key design engineering test pressure psi test liquid ... l stresses at nozzle openings have been...

Key Design Engineering

194-55 Northfield Dr. E

Waterloo, ON N2K 3T6

Canada

COMPRESS Pressure Vessel Design Calculations

Item: Split Stream DearatorVessel No: Sample Vessel 2Customer: Sample Project

Contract: KEY-026Designer: Michael Rodgers

Date: February 16, 2011

Hydrostatic Test

Shop test pressure determination for Chamber bounded by F&D Head #1 and Bolted Cover #1 based onMAWP per UG-99(b)

Shop hydrostatic test gauge pressure is 195 psi at 70 °F (the chamber MAWP = 150 psi)

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

IdentifierLocal testpressure

psi

Test liquidstatic head

psi

UG-99stressratio

UG-99pressure

factor

Stressduring test

psi

Allowabletest stress

psi

Stressexcessive?

Cylinder #1 195.778 0.778 1.0256 1.30 9,299 27,000 No

Straight Flange on F&D Head #1 195.781 0.781 1.0256 1.30 13,998 27,000 No

F&D Head #1 195.781 0.781 1.0256 1.30 14,096 27,000 No

Bolted Cover #1 195.778 0.778 1.0256 1.30 11,104 40,500 No

Flange #1 195.785 0.785 1.0256 1.30 16,982 40,500 No

Copy of Nozzle #1 (N2) (1) 195.921 0.921 1 1.30 21,170 40,500 No

Nozzle #1 (N1) 195.308 0.308 1.0256 1.30 21,103 40,500 No

Nozzle #3 (N3) 195.318 0.318 1 1.30 9,180 40,500 No

Notes:(1) Copy of Nozzle #1 (N2) 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) 1.5*0.9*Sy used as the basis for the maximum local primary membrane stress at the nozzle intersection PL.(4) The zero degree angular position is assumed to be up, and the test liquid height is assumed to the top-mostflange.

The field test condition has not been investigated for the Chamber bounded by F&D Head #1 and Bolted Cover #1.

The test temperature of 70 °F is warmer than the minimum recommended temperature of -25 °F so the brittle fractureprovision of UG-99(h) has been met.

1/78

Table Of ContentsHydrostatic Test1.

Deficiencies Summary2.

Long Seam Summary3.

Settings Summary4.

Pressure Summary5.

Nozzle Summary6.

Nozzle Schedule7.

Thickness Summary8.

F&D Head #19.

Bolted Cover #110.

Cylinder #111.

Legs #112.

Flange #113.

Nozzle #1 (N1)14.

Copy of Nozzle #1 (N2)15.

Nozzle #3 (N3)16.

Straight Flange on F&D Head #117.

Weight Summary18.

2/78

Deficiencies Summary

No deficiencies found.

3/78

Long Seam Summary

Shell Long SeamAngles

Component Seam 1

Cylinder #1 315°

Shell Plate Lengths

Component StartingAngle Plate 1

Cylinder #1 315° 55.9596"

*North is located at 0°*Plate Lengths use the circumfrence of the vessel based on the mid diameter of the components

4/78

Shell Rollout

5/78

Settings Summary

COMPRESS Build 7110

Units: U.S. Customary

Datum Line Location: 0.00" from bottom seam

Design

ASME Section VIII Division 1, 2010 Edition

Design or Rating: Get Thickness from PressureMinimum thickness: 0.0625" per UG-16(b)Design for cold shut down only: NoDesign for lethal service (full radiography required): NoDesign nozzles for: Design P, find nozzle MAWP and MAPCorrosion weight loss: 100% of theoretical lossUG-23 Stress Increase: 1.20Skirt/legs stress increase: 1.0Minimum nozzle projection: 0.01"Juncture calculations for α > 30 only: YesPreheat P-No 1 Materials > 1.25&#34 and <= 1.50" thick: NoUG-37(a) shell tr calculation considers longitudinal stress: NoButt welds are tapered per Figure UCS-66.3(a).

Hydro/Pneumatic Test

Shop Hydrotest Pressure: 1.3 times vesselMAWP

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

Required Marking - UG-116

UG-116(e) Radiography: RT4UG-116(f) Postweld heat treatment: None

Code Cases\Interpretations

Use Code Case 2547: NoApply interpretation VIII-1-83-66: NoApply interpretation VIII-1-86-175: YesApply interpretation VIII-1-83-115: NoApply interpretation VIII-1-01-37: YesNo UCS-66.1 MDMT reduction: NoNo UCS-68(c) MDMT reduction: NoDisallow UG-20(f) exemptions: No

6/78

UG-22 Loadings

UG-22(a) Internal or External Design Pressure : YesUG-22(b) Weight of the vessel and normal contents under operating or test conditions: YesUG-22(c) Superimposed static reactions from weight of attached equipment (external loads): NoUG-22(d)(2) Vessel supports such as lugs, rings, skirts, saddles and legs: YesUG-22(f) Wind reactions: NoUG-22(f) Seismic reactions: NoUG-22(j) Test pressure and coincident static head acting during the test: YesNote: UG-22(b),(c) and (f) loads only considered when supports are present.

7/78

Pressure Summary

Pressure Summary for Chamber bounded by F&D Head #1 and Bolted Cover #1

IdentifierP

Design( psi)

T

Design( °F)

MAWP( psi)

MAP( psi)

MAEP( psi)

Te

external( °F)

MDMT( °F)

MDMTExemption

ImpactTested

Bolted Cover #1 150 250 343.82 352.63 497.66 250 -320 Note 1 No

Cylinder #1 150 250 266.28 273.11 93.73 250 -320 Note 1 No

Straight Flange on F&D Head #1 150 250 231.49 237.43 46.41 250 -320 Note 1 No

F&D Head #1 150 250 177.2 181.75 50.44 250 -320 Note 2 No

Legs #1 150 250 150 N/A N/A N/A N/A N/A N/A

Flange #1 150 250 163.54 169.84 488.49 250 -55 Note 3 No

Nozzle #1 (N1) 150 250 245 257.44 68.55 250 -55 Note 4 No

Copy of Nozzle #1 (N2) 150 250 242.26 246.89 66.07 250 -55 Note 5 No

Nozzle #3 (N3) 150 250 409.67 420.17 93.73 250 -55 Note 5 No

Chamber design MDMT is -20 °FChamber rated MDMT is -55 °F @ 150 psiChamber MAWP was used in the MDMT determination

Chamber MAWP hot & corroded is 150 psi @ 250 °F

Chamber MAP cold & new is 169.84 psi @ 70 °F

Chamber MAEP is 46.41 psi @ 250 °FVacuum rings did not govern the external pressure rating.

Notes for MDMT Rating:

Note # Exemption Details

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

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

3. Flange Rated MDMT per UHA-51(d)(1)(a) = -320 °F Bolts rated MDMT per Fig UCS-66 note (c) = -55 °F

4. Flange rating governs: UCS-66(b)(1)(b)

5.Nozzle impact test exemption temperature from Fig UCS-66 Curve B = -20 °FFig UCS-66.1 MDMT reduction = 130.8 °F, (coincident ratio = 0.35893)Rated MDMT is governed by UCS-66(b)(2)

UCS-66 governing thickness = 0.1875 in.

Design notes are available on the Settings Summary page.

8/78

Nozzle Summary

Nozzlemark

OD(in)

tn

(in)Req t

n(in)

A1? A2?Shell Reinforcement

Pad Corr(in)

Aa/A

r(%)

Nom t(in)

Design t(in)

User t(in)

Width(in)

tpad(in)

N1 6.625 0.28 0.1318 Yes Yes 0.1875 0.1528 N/A N/A 0 100.0

N2 6.625 0.28 0.1272 Yes Yes 0.1875 0.1113 N/A N/A 0 100.0

N3 1.75 0.2175 0.0625 Yes Yes 0.1875 N/A N/A N/A 0 Exempt

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

9/78

Nozzle Schedule

Nozzlemark

Service SizeMaterials

Nozzle Impact Norm FineGrain Pad Impact Norm Fine

Grain Flange

N1 Nozzle #1 NPS 6 Sch 40S (Std) SA-312 TP304 Wld &smls pipe No No No N/A N/A N/A N/A

WN A105Class150

N2 Copy of Nozzle#1 NPS 6 Sch 40 (Std) SA-106 B Smls pipe No No No N/A N/A N/A N/A

WN A105Class300

N3 Nozzle #3 NPS 1 Class 3000 -threaded SA-105 No No No N/A N/A N/A N/A N/A

10/78

Thickness Summary

ComponentIdentifier

Material Diameter(in)

Length(in)

Nominal t(in)

Design t(in)

Total Corrosion(in)

JointE

Load

Bolted Cover #1 SA-240 304 21 OD 1.75 1.75* 1.1559 0 1.00 Internal

Cylinder #1 SA-240 304 18 OD 32 0.1875 0.1061 0 0.65 Internal

Straight Flange on F&D Head #1 SA-240 304 18 OD 2 0.125 0.0812 0 0.85 Internal

F&D Head #1 SA-240 304 18 OD 4.8285 0.125* 0.106 0 0.85 Internal

Nominal t: Vessel wall nominal thickness

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

Joint E: Longitudinal seam joint efficiency

* Head minimum thickness after forming

Load

internal: Circumferential stress due to internal pressure governs

external: External pressure governs

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

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

11/78

F&D Head #1

ASME Section VIII, Division 1, 2010 Edition

Component: F&D HeadMaterial Specification: SA-240 304 (II-D p.86, ln. 25)Material Rated MDMT per UHA-51(d)(1)(a) = -320 °F

Internal design pressure: P = 150 psi @ 250 °FExternal design pressure: Pe = 15 psi @ 250 °F

Static liquid head:

Ps= 0 psi (SG=1, Hs=0" Operating head)Pth= 0.7806 psi (SG=1, Hs=21.6259" Horizontal test head)

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

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

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

Radiography: Category A joints - Spot UW-11(b) Type 1 Head to shell seam - UserDefined (E = 0.5)

Estimated weight*: new = 17.5 lb corr = 17.5 lbCapacity*: new = 5.7 US gal corr = 5.7 US gal* includes straight flange

Outer diameter = 18"Crown radius L = 18"Knuckle radius r = 3.75"Minimum head thickness = 0.125"Straight flange length Lsf = 2"Nominal straight flange thickness tsf = 0.125"Results Summary

The governing condition is internal pressure.Minimum thickness per UG-16 = 0.0625" + 0" = 0.0625"Design thickness due to internal pressure (t) = 0.106"Design thickness due to external pressure (te) = 0.0543"Maximum allowable working pressure (MAWP) = 177.2 psiMaximum allowable pressure (MAP) = 181.75 psiMaximum allowable external pressure (MAEP) = 50.44 psi

Note: Appendix 1-4 footnote 1 used to determine allowable stress.

M (Corroded)

M=1/4*[3 + (L / r)1/2]=1/4*[3 + (18 / 3.75)1/2]=1.297723

12/78

M (New)

M=1/4*[3 + (L / r)1/2]=1/4*[3 + (18 / 3.75)1/2]=1.297723

Design thickness for internal pressure, (Corroded at 250 °F) Appendix 1-4(d)

t = P*Lo*M / (2*S*E + P*(M - 0.2)) + Corrosion= 150*18.125*1.2977 / (2*19,500*0.85 + 150*(1.2977 - 0.2)) + 0= 0.1059"

The head internal pressure design thickness is 0.106".

Maximum allowable working pressure, (Corroded at 250 °F) Appendix 1-4(d)

P = 2*S*E*t / (M*Lo - t*(M - 0.2)) - Ps= 2*19,500*0.85*0.125 / (1.2977*18.125 - 0.125*(1.2977 - 0.2)) - 0= 177.2 psi

The maximum allowable working pressure (MAWP) is 177.2 psi.

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

P = 2*S*E*t / (M*Lo - t*(M - 0.2)) - Ps= 2*20,000*0.85*0.125 / (1.2977*18.125 - 0.125*(1.2977 - 0.2)) - 0= 181.75 psi

The maximum allowable pressure (MAP) is 181.75 psi.

Design thickness for external pressure, (Corroded at 250 °F) UG-33(e)

Equivalent outside spherical radius (Ro)= Outside crown radius= 18.125 in

A = 0.125 / (Ro / t)= 0.125 / (18.125 / 0.054243)= 0.000374

From TableHA-1: B = 5,012.2065

psi

Pa = B / (Ro / t)= 5,012.207 / (18.125 / 0.0542)= 15 psi

t = 0.0542" + Corrosion = 0.0542" + 0" = 0.0542"Check the external pressure per UG-33(a)(1) Appendix 1-4(d)

t = 1.67*Pe*Lo*M / (2*S*E + 1.67*Pe*(M - 0.2)) + Corrosion= 1.67*15*18.125*1.2977 / (2*19,500*1 + 1.67*15*(1.2977 - 0.2)) + 0= 0.0151"

The head external pressure design thickness (te) is 0.0542".

Maximum Allowable External Pressure, (Corroded at 250 °F) UG-33(e)

Equivalent outside spherical radius (Ro)

13/78

= Outside crown radius= 18.125 in

A = 0.125 / (Ro / t)= 0.125 / (18.125 / 0.125)= 0.000862

From TableHA-1: B = 7,313.6406

psi

Pa = B / (Ro / t)= 7,313.641 / (18.125 / 0.125)= 50.4389 psi

Check the Maximum External Pressure, UG-33(a)(1) Appendix 1-4(d)

P = 2*S*E*t / ((M*Lo - t*(M - 0.2))*1.67) - Ps2= 2*19,500*1*0.125 / ((1.2977*18.125 - 0.125*(1.2977 - 0.2))*1.67) - 0= 124.84 psi

The maximum allowable external pressure (MAEP) is 50.44 psi.

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

EFE = (75*t / Rf)*(1 - Rf / Ro)= (75*0.125 / 3.8125)*(1 - 3.8125 / ∞)= 2.459%

14/78

Bolted Cover #1


Component: Bolted CoverAttached to: Flange #1Material specification: SA-240 304 (II-D p. 86, ln. 25)Rated MDMT per UHA-51(d)(1)(a) = -320 °F


Static liquid head:

Pth = 0.79 psi (SG = 1, Hs = 21.7509", Horizontal testhead)

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

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

Material is not produced to Fine Grain PracticePWHT is not performed

Radiography: Category A joints - Seamless No RT

Estimated weight: New = 175.8 lb corr = 175.8 lb

Head diameter, d = 20"Cover thickness, t = 1.75"Design thickness, (at 250 °F) UG-34 (c)(2), flange operating

t = d*Sqr(C*P / (S*E) + 1.9*W*hG / (S*E*d3)) + Corrosion= 20*Sqr(0.3*150 / (19,500*1) + 1.9*56,520*1.5 / (19,500*1*203)) + 0= 1.1559 in

Design thickness, (at 70 °F) UG-34 (c)(2), gasket seating

t = d*Sqr(1.9*W*hG / (S*E*d3)) + Corrosion= 20*Sqr(1.9*68,660*1.5 / (20,000*1*203)) + 0= 0.6994 in

Maximum allowable working pressure, (at 250 °F )

P = (S*E / C)*((t / d)2 - (1.9*W*hG / (S*E*d3))) - Ps= (19,500*1 / 0.3)*((1.75 / 20)2 - (1.9*129,550*1.5 / (19,500*1*203))) - 0= 343.82 psi

Maximum allowable pressure, (At 70 °F )

P = (S*E / C)*((t / d)2 - (1.9*W*hG / (S*E*d3)))= (20,000*1 / 0.3)*((1.75 / 20)2 - (1.9*132,871.7*1.5 / (20,000*1*203)))= 352.63 psi

Design thickness for external pressure, (at 250 °F) U-2(g)

t = d*Sqr(C*Pa / (S*E)) + Corrosion

15/78

= 20*Sqr(0.3*15 / (19,500*1)) + 0= 0.3038 in

Maximum allowable external pressure, (At 250 °F ) U-2(g)

Pa = (S*E / C)*(t / d)2

= (19,500*1 / 0.3)*(1.75 / 20)2

= 497.66 psi

16/78

Cylinder #1


Component: CylinderMaterial specification: SA-240 304 (II-D p. 86, ln. 25)Rated MDMT per UHA-51(d)(1)(a) = -320 °F


Static liquid head:


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



Radiography: Longitudinal joint - None UW-11(c) Type 2Top circumferential joint - N/ABottom circumferential joint - UserDefined

E = 0.5

Estimated weight New = 93.5 lb corr = 93.5 lbCapacity New = 33.8 US gal corr = 33.8 US gal

OD = 18"LengthLc

= 32"

t = 0.1875"

Design thickness, (at 250 °F) Appendix 1-1

t = P*Ro / (S*E + 0.40*P) + Corrosion= 150*9 / (19,500*0.65 + 0.40*150) + 0= 0.1061"

Maximum allowable working pressure, (at 250 °F) Appendix 1-1

P = S*E*t / (Ro - 0.40*t) - Ps= 19,500*0.65*0.1875 / (9 - 0.40*0.1875) - 0= 266.28 psi

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

P = S*E*t / (Ro - 0.40*t)= 20,000*0.65*0.1875 / (9 - 0.40*0.1875)= 273.11 psi

17/78

External Pressure, (Corroded & at 250 °F) UG-28(c)

L /Do

= 36.1178/ 18 = 2.0065

Do/ t = 18 /

0.0791 = 227.4320

From table G: A = 0.000191From tableHA-1: B = 2,558.6055

psi

Pa = 4*B / (3*(Do / t))

= 4*2,558.61 / (3*(18 /0.0791))

= 15 psi

Design thickness for external pressure Pa = 15 psi

ta = t +Corrosion = 0.0791

+ 0 = 0.0791"

Maximum Allowable External Pressure, (Corroded & at 250 °F) UG-28(c)

L /Do

= 36.1178/ 18 = 2.0065

Do/ t = 18 /

0.1875 = 96.0000


psi

Pa = 4*B / (3*(Do / t))

= 4*6,748.78 / (3*(18 /0.1875))

= 93.73 psi

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

EFE = (50*t / Rf)*(1 - Rf / Ro)= (50*0.1875 / 8.9063)*(1 - 8.9063 / ∞)= 1.0526%

External Pressure + Weight Check (Bergman, ASME paper 54-A-104)

Pv = W / (2*π*Rm) + M / (π*Rm2)

= 412.8 / (2*π*8.9063) + 261 / (π*8.90632)= 8.4235 lb/in

α = Pv / (Pe*Do)= 8.4235 / (15*18)= 0.0312

n = 4

m = 1.23 / (L / Do)2

= 1.23 / (36.1178 / 18)2

= 0.3055

18/78

Ratio Pe = (n2 - 1 + m + m*α) / (n2 - 1 + m)= (42 - 1 + 0.3055 + 0.3055*0.0312) / (42 - 1 + 0.3055)= 1.0006

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*π*Rm) + M / (π*Rm2)

= -20.5 / (2*π*8.9063) + 0 / (π*8.90632)= -0.3669 lb/in

α = Pv / (Pe*Do)= -0.3669 / (15*18)= -0.0014

n = 4

m = 1.23 / (L / Do)2

= 1.23 / (36.1178 / 18)2

= 0.3055

Ratio Pe = (n2 - 1 + m + m*α) / (n2 - 1 + m)= (42 - 1 + 0.3055 + 0.3055*-0.0014) / (42 - 1 + 0.3055)= 1.0000

Ratio Pe * Pe ≤ MAEP design cylinder thickness is satisfactory.

Design thickness = 0.1061"

The governing condition is due to internal pressure.

The cylinder thickness of 0.1875" is adequate.

Thickness Required Due to Pressure + External Loads

Condition Pressure P (psi)

Allowable StressBefore UG-23

Stress Increase (psi)

Temperature (°F)

Corrosion C(in) Location Load Req'd Thk Due to

Tension (in)

Req'd Thk Dueto

Compression(in)

St Sc

Operating, Hot & Corroded 150 19,500 10,322 250 0 Top Weight 0.0335 0.0334

Bottom Weight 0.0339 0.0339

Operating, Hot & New 150 19,500 10,322 250 0 Top Weight 0.0335 0.0334


Hot Shut Down, Corroded 0 19,500 10,322 250 0 Top Weight 0.0006 0.0008

Bottom Weight 0 0

Hot Shut Down, New 0 19,500 10,322 250 0 Top Weight 0.0006 0.0008

Bottom Weight 0 0

Empty, Corroded 0 20,000 12,142 70 0 Top Weight 0.0005 0.0007

Bottom Weight 0 0

Empty, New 0 20,000 12,142 70 0 Top Weight 0.0005 0.0007

Bottom Weight 0 0

Vacuum -15 19,500 10,322 250 0 Top Weight 0.007 0.0072

19/78


Hot Shut Down, Corroded,Weight & Eccentric MomentsOnly 0 19,500 10,322 250 0

Top Weight 0.0006 0.0008

Bottom Weight 0 0

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

= 0.125 / (9 / 0.1875)= 0.002604

B = 10,322 psi

S = 19,500 / 1.00 = 19,500 psi

ScHC = min(B, S) = 10,322 psi

Allowable Compressive Stress, Hot and New- ScHN

ScHN = ScHC

= 10,322 psi

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

= 0.125 / (9 / 0.1875)= 0.002604

B = 12,142 psi

S = 20,000 / 1.00 = 20,000 psi

ScCN = min(B, S) = 12,142 psi

Allowable Compressive Stress, Cold and Corroded- ScCC

ScCC = ScCN

= 12,142 psi

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

= 0.125 / (9 / 0.1875)= 0.002604

B = 10,322 psi

S = 19,500 / 1.00 = 19,500 psi

ScVC = min(B, S) = 10,322 psi

Operating, Hot & Corroded, Above Support Point

tp = P*R / (2*St*Ks*Ec + 0.40*|P|) (Pressure)= 150*8.8125 / (2*19,500*1.00*1.00 + 0.40*|150|)= 0.0338"

tm = M / (π*Rm2*St*Ks*Ec) (bending)

= 261 / (π*8.90632*19,500*1.00*1.00)= 0.0001"

20/78

tw = W / (2*π*Rm*St*Ks*Ec) (Weight)= 412.8 / (2*π*8.9063*19,500*1.00*1.00)= 0.0004"

tt = tp + tm - tw(total required,tensile)

= 0.0338 + 0.0001 - (0.0004)= 0.0335"

tc = |tmc + twc - tpc|(total, nettensile)

= |0.0001 + (0.0004) - (0.0338)|= 0.0334"

Maximum allowable working pressure, Longitudinal Stress

P = 2*St*Ks*Ec*(t - tm + tw) / (R - 0.40*(t - tm + tw))= 2*19,500*1.00*1.00*(0.1875 - 0.0001 + (0.0004)) / (8.8125 - 0.40*(0.1875 - 0.0001 + (0.0004)))= 838.37 psi

Operating, Hot & New, Above Support Point



= 261 / (π*8.90632*19,500*1.00*1.00)= 0.0001"

tw = W / (2*π*Rm*St*Ks*Ec) (Weight)= 412.8 / (2*π*8.9063*19,500*1.00*1.00)= 0.0004"


= 0.0338 + 0.0001 - (0.0004)= 0.0335"


= |0.0001 + (0.0004) - (0.0338)|= 0.0334"


P = 2*St*Ks*Ec*(t - tm + tw) / (R - 0.40*(t - tm + tw))= 2*19,500*1.00*1.00*(0.1875 - 0.0001 + (0.0004)) / (8.8125 - 0.40*(0.1875 - 0.0001 + (0.0004)))= 838.37 psi

Hot Shut Down, Corroded, Above Support Point

tp = 0" (Pressure)tm = M / (π*Rm

2*Sc*Ks) (bending)

21/78

= 261 / (π*8.90632*10,322.04*1.00)= 0.0001"

tw = W / (2*π*Rm*Sc*Ks) (Weight)= 412.8 / (2*π*8.9063*10,322.04*1.00)= 0.0007"

tt = |tp + tm - tw| (total, net compressive)= |0 + 0.0001 - (0.0007)|= 0.0006"

tc = tmc + twc - tpc (total required, compressive)= 0.0001 + (0.0007) - (0)= 0.0008"

Hot Shut Down, New, Above Support Point


2*Sc*Ks) (bending)= 261 / (π*8.90632*10,322.04*1.00)= 0.0001"




Empty, Corroded, Above Support Point


2*Sc*Ks) (bending)= 261 / (π*8.90632*12,141.51*1.00)= 0.0001"




22/78

Empty, New, Above Support Point


2*Sc*Ks) (bending)= 261 / (π*8.90632*12,141.51*1.00)= 0.0001"




Vacuum, Above Support Point

tp = P*R / (2*Sc*Ks + 0.40*|P|) (Pressure)= -15*8.8125 / (2*10,322.04*1.00 + 0.40*|15|)= -0.0064"

tm = M / (π*Rm2*Sc*Ks) (bending)

= 261 / (π*8.90632*10,322.04*1.00)= 0.0001"


tt = |tp + tm - tw| (total, net compressive)= |-0.0064 + 0.0001 - (0.0007)|= 0.007"

tc = tmc + twc - tpc (total required, compressive)= 0.0001 + (0.0007) - (-0.0064)= 0.0072"

Maximum Allowable External Pressure, Longitudinal Stress

P = 2*Sc*Ks*(t - tmc - twc) / (R - 0.40*(t - tmc - twc))= 2*10,322.04*1.00*(0.1875 - 0.0001 - 0.0007) / (8.8125 - 0.40*(0.1875 - 0.0001 - 0.0007))= 441.06 psi

Hot Shut Down, Corroded, Weight & Eccentric Moments Only, Above Support Point


2*Sc*Ks) (bending)= 261 / (π*8.90632*10,322.04*1.00)= 0.0001"

23/78




Operating, Hot & Corroded, Below Support Point



= 0 / (π*8.90632*19,500*1.00*1.00)= 0"

tw = W / (2*π*Rm*St*Ks*Ec) (Weight)= -20.5 / (2*π*8.9063*19,500*1.00*1.00)= 0"


= 0.0338 + 0 - (0)= 0.0339"


= |0 + (0) - (0.0338)|= 0.0339"


P = 2*St*Ks*Ec*(t - tm + tw) / (R - 0.40*(t - tm + tw))= 2*19,500*1.00*1.00*(0.1875 - 0 + (0)) / (8.8125 - 0.40*(0.1875 - 0 + (0)))= 836.83 psi

Operating, Hot & New, Below Support Point



= 0 / (π*8.90632*19,500*1.00*1.00)= 0"

tw = W / (2*π*Rm*St*Ks*Ec) (Weight)= -20.5 / (2*π*8.9063*19,500*1.00*1.00)

24/78

= 0"


= 0.0338 + 0 - (0)= 0.0339"


= |0 + (0) - (0.0338)|= 0.0339"



Hot Shut Down, Corroded, Below Support Point


2*St*Ks*Ec) (bending)= 0 / (π*8.90632*19,500*1.00*1.00)= 0"



= 0 + 0 - (0)= 0"


= |0 + (0) - (0)|= 0"

Hot Shut Down, New, Below Support Point


2*St*Ks*Ec) (bending)= 0 / (π*8.90632*19,500*1.00*1.00)= 0"



= 0 + 0 - (0)= 0"

25/78


= |0 + (0) - (0)|= 0"

Empty, Corroded, Below Support Point


2*St*Ks*Ec) (bending)= 0 / (π*8.90632*20,000*1.00*1.00)= 0"



= 0 + 0 - (0)= 0"


= |0 + (0) - (0)|= 0"

Empty, New, Below Support Point


2*St*Ks*Ec) (bending)= 0 / (π*8.90632*20,000*1.00*1.00)= 0"



= 0 + 0 - (0)= 0"


= |0 + (0) - (0)|= 0"

Vacuum, Below Support Point



26/78

= 0 / (π*8.90632*10,322.04*1.00)= 0"

tw = W / (2*π*Rm*Sc*Ks) (Weight)= -20.5 / (2*π*8.9063*10,322.04*1.00)= 0"

tt = |tp + tm - tw| (total, net compressive)= |-0.0064 + 0 - (0)|= 0.0064"

tc = tmc + twc - tpc (total required, compressive)= 0 + (0) - (-0.0064)= 0.0064"


P = 2*Sc*Ks*(t - tmc - twc) / (R - 0.40*(t - tmc - twc))= 2*10,322.04*1.00*(0.1875 - 0 - 0) / (8.8125 - 0.40*(0.1875 - 0 - 0))= 443.09 psi

Hot Shut Down, Corroded, Weight & Eccentric Moments Only, Below Support Point


2*St*Ks*Ec) (bending)= 0 / (π*8.90632*19,500*1.00*1.00)= 0"



= 0 + 0 - (0)= 0"


= |0 + (0) - (0)|= 0"

27/78

Legs #1

Leg material:

Leg description: 2x2x1/8 Equal Angle(Leg in)

Number of legs: N = 4Overall length: 16 inBase to girth seam length: 12.8 inBolt circle: 16 inAnchor bolt size: 0.375 inch series 8 threadedAnchor bolt material:Anchor bolts/leg: 1Anchor bolt allowable stress: Sb = 20,000 psiAnchor bolt corrosion allowance: 0 inAnchor bolt hole clearance: 0.375 inBase plate width: 4 inBase plate length: 4 inBase plate thickness: 0.375 in (0.0517 in required)Base plate allowable stress: 24,000 psiFoundation allowable bearing stress: 1,658 psiEffective length coefficient: K = 1.2Coefficient: Cm = 0.85Leg yield stress: Fy = 36,000 psiLeg elastic modulus: E = 29,000,000 psiLeg to shell fillet weld: 0.25 in (0.0014 in required)Legs braced: No

28/78

Note: The support attachment point is assumed to be 1 in up from the cylinder circumferential seam.

LoadingForceattack

angle °

Legposition °

Axialend load

lbf

Shearresisted

lbf

Axialfa

psi

Bendingfbxpsi

Bendingfbypsi

RatioH1-1

RatioH1-2

GoverningCondition

Weightoperatingcorroded

Moment =21.7 lbf-ft

0

0 97.7 0.0 202 526 0 0.0355 0.0370

90 112.2 0.0 232 604 0 0.0408 0.0425

180 126.7 0.0 262 682 0 0.0461 0.0480

270 112.2 0.0 232 604 0 0.0408 0.0425

LoadingForceattack

angle °

Legposition °

Axialend load

lbf

Shearresisted

lbf

Axialfa

psi

Bendingfbxpsi

Bendingfbypsi

RatioH1-1

RatioH1-2

Weightempty

corroded

Moment =21.7 lbf-ft

0

0 97.7 0.0 202 526 0 0.0355 0.0370

90 112.2 0.0 232 604 0 0.0408 0.0425

180 126.7 0.0 262 682 0 0.0461 0.0480

270 112.2 0.0 232 604 0 0.0408 0.0425

29/78

LoadingForceattack

angle °

Legposition °

Axialend load

lbf

Shearresisted

lbf

Axialfa

psi

Bendingfbxpsi

Bendingfbypsi

RatioH1-1

RatioH1-2

Weightvacuum

corroded

Moment =21.7 lbf-ft

0

0 97.7 0.0 202 526 0 0.0355 0.0370

90 112.2 0.0 232 604 0 0.0408 0.0425

180 126.7 0.0 262 682 0 0.0461 0.0480

270 112.2 0.0 232 604 0 0.0408 0.0425

Leg Calculations (AISC manual ninth edition)

Axial end load, P1 (Based on vessel total bending moment acting at leg attachment elevation)

30/78

P1 = W / N + 48*Mt / (N*D)= 448.89 / 4 + 48*21.7 / ( 4*18)= 126.71 lbf

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

Flexural-torsional buckling (AISC 5-317)

Shear center distance wo = 0.6838ro

2 = wo2 + (Iz + Iw) / A

= 0.68382 + (0.08 + 0.3) / 0.484= 1.25 in2

Torsional constant J = 0 in4

Shear modulus G = 11,165 ksi

Fej = G*J / (A*ro2)

= 11,165,000*0 / (0.484*1.2527)= 46 ksi

K*l / rw = 1.2*10.8 / 0.7917 = 16.3688

Few = π2*E / (K*l / rw)2

= π2*29,000 / (16.3688)2

= 1,068 ksi

H = 1 - (wo2 / ro

2)= 1 - (0.68382 / 1.2527)= 0.6267569

Fe = ((Few + Fej) / (2*H))*(1 - Sqr(1 - (4*Few*Fej*H) / (Few + Fej)2))= ((1,068 + 46) / (2*0.6268))*(1 - Sqr(1 - (4*1,068*46*0.6268) / (1,068 + 46)2))= 46 ksi

Equivalent slenderness ratio

K*l / r = π*Sqr(E / Fe)= π*Sqr(29,000 / 46)= 79.17258

Cc = Sqr(2*π2*E / (Fy*Qs))= Sqr(2*π2*29,000,000 / (36,000*0.9109))= 132.1241

K*l / r = 1.2*10.8 / 0.3978 = 32.5795

Fa = 1 * (1 - (K*l / r)2 / (2*Cc2))*Fy / (5 / 3 + 3*(K*l / r) / (8*Cc)-(K*l / r)3 / (8*Cc

3))= 1 * (1 - (79.1726)2 / (2*132.12412))*36,000 / (5 / 3 + 3*(79.1726) / (8*132.1241)-(79.1726)3 / (8*132.12413))= 15,842 psi

31/78

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*π2*E / (23*(K*l / r)2)

= 1*12*π2*29,000,000 / (23*(43.9823)2)= 77,196 psi

F'ey = 1*12*π2*E / (23*(K*l / r)2)

= 1*12*π2*29,000,000 / (23*(22.0979)2)= 305,808 psi

Fb = 1*0.6*Fy*Qs (local buckling governs)= 1*0.6*36,000*0.91088 (local buckling governs)= 19,675 psi

Compressive axial stress

fa = P1 / A= 126.71 / 0.484= 262 psi

Bending stresses

fbx = F*cos(α)*L / (Ix / Cx) + P1*Ecc / (Ix / Cx)= 0*cos(0)*10.8 / (0.0766 / 0.642) + 126.71*0.642 / (0.0766 / 0.642)= 682 psi

fby= F*sin(α)*L / (Iy / Cy)= 0*sin(0)*10.8 / (0.3 / 1.41)= 0 psi

AISC equation H1-1

H1-1 = fa / Fa + Cmx*fbx / ((1 - fa / F'ex)*Fbx) + Cmy*fby / ((1 - fa / F'

ey)*Fby)= 262 / 15,842 + 0.85*682 / ((1 - 262 / 77,196)*19,675) + 0.85*0 / ((1 - 262 / 305,808)*19,675)= 0.0461

AISC equation H1-2

H1-2 = fa / (0.6*1*Fy) + fbx / Fbx + fby / Fby= 262 / (0.6*1*36,000) + 682 / 19,675 + 0 / 19,675= 0.048

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*21.7 / (4*16) - 448.89 / 4= -95.92 lbfThere is no net uplift (R is negative).

0.375 inch series 8 threaded bolts are satisfactory.

32/78

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 isused).

Zw = (2*b*d + d2) / 3= (2*2.8284*5.2 + 5.22) / 3= 18.8185 in2

Jw = (b + 2*d)3 / 12 - d2*(b + d)2 / (b + 2*d)= (2.8284 + 2*5.2)3 / 12 - 5.22*(2.8284 + 5.2)2 / (2.8284 + 2*5.2)= 61.1517 in3

E = d2 / (b + 2*d)= 5.22 / (2.8284 + 2*5.2)= 2.044087 in

Governing weld load fx = Cos(0)*0 = 0 lbfGoverning weld load fy = Sin(0)*0 = 0 lbf

f1 = P1 / Lweld= 126.71 / 13.2284= 9.58 lbf/in (V

L direct shear)

f2= fy*Lleg*0.5*b / Jw= 0*10.8*0.5*2.8284 / 61.1517= 0 lbf/in (V

L torsion shear)

f3 = fy / Lweld= 0 / 13.2284= 0 lbf/in (V

c direct shear)

f4 = fy*Lleg*E / Jw= 0*10.8*2.0441 / 61.1517= 0 lbf/in (V

c torsion shear)

f5 = (fx*Lleg + P1*Ecc) / Zw= (0*10.8 + 126.71*0.642) / 18.8185= 4.32 lbf/in (M

L bending)

f6 = fx / Lweld= 0 / 13.2284= 0 lbf/in (Direct outward radial shear)

f = Sqr((f1 + f2)2 + (f3 + f4)2 + (f5 + f6)2)= Sqr((9.58 + 0)2 + (0 + 0)2 + (4.32 + 0)2)= 10.51 lbf/in (Resultant shear load)

Required leg to vessel fillet weld leg size (welded both sides + top)

tw = f / (0.707*0.55*Sa)= 10.51 / (0.707*0.55*19,500)= 0.0014 in

The 0.25 in leg to vessel attachment fillet weld size is adequate.

33/78

Base plate thickness check, AISC 3-106

fp = P / (B*N)= 128.52 / (4*4)= 8 psi

Required base plate thickness is the largest of the following: (0.0517 in)

tb = Sqr(0.5*P / Sb)= Sqr(0.5*128.52 / 24,000)= 0.0517 in

tb = 0.5*(N - d)*Sqr(3*fp / Sb)= 0.5*(4 - 2)*Sqr(3*8 / 24,000)= 0.0317 in

The base plate thickness is adequate.

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

Applied Loads

Radial load: Pr = 0 lbfCircumferential moment: Mc = 0 lbf-inCircumferential shear: Vc = 0 lbfLongitudinal moment: ML = 81.35 lbf-inLongitudinal shear: VL = 126.71 lbfTorsion moment: Mt = 0 lbf-inInternal pressure: P = 150 psiMean shell radius: Rm = 8.9063 inLocal shell thickness: t = 0.1875 inShell yield stress: Sy = 23,600 psi

34/78

Maximum stresses due to the applied loads at the leg edge (includes pressure)

Rm / t = 8.9063 / 0.1875 = 47.5

C1 = 1.4142, C2 = 4.1272 in

Local circumferential pressure stress = P*Ri / t =7,050 psi

Local longitudinal pressure stress = P*Ri / (2*t) =3,525 psi

Maximum combined stress (PL+P

b+Q) = 7,165 psi

Allowable combined stress (PL+P

b+Q) = +-3*S = +-58,500 psi

Note: The allowable combined stress (PL+P

b+Q) is based on the strain hardening characteristics of this material.

The maximum combined stress (PL+P

b+Q) is within allowable limits.

Maximum local primary membrane stress (PL) = 7,088 psi

Allowable local primary membrane (PL) = +-1.5*S = +-29,250 psi

The maximum local primary membrane stress (PL) is within allowable limits.

Stresses at the leg edge per WRC Bulletin 107

Figure value β Au Al Bu Bl Cu Cl Du Dl

3C* 1.604 0.3854 0 0 0 0 0 0 0 0

4C* 4.8136 0.3188 0 0 0 0 0 0 0 0

1C 0.0622 0.2427 0 0 0 0 0 0 0 0

2C-1 0.0219 0.2427 0 0 0 0 0 0 0 0

3A* 1.8994 0.2269 0 0 0 0 0 0 0 0

1A 0.0641 0.2687 0 0 0 0 0 0 0 0

3B* 3.0132 0.3243 -38 -38 38 38 0 0 0 0

1B-1 0.0143 0.2901 -77 77 77 -77 0 0 0 0

Pressure stress* 7,050 7,050 7,050 7,050 7,050 7,050 7,050 7,050

Total circumferential stress 6,935 7,089 7,165 7,011 7,050 7,050 7,050 7,050

Primary membranecircumferential stress* 7,012 7,012 7,088 7,088 7,050 7,050 7,050 7,050

3C* 2.1622 0.3188 0 0 0 0 0 0 0 0

4C* 4.0033 0.3854 0 0 0 0 0 0 0 0

1C-1 0.0292 0.3307 0 0 0 0 0 0 0 0

2C 0.03 0.3307 0 0 0 0 0 0 0 0

4A* 4.2003 0.2269 0 0 0 0 0 0 0 0

2A 0.0247 0.3441 0 0 0 0 0 0 0 0

4B* 1.6357 0.3243 -33 -33 33 33 0 0 0 0

2B-1 0.0199 0.3709 -84 84 84 -84 0 0 0 0

Pressure stress* 3,525 3,525 3,525 3,525 3,525 3,525 3,525 3,525

Total longitudinal stress 3,408 3,576 3,642 3,474 3,525 3,525 3,525 3,525

Primary membranelongitudinal stress* 3,492 3,492 3,558 3,558 3,525 3,525 3,525 3,525

Shear from Mt 0 0 0 0 0 0 0 0

35/78

Circ shear from Vc 0 0 0 0 0 0 0 0

Long shear from VL 0 0 0 0 -41 -41 41 41

Total Shear stress 0 0 0 0 -41 -41 41 41

Combined stress (PL+Pb+Q) 6,935 7,089 7,165 7,011 7,050 7,050 7,050 7,050

Note: * denotes primary stress.

36/78

Flange #1

ASME VIII-1, 2010 Edition, Appendix 2 Flange Calculations

Flange is attached to: Cylinder #1 (Top)Flange type: Ring type looseFlange material specification: SA-240 304 (II-D p. 86, ln. 25)

Bolt material specification: SA-193 B7 Bolt <= 2 1/2 (II-D p. 334,ln. 32)

Bolt Description: 0.625 in Series 8 ThreadInternal design pressure, P: 150 psi @ 250 °FRequired flange thickness: tr= 2.5505 inMaximum allowable working pressure,MAWP: 163.54 psi @ 250 °F

Maximum allowable pressure, MAP: 169.84 psi @ 70 °FExternal design pressure, Pe 15 psi @ 250 °FMaximum allowable external pressure,MAEP: 488.49 psi @ 250 °F

Corrosion allowance: Bore = 0 in Flange = 0 inBolt corrosion (root), Cbolt: 0 inDesign MDMT: -20 °F No impact test performedRated MDMT: -55 °F Flange material is normalized

Material is produced to fine grainpracticePWHT is not performed

Estimated weight: New = 70 lb corroded = 70 lb

Flange dimensions, new

flange OD A = 21 inbolt circle C = 23 ingasket OD = 20.5 ingasket ID = 19.5 inflange ID B = 18 inthickness t = 2.625 inbolting = 16- 0.625 in dialower fillet weld h = 0.1875 inupper fillet weld h1 = 0.1875 inlength e = 0.375 ingasket factor m = 2seating stress y = 2,500 psiGasket thickness T = 0.175 in

37/78

Note: this flange is calculated as a loose type.

Flange calculations for Internal Pressure + Weight Only

Longitudinal bending moment on flange

Pm = 16*Mb/(π*G3)= 16*0/(π*203)= 0 psi

Axial load on flange

Pr = -4*F/(π*G2)= -4*175.78/(π*202)= -0.5595 psi

Total design load on flange (used for H - ref. III-1 NC-3658.1)

= P + Ps + Pm + Pr= 150 + 0 + 0 + -0.5595= 150 psi

When the sum of equivalent pressures due to external loads (Pm + Pr) is a negative value, it is conservativelyignored.

The static head of liquid has not been included in the total design load because the vessel is supported below theflange.

Gasket details from facing sketch 1(a) or (b), Column II

Gasket width N = 0.5 in

b0 = N/2 = 0.25 in

Effective gasket seating width, b = b0 = 0.25 in

G = (gasket OD + gasket ID) / 2 = (20.5 + 19.5) / 2 = 20 in

hG = (C - G)/2 = (23 - 20)/2 = 1.5 in

hD = (C - B)/2 = (23 - 18)/2 = 2.5 in

hT = (hD + hG)/2 = (2.5 + 1.5)/2 = 2 in

Hp = 2*b*3.14*G*m*P= 2*0.25*3.14*20*2*150= 9,420 lbf

H = 0.785*G2*P= 0.785*202*150= 47,100 lbf

HD = 0.785*B2*P= 0.785*182*150= 38,151 lbf

38/78

HT = H - HD= 47,100 - 38,151= 8,949 lbf

Wm1 = H + Hp= 47,100 + 9,420= 56,520 lbf

Wm2 = 3.14*b*G*y= 3.14*0.25*20*2,500= 39,250 lbf

Required bolt area, Am = greater of Am1, Am2 = 2.2608 in2

Am1 = Wm1/Sb = 56,520/25,000 = 2.2608 in2

Am2 = Wm2/Sa = 39,250/25,000 = 1.57 in2

Total area for 16- 0.625 in dia bolts, corroded, Ab = 3.232 in2

W = (Am + Ab)*Sa/2= (2.2608 + 3.232)*25,000/2= 68,660 lbf

MD = HD*hD = 38,151*2.5 = 95,377.5 lbf-inMT = HT*hT = 8,949*2 = 17,898 lbf-in

HG = Wm1 - H = 56,520 - 47,100 = 9,420 lbf

MG = HG*hG = 9,420*1.5 = 14,130 lbf-in

Mo = MD + MT + MG = 95,377.5 + 17,898 + 14,130 = 127,405.5 lbf-in

Mg = W*hG = 68,660*1.5 = 102,990 lbf-in

From FIG. 2-7.1, where K = A/B = 21/18 = 1.1667, Y = 12.66625

Stresses at operating conditions - VIII-1, Appendix 2-7

SR = SH = 0

ST = Y*Mo/(t2*B)= 12.6662*127,405.5/(2.6252*18)= 13,011 psi

Allowable stress Sfo = 19,500 psi

ST does not exceed Sfo

Stresses at gasket seating - VIII-1, Appendix 2-7

ST = Y*Mg/(t2*B)= 12.6662*102,990/(2.6252*18)= 10,517 psi

Allowable stress Sfa = 20,000 psi

39/78

ST does not exceed Sfa

Flange rigidity per VIII-1, Appendix 2-14

J = 109.4*Mo/(E*t3*KL*ln(K))= 109.4*127,405.5/(27,250,000*2.6253*0.2*ln(1.1667))= 0.9172246

The flange rigidity index J does not exceed 1; satisfactory.

Flange calculations for External Pressure + Weight Only per VIII-1, Appendix 2-11

Longitudinal bending moment on flange

Pm = 16*Mb/(π*G3)= 16*0/(π*203)= 0 psi

Axial load on flange

Pr = 4*F/(π*G2)= 4*175.78/(π*202)= 0.5595 psi

Total design load on flange (used for H - ref. III-1 NC-3658.1)

= P + Ps + Pm + Pr= 15 + 0 + 0 + 0.5595= 15.5595 psi

The static head of liquid has not been included in the total design load because the vessel is supported below theflange.

Gasket details from facing sketch 1(a) or (b), Column II

Gasket width N = 0.5 in

b0 = N/2 = 0.25 in

Effective gasket seating width, b = b0 = 0.25 in

G = (gasket OD + gasket ID) / 2 = (20.5 + 19.5) / 2 = 20 in

hG = (C - G)/2 = (23 - 20)/2 = 1.5 in

hD = (C - B)/2 = (23 - 18)/2 = 2.5 in

hT = (hD + hG)/2 = (2.5 + 1.5)/2 = 2 in

Hp = 2*b*3.14*G*m*P= 2*0.25*3.14*20*2*15= 942 lbf

H = 0.785*G2*P= 0.785*202*15.5595= 4,885.68 lbf

40/78

HD = 0.785*B2*P= 0.785*182*15= 3,815.1 lbf

HT = H - HD= 4,885.68 - 3,815.1= 1,070.58 lbf

Wm1 = H + Hp= 4,885.68 + 942= 5,827.68 lbf

Wm2 = 3.14*b*G*y= 3.14*0.25*20*2,500= 39,250 lbf

Required bolt area, Am = greater of Am1, Am2 = 1.57 in2

Am1 = 0.785*G2*(Pm - Pr)/Sb = 0/25,000 = 0 in2

Am2 = Wm2/Sa = 39,250/25,000 = 1.57 in2

Total area for 16- 0.625 in dia bolts, corroded, Ab = 3.232 in2

W = (Am2 + Ab)*Sa/2= (1.57 + 3.232)*25,000/2= 60,025 lbf

Mo = HD*(hD - hG) + HT*(hT - hG)= 3,815.1*(2.5 - 1.5) + 1,070.58*(2 - 1.5)= 4,350.4 lbf-in

Mg = W*hG = 60,025*1.5 = 90,037.5 lbf-in

From FIG. 2-7.1, where K = A/B = 21/18 = 1.1667, Y = 12.66625

Stresses at operating conditions - VIII-1, Appendix 2-7

SR = SH = 0

ST = Y*Mo/(t2*B)= 12.6662*4,350.4/(2.6252*18)= 444 psi

Allowable stress Sfo = 19,500 psi

ST does not exceed Sfo

Stresses at gasket seating - VIII-1, Appendix 2-7

ST = Y*Mg/(t2*B)= 12.6662*90,037.5/(2.6252*18)= 9,195 psi

Allowable stress Sfa = 20,000 psi

ST does not exceed Sfa

41/78

Flange rigidity per VIII-1, Appendix 2-14

J = 109.4*Mo/(E*t3*KL*ln(K))= 109.4*90,037.5/(28,300,000*2.6253*0.2*ln(1.1667))= 0.624153

The flange rigidity index J does not exceed 1; satisfactory.

42/78

Nozzle #1 (N1)


tw(lower) = 0.1875 inLeg41 = 0.1875 in

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

Located on: Cylinder #1Liquid static head included: 0 psiNozzle material specification: SA-312 TP304 Wld & smls pipe (II-D p. 86, ln. 36)Nozzle longitudinal joint efficiency: 1Nozzle description: NPS 6 Sch 40S (Std)Flange description: 6 inch Class 150 WN A105Bolt Material: SA-193 B7 Bolt <= 2 1/2 (II-D p. 334, ln. 32)Flange rated MDMT: -55°F(UCS-66(b)(1)(b))Liquid static head on flange: 0 psiASME B16.5 flange rating MAWP: 245 psi @ 250°FASME B16.5 flange rating MAP: 285 psi @ 70°FASME B16.5 flange hydro test: 450 psi @ 70°FGasket Description: Flexitallic Spiral Wound CGI 304 S.S.PWHT performed: NoCircumferential joint radiography: Full UW-11(a) Type 1Nozzle orientation: 45°Local vessel minimum thickness: 0.1875 inNozzle center line offset to datum line: 5 inEnd of nozzle to shell center: 15 inNozzle inside diameter, new: 6.065 inNozzle nominal wall thickness: 0.28 inNozzle corrosion allowance: 0 inProjection available outside vessel, Lpr: 2.5 inProjection available outside vessel to flange face, Lf: 6 in

43/78

Reinforcement Calculations for Internal Pressure

The attached ASME B16.5 flange limits the nozzle MAWP.

UG-37 Area Calculation Summary (in2)For P = 245 psi @ 250 °F

The opening is adequately reinforced

UG-45 NozzleWall

ThicknessSummary (in)The nozzle passes

UG-45

Arequired

Aavailable A1 A2 A3 A5

Awelds treq tmin

0.6824 0.7165 0.4548 0.2265 -- -- 0.0352 0.1125 0.245

UG-41 Weld Failure Path Analysis Summary

The nozzle is exempt from weld strength calculationsper UW-15(b)(1)

UW-16 Weld Sizing Summary

Weld description Required weldthroat size (in)

Actual weldthroat size (in) Status

Nozzle to shell fillet (Leg41) 0.1312 0.1312 weld size is adequate

Calculations for internal pressure 245 psi @ 250 °F

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

Parallel Limit of reinforcement per UG-40

LR = MAX(d, Rn + (tn - Cn) + (t - C))= MAX(6.065, 3.0325 + (0.28 - 0) + (0.1875 - 0))= 6.065 in

Outer Normal Limit of reinforcement per UG-40

LH = MIN(2.5*(t - C), 2.5*(tn - Cn) + te)= MIN(2.5*(0.1875 - 0), 2.5*(0.28 - 0) + 0)= 0.4688 in

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

trn = P*Rn / (Sn*E - 0.6*P)= 245*3.0325 / (19,500*1 - 0.6*245)= 0.0384 in

Required thickness tr from UG-37(a)

tr = P*Ro / (S*E + 0.4*P)= 245*9 / (19,500*1 + 0.4*245)= 0.1125 in

44/78

Area required per UG-37(c)

Allowable stresses: Sn = 19,500, Sv = 19,500 psi

fr1 = lesser of 1 or Sn / Sv = 1


A = d*tr*F + 2*tn*tr*F*(1 - fr1)= 6.065*0.1125*1 + 2*0.28*0.1125*1*(1 - 1)= 0.6824 in2

Area available from FIG. UG-37.1

A1 = larger of the following= 0.4548 in2

= d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1)= 6.065*(1*0.1875 - 1*0.1125) - 2*0.28*(1*0.1875 - 1*0.1125)*(1 - 1)= 0.4548 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*0.1125) - 2*0.28*(1*0.1875 - 1*0.1125)*(1 - 1)= 0.0701 in2

A2 = smaller of the following= 0.2265 in2

= 5*(tn - trn)*fr2*t= 5*(0.28 - 0.0384)*1*0.1875= 0.2265 in2

= 5*(tn - trn)*fr2*tn= 5*(0.28 - 0.0384)*1*0.28= 0.3382 in2

A41 = Leg2*fr2= 0.18752*1= 0.0352 in2

Area = A1 + A2 + A41

= 0.4548 + 0.2265 + 0.0352= 0.7165 in2

As Area >= A the reinforcement is adequate.

45/78

UW-16(c) Weld Check

Fillet weld: tmin = lesser of 0.75 or tn or t = 0.1875 intc(min) = lesser of 0.25 or 0.7*tmin = 0.1312 intc(actual) = 0.7*Leg = 0.7*0.1875 = 0.1313 in

The fillet weld size is satisfactory.

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

UG-45 Nozzle Neck Thickness Check

ta UG-27 = P*R / (S*E - 0.6*P) + Corrosion= 245*3.0325 / (19,500*1 - 0.6*245) + 0= 0.0384 in

ta = max[ ta UG-27 , ta UG-22 ]= max[ 0.0384 , 0 ]= 0.0384 in

tb1 = P*Ro / (S*E + 0.4*P) + Corrosion= 245*9 / (19,500*1 + 0.4*245) + 0= 0.1125 in

tb1 = max[ tb1 , tb UG16 ]= max[ 0.1125 , 0.0625 ]= 0.1125 in

tb = min[ tb3 , tb1 ]= min[ 0.245 , 0.1125 ]= 0.1125 in

tUG-45 = max[ ta , tb ]= max[ 0.0384 , 0.1125 ]= 0.1125 in

46/78

Available nozzle wall thickness new, tn = 0.875*0.28 = 0.245 in

The nozzle neck thickness is adequate.

Reinforcement Calculations for MAP

Available reinforcement per UG-37 governs the MAP of this nozzle.

UG-37 Area Calculation Summary (in2)For P = 257.44 psi @ 70 °F


UG-45 NozzleWall


UG-45

Arequired


Awelds treq tmin

0.699 0.6991 0.4382 0.2257 -- -- 0.0352 0.1153 0.245







Calculations for internal pressure 257.44 psi @ 70 °F

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






trn = P*Rn / (Sn*E - 0.6*P)= 257.4357*3.0325 / (20,000*1 - 0.6*257.4357)= 0.0393 in

47/78


tr = P*Ro / (S*E + 0.4*P)= 257.4357*9 / (20,000*1 + 0.4*257.4357)= 0.1153 in





A = d*tr*F + 2*tn*tr*F*(1 - fr1)= 6.065*0.1153*1 + 2*0.28*0.1153*1*(1 - 1)= 0.699 in2






= 5*(tn - trn)*fr2*t= 5*(0.28 - 0.0393)*1*0.1875= 0.2257 in2

= 5*(tn - trn)*fr2*tn= 5*(0.28 - 0.0393)*1*0.28= 0.337 in2

A41 = Leg2*fr2= 0.18752*1= 0.0352 in2

Area = A1 + A2 + A41

= 0.4382 + 0.2257 + 0.0352

48/78

= 0.6991 in2


UW-16(c) Weld Check





ta UG-27 = P*R / (S*E - 0.6*P) + Corrosion= 257.4357*3.0325 / (20,000*1 - 0.6*257.4357) + 0= 0.0393 in


tb1 = P*Ro / (S*E + 0.4*P) + Corrosion= 257.4357*9 / (20,000*1 + 0.4*257.4357) + 0= 0.1153 in


tb = min[ tb3 , tb1 ]= min[ 0.245 , 0.1153 ]= 0.1153 in


49/78



Reinforcement Calculations for External Pressure

UG-37 Area Calculation Summary (in2)For Pe = 68.55 psi @ 250 °F


UG-45 NozzleWall


UG-45

Arequired


Awelds treq tmin

0.4635 0.4635 0.2103 0.218 -- -- 0.0352 0.0625 0.245


Weld strength calculations are not required for externalpressure





Calculations for external pressure 68.55 psi @ 250 °F





Nozzle required thickness per UG-28 trn = 0.0474 in

From UG-37(d)(1) required thickness tr = 0.1528 in

Area required per UG-37(d)(1)




50/78

A = 0.5*(d*tr*F + 2*tn*tr*F*(1 - fr1))= 0.5*(6.065*0.1528*1 + 2*0.28*0.1528*1*(1 - 1))= 0.4635 in2






= 5*(tn - trn)*fr2*t= 5*(0.28 - 0.0474)*1*0.1875= 0.218 in2

= 5*(tn - trn)*fr2*tn= 5*(0.28 - 0.0474)*1*0.28= 0.3256 in2

A41 = Leg2*fr2= 0.18752*1= 0.0352 in2

Area = A1 + A2 + A41

= 0.2103 + 0.218 + 0.0352= 0.4635 in2


UW-16(c) Weld Check




51/78


ta UG-28 = 0.0474 in




tb = min[ tb3 , tb2 ]= min[ 0.245 , 0.0625 ]= 0.0625 in





L /Do

= 6.6318 /6.625 = 1.0010

Do/ t = 6.625 /

0.0474 = 139.6917


psi

Pa = 4*B / (3*(Do / t))

= 4*7,181.8 / (3*(6.625 /0.0474))

= 68.55 psi

Design thickness for external pressure Pa = 68.55 psi


+ 0 = 0.0474"

52/78

Copy of Nozzle #1 (N2)


tw(lower) = 0.1875 inLeg41 = 0.1875 in


Located on: Cylinder #1Liquid static head included: 0 psiNozzle material specification: SA-106 B Smls pipe (II-D p. 10, ln. 40)Nozzle longitudinal joint efficiency: 1Nozzle description: NPS 6 Sch 40 (Std)Flange description: 6 inch Class 300 WN A105Bolt Material: SA-193 B7 Bolt <= 2 1/2 (II-D p. 334, ln. 32)Flange rated MDMT: -55°F(UCS-66(b)(3): Coincident ratio = 0.2027027)(Flange rated MDMT = -155 °FBolts rated MDMT per Fig UCS-66 note (c) = -55 °F)Liquid static head on flange: 0 psiASME B16.5 flange rating MAWP: 667.5 psi @ 250°FASME B16.5 flange rating MAP: 740 psi @ 70°FASME B16.5 flange hydro test: 1125 psi @ 70°FGasket Description: Flexitallic Spiral Wound CGI 304 S.S.PWHT performed: NoCircumferential joint radiography: Full UW-11(a) Type 1Nozzle orientation: 225°Local vessel minimum thickness: 0.1875 inNozzle center line offset to datum line: 22 inEnd of nozzle to shell center: 15 inNozzle inside diameter, new: 6.065 inNozzle nominal wall thickness: 0.28 inNozzle corrosion allowance: 0 inProjection available outside vessel, Lpr: 2.12 inProjection available outside vessel to flange face, Lf: 6 in

53/78


Available reinforcement per UG-37 governs the MAWP of this nozzle.



UG-45 NozzleWall


UG-45

Arequired


Awelds treq tmin

0.6825 0.6825 0.4571 0.1946 -- -- 0.0308 0.1113 0.245








Fig UCS-66.2 general note (1) applies.

Nozzle impact test exemption temperature from Fig UCS-66 Curve B = -20 °FFig UCS-66.1 MDMT reduction = 130.8 °F, (coincident ratio = 0.35893)Rated MDMT is governed by UCS-66(b)(2).

Nozzle UCS-66 governing thk: 0.1875 inNozzle rated MDMT: -55 °FParallel Limit of reinforcement per UG-40





trn = P*Rn / (Sn*E - 0.6*P)= 242.2648*3.0325 / (17,100*1 - 0.6*242.2648)

54/78

= 0.0433 in


tr = P*Ro / (S*E + 0.4*P)= 242.2648*9 / (19,500*1 + 0.4*242.2648)= 0.1113 in



fr1 = lesser of 1 or Sn / Sv = 0.8769


A = d*tr*F + 2*tn*tr*F*(1 - fr1)= 6.065*0.1113*1 + 2*0.28*0.1113*1*(1 - 0.8769)= 0.6825 in2



= d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1)= 6.065*(1*0.1875 - 1*0.1113) - 2*0.28*(1*0.1875 - 1*0.1113)*(1 - 0.8769)= 0.4571 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*0.1113) - 2*0.28*(1*0.1875 - 1*0.1113)*(1 - 0.8769)= 0.066 in2


= 5*(tn - trn)*fr2*t= 5*(0.28 - 0.0433)*0.8769*0.1875= 0.1946 in2

= 5*(tn - trn)*fr2*tn= 5*(0.28 - 0.0433)*0.8769*0.28= 0.2906 in2

A41 = Leg2*fr2= 0.18752*0.8769= 0.0308 in2

55/78

Area = A1 + A2 + A41

= 0.4571 + 0.1946 + 0.0308= 0.6825 in2


UW-16(c) Weld Check









tb = min[ tb3 , tb1 ]= min[ 0.245 , 0.1113 ]= 0.1113 in


56/78




Available reinforcement per UG-37 governs the MAP of this nozzle.



UG-45 NozzleWall


UG-45

Arequired


Awelds treq tmin

0.6795 0.6796 0.4605 0.189 -- -- 0.0301 0.1106 0.245













trn = P*Rn / (Sn*E - 0.6*P)= 246.8865*3.0325 / (17,100*1 - 0.6*246.8865)= 0.0442 in


tr = P*Ro / (S*E + 0.4*P)= 246.8865*9 / (20,000*1 + 0.4*246.8865)

57/78

= 0.1106 in





A = d*tr*F + 2*tn*tr*F*(1 - fr1)= 6.065*0.1106*1 + 2*0.28*0.1106*1*(1 - 0.855)= 0.6795 in2






= 5*(tn - trn)*fr2*t= 5*(0.28 - 0.0442)*0.855*0.1875= 0.189 in2

= 5*(tn - trn)*fr2*tn= 5*(0.28 - 0.0442)*0.855*0.28= 0.2823 in2

A41 = Leg2*fr2= 0.18752*0.855= 0.0301 in2

Area = A1 + A2 + A41

= 0.4605 + 0.189 + 0.0301= 0.6796 in2


58/78

UW-16(c) Weld Check









tb = min[ tb3 , tb1 ]= min[ 0.245 , 0.1106 ]= 0.1106 in


59/78




UG-37 Area Calculation Summary (in2)For Pe = 66.07 psi @ 250 °F


UG-45 NozzleWall


UG-45

Arequired


Awelds treq tmin

0.4582 0.4583 0.2285 0.199 -- -- 0.0308 0.0625 0.245














Area required per UG-37(d)(1)




60/78

A = 0.5*(d*tr*F + 2*tn*tr*F*(1 - fr1))= 0.5*(6.065*0.1494*1 + 2*0.28*0.1494*1*(1 - 0.8769))= 0.4582 in2






= 5*(tn - trn)*fr2*t= 5*(0.28 - 0.038)*0.8769*0.1875= 0.199 in2

= 5*(tn - trn)*fr2*tn= 5*(0.28 - 0.038)*0.8769*0.28= 0.2971 in2

A41 = Leg2*fr2= 0.18752*0.8769= 0.0308 in2

Area = A1 + A2 + A41

= 0.2285 + 0.199 + 0.0308= 0.4583 in2


UW-16(c) Weld Check




61/78


ta UG-28 = 0.038 in




tb = min[ tb3 , tb2 ]= min[ 0.245 , 0.0625 ]= 0.0625 in





L /Do

= 6.6318 /6.625 = 1.0010

Do /t = 6.625 /

0.038 = 174.4501

From table G: A = 0.000600From tableCS-2: B = 8,644.7656

psi

Pa = 4*B / (3*(Do / t))

= 4*8,644.77 / (3*(6.625 /0.038))

= 66.07 psi



+ 0 = 0.038"

62/78

Nozzle #3 (N3)


tw(lower) = 0 inLeg41 = 0.3125 in


Located on: Cylinder #1Liquid static head included: 0 psiNozzle material specification: SA-105 (II-D p. 18, ln. 5)Nozzle longitudinal joint efficiency: 1Nozzle description: NPS 1 Class 3000 - threadedNozzle orientation: 300°Local vessel minimum thickness: 0.1875 inNozzle center line offset to datum line: 7 inEnd of nozzle to shell center: 11 inNozzle inside diameter, new: 1.315 inNozzle nominal wall thickness: 0.2175 inNozzle corrosion allowance: 0 inProjection available outside vessel, Lpr: 2 in

63/78


The vessel wall thickness governs the MAWP of this nozzle.

UG-37 Area Calculation Summary(in2)

For P = 409.67 psi @ 250 °F

UG-45 NozzleWall


UG-45

Arequired


Awelds treq tmin

This nozzle is exempt from areacalculations per UG-36(c)(3)(a) 0.0625 0.2175








Nozzle impact test exemption temperature from Fig UCS-66 Curve B = -20 °FFig UCS-66.1 MDMT reduction = 130.8 °F, (coincident ratio = 0.35893)Rated MDMT is governed by UCS-66(b)(2).

Nozzle UCS-66 governing thk: 0.1875 inNozzle rated MDMT: -55 °FParallel Limit of reinforcement per UG-40





trn = P*Rn / (Sn*E - 0.6*P)= 409.6698*0.6575 / (20,000*1 - 0.6*409.6698)= 0.0136 in

64/78


tr = P*Ro / (S*E + 0.4*P)= 409.6698*9 / (19,500*1 + 0.4*409.6698)= 0.1875 in

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

Check the weld - From UW-16(f)(3)(a)(3)(a)

Wall thickness per UG-45(a): tr1 = 0.0178 in (E =1)Wall thickness per UG-45(b)(1): tr2 = 0.1875 inWall thickness per UG-16(b): tr3 = 0.0625 inStandard wall pipe per UG-45(b)(4): tr4 = 0.1269 inThe greater of tr2 or tr3: tr5 = 0.1875 inThe lesser of tr4 or tr5: tr6 = 0.1269 in

Required per UG-45 is the larger of tr1 or tr6 = 0.1269 in

tw(actual) = 0.7*Leg = 0.7*0.3125 = 0.2188 in


ASME B16.11 Coupling Wall Thickness Check

Wall thickness req'd per ASME B16.11 2.1.1: tr1 = 0.0178 in (E =1)Wall thickness per UG-16(b): tr3 = 0.0625 in

65/78

Available nozzle wall thickness new, tn = 0.2175 in



The vessel wall thickness governs the MAP of this nozzle.


For P = 420.17 psi @ 70 °F

UG-45 NozzleWall


UG-45

Arequired


Awelds treq tmin














trn = P*Rn / (Sn*E - 0.6*P)= 420.172*0.6575 / (20,000*1 - 0.6*420.172)= 0.014 in

66/78


tr = P*Ro / (S*E + 0.4*P)= 420.172*9 / (20,000*1 + 0.4*420.172)= 0.1875 in



Wall thickness per UG-45(a): tr1 = 0.0182 in (E =1)Wall thickness per UG-45(b)(1): tr2 = 0.1875 inWall thickness per UG-16(b): tr3 = 0.0625 inStandard wall pipe per UG-45(b)(4): tr4 = 0.1269 inThe greater of tr2 or tr3: tr5 = 0.1875 inThe lesser of tr4 or tr5: tr6 = 0.1269 in


tw(actual) = 0.7*Leg = 0.7*0.3125 = 0.2188 in


ASME B16.11 Coupling Wall Thickness Check

Wall thickness req'd per ASME B16.11 2.1.1: tr1 = 0.0182 in (E =1)Wall thickness per UG-16(b): tr3 = 0.0625 in

67/78





For Pe = 93.73 psi @ 250 °F

UG-45 NozzleWall


UG-45

Arequired


Awelds treq tmin
















68/78


Wall thickness per UG-45(a): tr1 = 0.0124 inWall thickness per UG-45(b)(1): tr2 = 0.0432 inWall thickness per UG-16(b): tr3 = 0.0625 inStandard wall pipe per UG-45(b)(4): tr4 = 0.1269 inThe greater of tr2 or tr3: tr5 = 0.0625 inThe lesser of tr4 or tr5: tr6 = 0.0625 in


tw(actual) = 0.7*Leg = 0.7*0.3125 = 0.2188 in



ta UG-28 = 0.0124 in




tb = min[ tb3 , tb2 ]= min[ 0.1269 , 0.0625 ]= 0.0625 in





L /Do

= 2.0426 /1.75 = 1.1672

Do/ t = 1.75 /

0.0124 = 140.9503

From table G: A = 0.000687B =

69/78

From tableCS-2:

9,908.3252psi

Pa = 4*B / (3*(Do / t))

= 4*9,908.33 / (3*(1.75 /0.0124))

= 93.73 psi



+ 0 = 0.0124"

70/78

Straight Flange on F&D Head #1


Component: Straight FlangeMaterial specification: SA-240 304 (II-D p. 86, ln. 25)Rated MDMT per UHA-51(d)(1)(a) = -320 °F


Static liquid head:


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



Radiography: Longitudinal joint - Spot UW-11(b) Type 1Circumferential joint - UserDefined

E = 0.5

Estimated weight New = 4.1 lb corr = 4.1 lbCapacity New = 2.14 US gal corr = 2.14 US gal

OD = 18"LengthLc

= 2"

t = 0.125"

Design thickness, (at 250 °F) Appendix 1-1

t = P*Ro / (S*E + 0.40*P) + Corrosion= 150*9 / (19,500*0.85 + 0.40*150) + 0= 0.0812"

Maximum allowable working pressure, (at 250 °F) Appendix 1-1

P = S*E*t / (Ro - 0.40*t) - Ps= 19,500*0.85*0.125 / (9 - 0.40*0.125) - 0= 231.49 psi

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

P = S*E*t / (Ro - 0.40*t)= 20,000*0.85*0.125 / (9 - 0.40*0.125)= 237.43 psi


L /Do

= 36.1178/ 18 = 2.0065

71/78

Do/ t = 18 /

0.0791 = 227.4320


psi

Pa = 4*B / (3*(Do / t))

= 4*2,558.61 / (3*(18 /0.0791))

= 15 psi

Design thickness for external pressure Pa = 15 psi


+ 0 = 0.0791"

Maximum Allowable External Pressure, (Corroded & at 250 °F) UG-28(c)

L /Do

= 36.1178/ 18 = 2.0065

Do/ t = 18 /

0.125 = 144.0000


psi

Pa = 4*B / (3*(Do / t))

= 4*5,012.46 / (3*(18 /0.125))

= 46.41 psi

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

EFE = (50*t / Rf)*(1 - Rf / Ro)= (50*0.125 / 8.9375)*(1 - 8.9375 / ∞)= 0.6993%

Design thickness = 0.0812"

The governing condition is due to internal pressure.

The cylinder thickness of 0.125" is adequate.

Thickness Required Due to Pressure + External Loads

Condition Pressure P (psi)

Allowable StressBefore UG-23

Stress Increase (psi)

Temperature (°F)

Corrosion C(in) Load Req'd Thk Due to

Tension (in)

Req'd Thk Dueto

Compression(in)

St Sc

Operating, Hot & Corroded 150 19,500 9,316 250 0 Weight 0.0681 0.0681

Operating, Hot & New 150 19,500 9,316 250 0 Weight 0.0681 0.0681

Hot Shut Down, Corroded 0 19,500 9,316 250 0 Weight 0 0

Hot Shut Down, New 0 19,500 9,316 250 0 Weight 0 0

Empty, Corroded 0 20,000 11,048 70 0 Weight 0 0

72/78

Empty, New 0 20,000 11,048 70 0 Weight 0 0

Vacuum -15 19,500 9,316 250 0 Weight 0.0071 0.0071

Hot Shut Down, Corroded, Weight& Eccentric Moments Only 0 19,500 9,316 250 0 Weight 0 0

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

= 0.125 / (9 / 0.125)= 0.001736

B = 9,316 psi

S = 19,500 / 1.00 = 19,500 psi

ScHC = min(B, S) = 9,316 psi

Allowable Compressive Stress, Hot and New- ScHN

ScHN = ScHC

= 9,316 psi

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

= 0.125 / (9 / 0.125)= 0.001736

B = 11,048 psi

S = 20,000 / 1.00 = 20,000 psi

ScCN = min(B, S) = 11,048 psi

Allowable Compressive Stress, Cold and Corroded- ScCC

ScCC = ScCN

= 11,048 psi

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

= 0.125 / (9 / 0.125)= 0.001736

B = 9,316 psi

S = 19,500 / 1.00 = 19,500 psi

ScVC = min(B, S) = 9,316 psi

Operating, Hot & Corroded, Top Seam



= 0 / (π*8.93752*19,500*1.00*0.50)= 0"

73/78



= 0.0681 + 0 - (0)= 0.0681"


= |0 + (0) - (0.0681)|= 0.0681"



Operating, Hot & New, Top Seam



= 0 / (π*8.93752*19,500*1.00*0.50)= 0"



= 0.0681 + 0 - (0)= 0.0681"


= |0 + (0) - (0.0681)|= 0.0681"



Hot Shut Down, Corroded, Top Seam


2*St*Ks*Ec) (bending)

74/78

= 0 / (π*8.93752*19,500*1.00*0.50)= 0"



= 0 + 0 - (0)= 0"


= |0 + (0) - (0)|= 0"

Hot Shut Down, New, Top Seam


2*St*Ks*Ec) (bending)= 0 / (π*8.93752*19,500*1.00*0.50)= 0"



= 0 + 0 - (0)= 0"


= |0 + (0) - (0)|= 0"

Empty, Corroded, Top Seam


2*St*Ks*Ec) (bending)= 0 / (π*8.93752*20,000*1.00*0.50)= 0"



= 0 + 0 - (0)= 0"

tc = |tmc + twc - tpc|

75/78

(total, nettensile)

= |0 + (0) - (0)|= 0"

Empty, New, Top Seam


2*St*Ks*Ec) (bending)= 0 / (π*8.93752*20,000*1.00*0.50)= 0"



= 0 + 0 - (0)= 0"


= |0 + (0) - (0)|= 0"

Vacuum, Top Seam



= 0 / (π*8.93752*9,316.21*1.00)= 0"

tw = W / (2*π*Rm*Sc*Ks) (Weight)= -17.5 / (2*π*8.9375*9,316.21*1.00)= 0"

tt = |tp + tm - tw| (total, net compressive)= |-0.0071 + 0 - (0)|= 0.0071"

tc = tmc + twc - tpc (total required, compressive)= 0 + (0) - (-0.0071)= 0.0071"


P = 2*Sc*Ks*(t - tmc - twc) / (R - 0.40*(t - tmc - twc))= 2*9,316.21*1.00*(0.125 - 0 - 0) / (8.875 - 0.40*(0.125 - 0 - 0))= 263.99 psi

76/78

Hot Shut Down, Corroded, Weight & Eccentric Moments Only, Top Seam


2*St*Ks*Ec) (bending)= 0 / (π*8.93752*19,500*1.00*0.50)= 0"



= 0 + 0 - (0)= 0"


= |0 + (0) - (0)|= 0"

77/78

Weight Summary

ComponentWeight ( lb) Contributed by Vessel Elements Surface

Areaft2Metal

New*

Metal

Corroded*Insulation &

Supports Lining Piping+ Liquid

OperatingLiquid

TestLiquid

Bolted Cover #1 175.8 175.8 0 0 0 0 0 3

Cylinder #1 93.5 93.5 0 0 0 0 291.8 12

F&D Head #1 17.5 17.5 0 0 0 0 47.7 4

Legs #1 15.6 15.6 0 0 0 0 0 4

TOTAL: 302.3 302.3 0 0 0 0 339.5 23

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

Component

Weight ( lb) Contributed by AttachmentsSurface Area

ft2Body Flanges Nozzles &Flanges Packed

BedsLadders &Platforms

Trays &Supports

Rings &Clips

VerticalLoads

New Corroded New Corroded

Bolted Cover #1 0 0 0 0 0 0 0 0 0 0

Cylinder #1 70 70 76.6 76.6 0 0 0 0 0 8

F&D Head #1 0 0 0 0 0 0 0 0 0 0

Legs #1 0 0 0 0 0 0 0 0 0 0

TOTAL: 70 70 76.6 76.6 0 0 0 0 0 4

Vessel operating weight, Corroded: 449 lbVessel operating weight, New: 449 lbVessel empty weight, Corroded: 449 lbVessel empty weight, New: 449 lbVessel test weight, New: 788 lbVessel surface area: 27 ft2

Vessel center of gravity location - from datum - lift condition

Vessel Lift Weight, New: 449 lbCenter of Gravity: 23.3864"

Vessel Capacity

Vessel Capacity** (New): 40 US galVessel Capacity** (Corroded): 40 US gal**The vessel capacity does not include volume of nozzle, piping or other attachments.

78/78

key design engineering test pressure psi test liquid ... l stresses at nozzle openings have been...

Documents