Sample 5 Calcs

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Sample Vessel 5

PVE-Sample 5Pressure Vessel Calculations

May 25, 2005

XYZ Vessel Inc.123 Anytown

Ontario, Canada H0H 0H0

Charles Liu P. Eng.

Laurence Brundrett P. Eng.

Pressure Vessel Engineering Ltd.

PVE-Sample 5 Rev. 0

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Table of Contents 25-May-05 Page 2 of 24

Contents Page

Cover 1

Table of Contents 2

Summary 3

Material Properties 4

Shell 5

Bottom Ferrule 6

Cone 7Cone Discontinuity 8 - 9

2" Nozzle A 10

2" 300# RFSO Flange 11

2" Nozzle B 12

Code Case 2148 13

10" Nozzle C 14

10" Nozzle C For App. 1-7 15

10" Nozzle App 1-7 16

10" Flange 17 - 18

Top Shell Flange 19 - 20

Cover Swing Bolts 21 - 22

Coupling E 23Weight and Volume 24

Note:

Ferrules registered under CRN# ASLOA7213.5124087.

No calculations are included.


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Pressure Vessel Design Summary 25-May-05 Page 3 of 24

Customer

Vessel

Part Number

Drawing

Job

12.75 Outside Diameter [inch]

20 straight Shell (not including straight flange on heads)2 Volume [cuft]

Water Fluid (value from Material Properties)

161 Weight Empty [lbs.]

277 Weight Full

277 Weight Under Test

Maximum Internal pressure, psi Maximum External Pressure, psi At Temperature, F

200 0 350Maximum Temperature, F Minimum Temperature, F At Pressure, psi

350 -20 200Test Pressure, psi At a Minimum Temperature of: F For a Minimum Duration of:

260 55F 1/2 hr

SA-240 304 Primary Material of Construction

18,600 Allowable Stress

0.0625 Minimum allowed thickness per UG-16(b)

no Material Normalized

no Material Impact Tested (not required per UHA-51(d)(1) )

none Radiography required

0 Corrosion Allowance

ASME VIII-1 Code

2004 Edition

none Addenda

IID Materials2148 Code Cases Required

UG-22 Loadings Considered

Yes (a) Internal pressure

- (a) External pressure

Yes (b) Vessel weight full, empty and at hydro test

- (c) Weight of attached equipment and piping

- (d)(1) Attachment of internals

- (d)(2) Attachment of vessel supports

- (d) Cyclic or dynamic reactions

- (f) Wind

- (f) Snow- (f) Seismic

- (g) Fluid impact shock reactions

- (h) Temperature gradients

- (h) Differential thermal expansion

- (i) Abnormal pressures like deflagration

Hydrostatic Test

Maximum Allowed Working Pressure

XYZ Vessel Inc.

PVE-Sample 5

PVE-Sample 5

PVE-Sample 5

Sample Vessel 5

Maximum Design Metal Temperature


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1 Material Properties ver 2.01 www.pveng.com 25-May-05 Page 4 of 242 ASME VIII, IID 2004 Edition no Addenda

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1 Pipe and Shellver 2.38 25-May-05 Page 5 of 242 ASME Code VIII Div I 2004 Edition No Addenda

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1 Pipe and Shellver 2.38 25-May-05 Page 6 of 242 ASME Code VIII Div I 2004 Edition No Addenda

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1 Cone ver 2.61 25-May-05 Page 7 of 242 ASME VIII 1-4 2004 Edition, No Addenda www.pveng.com

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1 Cone Discontinuity Stress ver 1.4 www.pveng.com 25-May-05 Page 8 of 242 Pressure Vessel Design Handbook - Second Edition - Henry H Bednar. Pages 231 to 240 & ASME VIII-1 5(g)

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59 Sample Vessel 5 - Cone Discontinuity 25-May-05 Page 9 of 24

61 Discontinuity Influence Coefficients:62 Large End XL = 4.669*V2L*TAN(Alpha) = 4.669*0.12*TAN(0.44) XL = 0.2689

63 YL = 1.285*(V1L - 2*V2L)*TAN(Alpha) YL = 0.1480

64 = 1.285*(0.487 - 2*0.122)*TAN(0.442)

65 UL = XL/nL^2 = 0.269/1^2 UL = 0.2689

67 Small End XS = 4.669*V2S*TAN(Alpha) = 4.669*0.1*TAN(0.44) XS = 0.223

68 YS = 1.285*(V1S - 2*V2S)*TAN(Alpha) YS = 0.082

69 = 1.285*(0.336 - 2*0.101)*TAN(0.442)70 US = XL/nL^2 = 0.223/2.404^2 US = 0.039

72 Equivalent Loads from W and M73 lL = (4*M/(Pi*2*RL)+(W/(pi*2*RL) lL = 0.000

74 PeL = P+(2*lL/RL) = 200.953+(2*0/6.281) PeL = 200.953

76 lS = (4*M/(Pi*2*RS)+(W/(pi*2*RS) lS = 0.000

77 PeS = P+(2*lS/RS) = 200.953+(2*0/3.976) PeS = 200.953

79 Maximum Allowed Stresses: ASME 1-5(g) & UG-23(e)80 Longitudinal = 3*Sl = 3*18600 Zone A LLmax = 55,800

81 Mem tangential = 1.5*Sl = 1.5*18600 Zone A MLmax = 27,900

83 Longitudinal = 3*Sc = 3*18600 Zone B & C LCmax = 55,80084 Mem tangential = 1.5*Sc = 1.5*18600 Zone B & C MCmax = 27,900

86 Longitudinal = 3*Ss = 3*18600 Zone D LSmax = 55,800

87 Mem tangential = 1.5*Ss = 1.5*18600 Zone D MSmax = 27,900

89 Combined Stresses - Large Cylinder - Zone A90 Longitudinal = Long. = 13,844 -7,112

91 = Acceptable

92 Mem tangential = Mem. Tan. = 964

93 = Acceptable

95 Combined Stresses - Large End of Cone - Zone B96 Longitudinal = Long. = 14,201 -6,755

97 = Acceptable

98 Mem tangential = Mem. Tan. = 1,678

99 = Acceptable

101 Combined Stresses - Small End of Cone - Zone C102 Longitudinal = Long. = 5,176 -463

103 = Acceptable

104 Mem tangential = Mem. Tan. = 10,684

105 = Acceptable

107 Combined Stresses - Small Cylinder - Zone D108 Longitudinal = Long. = 21,413 -11,170

109 = Acceptable

110 Mem tangential = (P*Rs/ts)*(1+(PeS/P)*Ys*SQRT(Rs/ts))


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28 Nozzle Reinforcement ver 3.81 UW16(c)


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18 B16.5/16.47 FlangeVer 2.6 SlipOn www.pveng.com 25-May-05 Page 11 of 2419ASME B16.5 & B16.47-1996 ASME VIII 2004 Edition No Addenda #VALUE!

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2 Code Case 2148 Ver. 2.1 25-May-05 Page 13 of 243 ASME Code VIII Div I 2004 edition, no addenda www.pveng.com

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11 App 1-7 Nozzle Ver 1.04 Fig 1-7-2 Case B 25-May-05 Page 16 of 2412 ASME Code VIII Div I 2004 Edition No Addenda

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18 Flanges ver 2.38 www.pveng.com 25-May-05 Page 17 of 2419

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173 25-May-05 Page 18 of 24

175 Flange Loads - lbs - (app 2-5):

176 W = (Am + Ab)*Sba/2 = (1.011 + 1.664)*25000/2 seating conditions W = 33,436

177 HG = Wm1 - H = 25272 - 21003 operating conditions HG = 4,269

179 Flange Moment Arms - inch - (Table App 2-6 - loose flanges):

195 mhD = (varC-B)/2 = (13-10.75)/2 end pressure mhD = 1.125

196 mhT = (mhD+mhG)/2 = (1.125+0.731)/2 face pressure mhT = 0.928

197 mhG = (varC-varG)/2 = (13-11.539)/2 gasket load mhG = 0.731

206 Flange Moments - inch*lbs - (App 2-6):207 MD = HD * mhD = 18239 * 1.125 end pressure MD = 20,519

208 MT = HT * mhT = 2764 * 0.928 face pressure MT = 2,564

209 MG = HG * mhG = 4269 * 0.731 gasket load MG = 3,119

214 Mo1i = MD+MT+MG = 20519 + 2564 + 3119 total operating Mo1i = 26,202

215 Mo1e = Hde*(mhD-mhG)+Hte*(mhT-mhG) total operating external pressure Mo1e = 0.000

216 = 0*(1.125-0.731)+0*(0.928-0.731)

217 Mo1 = Max(Mo1i,Mo1e) = Max(26202.181,0) Mo1 = 26,202

219 Mo2 = W*(varC-varG)/2 = 33436*(13-11.539)/2 total seating Mo2 = 24,430

242 Graph app 2-7.1 Value of Y

255 K = A/B = 14.75/10.75 K = 1.372

260 Y = (1/(K-1))*(0.66845+5.71690*(K^2*Log(K))/(K^2-1)) Figure 2.7-1 Y = 6.299

284

Flange Seating Stress (app 2-7):302 STs = Y*ABS(Mo2) / (t^2*B) = 6.299*ABS(24430) / (1^2*10.75) STs = 14,314

305 SBs = Wm2 / Ab = 2125 / 1.664 SBs = 1,277

309 Flange Operating Stress (app 2-7):

321 STo = y*ABS(Mo1) / (t^2*B) = 6.299*ABS(26202) / (1^2*10.75) STo = 15,353

325 SBo = Wm1 / Ab = 25272 / 1.664 SBo = 15,187

329 Allowed Stress (App2-8): SeatingAllowed Operating Allowed

334 ST


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18 Flanges ver 2.38 www.pveng.com 25-May-05 Page 19 of 2419

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173 25-May-05 Page 20 of 24

175 Flange Loads - lbs - (app 2-5):

176 W = (Am + Ab)*Sba/2 = (0.928 + 1.86)*25000/2 seating conditions W = 34,846

177 HG = Wm1 - H = 23191 - 23191 operating conditions HG = 0

178 Flange Moment Arms - inch - (Table App 2-6 - Integral flanges):

185 mhD = varR+0.5*gOne = 1+0.5*0.625 end pressure mhD = 1.313

186 mhT = (varR+gOne+mhG)/2 = (1+0.625+1.313)/2 face pressure mhT = 1.469

187 mhG = (varC-varG)/2 = (14.75-12.125)/2 gasket load mhG = 1.3134

206 Flange Moments - inch*lbs - (App 2-6):207 MD = HD * mhD = 20873 * 1.313 end pressure MD = 27,395

208 MT = HT * mhT = 2319 * 1.469 face pressure MT = 3,406

209 MG = HG * mhG = 0 * 1.313 gasket load MG = 0

214 Mo1i = MD+MT+MG = 27395 + 3406 + 0 total operating Mo1i = 30,801

215 Mo1e = Hde*(mhD-mhG)+Hte*(mhT-mhG) total operating external pressure Mo1e = 0.000

216 = 0*(1.313-1.313)+0*(1.469-1.313)

217 Mo1 = Max(Mo1i,Mo1e) = Max(30801.024,0) Mo1 = 30,801

219 Mo2 = W*(varC-varG)/2 = 34846*(14.75-12.125)/2 total seating Mo2 = 45,735

241 Graphs app 2-7.1-6 Values of F, f, T, U, V, Y and Z

243 h0 = sqrt(B*g0) = sqrt(11.5*0.188) h0 = 1.468

246 hh0 = hub/h0 = 1.5/1.468 hh0 = 1.022

247 g1g0 = gOne/g0 = 0.625/0.188 g1g0 = 3.333

248 F = from figure 2-7.2 F = 0.676

249 V = from figure 2-7.3 V = 0.067

252 smallF = from figure 2-7.6, min=1 actual small f = 0.935 smallF = 1.000

255 K = A/B = 12.75/11.5 K = 1.109

258 T = Figure 2.7-1 T = 1.874

259 U = (K^2(1+8.55246Log10K)-1)/(1.36136*(K^2-1)(K-1)) Figure 2.7-1 U = 20.648

260 Y = (1/(K-1))*(0.66845+5.71690*(K^2*Log(K))/(K^2-1)) Figure 2.7-1 Y = 18.790

261 Z = (K^2 + 1)/(K^2-1) Figure 2.7-1 Z = 9.726

262 d = (U/V)*h0*g0^2 = (20.648/0.067)*1.468*0.188^2 d = 15.896

265 e = F / h0 = 0.676 / 1.468 e = 0.460

268 L = (t*e + 1)/T + t^3/d = (3 *0.46 + 1)/1.874 + 3^3/15.896 L = 2.969

284 Flange Seating Stress (app 2-7):

285

SHs = smallF*ABS(Mo2) / ( L*gOne^2 * B) SHs = 3,429286 = 1*ABS(45735) / ( 2.969*0.625^2 * 11.5)

291 SRs = (1.33*t*e +1)*ABS(Mo2) / (L*t^2*B) SRs = 422

292 = (1.33*3*0.46 +1)*ABS(45735) / (2.969*3^2*11.5)

297 STs = (y*ABS(Mo2) / (t^2*B)) - Z*SRs STs = 4,197

298 = (18.79*ABS(45735) / (3^2*11.5)) - 9.726*422

304 SAs = (SHs + Max(SRs, STs))/2 = (3429+Max(422,4197))/2 SAs = 3,813

305 SBs = Wm2 / Ab = 0 / 1.86 SBs = 0

309 Flange Operating Stress (app 2-7):

310 SHo = smallF*Mo1/(L*gOne^2*B) = 1*30801 / ( 2.969*0.625^2 * 11.5) SHo = 2,310

314 SRo = (1.33*t*e+1)*Mo1/(L*t^2*B) = (1.33*3*0.46 +1)*30801.024 / (2.969*3^2*11.5) SRo = 284

318 STo = y*Mo1/(t^2*B)-Z*SRO = 18.79*30801 / (3^2*11.5) - 9.726*284.288 STo = 2,827

324 SAo = (SHo+Max(SRo,STo))/2 = (2310 + Max(284 , 2827))/2 SAo = 2,568

325 SBo = Wm1 / Ab = 23191 / 1.86 SBo = 12,469329 Allowed Stress (App2-8): SeatingAllowed OperatingAllowed

331 SH


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1 Swing Bolt and Cover ver 1.5 25-May-05 Page 21 of 242 ASME Code VIII Div I 2004 Edition No Addenda

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53 25-May-05 Page 22 of 24

54 Lug Ratio


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15 Coupling ver 2.11 UW16.2L 25-May-05 Page 23 of 2416 ASME Code VIII Div I 2004 Edition No Addenda www.pveng.com

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Vessel Weight and Volume ver. 1.1 25-May-05 Page 24 of 24

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Sample 5 Calcs