Vessel with Large Opening. PVE Samples. PVE Sample Vessels
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1 Vessel with Large Opening Sample 5 Pressure Vessel Calculations November 20, 2008 PVE Samples 120 Randall Drive Waterloo, Ontario N2V 1C6 PVE Sample Vessels Ben Vanderloo Laurence Brundrett P. Eng. Pressure Vessel Engineering Ltd. PVE-Sample 5 1 of 25
2 Table of Contents 20-Nov-08 Page 2 of 25 Contents Page Cover 1 Table of Contents 2 Summary 3 Material Properties 4 Shell 5 Bottom Ferrule 6 Cone 7 Cone Discontinuity " Ferrule - Nozzle A 11 2" 300# RFSO Flange 12 2" Heavy Ferrule - Nozzle B 13 10" Nozzle C 14 10" Nozzle App " Custom Flange Swing Bolts on Pipe Swing Bolt and Cover " Coupling E 24 Vessel Weight & Volume 25 Rev Revision(s) Description Date By 0 Initial Release 5/25/05 LB 1 Revised Calculations 11/20/08 BV 2
3 Pressure Vessel Design Summary 20-Nov-08 Page 3 of 25 PVE Samples Customer Vessel with Large Opening Vessel Vessel with Large Opening Part Number Sample 5 Drawing PVE-Sample 5 Job Outside Diameter [inch] 20 straight Shell (not including straight flange on heads) 2 Volume [cuft] Water Fluid (value from Material Properties) 160 Weight Empty [lbs.] 275 Weight Full 275 Weight Under Test Maximum Internal pressure, psi Maximum External Pressure, psi At Temperature, ºF Maximum Temperature, ºF Minimum Temperature, ºF At Pressure, psi Test Pressure, psi At a Minimum Temperature of: ºF For a Minimum Duration of: F 1/2 hr Maximum Allowed Working Pressure Maximum Design Metal Temperature Hydrostatic Test SA Primary Material of Construction 18,600 Allowable Stress Minimum allowed thickness per UG-16(b) No Material Normalized No Material Impact Tested (not required per UHA-51) None Radiography required 0 Corrosion Allowance ASME VIII-1 Code 2007 Edition - Addenda IID Materials 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
4 1 Material Properties ver Nov-08 Page 4 of Vessel with Large Opening <- Vessel 4 5 Design Pressure UG-22(a) <- P, internal operating pressure at top of vessel (psig) <- mpa, external operation pressure 8 Water <- Operating Fluid <- h, fluid height (ft) <- rho, fluid density (1.0 for water) 11 Design Pressure = P *rho*h = * 1 * 2.2 mdp = Hydro Test (UG-99(b)) pressure measured at top of vessel, rounded up 14 Test Press = P * 1.3 * MR = 200 * 1.3 * 1 mtp = Material Properties (ASME IID) <- mtemp, design temp ºF Test at ambient temp Material Where Used Ambient Design Strength Max ºF Ext 18 Strength Strength Ratio Graph 19 SA Plate shell, cone, cover HA-1 20 SA-312 TP304 Sms. and Wld. Pipe nozzle, bottom, ferrule HA-1 21 SA Bar side ferrule HA-1 22 SA-182 F304 Forging flange, coupling HA-1 23 SA-193 B7 Bolts <= 2.5" bolts Min Ratio (MR) =
5 1 Pipe and Shell ver 4.08 Page 5 of 25 2 Shell Description 3 Options: 4 Interior ip? - Calculate interior pressure 5 No Exterior ep? - Calculate exterior pressure 6 Rolled Plate pr? - Pipe or rolled plate 7 Non-Threaded pt? - Type of pipe 8 No relief? - Stress Relief Calculations Required 9 Dimensions: Do [in] - outside diameter t [in] - nominal wall thickness tminug16b [in] - minimum wall per UG-16(b) L [in] - length for volume and weight Corr [in] - corrosion allowance 15 Material and Conditions: 16 SA Material 17 18,600 S [psi] - allowable stress level El - longitudinal efficiency (circ. stress) Ec - circ. connecting efficiency (longitudinal stress) % UTP [%] - undertolerance allowance UTI [in] - undertolerance allowance P [psi] - interior pressure 23 Stress Classification: 24 NOTE: Both validity checks need to be "Acceptable" in order to use this sheet 25 If not, refer to sheet "Thick Cylindrical Shell" 26 ckvalidity1 = tmin < 0.5*(Do/2) < 0.5*(12.75/2) = Acceptable 27 ckvalidity2 = P< 0.385*S*El < 0.385*18600*0.7 = Acceptable 28 Variables: 29 Td = = UT [in] = t*utp+uti 0.188*0+0 = nt [in] = t-corr-ut-td = Ri [in] = Do/2-nt 12.75/ = Volume [cuft] = ((Do/2-t)^2)*π*L/1728 ((12.75/ )^2)*3.1416*15.5/1728 = Weight [lb] = (Do-t)*π*L*t*40.84/ ( )*3.1416*15.5*0.188*40.84/144 = Interior Pressure: VIII-1 UG-27(c)(1,2) 36 ta [in] = P*Ri/(S*El-0.6*P) *6.187/(18600* *200.95) = tb [in] = P*Ri/(2*S*Ec+0.4*P) *6.187/(2*18600* *200.95) = tmin [in] = MAX(ta,tb,tminUG16b) MAX(0.096,0.048,0.063) = tr1 [in] = P*Ri/(S*1-0.6*P) *6.187/(18600*1-0.6*200.95) = Checkt = tmin <= nt <= = Acceptable 41 PMaxA [psi] = (S*El*nt)/(Ri+0.6*nt) (18600*0.7*0.188)/( *0.188) = PMaxB [psi] = (2*S*Ec*nt)/(Ri-0.4*nt) (2*18600*0.7*0.188)/( *0.188) = PMax [psi] = Min(PMaxA,PMaxB) MIN(389,801) = CheckP = PMax >= P 389 >= = Acceptable t Do Long Seam Length
6 1 Pipe and Shell ver 4.08 Page 6 of 25 2 Bottom Ferrule - Machined From 8" SCH 80 Pipe Description 3 Options: 4 Interior ip? - Calculate interior pressure 5 No Exterior ep? - Calculate exterior pressure 6 Rolled Plate pr? - Pipe or rolled plate 7 Non-Threaded pt? - Type of pipe 8 No relief? - Stress Relief Calculations Required 9 Dimensions: Do [in] - outside diameter t [in] - nominal wall thickness tminug16b [in] - minimum wall per UG-16(b) L [in] - length for volume and weight Corr [in] - corrosion allowance 15 Material and Conditions: 16 SA-312 TP304 Material 17 18,600 S [psi] - allowable stress level El - longitudinal efficiency (circ. stress) Ec - circ. connecting efficiency (longitudinal stress) % UTP [%] - undertolerance allowance UTI [in] - undertolerance allowance P [psi] - interior pressure 23 Stress Classification: 24 NOTE: Both validity checks need to be "Acceptable" in order to use this sheet 25 If not, refer to sheet "Thick Cylindrical Shell" 26 ckvalidity1 = tmin < 0.5*(Do/2) < 0.5*(8.03/2) = Acceptable 27 ckvalidity2 = P< 0.385*S*El < 0.385*18600*0.85 = Acceptable 28 Variables: 29 Td = = UT [in] = t*utp+uti 0.078* = nt [in] = t-corr-ut-td = Ri [in] = Do/2-nt 8.03/ = Volume [cuft] = ((Do/2-t)^2)*π*L/1728 ((8.03/ )^2)*3.1416*1.102/1728 = Weight [lb] = (Do-t)*π*L*t*40.84/ ( )*3.1416*1.102*0.078*40.84/144 = Interior Pressure: VIII-1 UG-27(c)(1,2) 36 ta [in] = P*Ri/(S*El-0.6*P) *3.947/(18600* *200.95) = tb [in] = P*Ri/(2*S*Ec+0.4*P) *3.947/(2*18600* *200.95) = tmin [in] = MAX(ta,tb,tminUG16b) MAX(0.051,0.03,0.063) = tr1 [in] = P*Ri/(S*1-0.6*P) *3.947/(18600*1-0.6*200.95) = Checkt = tmin <= nt <= = Acceptable 41 PMaxA [psi] = (S*El*nt)/(Ri+0.6*nt) (18600*0.85*0.068)/( *0.068) = PMaxB [psi] = (2*S*Ec*nt)/(Ri-0.4*nt) (2*18600*0.7*0.068)/( *0.068) = PMax [psi] = Min(PMaxA,PMaxB) MIN(271,453) = CheckP = PMax >= P 271 >= = Acceptable t Do Long Seam Length
7 1 Cone ver Nov-08 Page 7 of Vessel with Large Opening <- Vessel 5 Cone <- Description 6 7 Dimensions (inch) <- ODL, outside diameter large end <- ODS, outside diameter small end <- t, thickness <- L, length <- Ln, length from small end to nozzle <- ca, Corrosion allowance Material Properties 16 SA <- Material 17 18,600 <- S, allowable stress Level (psi) <- E, long seam weld efficiency t Ln ODS P Long Seam a Length <- P, design pressure (psig) <- Pa, Exterior Pressure ODL Calculated Properties: <- Volume (cubic ft) 28 9 <- Material Weight (lbs cs) <- aº <- a, rad Interior Pressure 1-4(e) 32 nt = t-ca = nt = treq = P*ODL/(2*COS(a)*(S*E+0.4*P)) tl = = *12.75/(2*Cos(0.441)*(18600* * ) Acceptable 35 Outside diameter at nozzle location: ODN = = ODS+2*((ODL-ODS)/2/L)*Ln 37 = *(( )/2/5)* treq at nozzle = P*ODN/(2*COS(a)*(S*E+0.4*P)) tln = = = *10.39/(2*COS(0.441)*(18600* * )) 40 Pmax = 2*S*E*nt*cos(a)/(ODL-0.8*nt*cos(a)) Pmax = = 2*18600*0.7*0.188*cos(0.441)/( *0.188*cos(0.441)) Acceptable 42
8 1 Cone Discontinuity Stress ver 4.03 Page 8 of 25 2 Pressure Vessel Design Handbook - Second Edition - Henry H Bednar. Pages 231 to 240 & ASME VIII-1 5(g) 3 Cone Discontinuity Description 4 Large Cylinder - Zone A: 5 SA Material 6 18,600 Sl [psi] - allowed stress El - longitudinal efficiency ODL [in] - outside diameter tln [in] - thickness 10 Cone - Zones B and C: 11 SA Material 12 18,600 Sc [psi] - allowed stress Ec - longitudinal efficiency AlphaDeg - Angle in degrees tcn [in] - thickness 16 Small Cylinder - Zone D: 17 SA-312 TP304 Material 18 18,600 Ss [psi] - allowed stress Es - longitudinal efficiency ODS [in] - outside diameter tsn [in] - thickness 22 Operating Conditions: P [psi] - design internal pressure Ca [in] - corrosion allowance W [lb] - External load M [in-lb] - External moment 27 Geometry: 28 tl [in] = tln - Ca = tc [in] = tcn - Ca = ts [in] = tsn - Ca = RL [in] = (ODL-tL)/2 Large End ( )/2 = Rs [in] = (ODS-tS)/2 Small End ( )/2 = Alpha [rad] = AlphaDeg/180*π 25.3/180*3.142 = Constants - Large End: 35 nl = tc / tl / = kl = sqrt(cos(alpha)/nl) SQRT(COS(0.441)/1) = V1L = kl*(1+nl^2*(1+2*kl*nl))/(kl*nl^4+2*kl^2*nl^3+2*kl*nl^2+2*nl+kl) *(1+1^2*(1+2*0.951*1))/(0.951*1^4+2*0.951^2*1^3+2*0.951*1^2+2* ) = V2L = kl*nl*(1+v1l*(nl^2-1))/(4*(kl*nl^3+1)) *1*( *(1^2-1))/(4*(0.951*1^3+1)) = Constants - Small End: 42 ns = tc / ts / = ks = sqrt(cos(alpha)/ns) SQRT(COS(0.441)/2.41) = V1S = ks*(1+ns^2*(1+2*ks*ns))/(ks*ns^4+2*ks^2*ns^3+2*ks*ns^2+2*ns+ks) *(1+2.41^2*(1+2*0.613*2.41))/(0.613*2.41^4+2*0.613^2*2.41^3+2*0.613*2.41^2+2* ) = V2S = ks*ns*(1+v1s*(ns^2-1))/(4*(ks*ns^3+1)) *2.41*( *(2.41^2-1))/(4*(0.613*2.41^3+1)) = Discontinuity Influence Coefficients - Large End: 49 XL = 4.669*V2L*TAN(Alpha) 4.669*0.122*TAN(0.441) = YL = 1.285*(V1L - 2*V2L)*tan(Alpha) 1.285*( *0.122)*TAN(0.441) = UL = XL/nL^ /1^2 = A B C D
9 Cone Discontinuity Stress ver 4.03 Page 9 of 25 1 Discontinuity Influence Coefficients - Small End: 2 XS = 4.669*V2S*TAN(Alpha) 4.669*0.101*TAN(0.441) = YS = 1.285*(V1S - 2*V2S)*TAN(Alpha) 1.285*( *0.101)*TAN(0.441) = US = XL/nL^ /1^2 = Equivalent Loads from W and M: 6 ll [lb/in] = ( 4*M/(π*4*RL^2) + (W / (π*2*rl))) 7 ( 4*0/(3.142*4*6.281^2) + (0 / (3.142*2*6.281))) = PeL [psi] = P+(2*lL/RL) 201+(2*0/6.281) = ls [lb/in] = (4*M/(π*4*Rs^2)+(W/(π*2*Rs))) 10 (4*0/(3.142*4*3.976^2)+(0/(3.142*2*3.976))) = PeS [psi] = P+(2*lS/Rs) 201+(2*0/3.976) = Maximum Allowed Stresses: ASME 1-5(g) & UG-23(e) 13 LLmax [psi] = 3*Sl*El 3*18600*0.7 = 39, MLmax [psi] = 1.5*Sl*El 1.5*18600*0.7 = 19, LCmax [psi] = 3*Sc*Min(El,Es) 3*18600*MIN(0.7,0.85) = 39, MCmax [psi] = 1.5*Sc*Min(El,Es) 1.5*18600*MIN(0.7,0.85) = 19, LSmax [psi] = 3*Ss*Es 3*18600*0.85 = 47, MSmax [psi] = 1.5*Ss*Es 1.5*18600*0.85 = 23, Combined Stresses - Large Cylinder - Zone A: 20 Long1 [psi] = (PeL*RL/tL)*(0.5 + XL*SQRT(RL/tL)) 21 ( *6.281/0.188)*( *SQRT(6.281/0.188)) = 13, CkLong1 = ABS(Long1) <= LLmax ABS(13778) <= = Acceptable 23 Long2 [psi] = (PeL*RL/tL)*(0.5 - XL*SQRT(RL/tL)) 24 ( *6.281/0.188)*( *SQRT(6.281/0.188)) = -7, CkLong1 = ABS(Long2) <= LLmax ABS(-7064) <= = Acceptable 26 MemTan1 [psi] = (P*RL/tL)*(1-(PeL/P)*YL*SQRT(RL/tL)) 27 (201*6.281/0.188)*(1-( /201)*0.148*SQRT(6.281/0.188)) = CkMemTan1 = ABS(MemTan1) <= MLmax ABS(977) <= = Acceptable 29 Combined Stresses - Large End of Cone - Zone B: 30 Long3 [psi] = (PeL*RL/tL)*(0.5/(nL*cos(Alpha)) + UL*SQRT(RL/tL)) 31 ( *6.281/0.188)*(0.5/(1*COS(0.441)) *SQRT(6.281/0.188)) = 14, CkLong3 = ABS(Long3) <= LCmax ABS(14133) <= = Acceptable 33 Long4 [psi] = (PeL*RL/tL)*(0.5/(nL*cos(Alpha)) - UL*SQRT(RL/tL)) 34 ( *6.281/0.188)*(0.5/(1*COS(0.441)) *SQRT(6.281/0.188)) = -6, CkLong4 = ABS(Long4) <= LCmax ABS(-6709) <= = Acceptable 36 MemTan2 [psi] = (P*RL/tL)*(1/(nL*cos(Alpha))-(PeL/P)*YL*SQRT(RL/tL)) 37 (201*6.281/0.188)*(1/(1*COS(0.441))-( /201)*0.148*SQRT(6.281/0.188)) = 1, CkMemTan2 = ABS(MemTan2) <= MCmax ABS(1688) <= = Acceptable 39 Combined Stresses - Small End of Cone - Zone C: 40 Long5 [psi] = (PeS*Rs/tS)*(0.5/(nS*cos(Alpha)) + US*SQRT(Rs/tS)) 41 ( *3.976/0.078)*(0.5/(2.41*COS(0.441)) *SQRT(3.976/0.078)) = 21, CkLong5 = ABS(Long5) <= LCmax ABS(21990) <= = Acceptable 43 Long6 [psi] = (PeS*Rs/tS)*(0.5/(nS*cos(Alpha)) - US*SQRT(Rs/tS)) 44 ( *3.976/0.078)*(0.5/(2.41*COS(0.441)) *SQRT(3.976/0.078)) = -17, CkLong6 = ABS(Long6) <= LCmax ABS(-17290) <= = Acceptable 46 MemTan3 [psi] = (P*Rs/tS)*(1/(nS*cos(Alpha))+(PeS/P)*YS*SQRT(Rs/tS)) 47 (201*3.976/0.078)*(1/(2.41*COS(0.441))+( /201)*0.081*SQRT(3.976/0.078)) = 10, CkMemTan3 = ABS(MemTan3) <= MCmax ABS(10650) <= = Acceptable 49 Combined Stresses - Small Cylinder - Zone D: 50 Long7 [psi] = (PeS*Rs/tS)*(0.5 + XS*SQRT(Rs/tS)) 51 ( *3.976/0.078)*( *SQRT(3.976/0.078)) = 21,361
10 Cone Discontinuity Stress ver 4.03 Page 10 of 25 1 CkLong7 = ABS(Long7) <= LSmax ABS(21361) <= = Acceptable 2 Long8 [psi] = (PeS*Rs/tS)*(0.5 - XS*SQRT(Rs/tS)) 3 ( *3.976/0.078)*( *SQRT(3.976/0.078)) = -11,117 4 CkLong8 = ABS(Long8) <= LSmax ABS(-11117) <= = Acceptable 5 MemTan4 [psi] = (P*Rs/tS)*(1+(PeS/P)*YS*SQRT(Rs/tS)) 6 (201*3.976/0.078)*(1+( /201)*0.081*SQRT(3.976/0.078)) = 16,194 7 CkMemTan4 = ABS(MemTan4) <= MSmax ABS(16194) <= = Acceptable
11 30 Nozzle Reinforcement ver 3.90 UW16(c) <- SavedDesign 20-Nov-08 Page 11 of Manual dh for hillside nozzles 22 Vessel with Large Opening <- Vessel Automatic Limit Diameter 33 2" Ferrule - Nozzel A <- Description Curved Shell or Head Section 34 Shell: 35 SA <- Shell Material 36 18,600 <- Sv, shell allowable stress level, PSI Do <- E1, efficiency of shell at nozzle <- Ds, Shell ID Nt <- Vt, shell wall thick, uncorroded, UT removed <- tr, required shell wall thickness int. press.(e=1) <- tre, required shell wall thickness ext. press.(e=1) <- tmin16b, Min allowed wall per UG-16(b) 44 Nozzle: 45 SA-312 TP304 <- Nozzle Material 46 18,600 <- Sn, allowable stress level (Sn) 47 1,400 <- B, from A = <- E, nozzle efficiency <- P, internal design pressure <- Pa, external design pressure <- Do, outside diameter <- dh, id of hillside nozzle <- Nt, wall thick, uncorroded % <- UTp, undertolerance (%) <- L, exterior Projection 61 Reinforcing: <- Leg41, size of weld fillet <- F 87 Variables: Leg41 UW-16.1 (c) 88 UT = Nt*UTp = * Undertolerance UT = Rn = Do/2 - (Nt-nca) + UT = 2.375/2 - ( ) Effective Radius Rn = t = Vt-sca = Effective Shell Thickness t = tn = Nt-nca = Avail. Nozzle Thick. No UT tn = d = dh = Finished Opening Dia. d = fr1 = MIN(Sn/Sv,1) = MIN(18600/18600, 1) fr1 = fr2 = MIN(Sn/Sv,1) = MIN(18600/18600, 1) fr2 = tcleg41 = Min(0.25,0.7*Min(0.75,tn,t)) = Min(0.25,0.7*Min(0.75,0.154,0.188)) tc41 = F = Min(Fenterered, 1) F = Pipe Required Wall Thickness - trn from internal, trne from external pressure 142 LDo = L/Do LDo = Dot = Do/trnE Dot = trn = (P*Rn)/(Sn*E - 0.6*P) <= tn-ut = (201*1.053)/(18600*1-0.6*201) trn = Acceptable 145 trnr = (P*Rn)/(Sn*1-0.6*P) = (201*1.053)/(18600*1-0.6*201) E=1 trnr = trne = (3*Do*Pa)/(4*B) <= tn-ut = (3*2.375*0)/(4*1400) trne = Acceptable 148 Geometry Constraints: *Leg41 >= tc41 0.7*0.188 >= >= Acceptable 180 Appendix 1-7 Necessary Check 181 when Ds>60,if(2*Rn<=Ds/3,if(2*Rn<=40, "App. 1-7 calculations not required","app. 1-7 calculations required"),"app. 1-7 calculations required") 182 when Ds<=60,if(2*Rn<Ds/2,if(2*Rn<20,"App. 1-7 calculations not required","app. 1-7 calculations required"),"app. 1-7 calculations required") 183 App. 1-7 calculations not required 207 Area Replacement: Fig UG-37.1 Pressure From: Internal External 208 A = 1.0*d*tr*F + 2*tn*tr*F*(1-fr1) A Required (internal) = = 1.0*2.333*0.088*1 + 2*0.154*0.088*1*(1-1) 212 Ae = 0.5*(d*trE*1 + 2*tn*trE*1*(1-fr1)) = 0.5*(2.333*0*1 + 2*0.154*0*1*(1-1)) A Required (external) = A1 = max(d, 2*(t+tn)) * (E1*t-F*tr)-2*tn*(E1*t-F*tr)*(1-fr1) A1 = = max(2.333,2*( ))* (1* *0.088)-2*0.154*(1* *0.088)*(1-1) 219 A1e = max(d, 2*(t+tn)) * (E1*t-F*trE)-2*tn*(E1*t-F*trE)*(1-fr1) A1e = = max(2.333,2*( ))* (1* *0)-2*0.154*(1* *0)*(1-1) 225 A2 = min((tn-trnr)*fr2*min(5*t,2*l), (tn-trnr)*fr2*min(5*tn,2*l)) A2 = = min(( )*1*min(5*0.188,2*3), ( )*1*Min(5*0.154,2*3)) 230 A2e = min((tn-trne)*fr2*min(5*t,2*l), (tn-trne)*fr2*min(5*tn,2*l)) A2e = = min(( )*1*min(5*0.188,2*3), ( )*1*Min(5*0.154,2*3)) 240 A41 = Leg41^2*fr2 = 0.188^2*1 A41 = Actual Area = Acceptable Actual-Required = Tstd = Standard pipe wall thickness from chart Tstd = Swre = tr * Pa / P = * 0 / Req. Exterior pressure Swre = Nact = Nt * (1-UTp) = * ( ) Actual Wall Thick. Nact = Tt = 0.8/Nth = 0.8/0 Ug-31(c)(2) threads Tt = UG-45 Acceptable 336 UG45 = Max(UG45a, UG45b) <= Nact = Max(0.011, 0.088) <= UG45 = UG45a = Max(trn,trnE) + Nca + Tt = Max(0.011,0) UG45a = UG45b = Min(UG45b3,UG45b4) = Min(0.088, 0.135) UG45b = UG45b1 = Max(tr + Sca, tmin16b + Sca) = Max( , ) UG45b1 = UG45b2 = Max(Swre + Sca,tmin16b + Sca) = Max(0 + 0, ) UG45b2 = 341 UG45b3 = Max(UG45b1,UG45b2) = Max(0.088,) UG45b3 = UG45b4 = Tstd* Nca = 0.154* UG45b4 = Nozzle t Leg41 Shell Vt
12 18 B16.5/16.47 Flange Ver 2.61 SlipOn 20-Nov-08 Page 12 of #VALUE! Sample Vessel 5 <- Vessel 22 2" 300# RFSO Flange <- Description Select Flange 25 SA <- Category 26 Forged <- Material Type 27 SA 182 Gr. F304 <- Material <- Pressure Class <- Nominal Size Nominal - 18Cr-8Ni 33 Table Max Temp ºF Pod, pipe OD Nozzle <- tn, Nozzle Wall Thickness (inch) <- tnr, Required Nozzle Wall Thickness (inch) Operating Conditions Acceptable <- T, temperature ºF Max [p1] <- P, pressure, psig Max [p2] <- Corr, corrosion allowance Flange Welds: <- F1, pipe fillet size <- F2, flange fillet size F <- Sp, allowable stress, pipe <- Sf, allowable stress, flange Geometry constraint: VIII UW-21 (b) 61 wtmin = 0.7*tn = 0.7*0.154 Req. weld throat wtmin = wt = 0.7*MIN(F1,F2) Actual weld throat wt = =0.7*MIN(0.154,0.154) Acceptable Weld Strength: 69 Min Sa = MIN(Sp,Sf) = MIN(18600,17400) Min Sa = 17, Max Weld Stress = Sa * 0.49 = * 0.49 Max S = 8, Weld Load = POD^2*pi*P/4 = 2.375^2*pi* /4 Load = Weld Area = Pod*pi*(F1-corr + F2) Area = = 2.375*pi*( ) 78 Weld Stress = Load/Area = /2.298 Stress = Acceptable
13 30 Nozzle Reinforcement ver 3.90 UW16(c) <- SavedDesign 20-Nov-08 Page 13 of Automatic dh - not hillside 22 Vessel with Large Opening <- Vessel Automatic Limit Diameter 33 2" Heavy Ferrule - Nozzle B <- Description Curved Shell or Head Section 34 Shell: 35 SA <- Shell Material 36 18,600 <- Sv, shell allowable stress level, PSI Do <- E1, efficiency of shell at nozzle <- Ds, Shell ID Nt <- Vt, shell wall thick, uncorroded, UT removed <- tr, required shell wall thickness int. press.(e=1) <- tre, required shell wall thickness ext. press.(e=1) <- tmin16b, Min allowed wall per UG-16(b) 44 Nozzle: 45 SA <- Nozzle Material 46 18,600 <- Sn, allowable stress level (Sn) 47 1,400 <- B, from A = <- E, nozzle efficiency <- P, internal design pressure <- Pa, external design pressure <- Do, outside diameter <- Nt, wall thick, uncorroded % <- UTp, undertolerance (%) <- L, exterior Projection 61 Reinforcing: <- Leg41, size of weld fillet <- F 87 Variables: Leg41 UW-16.1 (c) 88 UT = Nt*UTp = * 0 Undertolerance UT = Rn = Do/2 - (Nt-nca) + UT = 2.192/2 - ( ) + 0 Effective Radius Rn = t = Vt-sca = Effective Shell Thickness t = tn = Nt-nca = Avail. Nozzle Thick. No UT tn = d = Do-2*tn = *0.161 Opening Dia. d = fr1 = MIN(Sn/Sv,1) = MIN(18600/18600, 1) fr1 = fr2 = MIN(Sn/Sv,1) = MIN(18600/18600, 1) fr2 = tcleg41 = Min(0.25,0.7*Min(0.75,tn,t)) = Min(0.25,0.7*Min(0.75,0.161,0.188)) tc41 = F = Min(Fenterered, 1) F = Pipe Required Wall Thickness - trn from internal, trne from external pressure 142 LDo = L/Do LDo = Dot = Do/trnE Dot = trn = (P*Rn)/(Sn*E - 0.6*P) <= tn-ut = (201*0.935)/(18600*1-0.6*201) trn = Acceptable 145 trnr = (P*Rn)/(Sn*1-0.6*P) = (201*0.935)/(18600*1-0.6*201) E=1 trnr = trne = (3*Do*Pa)/(4*B) <= tn-ut = (3*2.192*0)/(4*1400) trne = Acceptable 148 Geometry Constraints: *Leg41 >= tc41 0.7*0.188 >= >= Acceptable 180 Appendix 1-7 Necessary Check 181 when Ds>60,if(2*Rn<=Ds/3,if(2*Rn<=40, "App. 1-7 calculations not required","app. 1-7 calculations required"),"app. 1-7 calculations required") 182 when Ds<=60,if(2*Rn<Ds/2,if(2*Rn<20,"App. 1-7 calculations not required","app. 1-7 calculations required"),"app. 1-7 calculations required") 183 App. 1-7 calculations not required 207 Area Replacement: Fig UG-37.1 Pressure From: Internal External 208 A = 1.0*d*tr*F + 2*tn*tr*F*(1-fr1) A Required (internal) = = 1.0*1.87*0.067*1 + 2*0.161*0.067*1*(1-1) 212 Ae = 0.5*(d*trE*1 + 2*tn*trE*1*(1-fr1)) = 0.5*(1.87*0*1 + 2*0.161*0*1*(1-1)) A Required (external) = A1 = max(d, 2*(t+tn)) * (E1*t-F*tr)-2*tn*(E1*t-F*tr)*(1-fr1) A1 = = max(1.87,2*( ))* (1* *0.067)-2*0.161*(1* *0.067)*(1-1) 219 A1e = max(d, 2*(t+tn)) * (E1*t-F*trE)-2*tn*(E1*t-F*trE)*(1-fr1) A1e = = max(1.87,2*( ))* (1* *0)-2*0.161*(1* *0)*(1-1) 225 A2 = min((tn-trnr)*fr2*min(5*t,2*l), (tn-trnr)*fr2*min(5*tn,2*l)) A2 = = min(( )*1*min(5*0.188,2*1.5), ( )*1*Min(5*0.161,2*1.5)) 230 A2e = min((tn-trne)*fr2*min(5*t,2*l), (tn-trne)*fr2*min(5*tn,2*l)) A2e = = min(( )*1*min(5*0.188,2*1.5), ( )*1*Min(5*0.161,2*1.5)) 240 A41 = Leg41^2*fr2 = 0.188^2*1 A41 = Actual Area = Acceptable Actual-Required = Tstd = Standard pipe wall thickness from chart Tstd = Swre = tr * Pa / P = * 0 / Req. Exterior pressure Swre = Nact = Nt * (1-UTp) = * (1-0) Actual Wall Thick. Nact = Tt = 0.8/Nth = 0.8/0 Ug-31(c)(2) threads Tt = UG-45 Acceptable 336 UG45 = Max(UG45a, UG45b) <= Nact = Max(0.01, 0.067) <= UG45 = UG45a = Max(trn,trnE) + Nca + Tt = Max(0.01,0) UG45a = UG45b = Min(UG45b3,UG45b4) = Min(0.067, 0.127) UG45b = UG45b1 = Max(tr + Sca, tmin16b + Sca) = Max( , ) UG45b1 = UG45b2 = Max(Swre + Sca,tmin16b + Sca) = Max(0 + 0, ) UG45b2 = 341 UG45b3 = Max(UG45b1,UG45b2) = Max(0.067,) UG45b3 = UG45b4 = Tstd* Nca = 0.145* UG45b4 = Nozzle t Leg41 Shell Vt
14 30 Nozzle Reinforcement ver 3.90 UW16(c) <- SavedDesign 20-Nov-08 Page 14 of Automatic dh - not hillside 22 Vessel with Large Opening <- Vessel Manually enter Limit Diameter 33 10" Nozzle With Limit Radius - Nozzle C <- Description Curved Shell or Head Section 34 Shell: 35 SA <- Shell Material 36 18,600 <- Sv, shell allowable stress level, PSI Do <- E1, efficiency of shell at nozzle <- Ds, Shell ID Nt <- Vt, shell wall thick, uncorroded, UT removed <- tr, required shell wall thickness int. press.(e=1) <- tre, required shell wall thickness ext. press.(e=1) <- tmin16b, Min allowed wall per UG-16(b) 44 Nozzle: 45 SA-312 TP304 <- Nozzle Material 46 18,600 <- Sn, allowable stress level (Sn) 47 1,400 <- B, from A = <- E, nozzle efficiency <- P, internal design pressure <- Pa, external design pressure <- Do, outside diameter <- dlr, Limit radius <= d <- Nt, wall thick, uncorroded % <- UTp, undertolerance (%) <- L, exterior Projection 61 Reinforcing: <- Leg41, size of weld fillet <- F 87 Variables: Leg41 UW-16.1 (c) 88 UT = Nt*UTp = * Undertolerance UT = Rn = Do/2 - (Nt-nca) + UT = 10.75/2 - ( ) Effective Radius Rn = t = Vt-sca = Effective Shell Thickness t = tn = Nt-nca = Avail. Nozzle Thick. No UT tn = d = Do-2*tn = *0.365 Opening Dia. d = fr1 = MIN(Sn/Sv,1) = MIN(18600/18600, 1) fr1 = fr2 = MIN(Sn/Sv,1) = MIN(18600/18600, 1) fr2 = tcleg41 = Min(0.25,0.7*Min(0.75,tn,t)) = Min(0.25,0.7*Min(0.75,0.365,0.188)) tc41 = F = Min(Fenterered, 1) F = Pipe Required Wall Thickness - trn from internal, trne from external pressure 142 LDo = L/Do LDo = Dot = Do/trnE Dot = trn = (P*Rn)/(Sn*E - 0.6*P) <= tn-ut = (201*5.056)/(18600*1-0.6*201) trn = Acceptable 145 trnr = (P*Rn)/(Sn*1-0.6*P) = (201*5.056)/(18600*1-0.6*201) E=1 trnr = trne = (3*Do*Pa)/(4*B) <= tn-ut = (3*10.75*0)/(4*1400) trne = Acceptable 148 Geometry Constraints: *Leg41 >= tc41 0.7*0.25 >= >= Acceptable 180 Appendix 1-7 Necessary Check 181 when Ds>60,if(2*Rn<=Ds/3,if(2*Rn<=40, "App. 1-7 calculations not required","app. 1-7 calculations required"),"app. 1-7 calculations required") 182 when Ds<=60,if(2*Rn<Ds/2,if(2*Rn<20,"App. 1-7 calculations not required","app. 1-7 calculations required"),"app. 1-7 calculations required") 183 App. 1-7 calculations required 207 Area Replacement: Fig UG-37.1 Pressure From: Internal External 208 A = 1.0*d*tr*F + 2*tn*tr*F*(1-fr1) A Required (internal) = = 1.0*10.02*0.067*1 + 2*0.365*0.067*1*(1-1) 212 Ae = 0.5*(d*trE*1 + 2*tn*trE*1*(1-fr1)) = 0.5*(10.02*0*1 + 2*0.365*0*1*(1-1)) A Required (external) = A1 = (2*dLr-d) * (E1*t-F*tr)-2*tn*(E1*t-F*tr)*(1-fr1) A1 = = 5.01* (1* *0.067)-2*0.365*(1* *0.067)*(1-1) 219 A1e = (2*dLr-d) * (E1*t-F*trE)-2*tn*(E1*t-F*trE)*(1-fr1) A1e = = 5.01* (1* *0)-2*0.365*(1* *0)*(1-1) 225 A2 = min((tn-trnr)*fr2*min(5*t,2*l), (tn-trnr)*fr2*min(5*tn,2*l)) A2 = = min(( )*1*min(5*0.188,2*4), ( )*1*Min(5*0.365,2*4)) 230 A2e = min((tn-trne)*fr2*min(5*t,2*l), (tn-trne)*fr2*min(5*tn,2*l)) A2e = = min(( )*1*min(5*0.188,2*4), ( )*1*Min(5*0.365,2*4)) 240 A41 = Leg41^2*fr2 = 0.25^2*1 A41 = Actual Area = Acceptable Actual-Required = Tstd = Standard pipe wall thickness from chart Tstd = Swre = tr * Pa / P = * 0 / Req. Exterior pressure Swre = Nact = Nt * (1-UTp) = * ( ) Actual Wall Thick. Nact = Tt = 0.8/Nth = 0.8/0 Ug-31(c)(2) threads Tt = UG-45 Acceptable 336 UG45 = Max(UG45a, UG45b) <= Nact = Max(0.055, 0.067) <= UG45 = UG45a = Max(trn,trnE) + Nca + Tt = Max(0.055,0) UG45a = UG45b = Min(UG45b3,UG45b4) = Min(0.067, 0.319) UG45b = UG45b1 = Max(tr + Sca, tmin16b + Sca) = Max( , ) UG45b1 = UG45b2 = Max(Swre + Sca,tmin16b + Sca) = Max(0 + 0, ) UG45b2 = 341 UG45b3 = Max(UG45b1,UG45b2) = Max(0.067,) UG45b3 = UG45b4 = Tstd* Nca = 0.365* UG45b4 = Nozzle t Leg41 Shell Vt
15 t 11 App 1-7 Nozzle Ver 1.07 Fig Case B 20-Nov-08 Page 15 of Vessel with Large Opening <- Vessel 14 10" Nozzle App. 1-7 <- Description Dimensions: <- Dv, vessel outside diameter <- t, vessel wall <- Dn, nozzle outside diameter <- tn, nozzle wall <- Fw, flange width <- tf, flange thickness <- Hf, flange standoff <- P, pressure 31 18,600 <- Ss, stress limit for shell 32 18,600 <- Sn, stress limit for nozzle <- Aactual, actual area from limit radius by app. 1-7(a) <- Arequired, required area Geometry 38 Rv = Dv/2-t = 12.75/ Rv = Rn = Dn/2-tn = 10.75/ Rn = Rm = Rv + t/2 = /2 Rm = Rnm = Rn + tn/2 = /2 Rnm = B = Sqrt(Rm*t) = Sqrt(6.281*0.188) B = H = Hf = 5 H = Hfmax = Max(Sqrt(Rnm*tn),16*tn) >= Hf Acceptable Hmax = = Max(Sqrt(5.193*0.365),16*0.365) >= App. 1-7(a) 54 Limit radius = Max(0.75*2*Rn, Rn+t+tn) dlr = = Max(0.75*2*5.01, ) 56 Aactual >= (2/3)*Arequired >= 0.674*2/3 Acceptable App. 1-7(b) necessary check 0 App. 1-7(b) not requir 59 If(Rn/Rv>0.7,"U-2(g) needed","u-2(g) not needed") U-2(g) needed 60 If(2*Rv>60,"Required","not required) 0 Not required 61 If(2*Rn>40,if(2*Rn>3.4*Sqrt(Rv*t),"Required","Not required"),"not required") 0 Not Required 62 Moment of Inertia about Neutral Axis a 63 Width Depth Y Area A*Y A*Y^2 Io Depth Shell - As Flange - Af Nozzle - An 68 Area = As Total a = AY/As = /4.098 a = I = AYtwo+IoD - Cxx*Ay = * I = Stress Limts 74 SmMax = Min(Ss,Sn) = Min(18600,18600) SmMax = 18, SbMax = 1.5*SmMax = 1.5*18600 SbMax = 27, Membrane Stress 78 Sm = P*(Rv*(Rn+tn+B) + Rn*(t+te+H))/As <= SmMax Sm = 3, = *(6.187*( ) *( ))/4.098 <= Acceptable Bending Stress 82 e = a-t/2 = /2 e = M = P*(Rn^3/6 + Rv*Rn*e) M = 25, = *(5.01^3/ *5.01*3.397) 85 Sb = M*a/I = 25373*3.491/ Sb = 7, Nozzle C L C L Cylindrical Shell 87 Limit = Sb + Sm <= SbMax = <= Limit = 11, Acceptable Rnm Rn Hf a An tn Af Fw Neutral Axis As B tf Fig Case B e Rv Rm
16 1 Flange ver 4.27 Page 16 of 25 2 ASME VIII Div I Appendix " Custom Flange Description 4 Dimensions: 5 Fig2-4(3a) fd? - Select a flange design A [in] - flange OD Bn [in] - ID, uncorroded t [in] - flange thickness tn [in] - nozzle wall thickness treq [in] - required nozzle wall 11 Gasket: GOD [in] - gasket OD GID [in] - gasket ID m - gasket factor gy - gasket factor y 16 Bolting: varc [in] - bolt circle dia BoltOD [in] - bolt size Nbolt - number of bolts Leg1 [in] Leg3 [in] 22 Operating Conditions: Corr [in] - corrosion allowance P [psi] - internal operating pressure Pe [psi] - external operating pressure 26 Material Properties: 27 NonCast CastMaterial? - Cast Or NonCast 28 18,600 Sf [psi] - allowable flange stress at DESIGN temp ,000 Sfa [psi] - Allowable Flange Stress at ASSEMBLY temp ,400,000 Efo [psi] -Operating Flange Modulus 31 28,300,000 Efs [psi] - Seating Flange Modulus 32 25,000 Sb [psi] - allowable bolt stress at DESIGN temp 33 25,000 Sba [psi] - allowable bolt stress at ASSEMBLY temp 34 Geometry Constraints: 35 tx = max(1/4,2*treq) MAX(1/4,2*0.055) = c = MIN(tn,tx) MIN(0.365,0.25) = mtc = 0.7*c ~~ Min Throat 0.7*0.25 = ThroatLeg1 = 0.7*Leg1 0.7*0.365 = ChTL1 = ThroatLeg1 >= mtc >= = Acceptable 40 ChTL3 = 0.7*Leg3 >= mtc 0.7*0.365 >= = Acceptable 41 MaxSetback = c + 1/ /4 = NutG [in] = PVELookup("TEMATableD5","Lookup","NutWidth",BoltOD) Rb [in] = PVELookup("TEMATableD5","Lookup","Rb",BoltOD) E [in] = PVELookup("TEMATableD5","Lookup","E",BoltOD) WrenchClearance = varc/2-b/2-leg1-rb ~~ TEMA Table D-5 13/ / = CkWrenchClr = WrenchClearance > > 0 = Acceptable 47 NutClearance = varc/2-b/2-leg1-nutg/2 ~~ TEMA Table D / / /2 = CkNutClr = NutClearance > > 0 = Acceptable 50 EdgeClearance = (A-E)-varC ~~ TEMA Table D-5 ( )-13 = ckedge = EdgeClearance > 0 1 > 0 = Acceptable 3 1 Leg3 Leg1
17 Flange ver 4.27 Page 17 of 25 1 Calculated Dimensions: 2 B = Bn+2*Corr *0 = varn = (GOD-GID)/2 ~~ Gasket width in contact ( )/2 = b0 = varn / 2 ~~ Gasket seating width / 2 = varb = IF(b0>0.25,Sqrt(b0)/2,b0) ~~ Effective seating width 6 IF(0.344>0.25,SQRT(0.344)/2,0.344) = varg = IF(b0>0.25,GOD-2*varb,(GOD-GID)/2 + GID) 8 IF(0.344>0.25, *0.293,( )/ ) = Bolt Loads: (VIII App 2-5) 10 Bolt size and class: 5/8-11 UNC 2A 11 H = 0.785*varG^2*P ~~ end load 0.785*11.539^2*201 = 21, He = 0.785*varG^2*Pe ~~ end load external pressure 0.785*11.539^2*0 = 0 13 HP = 2*varb*3.14*varG*m*P ~~ contact load 2*0.293*3.14*11.539*1*201 = 4, HD = pi()/4 * B^2 * P ~~ end load PI()/4 * 10.75^2 * 201 = 18, HDe = pi()/4 * B^2 * Pe ~~ end load external pressure PI()/4 * 10.75^2 * 0 = 0 16 HT = H - HD ~~ face load = 2, HTe = He - HDe ~~ face load external 0-0 = 0 18 Wm1 = H + HP ~~ bolt load = 25, Wm2 = pi()*varb*varg*gy ~~ seating load PI()*0.293*11.539*200 = 2, Am = Max(Wm1/Sb, Wm2/Sba) ~~ Bolt area required 21 MAX(25272/25000, 2125/25000) = RootArea [sq. in] = PVELookup("BoltSizing","Lookup","Root Area",BoltOD) Ab = RootArea*Nbolt 0.208*8 = CheckExcess = Ab>=Am 1.664>=1.011 = Acceptable 25 Flange Loads: (App 2-5) 26 W [lb] = (Am + Ab)*Sba/2 ~~ seating conditions ( )*25000/2 = 33, HG [lb] = Wm1 - H ~~ operating conditions = 4, TBoltLoad [lb] = (W+Wm1)/Nbolt ( )/8 = 7, Flange Moment Arms: (Table App loose flanges) 30 mhd [in] = (varc-b)/2 ( )/2 = mht [in] = (mhd+mhg)/2 ( )/2 = mhg [in] = (varc-varg)/2 ( )/2 = Flange Moments: (App 2-6) 34 MD [in-lb] = HD * mhd ~~ end pressure * = 20, MT [in-lb] = HT * mht ~~ face pressure 2764 * = 2, MG [in-lb] = HG * mhg ~~ gasket load 4269 * = 3, Mo1e [in-lb] = HDe*(mhD-mhG)+HTe*(mhT-mhG) ~~ total operating external 38 0*( )+0*( ) = 0 39 Mo1 [in-lb] = Max(MD+MT+MG,Mo1e) ~~ total operating 40 MAX( ,0) = 26, Mo2 [in-lb] = W*(varC-varG)/2 ~~ total seating 33436*( )/2 = 24, Graph: App Value of Y 43 K = A/B 14.75/10.75 = Y = PVELookup("Y","FlangeFactorK",K) Flange Seating Stress: (App 2-7,8) 46 STs = Y*ABS(Mo2) / (t^2*b) 6.299*ABS(24430) / (1.25^2*10.75) = 9, CheckSTs = ABS(STs) <= Sfa ABS(9161) <= = Acceptable 48 Flange Operating Stress: (App 2-7,8) 49 STo = Y*ABS(Mo1) / (t^2*b) 6.299*ABS(26202) / (1.25^2*10.75) = 9, CheckSTo = STo <= Sf 9826 <= = Acceptable 51 Flange Flexibility: (App 2-14) 52 Jseating = (109.4*Mo2) / (Efs*t^3*ln(K)*0.2) 53 (109.4*24430) / ( *1.25^3*LN(1.372)*0.2) = 0.764
18 Flange ver 4.27 Page 18 of 25 1 CheckJSt = ABS(Jseating) <= 1 ABS(0.764) <= 1 = Acceptable 2 Joperating = (109.4*Mo1) / (Efo*t^3*ln(K)*0.2) 3 (109.4*26202) / ( *1.25^3*LN(1.372)*0.2) = CheckJOp = ABS(Joperating) <= 1 ABS(0.879) <= 1 = Acceptable
19 1 Flange ver 4.27 Page 19 of 25 2 ASME VIII Div I Appendix 2 3 Swing Bolts on Pipe Description 4 Dimensions: 5 Fig2-4(6)modified fd? - Select a flange design A [in] - flange OD Bn [in] - ID, uncorroded t [in] - flange thickness h [in] - hub length g0f [in] - hub thickness g1 [in] - hub base thickness 12 Gasket: GOD [in] - gasket OD GID [in] - gasket ID m - gasket factor 16 0 gy - gasket factor y 17 Bolting: varc [in] - bolt circle dia BoltOD [in] - bolt size Nbolt - number of bolts 21 Operating Conditions: Corr [in] - corrosion allowance P [psi] - internal operating pressure Pe [psi] - external operating pressure 25 Material Properties: 26 NonCast CastMaterial? - Cast Or NonCast 27 18,600 Sf [psi] - allowable flange stress at DESIGN temp ,000 Sfa [psi] - Allowable Flange Stress at ASSEMBLY temp ,400,000 Efo [psi] -Operating Flange Modulus 30 28,300,000 Efs [psi] - Seating Flange Modulus 31 25,000 Sb [psi] - allowable bolt stress at DESIGN temp 32 25,000 Sba [psi] - allowable bolt stress at ASSEMBLY temp 33 Geometry Constraints: 34 NutG [in] = PVELookup("TEMATableD5","Lookup","NutWidth",BoltOD) Rh [in] = PVELookup("TEMATableD5","Lookup","Rh",BoltOD) E [in] = PVELookup("TEMATableD5","Lookup","E",BoltOD) EdgeClearance = (A-E)-varC ~~ TEMA Table D-5 ( ) = Calculated Dimensions: 39 g0 = g0f-corr = gone = g1-corr = B = Bn+2*Corr *0 = varr = (varc-b)/2 - gone ~~ Gasket width in contact ( )/ = varn = (GOD-GID)/2 ~~ Gasket width in contact ( )/2 = b0 = varn / 2 ~~ Gasket seating width 0.27 / 2 = varb = IF(b0>0.25,Sqrt(b0)/2,b0) ~~ Effective seating width 46 IF(0.135>0.25,SQRT(0.135)/2,0.135) = varg = IF(b0>0.25,GOD-2*varb,(GOD-GID)/2 + GID) 48 IF(0.135>0.25, *0.135,( )/ ) = hub = h ~~ Length of Hub 1.5 = Bolt Loads: (VIII App 2-5) 51 Bolt size and class: 3/4-10 UNC 2A 52 H = 0.785*varG^2*P ~~ end load 0.785*12.125^2*201 = 23,191 t h GOD GID B A C Bolt Circle Line Fig. 2-4 (6) Modified
20 Flange ver 4.27 Page 20 of 25 1 He = 0.785*varG^2*Pe ~~ end load external pressure 0.785*12.125^2*0 = 0 2 HP = 2*varb*3.14*varG*m*P ~~ contact load 2*0.135*3.14*12.125*0*201 = 0 3 HD = pi()/4 * B^2 * P ~~ end load PI()/4 * ^2 * 201 = 20,425 4 HDe = pi()/4 * B^2 * Pe ~~ end load external pressure PI()/4 * ^2 * 0 = 0 5 HT = H - HD ~~ face load = 2,766 6 HTe = He - HDe ~~ face load external 0-0 = 0 7 Wm1 = H + HP ~~ bolt load = 23,191 8 Wm2 = pi()*varb*varg*gy ~~ seating load PI()*0.135*12.125*0 = 0 9 Am = Max(Wm1/Sb, Wm2/Sba) ~~ Bolt area required 10 MAX(23191/25000, 0/25000) = RootArea [sq. in] = PVELookup("BoltSizing","Lookup","Root Area",BoltOD) Ab = RootArea*Nbolt 0.311*6 = CheckExcess = Ab>=Am 1.866>=0.928 = Acceptable 14 Flange Loads: (App 2-5) 15 W [lb] = (Am + Ab)*Sba/2 ~~ seating conditions ( )*25000/2 = 34, HG [lb] = Wm1 - H ~~ operating conditions = 0 17 TBoltLoad [lb] = (W+Wm1)/Nbolt ( )/6 = 9, Flange Moment Arms: (Table App Integral flanges) 19 mhd [in] = varr+0.5*gone *0.625 = mht [in] = (varr+gone+mhg)/2 ( )/2 = mhg [in] = (varc-varg)/2 ( )/2 = Flange Moments: (App 2-6) 23 MD [in-lb] = HD * mhd ~~ end pressure * = 28, MT [in-lb] = HT * mht ~~ face pressure 2766 * 1.5 = 4, MG [in-lb] = HG * mhg ~~ gasket load 0 * = 0 26 Mo1e [in-lb] = HDe*(mhD-mhG)+HTe*(mhT-mhG) ~~ total operating external 27 0*( )+0*( ) = 0 28 Mo1 [in-lb] = Max(MD+MT+MG,Mo1e) ~~ total operating 29 MAX( ,0) = 32, Mo2 [in-lb] = W*(varC-varG)/2 ~~ total seating 34921*( )/2 = 45, Graphs: App Values of F, f, T, U, V, Y and Z 32 h0 = sqrt(b*g0) SQRT(11.376*0.188) = hh0 = hub/h0 1.5/1.462 = g1g0 = gone/g /0.188 = F = PVELookup("F","FlangeFactor",hh0,g1g0) V = PVELookup("V","FlangeFactor",hh0,g1g0) smallf = MAX(PVELookup("smallF","FlangeFactor",hh0,g1g0),1) K = A/B 12.75/ = T = PVELookup("T","FlangeFactorK",K) U = PVELookup("U","FlangeFactorK",K) Y = PVELookup("Y","FlangeFactorK",K) Z = PVELookup("Z","FlangeFactorK",K) d = (U/V)*h0*g0^2 (18.713/0.069)*1.462*0.188^2 = e = F / h / = L = (t*e + 1)/T + t^3/d (3* )/ ^3/ = Flange Seating Stress: (App 2-7,8) 47 SHs = smallf*abs(mo2) / ( L*gOne^2 * B) 48 1*ABS(45833) / ( 3.203*0.625^2 * ) = 3, CheckSHs = SHs <= 1.5*(Sfa) 3220 <= 1.5*(20000) = Acceptable 50 SRs = (1.33*t*e+1)*ABS(Mo2) / (L*t^2*B) 51 (1.33*3* )*ABS(45833) / (3.203*3^2*11.376) = CheckSRs = SRs <= Sfa 398 <= = Acceptable 53 STs = (Y*ABS(Mo2) / (t^2*b)) - Z*SRs 54 (17.029*ABS(45833) / (3^2*11.376)) *398 = 4,122
21 Flange ver 4.27 Page 21 of 25 1 CheckSTs = ABS(STs) <= Sfa ABS(4122) <= = Acceptable 2 SAs = (SHs + Max(SRs, STs))/2 ( MAX(398, 4122))/2 = 3,671 3 CheckSAs = SAs <= Sfa 3671 <= = Acceptable 4 Flange Operating Stress: (App 2-7,8) 5 SHo = smallf*mo1/(l*gone^2*b) 1*32223/(3.203*0.625^2*11.376) = 2,264 6 CheckSHo = SHo <= 1.5*(Sf) 2264 <= 1.5*(18600) = Acceptable 7 SRo = (1.33*t*e+1)*Mo1/(L*t^2*B) 8 (1.33*3* )*32223/(3.203*3^2*11.376) = CheckSRo = SRo <= Sf 279 <= = Acceptable 10 STo = Y*Mo1/(t^2*B)-Z*SRo *32223/(3^2*11.376)-8.808*279 = 2, CheckSTo = STo <= Sf 2898 <= = Acceptable 12 SAo = (SHo+Max(SRo,STo))/2 (2264+MAX(279,2898))/2 = 2, CheckSAo = SAo <= Sf 2581 <= = Acceptable 14 Flange Flexibility: (App 2-14) 15 Jseating = (52.14*Mo2*V) / (L*Efs*g0^2*h0*0.3) 16 (52.14*45833*0.069) / (3.203* *0.188^2*1.462*0.3) = CheckJSt = ABS(Jseating) <= 1 ABS(0.117) <= 1 = Acceptable 18 Joperating = (52.14*Mo1*V) / (L*Efo*g0^2*h0*0.3) 19 (52.14*32223*0.069) / (3.203* *0.188^2*1.462*0.3) = CheckJOp = ABS(Joperating) <= 1 ABS(0.088) <= 1 = Acceptable
22 1 Swing Bolt and Cover ver 4.03 Page 22 of Cover Swing Bolts Description 4 Cover: P [psi] - Pressure GOd [in] - Gasket OD Dc [in] - Cover OD tc [in] - Cover Thickness wc [in] - Tab Width BCD [in] - Bolt Circle Diameter 11 SA Cover Material 12 18,600 CSA [psi] - Allowable Stress 13 Eye Bolt: 14 6 n - Number of bolts Dia [in] - Bolt Diameter Rdia [in] - Thread Root Diameter ID [in] - ID of Eye OD [in] - OD of Eye 19 SA-193 B7 Bolt Material 20 25,000 BSA [psi] - Allowable Stress 21 Pin: 22 SA-193 B7 PinMat - Pin Material Pin [in] - Pin OD 24 25,000 PSA [psi] - Allowable Stress 25 Lugs: L [in] - Height ch [in] - Half Width tl [in] - Thickness F [in] - Weld Fillet Size 30 SA Lug Material 31 18,600 LSA [psi] - Allowable Stress 32 Load: no gasket seating load, pf: Pressure Load 33 Do [in] = BCD-2*cH *1 = pf [lb] = (P*π*GOd^2)/4 (201*3.14*12.395^2)/4 = Eye bolts: Baa: Actual Area 1, Bab: Actual Area 2, ra: Required Area, Ba: Minimum Area, SF: Seating Force, LpB: Load per Bolt 36 Baa [in 2 ] = n*π*rdia^2/4 6*3.14*0.627^2/4 = Bab [in 2 ] = n*(od-id)*dia 6*( )*0.75 = ra [in 2 ] = pf/bsa /25000 = CheckrA = ra<=min(baa,bab) 0.97<=MIN(1.853,3.375) = Acceptable 40 Ba [in 2 ] = Min(Baa,Bab) MIN(1.853,3.375) = SF [lb] = Max(Ba*BSA/2,pF) MAX(1.853*25000/2, ) = LpB [lb] = SF/n /6 = Pin: PA: Pin Area, MSp: Max Sp, Sp: Shear 44 PA [in 2 ] = (π*pin^2/4) (3.14*0.75^2/4) = MSp [psi] = 0.8*PSA 0.8*25000 = Sp [psi] = LpB/(2*PA) /(2*0.442) = CheckShear = Sp <= MSp 4574 <= = Acceptable
23 Swing Bolt and Cover ver 4.03 Page 23 of 25 1 Lug: Ratio <= 1, msl: Max Shear, LL: Lug Load, LS: Lug Shear, rls: Load Ratio, mbl: Max Bending, il: Moment of Inertia 2 ml: Moment, LB: Bending Load, rlb: Load Ratio, LugRatio: Factored Load 3 msl [psi] = LSA* *0.8 = LL [lb] = LpB/ /2 = LS [psi] = LL/(tL*L) /(0.375*2.5) = rls = LS/msL 2155/14880 = mbl [psi] = LSA* *1.5 = cl [in] = L/2 2.5/2 = il [in 4 ] = (tl*l^3)/12 (0.375*2.5^3)/12 = ml [in-lb] = LL*cH *1 = LB [lb] = ml*cl/il *1.25/0.488 = rlb = LB/mbL /27900 = LugRatio = SQRT(rLS^2+rLB^2) SQRT(0.145^ ^2) = CheckLug = LugRatio <= <= 1 = Acceptable 15 Lug Weld: Factored load ratio must be less than 1, msw: Max Shear/Bending, WS: Weld Shear, rws: Load Ratio 16 WB: Bending Load, rwb: Load Ratio 17 LugWeldRatio: Factored Load 18 msw [psi] = 0.49*MIN(LSA, PSA) 0.49*MIN(18600, 25000) = Wa [in 2 ] = (L+2*F)*(tL+2*F)-tL*L (2.5+2*0.25)*( *0.25)-0.375*2.5 = WS [psi] = LL/Wa /1.688 = rws = WS/msW 1197/9114 = iw [in 4 ] = (tl + 2*F)*(L + 2*F)^3/12 - il 22 ( *0.25)*( *0.25)^3/ = WB [psi] = ml*(cl+f)/iw *( )/1.48 = rwb = WB/msW 2047/9114 = LugWeldRatio = SQRT(rWS^2+rWB^2) SQRT(0.131^ ^2) = CheckWeld = LugWeldRatio <= <= 1 = Acceptable 27 Cover: mbc: Max Bending, mc1: Pressure Moment, mc2: Bolt Unit Moment, mct: Total Moment, tca: Required Thickness 28 Required thickness - Roarks Table 24 Case 10a and mbc [psi] = 1.5*CSA 1.5*18600 = mc1 [in-lb] = P*Do^2*3.3/64 201*12.75^2*3.3/64 = mc2 [in-lb] = SF*cH/(Do*π) *1/(12.75*3.14) = mct [in-lb] = mc1 + mc = tca [in] = sqrt(6*mct/mbc) SQRT(6* /27900) = Required thickness - Table UG-34 (j), C = 0.3, W = SF, hg = ch, S = CSA, d=do, E=1 tcb [in] = Do*sqrt((0.3*P)/(CSA*E)+(1.9*SF*cH)/(CSA*E*Do^3)) *SQRT((0.3*201)/(18600*1)+(1.9* *1)/(18600*1*12.75^3)) = ReqCThick [in] = Max(tca, tcb) MAX(0.702, 0.849) = CheckThick = ReqCThick <= tc <= 1 = Acceptable 38 Cover Tabs: it: Moment of Inertia, mt: Moment, LT: Bending Load 39 ct [in] = tc/2 1/2 = it [in 4 ] = (wc*tc^3*2)/12 Moment of Inertia (1*1^3*2)/12 = mt [in-lb] = LpB*(BCD-Dc)/4 Moment *( )/4 = LT [lb] = mt*ct/it Bending Load *0.5/0.167 = CheckLT = LT <= mbc <= = Acceptable
24 15 Coupling ver 2.11 UW16.1Z1M 20-Nov-08 Page 24 of Vessel with Large Opening <- Vessel 18 2" Coupling E <- Description Shell: COD <- t, Shell Wall Thick (inch) POD <- tmin, Min Required Wall at E=1 (inch) <- D, Shell Opening Diameter (inch) <- P,design Pressure (psi) Coupling: t inch 3000# <- Coupling 32 SA-182 F304 <- Coupling Material 33 17,400 <- Sn, Allowable Stress Level (Sn) D <- F1, Weld Size <- tmin16b, Min allowed wall per UG-16(b) <- Corrc, Coupling Corrosion Allowance (inch) <- COD - Coupling OD <- POD - Pipe OD <- n, Threads Per Inch <- pt, Corresponding sch160 Wall Thickness (inch) % <- UT, Under Tolerence (%) Geometry Restrictions Fig. UW tcp = (COD-POD)/2-CORRC = ( )/2-0 Tcp = Tmin = Min(0.75,tcp,t) = Min(0.75,0.313,1) Tmin = tcmin = Min(0.25,0.7*Tmin) = Min(0.25,0.7*0.313) tcmin = t1 = 0.7*F1 = 0.7*0.313 t1 = t1 > = tcmin = >= Acceptable Required Coupling Wall Thickness UG-44(c), B and UG-31(c)(2) 76 Ro = POD/2-0.8/n = 2.375/2-0.8/11.5 Ro = tp = (1-UT)*pt-Corrc-0.8/n = ( )* /11.5 tp = Min Thick = P*Ro/(Sn*1+0.4*P) = 201*1.118/(17400*1+0.4*200.9Acceptable trn = Pressure Weld Stress UW-18(d) - Pressure Load only UW-16(f)(3)(a)(3)(b) 81 Load = COD^2*(PI()/4)*P = 3^2*(PI()/4)* Load = Weld Area = pi()*((cod+f1)^2-cod^2)/4 Weld Area = = pi()*(( )^2-3^2)/4 88 Max Stress = Min(Sn,Sv) * 0.55 = Min(17400,0) * 0.55 Max Stress = Weld Stress = Load / Area = 1420 / Weld Stress = Acceptable 95 UG Tstd = Standard pipe wall thickness from chart Tstd = Nact = Pt * (1-UT) Actual Wall Thick. Nact = Tt = 0.8/n Ug-31(c)(2) threads Tt = UG45 = Max(UG45a, UG45b) <= Nact UG45 = = Max(0.082, 0.135) <= Acceptable 101 UG45a = trn + corrc + Tt UG45a = UB45b = Min(UG45b1, UG45b4) UB45b = = Min(0.849, 0.135) 105 UG45b1 = Max(tmin+ CORRC, Tmin16b + CORRC) UG45b1 = = Max( , ) 107 UG45b4 = Tstd* corrc = 0.154* UG45b4 = t F1 Outside Inside Vessel UW-16.1 (Z-1) (Modified) FULL PEN. t
Weight [lb] = (Do-t)*π*L*t*40.84/ (60-1)*3.1416*100*1*40.84/144 = (20000*1*1)/(29+0.6*1) = Pipe and Shell ver 4.
![Weight [lb] = (Do-t)*π*L*t*40.84/ (60-1)*3.1416*100*1*40.84/144 = (20000*1*1)/(29+0.6*1) = Pipe and Shell ver 4.](/thumbs/76/73791559.jpg "Weight [lb] = (Do-t)*π*L*t*40.84/ (60-1)*3.1416*100*1*40.84/144 = (20000*1*1)/(29+0.6*1) = Pipe and Shell ver 4.")
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