lp flare 62 inch wnrf flange

8/10/2019 LP Flare 62 Inch WNRF Flange

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NATCO-AL-RUSHAID MIDDLE EAST LTD

Jubail Industrial City 31961

COMPRESS Pressure Vessel Design Calculations

Item: ADSORBER VESSEL

Vessel No: 4075-VE-02-V00

Customer: PETROFACContract:

Designer: VP JAGANNAATH

Date: Sunday, January 12, 2014

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Table of Contents

Deficiencies Summary..............................................................................................................................................1/19

Pressure Summary...................................................................................................................................................2/19

Revision History........................................................................................................................................................3/19

Settings Summary.....................................................................................................................................................4/19

Radiography Summary.............................................................................................................................................6/19

Thickness Summary.................................................................................................................................................7/19

Weight Summary.......................................................................................................................................................8/19

Hydrostatic Test........................................................................................................................................................9/19

Corroded Hydrostatic Test.....................................................................................................................................10/19

Flange #1..................................................................................................................................................................11/19



Deficiencies Summary

No deficiencies found.

1/19



Pressure Summary

Identifier

P

Design

( kPa)

T

Design

( °C)

MAWP

( kPa)

MAP

( kPa)

MAEP

( kPa)

Te

external

( °C)

MDMT

( °C)

MDMT

Exemption

Impact

Tested

Flange #1 350 192 1,988.43 2,509.26 4,729.9 192 -48 Note 1 No

Flange #1 - Flange Hub 350 192 1,195.68 1,761.33 663.26 192 -49 Note 2 No

Chamber design MDMT is 0 °CChamber rated MDMT is -48 °C @ 1,195.68 kPa

Chamber MAWP hot & corroded is 1,195.68 kPa @ 192 °C

Chamber MAP cold & new is 1,761.33 kPa @ 40 °C

Chamber MAEP is 663.26 kPa @ 192 °CVacuum rings did not govern the external pressure rating.

Notes for MDMT Rating:

Note # Exemption Details

1.Flange is impact tested to -46 °C with an additional 3 °C reduction per UCS-66(g)

UCS-66 governing thickness = 10 mm

Bolts rated MDMT per Fig UCS-66 note (c) = -48 °C

2. Material is impact tested to -46 °C with an additional 3 °C reduction per UCS-66(g) UCS-66 governing thickness = 10 mm

Design notes are available on the Settings Summary page.

2/19



Revision History

No. Date Operator Notes

0 1/15/2014 vp.jagannaath New vessel created ASME Section VIII Division 1 [COMPRESS 2014 Build 7400]

3/19



Settings Summary

COMPRESS 2014 Build 7400

Units: SI

Datum Line Location: 0.00 mm from bottom seam

Design

ASME Section VIII Division 1, 2013 Edition Metric

Design or Rating: Get Thickness from Pressure

Minimum thickness: 1.5 mm per UG-16(b)

Design for cold shut down only: No

Design for lethal service (full radiography required): No

Design nozzles for: Design P, find nozzle MAWP and MAP

Corrosion weight loss: 100% of theoretical loss

UG-23 Stress Increase: 1.20

Skirt/legs stress increase: 1.0

Minimum nozzle projection: 300 mmJuncture calculations for α > 30 only: Yes

Preheat P-No 1 Materials > 1.25" and <= 1.50" thick: No

UG-37(a) shell tr calculation considers longitudinal stress: No

Pipe under-tolerance is not applied to pipe cap thicknesses.Butt welds are tapered per Figure UCS-66.3(a).

Hydro/Pneumatic Test

Shop Hydrotest Pressure:1.3 times vesselMAWP

Test liquid specific gravity: 1.00

Field Hydrotest Pressure:1.3 times vessel

MAWP

Wind load present @ field: 33% of design

Maximum stress during test: 90% of yield

Required Marking - UG-116

UG-116(e) Radiography: None

UG-116(f) Postweld heat treatment: None

Code Cases\Interpretations

Use Code Case 2547: No

Use Code Case 2695: No

Apply interpretation VIII-1-83-66: Yes



No UCS-66.1 MDMT reduction: Yes

No UCS-68(c) MDMT reduction: Yes

Disallow UG-20(f) exemptions: Yes

4/19



UG-22 Loadings

UG-22(a) Internal or External Design Pressure : No

UG-22(b) Weight of the vessel and normal contents under operating or test conditions: No

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: No

UG-22(f) Wind reactions: No

UG-22(f) Seismic reactions: No

UG-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.

5/19



Radiography Summary

Radiography for Chamber bounded by Top of vessel and Top of vessel

ComponentLongitudinal Seam Top Circumferential Seam Bottom Circumferential Seam

MarkCategory

(Fig UW-3)Radiography / Joint Type

Category


Category


Chamber bounded by Top of vessel and Top of vessel - UG-116(e) Radiography: None

6/19



Thickness Summary

Component

IdentifierMaterial Diameter

(mm)

Length

(mm)

Nominal t

(mm)

Design t

(mm)

Total Corrosion

(mm)

Joint

ELoad

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

7/19



Weight Summary

Component

Weight ( kg) Contributed by Vessel Elements

Surface Aream2

Metal

New*

Metal

Corroded*Insulation

InsulationSupports

LiningPiping

+ Liquid

Operating

LiquidTest Liquid

New Corroded New Corroded

TOTAL: 0 0 0 0 0 0 0 0 0 0 0

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

Component

Weight ( kg) Contributed by Attachments SurfaceArea

m2Body FlangesNozzles &Flanges

PackedBeds

Ladders &Platforms

TraysTray

SupportsRings &

ClipsVerticalLoads

New Corroded New Corroded

TOTAL: 1,286.4 1,258.2 0 0 0 0 0 0 0 0 1.37

Vessel operating weight, Corroded: 1,258 kg

Vessel operating weight, New: 1,286 kg

Vessel empty weight, Corroded: 1,258 kg

Vessel empty weight, New: 1,286 kg

Vessel test weight, New: 1,286 kg

Vessel test weight, Corroded: 1,258 kgVessel surface area: 1.37 m2

Vessel center of gravity location - from datum - lift condition

Vessel Lift Weight, New: 1,286 kg

Center of Gravity: 115 mm

Vessel Capacity

Vessel Capacity** (New): 0 liters

Vessel Capacity** (Corroded): 0 liters

**The vessel capacity does not include volume of nozzle, piping or other attachments.

8/19



Hydrostatic Test

Shop test pressure determination for Chamber bounded by Top of vessel and Top of vessel based on MAWPper UG-99(b)

Shop hydrostatic test gauge pressure is 1,554.38 kPa at 40 °C (the chamber MAWP = 1,195.68 kPa)

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

IdentifierLocal testpressure

kPa

Test liquidstatic head

kPa

UG-99(b)stressratio

UG-99(b)pressure

factor

Stressduring test

MPa

Allowabletest stress

MPa

Stressexcessive?

Flange #1 - Flange Hub (1) 1,569.62 15.24 1 1.30 122.821 223.2 No

Flange #1 1,569.62 15.24 1 1.30 172.646 334.8 No

Notes:

(1) Flange #1 - Flange Hub limits the UG-99(b) stress ratio.(2) 1.5*0.9*Sy used as the basis for the maximum local primary membrane stress at the nozzle intersection PL.

(3) The zero degree angular position is assumed to be up, and the test liquid height is assumed to the top-most

flange.

The test temperature of 40 °C is warmer than the minimum recommended temperature of -31 °C so the brittlefracture provision of UG-99(h) has been met.

Field test pressure determination for Chamber bounded by Top of vessel and Top of vessel based on MAWPper UG-99(b)

Field hydrostatic test gauge pressure is 1,554.38 kPa at 40 °C (the chamber MAWP = 1,195.68 kPa)

The field test is performed with the vessel in the vertical position.

Identifier Local testpressurekPa

Test liquidstatic headkPa

UG-99(b)stressratio

UG-99(b)pressurefactor

Stressduring testMPa

Allowabletest stressMPa

Stressexcessive?

Flange #1 - Flange Hub (1) 1,556.64 2.25 1 1.30 121.805 223.2 No

Flange #1 1,556.64 2.25 1 1.30 171.218 334.8 No

Notes:(1) Flange #1 - Flange Hub limits the UG-99(b) stress ratio.

(2) 1.5*0.9*Sy used as the basis for the maximum local primary membrane stress at the nozzle intersection PL.

The test temperature of 40 °C is warmer than the minimum recommended temperature of -31 °C so the brittlefracture provision of UG-99(h) has been met.

9/19



Corroded Hydrostatic Test

The shop test condition has not been investigated for the Chamber bounded by Top of vessel and Top of vessel.

Field test pressure determination for Chamber bounded by Top of vessel and Top of vessel based on designP per UG-99(b)

Field hydrostatic test gauge pressure is 455 kPa at 40 °C (the chamber design P = 350 kPa)

The field test is performed with the vessel in the vertical position.

IdentifierLocal testpressure

kPa

Test liquidstatic head

kPa

UG-99(b)stressratio

UG-99(b)pressure

factor

Stressduring test

MPa

Allowabletest stress

MPa

Stressexcessive?

Flange #1 - Flange Hub (1) 457.25 2.25 1 1.30 52.728 223.2 No

Flange #1 457.25 2.25 1 1.30 50.531 334.8 No

Notes:(1) Flange #1 - Flange Hub limits the UG-99(b) stress ratio.

(2) 1.5*0.9*Sy used as the basis for the maximum local primary membrane stress at the nozzle intersection PL.

10/19



Flange #1

ASME VIII-1, 2013 Edition Metric, Appendix 2 Flange Calculations

Flange type: Weld neck integralFlange material specification: SA-350 LF2 Cl 1 (II-D Metric p. 18, ln. 37)

Bolt material specification:SA-193 B7 Bolt <= 64 (II-D Metric p. 352, ln.31)

Bolt Description: 1.75 in Series 8 ThreadInternal design pressure, P: 350 kPa @ 192 °CRequired flange thickness, tr: 162.32 mm

Maximum allowable working pressure,MAWP:

1,988.43 kPa @ 192 °C

Maximum allowable pressure, MAP: 2,509.26 kPa @ 40 °CExternal design pressure, Pe 101.33 kPa @ 192 °C

Maximum allowable external pressure,MAEP:

4,729.9 kPa @ 192 °C

Corrosion allowance: Bore = 3.2 mm Flange = 0 mm

Bolt corrosion (root), Cbolt: 0 mmDesign MDMT: 0 °C No impact test performed

Rated MDMT: -48 °C Flange material is normalized

Material is not produced tofine grain practicePWHT is not performed

Estimated weight: New = 1,286.43 kg corroded = 1,258.22 kg

Flange dimensions, new

flange OD A = 1,900 mm

bolt circle C = 1,800 mm

raised face OD Rf = 1,718 mm

gasket OD = 1,755 mm

gasket ID = 1,555 mm

flange ID B = 1,555 mm

facing height trf = 1.52 mm

thickness t = 170 mm

bolting = 52- 1.75 in dia

hub thickness g1 = 20 mm

hub thickness g0 = 10 mm

hub length h = 60 mm

length e = 230 mm

gasket factor m = 3

seating stress y = 68.948 MPaGasket thickness T = 4.45 mm

gasket descriptionFlexitallic Spiral

Wound CG 316 S.S.Note: this flange is calculated as an integral type.

Determination of Flange MDMT

11/19



Flange is impact tested to -46 °C with an additional 3 °C reduction per UCS-66(g)UCS-66 governing thickness = 10 mm

Bolts rated MDMT per Fig UCS-66 note (c) = -48 °C

The rated flange MDMT is -48 °C

Flange calculations for Internal Pressure + Weight Only

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

Gasket width N = 81.5 mm

b0 = N/2 = 40.75 mm

Effective gasket seating width, b = 2.5*b01/2 = 15.96 mm

G = OD of contact face - 2*b = 1,718 - 2*15.96 = 1,686.08 mm

hG = (C - G)/2 = (1,800 - 1,686.08)/2 = 56.96 mm

hD = R + g1 /2 = 102.5 + 16.8/2 = 110.9 mm

hT = (R + g1 + hG)/2 = (102.5 + 16.8 + 56.96)/2 = 88.13 mm

Hp = 2*b*3.14*G*m*P= 2*15.96*3.14*1,686.08*3*0.35

= 177,430.61 N

H = 0.785*G2*P= 0.785*1,686.082*0.35= 781,079.64 N

HD = 0.785*B2*P

= 0.785*1,561.42*0.35

= 669,833.02 N

HT = H - HD

= 781,079.64 - 669,833.02

= 111,246.62 N

Wm1 = H + Hp

= 781,079.64 + 177,430.61

= 958,510.25 N

Wm2 = 3.14*b*G*y

= 3.14*15.96*1,686.08*68.9476= 5,825,433.17 N

Required bolt area, Am = greater of Am1, Am2 = 338.6879 cm2

Am1 = Wm1 /Sb = 958,510.25/(100*172) = 55.7273 cm2

Am2 = Wm2 /Sa = 5,825,433.17/(100*172) = 338.6879 cm2

Total area for 52- 1.75 in dia bolts, corroded, Ab = 664.2567 cm2

W = (Am + Ab)*Sa /2

12/19



= (33,868.79 + 66,425.67)*172/2= 8,625,325.31 N

MD = HD*hD = 669,833.02*0.1109 = 74,284.3 N-mMT = HT*hT = 111,246.62*0.0881 = 9,804.1 N-m

HG = Wm1 - H = 958,510.25 - 781,079.64 = 177,430.61 N

MG = HG*hG = 177,430.61*0.057 = 10,106.2 N-m

Mo = MD + MT + MG = 74,284.3 + 9,804.1 + 10,106.2 = 94,194.6 N-m

Mg = W*hG = 8,625,325.31*0.057 = 491,288.3 N-m

13/19



Hub and Flange Factors

g0 = min(g0, tn) = min(6.8, 6.8) = 6.8

h0 = (B*g0)1/2 = (1,561.4*6.8)1/2 = 103.04 mm

From FIG. 2-7.1, where K = A/B = 1,900/1,561.4 = 1.2169

T = 1.8321 Z = 5.1603 Y = 10.0039 U = 10.9933

h/h0 = 0.5823 g1 /g0 = 2.4707

F = 0.7961 V = 0.1657 e = F/h0 = 0.0773

d = (U/V)*h0*g02= (10.9933/0.1657)*10.3038*0.682

= 316.0218 cm3

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

f = 1.5449

L = (t*e + 1)/T + t3 /d

= (17*0.0773 + 1)/1.8321 + 173

/316.0218= 16.8091

SH = f*Mo /(L*g12*B)

= 1e3*1.5449*94,194.6/(16.8091*16.82*1,561.4)

= 19.646 MPa

SR = (1.33*t*e + 1)*Mo /(L*t2*B)= (1.33*170*0.0077 + 1)*1e3*94,194.6/(16.8091*1702*1,561.4)

= 0.341 MPa

ST = Y*Mo /(t2*B) - Z*SR

= 1e3*10.0039*94,194.6/(1702*1,561.4) - 5.1603*0.341

= 19.122 MPa

Allowable stress Sfo = 138 MPa

Allowable stress Sno = 138 MPa

ST does not exceed Sfo

SH does not exceed Min[ 1.5*Sfo, 2.5*Sno ] = 207 MPaSR does not exceed Sfo

0.5(SH + SR) = 9.994 MPa does not exceed Sfo

0.5(SH + ST) = 19.384 MPa does not exceed Sfo

Flange rigidity at operating per VIII-1 Appendix 2-14

J = 52.14*V*Mo /(L*E*g02*KI*h0)

= 1e3*52.14*0.1657*94,194.6/(16.8091*192.48E+03*6.82*0.3*103.04)

= 0.176

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

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

SH = f*Mg /(L*g12*B)

= 1e3*1.5449*491,288.3/(16.8091*16.82*1,561.4)

14/19



= 102.467 MPa

SR = (1.33*t*e + 1)*Mg /(L*t2*B)= (1.33*170*0.0077 + 1)*1e3*491,288.3/(16.8091*1702*1,561.4)= 1.779 MPa

ST = Y*Mg /(t2*B) - Z*SR

= 10.0039*1e3*491,288.3/(1702*1,561.4) - 5.1603*1.779= 99.736 MPa

Allowable stress Sfa = 138 MPaAllowable stress Sna = 138 MPa

ST does not exceed Sfa

SH does not exceed Min[ 1.5*Sfa, 2.5*Sna ] = 207 MPaSR does not exceed Sfa

0.5(SH + SR) = 52.123 MPa does not exceed Sfa

0.5(SH + ST) = 101.102 MPa does not exceed Sfa

Flange rigidity at gasket seating per VIII-1 Appendix 2-14

J = 52.14*V*Mo /(L*E*g02*KI*h0)

= 1e3*52.14*0.1657*491,288.3/(16.8091*201.2E+03*6.82*0.3*103.04)= 0.8783


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

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

Gasket width N = 81.5 mm

b0 = N/2 = 40.75 mm

Effective gasket seating width, b = 2.5*b01/2 = 15.96 mm

G = OD of contact face - 2*b = 1,718 - 2*15.96 = 1,686.08 mm

hG = (C - G)/2 = (1,800 - 1,686.08)/2 = 56.96 mm

hD = R + g1 /2 = 102.5 + 16.8/2 = 110.9 mm

hT = (R + g1 + hG)/2 = (102.5 + 16.8 + 56.96)/2 = 88.13 mm

Hp = 2*b*3.14*G*m*P= 2*15.96*3.14*1,686.08*3*0.1013

= 51,366.25 N

H = 0.785*G2*P= 0.785*1,686.082*0.1013= 226,122.95 N

HD = 0.785*B2*P

= 0.785*1,561.42*0.1013= 193,917 N

15/19



HT = H - HD

= 226,122.95 - 193,917

= 32,205.95 N

Wm1 = H + Hp

= 226,122.95 + 51,366.25= 277,489.2 N

Wm2 = 3.14*b*G*y

= 3.14*15.96*1,686.08*68.9476= 5,825,433.17 N

Required bolt area, Am = greater of Am1, Am2 = 338.6879 cm2

Am1 = 0.785*G2*(Pm - Pr)/Sb = 0/(100*172) = 0 cm2

Am2 = Wm2 /Sa = 5,825,433.17/(100*172) = 338.6879 cm2

Total area for 52- 1.75 in dia bolts, corroded, Ab = 664.2567 cm2

W = (Am2 + Ab)*Sa /2

= (33,868.79 + 66,425.67)*172/2

= 8,625,325.31 N

Mo = HD*(hD - hG) + HT*(hT - hG)

= 193,917*(0.1109 - 0.057) + 32,205.95*(0.0881 - 0.057)= 11,463.9 N-m

Mg = W*hG = 8,625,325.31*0.057 = 491,288.3 N-m

16/19



Hub and Flange Factors

g0 = min(g0, tn) = min(6.8, 6.8) = 6.8

h0 = (B*g0)1/2 = (1,561.4*6.8)1/2 = 103.04 mm

From FIG. 2-7.1, where K = A/B = 1,900/1,561.4 = 1.2169

T = 1.8321 Z = 5.1603 Y = 10.0039 U = 10.9933

h/h0 = 0.5823 g1 /g0 = 2.4707

F = 0.7961 V = 0.1657 e = F/h0 = 0.0773

d = (U/V)*h0*g02= (10.9933/0.1657)*10.3038*0.682

= 316.0218 cm3

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

f = 1.5449

L = (t*e + 1)/T + t3 /d

= (17*0.0773 + 1)/1.8321 + 173

/316.0218= 16.8091

SH = f*Mo /(L*g12*B)

= 1e3*1.5449*11,463.9/(16.8091*16.82*1,561.4)

= 2.391 MPa

SR = (1.33*t*e + 1)*Mo /(L*t2*B)= (1.33*170*0.0077 + 1)*1e3*11,463.9/(16.8091*1702*1,561.4)

= 0.042 MPa

ST = Y*Mo /(t2*B) - Z*SR

= 1e3*10.0039*11,463.9/(1702*1,561.4) - 5.1603*0.042

= 2.327 MPa

Allowable stress Sfo = 138 MPa

Allowable stress Sno = 138 MPa

ST does not exceed Sfo

SH does not exceed Min[ 1.5*Sfo, 2.5*Sno ] = 207 MPaSR does not exceed Sfo

0.5(SH + SR) = 1.216 MPa does not exceed Sfo

0.5(SH + ST) = 2.359 MPa does not exceed Sfo

Flange rigidity at operating per VIII-1 Appendix 2-14

J = 52.14*V*Mo /(L*E*g02*KI*h0)

= 1e3*52.14*0.1657*11,463.9/(16.8091*192.48E+03*6.82*0.3*103.04)

= 0.0214


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

SH = f*Mg /(L*g12*B)

= 1e3*1.5449*491,288.3/(16.8091*16.82*1,561.4)

17/19



= 102.467 MPa

SR = (1.33*t*e + 1)*Mg /(L*t2*B)= (1.33*170*0.0077 + 1)*1e3*491,288.3/(16.8091*1702*1,561.4)= 1.779 MPa

ST = Y*Mg /(t2*B) - Z*SR

= 10.0039*1e3*491,288.3/(1702*1,561.4) - 5.1603*1.779= 99.736 MPa

Allowable stress Sfa = 138 MPaAllowable stress Sna = 138 MPa

ST does not exceed Sfa

SH does not exceed Min[ 1.5*Sfa, 2.5*Sna ] = 207 MPaSR does not exceed Sfa

0.5(SH + SR) = 52.123 MPa does not exceed Sfa

0.5(SH + ST) = 101.102 MPa does not exceed Sfa

Flange rigidity at gasket seating per VIII-1 Appendix 2-14

J = 52.14*V*Mo /(L*E*g02*KI*h0)

= 1e3*52.14*0.1657*491,288.3/(16.8091*201.2E+03*6.82*0.3*103.04)= 0.8783


Flange #1 - Flange hub

ASME Section VIII Division 1, 2013 Edition Metric

Component: Flange hub

Material specification: SA-350 LF2 Cl 1 (II-D Metric p. 18, ln. 37)Material is impact tested to -46 °C with an additional 3 °C reduction per UCS-66(g)UCS-66 governing thickness = 10 mm

Internal design pressure: P = 350 kPa @ 192 °C

External design pressure: Pe = 101.33 kPa @ 192 °C

Static liquid head:

Not Considered

Corrosion allowance Inner C = 3.2 mm Outer C = 0 mm

Design MDMT = 0 °C No impact test performed

Rated MDMT = -49 °C Material is normalized

Material is not produced to Fine Grain PracticePWHT is not performed

Radiography: Longitudinal joint - Seamless No RT

Top circumferential joint - Full UW-11(a) Type 1Bottom circumferential joint - N/A

Estimated weight New = 23 kg corr = 15.7 kg

Capacity New = 113.95 liters corr = 114.89 liters

18/19



ID = 1,555 mmLength

Lc

= 60 mm

t = 10 mm

Design thickness, (at 192 °C) UG-27(c)(1)

t = P*R / (S*E - 0.60*P) + Corrosion= 350*780.7 / (138,000*1.00 - 0.60*350) + 3.2

= 5.18 mm

Maximum allowable working pressure, (at 192 °C) UG-27(c)(1)

P = S*E*t / (R + 0.60*t) - Ps

= 138,000*1.00*6.8 / (780.7 + 0.60*6.8) - 0= 1,195.68 kPa

Maximum allowable pressure, (at 40 °C) UG-27(c)(1)

P = S*E*t / (R + 0.60*t)= 138,000*1.00*10 / (777.5 + 0.60*10)

= 1,761.33 kPa

External Pressure, (Corroded & at 192 °C) UG-28(c)

L / Do = 60 / 1,575 = 0.0500Do / t = 1,575 / 1.18 = 1330.5055

Experimental basin formula

Pa = [2.42*E / (1 - µ2)0.75]*[(t / Do)2.50 / (L / Do - 0.45*(t / Do)

0.50)] / 3

= [2.42*194654544.68 / (1 - 0.302)0.75]*[(1.18 / 1,575)2.50 / (60 / 1,575 - 0.45*(1.18 / 1,575)0.50)] / 3= 101.32 kPa

Design thickness for external pressure Pa = 101.32 kPa

ta = t + Corrosion = 1.18 + 3.2 = 4.38mm

Maximum Allowable External Pressure, (Corroded & at 192 °C) UG-28(c)

L / Do = 60 / 1,575 = 0.0500Do / t = 1,575 / 6.8 = 231.6313From table G: A = 0.015361

From table CS-2Metric:

B = 115.2246 MPa

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

= 4*115,224.62 / (3*(1,575 / 6.8))

= 663.26 kPa

lp flare 62 inch wnrf flange

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