855) = 0.3455 in2 A1 = larger of the following= 0.0001 in2 = d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 1.8014*(1*0.1875 - 1*0.18744) - 2*0.145*(1*0.1875 - 1*0.18744)*(1 - 0.855) = 0.0001 in2 = 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 2*(0.1875 + 0.145)*(1*0.1875 - 1*0.18744) - 2*0.145*(1*0.1875 - 1*0.18744)*(1 - 0.855) = 0.0000 in2 A2 = smaller of the following= 0.0837 in2 = 5*(tn - trn)*fr2*t = 5*(0.145 - 0.0099)*0.855*0.1875 = 0.1083 in2 = 5*(tn - trn)*fr2*tn = 5*(0.145 - 0.0099)*0.855*0.145 = 0.0837 in2 A41 = Leg2*fr2 = 0.1872*0.855 =0.0299 in2 UW-16(d) Weld Check tmin = lesser of 0.75 or tn or t = 0.1450 in t1(min) or t2(min) = lesser of 0.25 or 0.7*tmin = 0.1015 in t1(actual) = 0.7*Leg = 0.7*0.187 = 0.1309 in

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Nozzle #2 (N2)

The weld size t1 is satisfactory. t2(actual) = 0.125 in The weld size t2 is satisfactory. t1 + t2 = 0.2559 >= 1.25*tmin The combined weld sizes for t1 and t2 are satisfactory. UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a): Wall thickness per UG-45(b)(1): Wall thickness per UG-16(b): tr1 = 0.0099 in (E =1) tr2 = 0.1874 in tr3 = 0.0625 in

Standard wall pipe per UG-45(b)(4): tr4 = 0.1269 in The greater of tr2 or tr3: tr5 = 0.1874 in The lesser of tr4 or tr5: tr6 = 0.1269 in

Required per UG-45 is the larger of tr1 or tr6 = 0.1269 in Available nozzle wall thickness new, tn = 0.8750*0.1450 = 0.1269 in The nozzle neck thickness is adequate. Reinforcement Calculations for External Pressure UG-37 Area Calculation Summary (in2)

For Pe = 33.33 psi @ 150.00 °F A required A available A1 A2 A3 A5 A welds

UG-45 Nozzle Wall Thickness Summary (in)

The nozzle passes UG-45 treq tmin

This nozzle is exempt from area calculations per UG-36(c)(3)(a) 0.0625 Weld Failure Path Analysis Summary Weld strength calculations are not required for external pressure UW-16 Weld Sizing Summary

0.1269

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Nozzle #2 (N2)

Weld description Nozzle to shell fillet (Leg41)

Required weld Actual weld Status throat size (in) throat size (in)

0.1015

0.1309 0.1250

weld size is adequate weld size is adequate

Nozzle to shell groove (Lower) 0.1015

Calculations for external pressure 33.33 psi @ 150.00 °F Limits of reinforcement per UG-40 Parallel to the vessel wall: d = 1.8002 in Normal to the vessel wall outside: 2.5*(tn - Cn) + te = 0.3625 in Nozzle required thickness per UG-28 trn = 0.0140 in From UG-37(d)(1) required thickness tr = 0.1875 in This opening does not require reinforcement per UG-36(c)(3)(a) UW-16(d) Weld Check tmin = lesser of 0.75 or tn or t = 0.1450 in t1(min) or t2(min) = lesser of 0.25 or 0.7*tmin = 0.1015 in t1(actual) = 0.7*Leg = 0.7*0.187 = 0.1309 in The weld size t1 is satisfactory. t2(actual) = 0.125 in The weld size t2 is satisfactory. t1 + t2 = 0.2559 >= 1.25*tmin The combined weld sizes for t1 and t2 are satisfactory. UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a): Wall thickness per UG-45(b)(2): Wall thickness per UG-16(b): tr1 = 0.0140 in tr2 = 0.0300 in tr3 = 0.0625 in

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Nozzle #2 (N2)

Standard wall pipe per UG-45(b)(4): tr4 = 0.1269 in The greater of tr2 or tr3: tr5 = 0.0625 in The lesser of tr4 or tr5: tr6 = 0.0625 in

Required per UG-45 is the larger of tr1 or tr6 = 0.0625 in Available nozzle wall thickness new, tn = 0.8750*0.1450 = 0.1269 in The nozzle neck thickness is adequate. External Pressure, (Corroded & at 150.00°F) UG-28(c) L/Do = 6.3828/1.9000 = 3.3594 Do/t = 1.9000/0.013962 = 136.0829 From table G: A = 0.000237 From table CS-2: B = 3402.0903 Pa = 4*B/(3*(Do/t)) = 4*3402.0903/(3*(1.9000/0.013962)) = 33.3335 psi Design thickness for external pressure Pa = 33.3335 psi = t + Corrosion = 0.013962 + 0.0000 = 0.0140"

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Nozzle #3 (N3)

Nozzle #3 (N3)

ASME Section VIII Division 1, 2001 Edition, A03 Addenda

tw(lower) = 0.1250 in Leg41 = 0.1870 in

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

Located on: Cylinder #1 Liquid static head included: 0 psi Nozzle material specification: SA-106 B Smls pipe (ASME II-D p. 10, ln. 15) Nozzle longitudinal joint efficiency: 1.00 Nozzle description: 1.500" Sch 40 (Std) Flange description: 1.5 inch 150# WN A105 Bolt Material: SA-193 B7 Bolt <= 2 1/2 Flange rated MDMT: -55.00 °F (UCS-66(b)(1)(b)) Liquid static head on flange: 0 psi ASME B16.5 flange rating MAWP: 272.50 psi @ 150.00°F ASME B16.5 flange rating MAP: 285.00 psi @ 70.00°F ASME B16.5 flange hydro test: 450.00 psi @ 70.00°F Nozzle orientation: 0 ° Local vessel minimum thickness: 0.1875 in Nozzle center line offset to datum line: 36.0000 in End of nozzle to shell center: 22.0000 in Offset from center, Lo: -8.0000 in Nozzle inside diameter, new: 1.6100 in Nozzle nominal wall thickness: 0.1450 in Nozzle corrosion allowance: 0.0000 in Opening chord length: 1.8014 in Projection available outside vessel, Lpr: 5.4381 in

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Nozzle #3 (N3)

Reinforcement Calculations for Internal Pressure The vessel wall thickness governs the MAWP of this nozzle. UG-37 Area Calculation Summary (in2)

For P = 209.14 psi @ 150.00 °F A required A available A1 A2 A3 A5 A welds

UG-45 Nozzle Wall Thickness Summary (in)

The nozzle passes UG-45 treq tmin

This nozzle is exempt from area calculations per UG-36(c)(3)(a) 0.1269 Weld Failure Path Analysis Summary The nozzle is exempt from weld strength calculations per UW-15(b)(2) UW-16 Weld Sizing Summary

Weld description Nozzle to shell fillet (Leg41) Required weld Actual weld Status throat size (in) throat size (in)

0.1269

0.1015

0.1309 0.1250

weld size is adequate weld size is adequate

Nozzle to shell groove (Lower) 0.1015

Calculations for internal pressure 209.14 psi @ 150.00 °F Fig UCS-66.2 general note (1) applies. Nozzle is impact test exempt per UCS-66(d)(NPS 4 or smaller pipe). Nozzle UCS-66 governing thk: 0.1269 in Nozzle rated MDMT: -155.00 °F Limits of reinforcement per UG-40 Parallel to the vessel wall: d = 1.8014 in Normal to the vessel wall outside: 2.5*(tn - Cn) + te = 0.3625 in Nozzle required thickness per UG-27(c)(1)

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Nozzle #3 (N3)

trn = P*Rn/(Sn*E - 0.6*P) = 209.1423*0.805/(17,100.00*1 - 0.6*209.1423) = 0.0099 in Required thickness tr from UG-37(a) tr = P*Ro/(S*E + 0.4*P) = 209.1423*18/(20,000.00*1 + 0.4*209.1423) = 0.1874 in This opening does not require reinforcement per UG-36(c)(3)(a)

Area calculations for weld failure path analysis Allowable stresses: Sn = 17,100.00, Sv = 20,000.00 psi fr1 = lesser of 1 or Sn/Sv = 0.855 fr2 = lesser of 1 or Sn/Sv = 0.855 A = d*tr*F + 2*tn*tr*F*(1 - fr1) = 1.8014*0.18744*1 + 2*0.145*0.18744*1*(1 - 0.855) = 0.3455 in2 A1 = larger of the following= 0.0001 in2 = d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 1.8014*(1*0.1875 - 1*0.18744) - 2*0.145*(1*0.1875 - 1*0.18744)*(1 - 0.855) = 0.0001 in2 = 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 2*(0.1875 + 0.145)*(1*0.1875 - 1*0.18744) - 2*0.145*(1*0.1875 - 1*0.18744)*(1 - 0.855) = 0.0000 in2 A2 = smaller of the following= 0.0837 in2 = 5*(tn - trn)*fr2*t = 5*(0.145 - 0.0099)*0.855*0.1875 = 0.1083 in2 = 5*(tn - trn)*fr2*tn

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Nozzle #3 (N3)

= 5*(0.145 - 0.0099)*0.855*0.145 = 0.0837 in2 A41 = Leg2*fr2 = 0.1872*0.855 =0.0299 in2 UW-16(d) Weld Check tmin = lesser of 0.75 or tn or t = 0.1450 in t1(min) or t2(min) = lesser of 0.25 or 0.7*tmin = 0.1015 in t1(actual) = 0.7*Leg = 0.7*0.187 = 0.1309 in The weld size t1 is satisfactory. t2(actual) = 0.125 in The weld size t2 is satisfactory. t1 + t2 = 0.2559 >= 1.25*tmin The combined weld sizes for t1 and t2 are satisfactory. UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a): Wall thickness per UG-45(b)(1): Wall thickness per UG-16(b): tr1 = 0.0099 in (E =1) tr2 = 0.1874 in tr3 = 0.0625 in

Standard wall pipe per UG-45(b)(4): tr4 = 0.1269 in The greater of tr2 or tr3: tr5 = 0.1874 in The lesser of tr4 or tr5: tr6 = 0.1269 in

Required per UG-45 is the larger of tr1 or tr6 = 0.1269 in Available nozzle wall thickness new, tn = 0.8750*0.1450 = 0.1269 in The nozzle neck thickness is adequate. Reinforcement Calculations for MAP The vessel wall thickness governs the MAP of this nozzle.

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Nozzle #3 (N3)

UG-37 Area Calculation Summary (in2)

For P = 209.14 psi @ 70.00 °F A required A available A1 A2 A3 A5 A welds

UG-45 Nozzle Wall Thickness Summary (in)

The nozzle passes UG-45 treq tmin

This nozzle is exempt from area calculations per UG-36(c)(3)(a) 0.1269 Weld Failure Path Analysis Summary The nozzle is exempt from weld strength calculations per UW-15(b)(2) UW-16 Weld Sizing Summary

Weld description Nozzle to shell fillet (Leg41) Required weld Actual weld Status throat size (in) throat size (in)

0.1269

0.1015

0.1309 0.1250

weld size is adequate weld size is adequate

Nozzle to shell groove (Lower) 0.1015

Calculations for internal pressure 209.14 psi @ 70.00 °F Limits of reinforcement per UG-40 Parallel to the vessel wall: d = 1.8014 in Normal to the vessel wall outside: 2.5*(tn - Cn) + te = 0.3625 in Nozzle required thickness per UG-27(c)(1) trn = P*Rn/(Sn*E - 0.6*P) = 209.1423*0.805/(17,100.00*1 - 0.6*209.1423) = 0.0099 in Required thickness tr from UG-37(a) tr = P*Ro/(S*E + 0.4*P) = 209.1423*18/(20,000.00*1 + 0.4*209.1423) = 0.1874 in This opening does not require reinforcement per UG-36(c)(3)(a)

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Nozzle #3 (N3)

Area calculations for weld failure path analysis Allowable stresses: Sn = 17,100.00, Sv = 20,000.00 psi fr1 = lesser of 1 or Sn/Sv = 0.855 fr2 = lesser of 1 or Sn/Sv = 0.855 A = d*tr*F + 2*tn*tr*F*(1 - fr1) = 1.8014*0.18744*1 + 2*0.145*0.18744*1*(1 - 0.855) = 0.3455 in2 A1 = larger of the following= 0.0001 in2 = d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 1.8014*(1*0.1875 - 1*0.18744) - 2*0.145*(1*0.1875 - 1*0.18744)*(1 - 0.855) = 0.0001 in2 = 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 2*(0.1875 + 0.145)*(1*0.1875 - 1*0.18744) - 2*0.145*(1*0.1875 - 1*0.18744)*(1 - 0.855) = 0.0000 in2 A2 = smaller of the following= 0.0837 in2 = 5*(tn - trn)*fr2*t = 5*(0.145 - 0.0099)*0.855*0.1875 = 0.1083 in2 = 5*(tn - trn)*fr2*tn = 5*(0.145 - 0.0099)*0.855*0.145 = 0.0837 in2 A41 = Leg2*fr2 = 0.1872*0.855 =0.0299 in2 UW-16(d) Weld Check tmin = lesser of 0.75 or tn or t = 0.1450 in t1(min) or t2(min) = lesser of 0.25 or 0.7*tmin = 0.1015 in t1(actual) = 0.7*Leg = 0.7*0.187 = 0.1309 in

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Nozzle #3 (N3)

The weld size t1 is satisfactory. t2(actual) = 0.125 in The weld size t2 is satisfactory. t1 + t2 = 0.2559 >= 1.25*tmin The combined weld sizes for t1 and t2 are satisfactory. UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a): Wall thickness per UG-45(b)(1): Wall thickness per UG-16(b): tr1 = 0.0099 in (E =1) tr2 = 0.1874 in tr3 = 0.0625 in

Standard wall pipe per UG-45(b)(4): tr4 = 0.1269 in The greater of tr2 or tr3: tr5 = 0.1874 in The lesser of tr4 or tr5: tr6 = 0.1269 in

Required per UG-45 is the larger of tr1 or tr6 = 0.1269 in Available nozzle wall thickness new, tn = 0.8750*0.1450 = 0.1269 in The nozzle neck thickness is adequate. Reinforcement Calculations for External Pressure UG-37 Area Calculation Summary (in2)

For Pe = 33.33 psi @ 150.00 °F A required A available A1 A2 A3 A5 A welds

UG-45 Nozzle Wall Thickness Summary (in)

The nozzle passes UG-45 treq tmin

This nozzle is exempt from area calculations per UG-36(c)(3)(a) 0.0625 Weld Failure Path Analysis Summary Weld strength calculations are not required for external pressure UW-16 Weld Sizing Summary

0.1269

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Nozzle #3 (N3)

Weld description Nozzle to shell fillet (Leg41)

Required weld Actual weld Status throat size (in) throat size (in)

0.1015

0.1309 0.1250

weld size is adequate weld size is adequate

Nozzle to shell groove (Lower) 0.1015

Calculations for external pressure 33.33 psi @ 150.00 °F Limits of reinforcement per UG-40 Parallel to the vessel wall: d = 1.8002 in Normal to the vessel wall outside: 2.5*(tn - Cn) + te = 0.3625 in Nozzle required thickness per UG-28 trn = 0.0140 in From UG-37(d)(1) required thickness tr = 0.1875 in This opening does not require reinforcement per UG-36(c)(3)(a) UW-16(d) Weld Check tmin = lesser of 0.75 or tn or t = 0.1450 in t1(min) or t2(min) = lesser of 0.25 or 0.7*tmin = 0.1015 in t1(actual) = 0.7*Leg = 0.7*0.187 = 0.1309 in The weld size t1 is satisfactory. t2(actual) = 0.125 in The weld size t2 is satisfactory. t1 + t2 = 0.2559 >= 1.25*tmin The combined weld sizes for t1 and t2 are satisfactory. UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a): Wall thickness per UG-45(b)(2): Wall thickness per UG-16(b): tr1 = 0.0140 in tr2 = 0.0300 in tr3 = 0.0625 in

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Nozzle #3 (N3)

Standard wall pipe per UG-45(b)(4): tr4 = 0.1269 in The greater of tr2 or tr3: tr5 = 0.0625 in The lesser of tr4 or tr5: tr6 = 0.0625 in

Required per UG-45 is the larger of tr1 or tr6 = 0.0625 in Available nozzle wall thickness new, tn = 0.8750*0.1450 = 0.1269 in The nozzle neck thickness is adequate. External Pressure, (Corroded & at 150.00°F) UG-28(c) L/Do = 6.3828/1.9000 = 3.3594 Do/t = 1.9000/0.013962 = 136.0829 From table G: A = 0.000237 From table CS-2: B = 3402.0903 Pa = 4*B/(3*(Do/t)) = 4*3402.0903/(3*(1.9000/0.013962)) = 33.3335 psi Design thickness for external pressure Pa = 33.3335 psi = t + Corrosion = 0.013962 + 0.0000 = 0.0140"

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Nozzle #4 (N4)

Nozzle #4 (N4)

ASME Section VIII Division 1, 2001 Edition, A03 Addenda

tw(lower) = 0.1313 in Leg41 = 0.1875 in

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

Located on: Cylinder #1 Liquid static head included: 0 psi Nozzle material specification: SA-106 B Smls pipe (ASME II-D p. 10, ln. 15) Nozzle longitudinal joint efficiency: 1.00 Nozzle description: 6" Sch 40 (Std) Flange description: 6 inch 150# WN A105 Bolt Material: SA-193 B7 Bolt <= 2 1/2 Flange rated MDMT: -55.00 °F (UCS-66(b)(1)(b)) Liquid static head on flange: 0 psi ASME B16.5 flange rating MAWP: 272.50 psi @ 150.00°F ASME B16.5 flange rating MAP: 285.00 psi @ 70.00°F ASME B16.5 flange hydro test: 450.00 psi @ 70.00°F Nozzle orientation: 0 ° Local vessel minimum thickness: 0.1875 in Nozzle center line offset to datum line: 22.0000 in End of nozzle to shell center: 24.0000 in Nozzle inside diameter, new: 6.0650 in Nozzle nominal wall thickness: 0.2800 in Nozzle corrosion allowance: 0.0000 in Projection available outside vessel, Lpr: 6.0000 in

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Nozzle #4 (N4)

Reinforcement Calculations for Internal Pressure Available reinforcement per UG-37 governs the MAWP of this nozzle. UG-37 Area Calculation Summary (in2)

For P = 124.70 psi @ 150.00 °F The opening is adequately reinforced A A A1 required available A2 A3 A5 A welds

UG-45 Nozzle Wall Thickness Summary (in)

The nozzle passes UG-45 treq tmin

0.6881

0.6888

0.4521 0.2066 --

--

0.0301 0.1119

0.2450

Weld Failure Path Analysis Summary (lbf)

All failure paths are stronger than the applicable weld loads Weld load Weld load Path 1-1 W1-1 W strength Weld load Path 2-2 W2-2 strength

5,442.81 4,734.00 49,753.70 6,529.50 36,563.98 UW-16 Weld Sizing Summary

Weld description Nozzle to shell fillet (Leg41) Required weld Actual weld Status throat size (in) throat size (in)

0.1312

0.1312 0.1313

weld size is adequate weld size is adequate

Nozzle to shell groove (Lower) 0.1313

Calculations for internal pressure 124.70 psi @ 150.00 °F Fig UCS-66.2 general note (1) applies. Nozzle impact test exemption temperature from Fig UCS-66 Curve B = -20 °F Fig UCS-66.1 MDMT reduction = 65.7 °F, (coincident ratio = 0.47904) Rated MDMT is governed by UCS-66(b)(2). Nozzle UCS-66 governing thk: 0.1875 in Nozzle rated MDMT: -55.00 °F Limits of reinforcement per UG-40 Parallel to the vessel wall: d = 6.0650 in

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Nozzle #4 (N4)

Normal to the vessel wall outside: 2.5*(t - C) = 0.4688 in Nozzle required thickness per UG-27(c)(1) trn = P*Rn/(Sn*E - 0.6*P) = 124.6986*3.0325/(17,100.00*1 - 0.6*124.6986) = 0.0222 in Required thickness tr from UG-37(a) tr = P*Ro/(S*E + 0.4*P) = 124.6986*18/(20,000.00*1 + 0.4*124.6986) = 0.1120 in Area required per UG-37(c) Allowable stresses: Sn = 17,100.00, Sv = 20,000.00 psi fr1 = lesser of 1 or Sn/Sv = 0.855 fr2 = lesser of 1 or Sn/Sv = 0.855 A = d*tr*F + 2*tn*tr*F*(1 - fr1) = 6.065*0.11195*1 + 2*0.28*0.11195*1*(1 - 0.855) = 0.6881 in2 Area available from FIG. UG-37.1 A1 = larger of the following= 0.4521 in2 = d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 6.065*(1*0.1875 - 1*0.11195) - 2*0.28*(1*0.1875 - 1*0.11195)*(1 - 0.855) = 0.4521 in2 = 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 2*(0.1875 + 0.28)*(1*0.1875 - 1*0.11195) - 2*0.28*(1*0.1875 - 1*0.11195)*(1 - 0.855) = 0.0645 in2 A2 = smaller of the following= 0.2066 in2 = 5*(tn - trn)*fr2*t = 5*(0.28 - 0.0222)*0.855*0.1875 = 0.2066 in2

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Nozzle #4 (N4)

= 5*(tn - trn)*fr2*tn = 5*(0.28 - 0.0222)*0.855*0.28 = 0.3086 in2 A41 = Leg2*fr2 = 0.18752*0.855 =0.0301 in2 Area = A1 + A2 + A41 = 0.4521 + 0.2066 + 0.0301 = 0.6888 in2 As Area >= A the reinforcement is adequate. UW-16(d) Weld Check tmin = lesser of 0.75 or tn or t = 0.1875 in t1(min) or t2(min) = lesser of 0.25 or 0.7*tmin = 0.1312 in t1(actual) = 0.7*Leg = 0.7*0.1875 = 0.1312 in The weld size t1 is satisfactory. t2(actual) = 0.1312 in The weld size t2 is satisfactory. t1 + t2 = 0.26245 >= 1.25*tmin The combined weld sizes for t1 and t2 are satisfactory. UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a): Wall thickness per UG-45(b)(1): Wall thickness per UG-16(b): tr1 = 0.0222 in (E =1) tr2 = 0.1119 in tr3 = 0.0625 in

Standard wall pipe per UG-45(b)(4): tr4 = 0.2450 in The greater of tr2 or tr3: tr5 = 0.1119 in The lesser of tr4 or tr5: tr6 = 0.1119 in

Required per UG-45 is the larger of tr1 or tr6 = 0.1119 in Available nozzle wall thickness new, tn = 0.8750*0.2800 = 0.2450 in The nozzle neck thickness is adequate.

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Nozzle #4 (N4)

Allowable stresses in joints UG-45(c) and UW-15(c) Groove weld in tension: 0.74*20,000.00 = 14,800.00 psi Nozzle wall in shear: 0.7*17,100.00 = 11,970.00 psi Inner fillet weld in shear: 0.49*17,100.00 = 8,379.00 psi Strength of welded joints: (1) Inner fillet weld in shear (/2)*Nozzle OD*Leg*Si = (/2)*6.625*0.1875*8,379.00 = 16,349.30 lbf (3) Nozzle wall in shear (/2)*Mean nozzle dia*tn*Sn = (/2)*6.345*0.28*11,970.00 = 33,404.40 lbf (4) Groove weld in tension (/2)*Nozzle OD*tw*Sg = (/2)*6.625*0.13125*14,800.00 = 20,214.68 lbf Loading on welds per UG-41(b)(1) W = (A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv = (0.6880671 - 0.4521 + 2*0.28*0.855*(1*0.1875 - 1*0.11195))*20,000.00 = 5,442.81 lbf W1-1 = (A2 + A5 + A41 + A42)*Sv = (0.2066 + 0 + 0.0301 + 0)*20,000.00 = 4,734.00 lbf W2-2 = (A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv = (0.2066 + 0 + 0.0301 + 0 + 2*0.28*0.1875*0.855)*20,000.00 = 6,529.50 lbf Load for path 1-1 lesser of W or W1-1 = 4,734.00 lbf Path 1-1 through (1) & (3) = 16,349.30 + 33,404.40 = 49,753.70 lbf Path 1-1 is stronger than W1-1 so it is acceptable per UG-41(b)(1). Load for path 2-2 lesser of W or W2-2 = 5,442.81 lbf Path 2-2 through (1), (4) = 16,349.30 + 20,214.68 = 36,563.98 lbf Path 2-2 is stronger than W so it is acceptable per UG-41(b)(2). Reinforcement Calculations for MAP

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Nozzle #4 (N4)

Available reinforcement per UG-37 governs the MAP of this nozzle. UG-37 Area Calculation Summary (in2)

For P = 124.70 psi @ 70.00 °F The opening is adequately reinforced A A A1 required available A2 A3 A5 A welds

UG-45 Nozzle Wall Thickness Summary (in)

The nozzle passes UG-45 treq tmin

0.6881

0.6888

0.4521 0.2066 --

--

0.0301 0.1119

0.2450

Weld Failure Path Analysis Summary (lbf)

All failure paths are stronger than the applicable weld loads Weld load Weld load Path 1-1 W1-1 W strength Weld load Path 2-2 W2-2 strength

5,442.81 4,734.00 49,753.70 6,529.50 36,563.98 UW-16 Weld Sizing Summary

Weld description Nozzle to shell fillet (Leg41) Required weld Actual weld Status throat size (in) throat size (in)

0.1312

0.1312 0.1313

weld size is adequate weld size is adequate

Nozzle to shell groove (Lower) 0.1313

Calculations for internal pressure 124.70 psi @ 70.00 °F Limits of reinforcement per UG-40 Parallel to the vessel wall: d = 6.0650 in Normal to the vessel wall outside: 2.5*(t - C) = 0.4688 in Nozzle required thickness per UG-27(c)(1) trn = P*Rn/(Sn*E - 0.6*P) = 124.6986*3.0325/(17,100.00*1 - 0.6*124.6986) = 0.0222 in Required thickness tr from UG-37(a)

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Nozzle #4 (N4)

tr = P*Ro/(S*E + 0.4*P) = 124.6986*18/(20,000.00*1 + 0.4*124.6986) = 0.1120 in Area required per UG-37(c) Allowable stresses: Sn = 17,100.00, Sv = 20,000.00 psi fr1 = lesser of 1 or Sn/Sv = 0.855 fr2 = lesser of 1 or Sn/Sv = 0.855 A = d*tr*F + 2*tn*tr*F*(1 - fr1) = 6.065*0.11195*1 + 2*0.28*0.11195*1*(1 - 0.855) = 0.6881 in2 Area available from FIG. UG-37.1 A1 = larger of the following= 0.4521 in2 = d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 6.065*(1*0.1875 - 1*0.11195) - 2*0.28*(1*0.1875 - 1*0.11195)*(1 - 0.855) = 0.4521 in2 = 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 2*(0.1875 + 0.28)*(1*0.1875 - 1*0.11195) - 2*0.28*(1*0.1875 - 1*0.11195)*(1 - 0.855) = 0.0645 in2 A2 = smaller of the following= 0.2066 in2 = 5*(tn - trn)*fr2*t = 5*(0.28 - 0.0222)*0.855*0.1875 = 0.2066 in2 = 5*(tn - trn)*fr2*tn = 5*(0.28 - 0.0222)*0.855*0.28 = 0.3086 in2 A41 = Leg2*fr2 = 0.18752*0.855 =0.0301 in2 Area = A1 + A2 + A41

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Nozzle #4 (N4)

= 0.4521 + 0.2066 + 0.0301 = 0.6888 in2 As Area >= A the reinforcement is adequate. UW-16(d) Weld Check tmin = lesser of 0.75 or tn or t = 0.1875 in t1(min) or t2(min) = lesser of 0.25 or 0.7*tmin = 0.1312 in t1(actual) = 0.7*Leg = 0.7*0.1875 = 0.1312 in The weld size t1 is satisfactory. t2(actual) = 0.1312 in The weld size t2 is satisfactory. t1 + t2 = 0.26245 >= 1.25*tmin The combined weld sizes for t1 and t2 are satisfactory. UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a): Wall thickness per UG-45(b)(1): Wall thickness per UG-16(b): tr1 = 0.0222 in (E =1) tr2 = 0.1119 in tr3 = 0.0625 in

Standard wall pipe per UG-45(b)(4): tr4 = 0.2450 in The greater of tr2 or tr3: tr5 = 0.1119 in The lesser of tr4 or tr5: tr6 = 0.1119 in

Required per UG-45 is the larger of tr1 or tr6 = 0.1119 in Available nozzle wall thickness new, tn = 0.8750*0.2800 = 0.2450 in The nozzle neck thickness is adequate. Allowable stresses in joints UG-45(c) and UW-15(c) Groove weld in tension: 0.74*20,000.00 = 14,800.00 psi Nozzle wall in shear: 0.7*17,100.00 = 11,970.00 psi Inner fillet weld in shear: 0.49*17,100.00 = 8,379.00 psi Strength of welded joints:

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Nozzle #4 (N4)

(1) Inner fillet weld in shear (/2)*Nozzle OD*Leg*Si = (/2)*6.625*0.1875*8,379.00 = 16,349.30 lbf (3) Nozzle wall in shear (/2)*Mean nozzle dia*tn*Sn = (/2)*6.345*0.28*11,970.00 = 33,404.40 lbf (4) Groove weld in tension (/2)*Nozzle OD*tw*Sg = (/2)*6.625*0.13125*14,800.00 = 20,214.68 lbf Loading on welds per UG-41(b)(1) W = (A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv = (0.6880671 - 0.4521 + 2*0.28*0.855*(1*0.1875 - 1*0.11195))*20,000.00 = 5,442.81 lbf W1-1 = (A2 + A5 + A41 + A42)*Sv = (0.2066 + 0 + 0.0301 + 0)*20,000.00 = 4,734.00 lbf W2-2 = (A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv = (0.2066 + 0 + 0.0301 + 0 + 2*0.28*0.1875*0.855)*20,000.00 = 6,529.50 lbf Load for path 1-1 lesser of W or W1-1 = 4,734.00 lbf Path 1-1 through (1) & (3) = 16,349.30 + 33,404.40 = 49,753.70 lbf Path 1-1 is stronger than W1-1 so it is acceptable per UG-41(b)(1). Load for path 2-2 lesser of W or W2-2 = 5,442.81 lbf Path 2-2 through (1), (4) = 16,349.30 + 20,214.68 = 36,563.98 lbf Path 2-2 is stronger than W so it is acceptable per UG-41(b)(2). Reinforcement Calculations for External Pressure UG-37 Area Calculation Summary (in2)

For Pe = 18.93 psi @ 150.00 °F The opening is adequately reinforced A A A1 required available A2 A3 A5 A welds

UG-45 Nozzle Wall Thickness Summary (in)

The nozzle passes UG-45 treq tmin

0.4608

0.4609

0.2247 0.2061 --

--

0.0301 0.0625

0.2450

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Nozzle #4 (N4)

Weld Failure Path Analysis Summary Weld strength calculations are not required for external pressure UW-16 Weld Sizing Summary

Weld description Nozzle to shell fillet (Leg41) Required weld Actual weld Status throat size (in) throat size (in)

0.1312

0.1312 0.1313

weld size is adequate weld size is adequate

Nozzle to shell groove (Lower) 0.1313

Calculations for external pressure 18.93 psi @ 150.00 °F Limits of reinforcement per UG-40 Parallel to the vessel wall: d = 6.0650 in Normal to the vessel wall outside: 2.5*(t - C) = 0.4688 in Nozzle required thickness per UG-28 trn = 0.0229 in From UG-37(d)(1) required thickness tr = 0.1500 in Area required per UG-37(d)(1) Allowable stresses: Sn = 17,100.00, Sv = 20,000.00 psi fr1 = lesser of 1 or Sn/Sv = 0.855 fr2 = lesser of 1 or Sn/Sv = 0.855 A = 0.5*(d*tr*F + 2*tn*tr*F*(1 - fr1)) = 0.5*(6.065*0.14995*1 + 2*0.28*0.14995*1*(1 - 0.855)) = 0.4608 in2 Area available from FIG. UG-37.1 A1 = larger of the following= 0.2247 in2 = d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1)

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Nozzle #4 (N4)

= 6.065*(1*0.1875 - 1*0.14995) - 2*0.28*(1*0.1875 - 1*0.14995)*(1 - 0.855) = 0.2247 in2 = 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1) = 2*(0.1875 + 0.28)*(1*0.1875 - 1*0.14995) - 2*0.28*(1*0.1875 - 1*0.14995)*(1 - 0.855) = 0.0321 in2 A2 = smaller of the following= 0.2061 in2 = 5*(tn - trn)*fr2*t = 5*(0.28 - 2.290549E-02)*0.855*0.1875 = 0.2061 in2 = 5*(tn - trn)*fr2*tn = 5*(0.28 - 2.290549E-02)*0.855*0.28 = 0.3077 in2 A41 = Leg2*fr2 = 0.18752*0.855 =0.0301 in2 Area = A1 + A2 + A41 = 0.2247 + 0.2061 + 0.0301 = 0.4609 in2 As Area >= A the reinforcement is adequate. UW-16(d) Weld Check tmin = lesser of 0.75 or tn or t = 0.1875 in t1(min) or t2(min) = lesser of 0.25 or 0.7*tmin = 0.1312 in t1(actual) = 0.7*Leg = 0.7*0.1875 = 0.1312 in The weld size t1 is satisfactory. t2(actual) = 0.1312 in The weld size t2 is satisfactory. t1 + t2 = 0.26245 >= 1.25*tmin The combined weld sizes for t1 and t2 are satisfactory. UG-45 Nozzle Neck Thickness Check

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Nozzle #4 (N4)

Wall thickness per UG-45(a): Wall thickness per UG-45(b)(2): Wall thickness per UG-16(b):

tr1 = 0.0229 in tr2 = 0.0170 in tr3 = 0.0625 in

Standard wall pipe per UG-45(b)(4): tr4 = 0.2450 in The greater of tr2 or tr3: tr5 = 0.0625 in The lesser of tr4 or tr5: tr6 = 0.0625 in

Required per UG-45 is the larger of tr1 or tr6 = 0.0625 in Available nozzle wall thickness new, tn = 0.8750*0.2800 = 0.2450 in The nozzle neck thickness is adequate. External Pressure, (Corroded & at 150.00°F) UG-28(c) L/Do = 6.3074/6.6250 = 0.9521 Do/t = 6.6250/0.022905 = 289.2320 From table G: A = 0.000286 From table CS-2: B = 4106.4595 Pa = 4*B/(3*(Do/t)) = 4*4106.4595/(3*(6.6250/0.022905)) = 18.9304 psi Design thickness for external pressure Pa = 18.9304 psi = t + Corrosion = 0.022905 + 0.0000 = 0.0229"

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Legs

Legs Leg material: Leg description: Number of legs: N= 4 Overall length: 31.0000 Base to girth seam length: 23.0000 Bolt circle: 42.0000 Anchor bolt size: 0.75 Anchor bolt material: Anchor bolts/leg: 1 Sb = 20,000 Anchor bolt allowable stress: Anchor bolt corrosion allowance: 0.0000 Anchor bolt hole clearance: 0.3750 Base plate width: 6.0000 Base plate length: 6.0000 Base plate thickness: 0.5000 Base plate allowable stress: 36,000 Foundation allowable bearing stress: 750 Effective length coefficient: K = 1.2 Cm = 0.85 Coefficient: Fy = 36,000 Leg yield stress: Leg elastic modulus: Leg to shell fillet weld: Legs braced: Leg Mat'l 2x2x1/8 Equal Angle (Leg in) in in in inch series 8 threaded Bolt Material psi in in in in in (0.0463 in required) psi psi

psi E = 29,600,000 psi in (0.0009 in required) 0.2500 No

Note: The support attachment point is assumed to be 1 in up from the cylinder circumferential seam. Axial Shear Axial Bending Bending Force Ratio Ratio Leg fbx fby end load resisted fa attack H1-1 H1-2 position ° lbf lbf angle ° psi psi psi

0 90 0 180 158.2 0.0 327 851 0 0.0582 0.0599 102.5 130.3 0.0 0.0 212 269 551 701 0 0 0.0375 0.0388 0.0478 0.0493

Loading Governing Condition

Weight operating corroded Moment =

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Legs

83.6 lb-ft

270

130.3

0.0

269

701

0

0.0478 0.0493

Axial Shear Axial Bending Bending Force Ratio Ratio Leg fbx fby end load resisted fa Loading attack H1-1 H1-2 position ° lbf lbf angle ° psi psi psi

Weight empty corroded Moment = 83.6 lb-ft 0 90 0 180 270 158.2 130.3 0.0 0.0 327 269 851 701 0 0 0.0582 0.0599 0.0478 0.0493 102.5 130.3 0.0 0.0 212 269 551 701 0 0 0.0375 0.0388 0.0478 0.0493

Axial Shear Axial Bending Bending Force Ratio Ratio Leg fbx fby end load resisted fa Loading attack H1-1 H1-2 position ° lbf lbf angle ° psi psi psi

Weight vacuum corroded Moment = 83.6 lb-ft 0 90 0 180 270 158.2 130.3 0.0 0.0 327 269 851 701 0 0 0.0582 0.0599 0.0478 0.0493 102.5 130.3 0.0 0.0 212 269 551 701 0 0 0.0375 0.0388 0.0478 0.0493

Leg Calculations (AISC manual ninth edition)

Axial end load, P1 P1 = W/N + 48*Mt/(N*D) = 521.3592/ 4 + 48*83.62269/( 4*36) = 158.2140 lb Allowable axial compressive stress, Fa (AISC chapter E) Local buckling check (AISC 5-99) Qs = 1.34 - 0.00447*(b/t)*Sqr(Fy) = 1.34 - 0.00447*(2/0.125)*Sqr(36) = 0.91088

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Legs

Flexural-torsional buckling (AISC 5-317) Shear center distance wo = 0.683772 ro2 = wo2 + (Iz + Iw)/A = 0.6837722 + (7.658909E-02 + 0.3034036)/0.484 = 1.252653 Torsional constant J = 2.520833E-03 Shear modulus G = 11,396.00 kips/in2 Fej = G*J / (A*ro2) = 11,396.00*2.520833E-03 / (0.484*1.252653) = 47.38277 K*l/rw = 1.2*21/0.7917493 = 31.82826 Few = 2*E/(Kl/rw)2 = 2*29,600.00/(31.82826)2 = 288.3804 H = 1 - (wo2 / ro2) = 1 - (0.6837722 / 1.252653) = 0.6267569 Fe = ((Few + Fej)/(2*H))*(1 - Sqr(1 - (4*Few*Fej*H)/(Few + Fej)2)) = ((288.3804 + 47.38277)/(2*0.6267569))*(1 - Sqr(1 - (4*288.3804*47.38277*0.6267569)/(288.3804 + 47.38277)2)) = 44.37123 Equivalent slenderness ratio Kl/r = *Sqr(E/Fe) = *Sqr(29,600.00/44.37123) = 81.14187 Cc = Sqr(2*2*E/(Fy*Qs)) = Sqr(2*2*29,600,000/(36,000.00*0.91088)) = 133.4839 K*l/r= 1.2*21/0.3977963 = 63.349

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Legs

Fa = 1 * (1 - (Kl/r)2/(2*Cc2))*Fy / (5/3 + 3*(Kl/r)/(8*Cc)-(Kl/r)3/(8*Cc3)) = 1 * (1 - (81.14187)2/(2*133.48392))*36,000.00 / (5/3 + 3*(81.14187)/(8*133.4839)(81.14187)3/(8*133.48393)) = 15,723.57 psi Allowable axial compression and bending (AISC chapter H) Note: r is divided by 1.35 - See AISC 6.1.4, pg. 5-314 F'ex = 1*12*2*E/(23*(Kl/r)2) = 1*12*2*29,600,000/(23*(85.52116)2) = 20,840.00 psi F'ey = 1*12*2*E/(23*(Kl/r)2) = 1*12*2*29,600,000/(23*(42.96815)2) = 82,556.56 psi Fb = 1*0.6*Fy*Qs (local buckling governs) = 19,675.01 psi Compressive axial stress fa = P1/A = 158.214/0.484 = 326.8885 psi Bending stresses fbx = F*Cos()*L/(Ix/Cx) + P1*Ecc/(Ix/Cx) = 0*Cos(0)*21/(7.658909E-02/0.6420397) + 158.214*0.642/(7.658909E-02/0.6420397) = 851.481 psi fby= F*Sin()*L/(Iy/Cy) = 0*Sin(0)*21/(0.3034036/1.4142) = 0 psi AISC equation H1-1 H1-1 = fa/Fa + Cmx*fbx/((1 - fa/F'ex)*Fbx) + Cmy*fby/((1 - fa/F'ey)*Fby) = 326.8885/15,723.57 + 0.85*851.481/((1 - 326.8885/20,840.00)*19,675.01) + 0.85*0/((1 326.8885/82,556.56)*19,675.01) = 0.0581616

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Legs

AISC equation H1-2 H1-2 = fa/(0.6*1*Fy) + fbx/Fbx + fby/Fby = 326.8885/(0.6*1*36,000.00) + 851.481/19,675.01 + 0/19,675.01 = 5.989169E-02 4, 2x2x1/8 Equal Angle legs are adequate. Anchor bolts - Weight operating corroded condition governs Tensile loading per leg (1 bolt per leg) R = 48*M/(N*BC) - W/N = 48*83.62269/(4*42) - 521.3592/4 = -106.4476 lbf There is no net uplift (R is negative). 0.75 inch series 8 threaded bolts are satisfactory. Check the leg to vessel fillet weld, Bednar 10.3, Weight operating corroded governs Note: continuous welding is assumed for all support leg fillet welds. The following leg attachment weld analysis assumes the fillet weld is present on three sides (leg top closure plate is used). Zw = (2*b*d + d2)/3 = (2*2.8284*10 + 102)/3 = 52.18933 Jw = (b + 2*d)3/12 - d2*(b + d)2/(b + 2*d) = (2.8284 + 2*10)3/12 - 102*(2.8284 + 10)2/(2.8284 + 2*10) = 270.5006 E = d2/(b + 2*d) = 102/(2.8284 + 2*10) = 4.380508 Governing weld load fx = Cos(0)*0 = 0 lbf Governing weld load fy = Sin(0)*0 = 0 lbf f1 = P1/Lweld = 158.214/22.8284

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Legs

= 6.930579 lbf/in (VL direct shear) f2= fy*Lleg*0.5*b/Jw = 0*21*0.5*2.8284/270.5006 = 0 lbf/in (VL torsion shear) f3 = fy/Lweld = 0/22.8284 = 0 lbf/in (Vc direct shear) f4 = fy*Lleg*E/Jw = 0*21*4.380508/270.5006 = 0 lbf/in (Vc torsion shear) f5 = fx*Lleg/Zw = 0*21/52.18933 = 0 lbf/in (ML bending) f6 = fx/Lweld = 0/22.8284 = 0 lbf/in (Direct outward radial shear) f = Sqr((f1 + f2)2 + (f3 + f4)2 + (f5 + f6)2) = Sqr((6.930579 + 0)2 + (0 + 0)2 + (0 + 0)2) = 6.930579 lbf/in (Resultant shear load) Required leg to vessel fillet weld leg size (welded both sides + top) tw = f / (0.707*0.55*Sa) = 6.930579 / (0.707*0.55*20,000.00) = 0.0009 in The 0.2500 in leg to vessel attachment fillet weld size is adequate. Base plate thickness check, AISC 3-106 fp = P/(B*N) = 154.232/(6*6) = 4.284222 psi Required base plate thickness is the largest of the following: (0.0463 in)

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Legs

tb = Sqr(0.5*P/Sb) = Sqr(0.5*154.232/36,000.00) = 0.0463 in tb = 0.5*(N - d)*Sqr(3*fp/Sb) = 0.5*(6 - 2)*Sqr(3*4.284222/36,000.00) = 0.0378 in The base plate thickness is adequate.

Check the leg to vessel attachment stresses, WRC-107 (Weight operating corroded governs)

Applied Loads Pr = 0.00 Circumferential moment: Mc = 0.00 Radial load: Circumferential shear: Longitudinal moment: Longitudinal shear: Torsion moment: Internal pressure: Mean shell radius: Local shell thickness: Shell yield stress: Vc = 0.00 ML = 101.57 VL = 158.21 Mt = 0.00 lbf lbf-in lbf lbf-in lbf lbf-in

P = 100.000 psi Rm = 17.9063 in t = 0.1875 in Sy = 35,700.00 psi

Maximum stresses due to the applied loads at the leg edge (includes pressure) Rm/t =95.5 C1 = 1.4142, C2 = 5.6568 in Note: Actual lug C1/C2 < 1/4, C1/C2 = 1/4 used as this is the minimum ratio covered by WRC 107. Local circumferential pressure stress = P*Ri/t = 9,500.00 psi Local longitudinal pressure stress = P*Ri/2t = 4,750.00 psi Maximum combined stress (PL+Pb+Q) = 9,648.00 psi

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Legs

Allowable combined stress (PL+Pb+Q) = +-3*S = +-60,000.00 psi The maximum combined stress (PL+Pb+Q) is within allowable limits. Maximum local primary membrane stress (PL) = 9,532.00 psi Allowable local primary membrane (PL) = +-1.5*S = +-30,000.00 psi The maximum local primary membrane stress (PL) is within allowable limits. Stresses at the leg edge per WRC Bulletin 107 Figure

3C* 4C* 1C 2C-1 3A* 1A 3B* 1B-1

value

4.0903 11.0431 0.0674 0.0360 3.8081 0.0703 7.3137 0.0194

0.2338 0.1895 0.1390 0.1390 0.1254 0.1463 0.1990 0.1621

Au

0 0 0 0 0 0 -32 -116 0 0 0 0 0 0

Al

Bu

0 0 0 0 0 0 32 116 0 0 0 0 0 0

Bl

Cu

0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0

Cl

Du

0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0

Dl

-32 116

32 -116

Pressure stress* Total circumferential stress

9,500 9,500 9,500 9,500 9,500 9,500 9,500 9,500 9,352 9,584 9,648 9,416 9,500 9,500 9,500 9,500

Primary membrane circumferential stress* 9,468 9,468 9,532 9,532 9,500 9,500 9,500 9,500 3C* 4C* 1C-1 2C 4A* 2A 4B* 2B-1 5.6148 9.6078 0.0432 0.0342 7.0586 0.0281 3.4274 0.0177 0.1895 0.2338 0.1974 0.1974 0.1254 0.1837 0.1990 0.2242 0 0 0 0 0 0 -30 -76 0 0 0 0 0 0 -30 76 0 0 0 0 0 0 30 76 0 0 0 0 0 0 30 -76 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0

Pressure stress* Total longitudinal stress

4,750 4,750 4,750 4,750 4,750 4,750 4,750 4,750 4,644 4,796 4,856 4,704 4,750 4,750 4,750 4,750

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Legs

Primary membrane longitudinal stress* Shear from Mt Circ shear from Vc Long shear from VL Total Shear stress Combined stress (PL+Pb+Q)

4,720 4,720 4,780 4,780 4,750 4,750 4,750 4,750 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 -37 -37 0 0 -37 -37 0 0 37 37 0 0 37 37

9,352 9,584 9,648 9,416 9,500 9,500 9,500 9,500

Note: * denotes primary stress.

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