Sample Vessel 8 - pveng.com

1 Sample Vessel 8 PVE- Sample 8 Pressure Vessel CalculationsApril 27, 2007 XYZ Vessel AnytownOntario, Canada H0H 0H0 Charles Liu P. EngLaurence Brundrett P. Vessel Engineering 8 Rev 01 of 25 Table of Contents27-Apr-07 Page2 of 25 ContentsPageCover1 Table of Contents2 Summary3 Material Properties4 Shell5 Heads6 Nozzle A7 - 8 Nozzle A - For App. 1-79 - 10 Nozzle A - App 1-711 Flange A12 Nozzle B13 - 14 Flange B15 Nozzle C & D16 Nozzle E17 Flange C, D & E18 Flange 42"19 Weight and Volume20 Lifting Lug21 Seismic - Vessel on Beams22 - 25 Pressure Vessel Design Summary27-Apr-07 Page3 of 25 CustomerVesselPart NumberDrawingJob42 Outside Diameter [inch]72straight Shell (not including straight flange on heads)66 Volume [cuft]KeroseneFluid (value from Material Properties)9000 Weight Empty [lbs.]

2 ]12300 Weight Full12300 Weight Under TestMaximum Internal pressure, psiMaximum External Pressure, psiAt Temperature, Temperature, FMinimum Temperature, FAt Pressure, psi650-20350 Test Pressure, psiAt a Minimum Temperature of: FFor a Minimum Duration of:45555 F1/2 hrSA-240 304 Primary Material of Construction16,200 Allowable allowed thickness per UG-16(b)NoMaterial NormalizedNoMaterial Impact Tested (not required per UHA-51(d))NoRadiography required0 Corrosion AllowanceASME VIII-1 Code2004 EditionnoneAddendaIIDM aterialsnoneCode Cases RequiredUG-22 Loadings ConsideredYes(a) Internal pressureYes(a) External pressureYes(b) Vessel weight full, empty and at hydro testYes(c) Weight of attached equipment and piping(d)(1) Attachment of internalsYes(d)(2) Attachment of Vessel supports(d) Cyclic or dynamic reactions(f) Wind(f) SnowYes(f) Seismic(g) Fluid impact shock reactions(h) Temperature gradients(h) Differential thermal expansion(i)

3 Abnormal pressures like deflagrationHydrostatic TestMaximum Allowed Working PressureXYZ Vessel 8 Rev 0 PVE- Sample 8 PVE- Sample 8 Sample Vessel 8 Maximum Design Metal Temperature1 Material Properties ver of 252 ASME VIII, IID 2004 Edition no Addenda3<- Vessel45 Design Pressure UG-22(a) <- P, internal operating pressure at top of Vessel (psig) <- mPa, external operation pressure8 Kerosene<- Operating FluidSource - Machinery's handbook - 26th <- h, fluid height (ft) <- rho, fluid density ( for water) 11 Design Pressure = P + *rho*h= 350 + * * mDp = Test (UG-99(b))pressure measured at top of Vessel , rounded up14 Test Press = P * * MR= 350 * * 1mTp = 4551516 Material Properties (ASME IID)17650<- mTemp, design temp FTest at ambient temp18 Where UsedAmbient StrengthDesign StrengthStrength RatioMax FExt Graph19 Shell & 34 35 36 37 38 39 40 41 42 43 44 Min Ratio (MR) = TP304 Sms.

4 And Wld. PipeMaterialSA-240 304 PlateSample Vessel 8 44 WSA-182 F304 Forging3 Pipe and Shell ver of 254 ASME Code VIII Div I 2004 Edition No Addenda 5<- Vessel6<- Description78 <- Do - Outside Diameter (inch) <- t - Nominal Wall Thickness (inch) <- tminUG16(b) - Minimum Wall Thickness Per UG-16(b) <- Le - Effective Length (inch) <- Length for volume and weight (inch) <- Corr, Corrosion Allowance (inch)15N/A<- n, Number of Threads1617 Material and Conditions:18SA-240 304<- Material1916,200<- S, Allowable Stress Level (psi) <- El - Longitudinal Efficiency (circ. stress) <- Ec - Circ. Connecting Efficiency (longitudinal stress) <- UTP, Undertolerance allowance (%) <- Volume (cubic ft) <- UTI, Undertolerance allowance (inch)1, <- Material Weight (lbs cs) <- P, Interior <- Pa, Exterior Pressure277,915<- Ba, From exterior pressure <- Aa (use to lookup Ba)281,759<- Bb, From exterior pressure <- Ab (use to lookup Bb)2930 Variables.

5 31UT = t*UTP+UTI = *0+0undertolleranceUT = = = NAThread depthTd = = t-Corr-UT-Td = thicknt = = Do/2-nt = 42 inside radiusRi = = Le/Do = 79/42 LDo = Pressure UG-27 (c) (1,2)38ta = P*Ri/(S* *P) = * (16200* * )ta = = P*Ri/(2*S*Ec+ *P) = * (2*16200* + * )tb = = Max(ta,tb,tminUG16b) <= ntAcceptabletmin = =PMaxA = =PMaxB = = Min(PMaxA,PMaxB)AcceptablePMax = = P*Ri/(S* *P) = * (16200* * )tr1 = Pressure UG-28 (c)47 DoT = Do/nt = 42 = = Interpolated from IID Part D Table GAa = = 4*Ba/(3*DoT) = 4* (3*56)AcceptablePaMax = = Do/tre = 42 = = Interpolated from IID Part D Table GAb = = (3*Do*Pa)/(4*Bb) = (3*42* )/(4* )tre = = tre+corr+ut+td = +0+0+0 AcceptabletreCorr = stress relief -UCS-79(d), UNF-79(d), UHA-44(d)57Rf = (do-t)/2 = ( ) elong = (50*t/Rf)*(1-0) = (50* )*(1-0)% elongation = <- Max Elongation60 Yes<- Cold <- ElongationRequiredno61no<- Vessel carries lethal substances (Yes/no)nono62no<- Impact testing is required (Yes/no)nono63no<- Greater than 10% reduction in thicknessnono64no<- Formed between 250 and 900 Degrees Fnono65 YES<- Shell is greater than 5/8" thick before formingYes ?

6 No66 Stress Relieve ?no(2*S*Ec*nt)/( *nt) = (2*16200* * )/( * ) Vessel 842" OD Rolled Plate(S*El*nt)/(Ri+ *nt) = (16200* * )/( + * )39 Heads ver of 2540 ASME Code VIII Div I 2004 Edition No AddendaNO Appendix 1-4(f)22<- Vessel42<- Desc4344 <- Do, outside <- <- <- tb, thickness before <- tf, thickness after <- tminUG16(b) - Per UG-16(b) <- Corr, corrosion <- Skirt, straight skirt length5758 Material and Conditions:59SA-240 304<- material6016,200<- S, allowable stress level (psi) <- E, <- P, interior <- Pa, exterior pressure678,578<- Ba, from exterior pressure <- Aa value to lookup Ba683,484<- Bb, from exterior pressure <- Ab value to lookup Bb6970 Calculated <- Approximate blank <- Volume (cuft, includes skirt) <- Approximate weight for steel, (lbs) <- Spherical Limit ( * D)78115 Variables.

7 116D = Do-2*t = 42-2* = =h+t = + = = D/(2*h)UG-37 & Ap 1-4(c) = (2* )D/2h = = Do/(2*ho)UG-37 & Ap 1-4(c) = 42/(2* )Do/2ho = = Interpolated value from table = = Interpolated value from table UG-37D/2hsphericalKone = = Interpolated value from table = = tf-corr = = = Ko*DoUG-33(d) = *42Ro = Pressure App 1-4(a), App 1-4(c), UG-37(a)(1):135 App. 1-4(a) <= tf/(Kone*D) < (Kone*D) = <= ( * )< 1-4(f) calculation not needed139 TMinI = (P*D*K)/(2*S* *P) <= tTMinI (min thickness) = = ( * *1)/(2*16200* * ) <= = Max(Tminl,tminUG16(b))<=tf-corrAcceptableTMin = = (2*S*E*t)/(K*D+ *t) >= PAcceptablePMax = = (2*16200* * )/(1* + * ) >= 354153160 Interior Pressure for Nozzles App 1-4(a), App 1-4(c), UG-37(a)(1):161 TMinE1 = (P*D*K)/(2*S* *P) <= t(Nozzle in Knuckle) TMinE1 = = ( * *1)/(2*16200* * ) <= = (P*D*Kone)/(2*S* *P)(Nozzle in Crown) TSpI = = ( * * )/(2*16200* * )167169 Exterior Pressure UG-33(d), UG-28(d).

8 171Aa = (Ro/t) = ( )Aa = = Ba/(Ro/t) >= Pa = ( ) >= = = (Ro/tMinE) = ( )Ab = = (Ro*Pa)/Bb = ( * ) = = TMinE + corr = + 0 AcceptableTMinEC = stress relief UCS-79(d), UNF-79(d), UHA-44(d)182% elong = ((75*t)/h)*(1-0) = ((75* ) )*(1-0)% elong = <- Max Elongation185 Yes<- Cold <- ElongationRequiredno186no<- Vessel carries lethal substances(Yes/no)nono187no<- Impact testing is required (Yes/no)nono188no<- Formed between 250 and 900 Degrees Fnono189no<- Greater than 10% reduction in thicknessnono190 Yes<- Head is greater than 5/8" thick before formingYes ?no191 Stress Relieve ?noSample Vessel 8 ASME SE Head28 Nozzle Reinforcement ver (q)<- SavedDesign27-Apr-07 Page7 of 2529 ASME Code VIII Div I 2004 Edition No AddendaAutomatic dh - not hillside22<- VesselAutomatic Limit Diameter31<- DescriptionCurved Shell or Head Section32 Shell:33SA-240 304<- Shell Material3416,200<- Sv, shell allowable stress level, <- Eone, efficiency of shell at <- Ds, Shell <- Vt, shell wall thick, uncorroded, UT <- tr, required shell wall thickness int.

9 Press.(E=1) <- trE, required shell wall thickness ext. press.(E=1) <- sca, shell corrosion <- tmin16b, Min allowed wall per UG-16(b) 42 Nozzle:43SA-312 TP304<- Nozzle Material4416,200<- Sn, allowable stress level (Sn)454,071<- B, from A = <- E, nozzle efficiency <- P, internal design <- Pa, external design <- Do, outside <- Nt, wall thick, uncorrodedNote: Nozzle load calculations see "Nozzle A FEA Report". <- UTp, undertolerance (%) <- nca, nozzle corrosion <- L, exterior Projection59 Reinforcing:61SA-240 304<- Reinforcing plate materialAt least one telltale hole (max. size NPS 1/4 tap) in repad required6316,200<- Sp, allowable stress <- Dp, outside <- te, reinforcement <- Leg41, size of weld <- Leg42, size of weld <- LegG, depth of <- Leg5, depth of groove85 Variables:86UT = Nt*UTp= * = = Do/2 - (Nt-nca) + UT= 24/2 - ( ) + RadiusRn = = Min(2*d,DpEntered)= Min(2* ,30)Effective Reinforcing Dp = = Vt-sca= - 0 Effective Shell Thicknesst = = Nt-2*nca= - 2 * 0 Nom Thick of Int.

10 = = teEnteredEffective Reinf. = = Nt-nca= Nozzle Thick. No UTtn = = Do-2*tn= 24 - 2* = = MIN(Sn/Sv,1)= MIN(16200/16200, 1)fr1 = = MIN(Sn/Sv,1)= MIN(16200/16200, 1)fr2 = = MIN(Sn/Sv,Sp/Sv,1)= MIN(16200/16200, 16200/16200,1)fr3 = = MIN(Sp/Sv,1)= MIN(16200/16200,1)fr4 = = Do/2= 24/2Ro = = Min( , *Min( ,Nt,te))= Min( , *Min( , , ))tc41 = = = Required Wall Thickness - trn from internal, trnE from external pressure143trn = (P*Rn)/(Sn*E - *P) <= tn-UT= ( * )/(16200* - * )trn = = (P*Rn)/(Sn*1 - *P)= ( * )/(16200*1 - * )E=1trnR = = (3*Do*Pa)/(4*B) <= tn-uttrnE = *Leg41 >= * >= >= *Leg42 >= *Min( ,te,Vt) * >= >= >= *Min( ,te,Nt) >= >= >= *Min( ,Vt,Nt) >= >= *Min( , , ) *Min( , , ) *Min( , , )