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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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28 Nozzle Reinforcement ver 3.81 UW16(c)
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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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28 Nozzle Reinforcement ver 3.81 UW16(c)
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28 Nozzle Reinforcement ver 3.81 UW16(c)
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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
3
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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
www.pveng.com