ASME支腿计算

Design CalculationITEM NAME:xxxxxxxxxxxxxx DWG.NO.xxxxxxxxxxxxxx REVISION:xDate:Date:Date:PREPARED BY ：REVIEWED BY ：APPROVED BY ：CONTENT1Loadings Considered3 2Vessel Technology Parameters4 3Design Data4 Required Thickness of Ellipsoidal Head 44 5Required Thickness of Shell5 6Opening Reinforcement Calculation5 7Required Nozzle Thickness Under Internal Pressure 9 8Impact Test Exemption Evaluation10 9 Post Weld Heat Treatment Exemption Evaluation11 10Check for Flange11 11 Check Inspection Openings11 12Standard Hydrostatic Test11 13Leg Design Calculation 12 14Lifting Lug Design Calculation 15xxxxxxxxxxxxxxAPPLIES ITEM YES (a) External pressure NO (b) Weight of the vesselYES (b) Weight of normal condition under operating condition YES (b) Weight of normal condition under test conditionYES (c) Superimposed static reactions from weight of attached equipment NO (d) The attachment of internalsNO (d) The attachment of vessel supports (saddles, lifting lugs) YES (e) Cyclic and dynamic reactions due to pressure NO (e) Cyclic and dynamic reactions due to thermal variations NO (e) Cyclic and dynamic reactions due to equipment mounted on a vessel NO (e) Cyclic and dynamic reactions due to mechanical loadings NO (f) Wind reactions NO (f) Snow reactions NO (f) Seismic reactionsNO (g) Impact reactions such as those due to fluid shock NO (h) Temperature gradients NO (h) Differential thermal expansions NO (i) Abnormal pressureNO (j) Test pressure and coincident static head acting during the testYES1. Loadings Considered◆ AS PER ASME CODE SECTION VIII , DIV.1,2015 UG-22 ◆ General Arrangement Drawing NO. (a) Internal pressure2. Vessel Technology ParametersItem Symbol Parameter Unit Remark Medium Compressed AirMAWP MAWP1MPaStatic Head of Liquids0.02MPa For hydrostatic test Design Pressure P 1MPaHydrostatic test#NAME?MPaWorking temperature0~90℃Design temperature Temp 93℃MDMT MDMT-20℃Shell Nominal thickness t3mmShell Inside Dimmeter D 400mmShell Material SA-240M 304Shell Allowable Stress at design Temperature S 137MPaShell Allowable Stress At Ambient Sa 138MPaJoint Efficiency of Shell,Shell to Head E1 0.85 ShellE20.85 Shell to Head Joint NDT SPOT RT : A1,B1,B2UW-52 Corrosion Allowance C0 mmTotal Volume0.20m3Vessel fully loading mass m270 kg3. Design Data3.1 Nozzle listLine Size Schedule tn O.D.Material UNS TYPE Sn Function N1DN100/NPS410S 3.05 114.3SA-312M TP304S30400sml.137Medium Inlet N2DN100/NPS410S 3.05114.3SA-312M TP304S30400sml.137Medium Outlet N3DN20/NPT3/440S 2.8726.7SA-312M TP304S30400sml.137Vent N4DN20/NPT3/440S 2.8726.7SA-312M TP304S30400sml.137Drain◆ The thickness of threading port N3~N4 is larger than schedules 10S, meet the requirement of SA-312M appendix.3.2Main MaterialPart MaterialShell&Head SA-240M 304 (II-D Metric p.86, ln.43)Pipe SA-312M TP304 (II-D Metric p.90, ln. 9)Flange SA-182M F304 (II-D Metric p. 86, ln. 32)4. Required Thickness of Ellipsoidal HeadDESCRIPTION Symbol DATA UnitDesign Pressure P 1MPaInside Diameter of Head Di400 mmHead Nominal thickness tn3mmHead Finished (Minimum) Thickness t 2.4mmAllowable Stress at design Temperature S 137MPaHead Ratio D/2h Ar 2Joint Effiency of Head E0.85◆ Minimum thickness per UG-16 (b)1.5mmt= 2.4L=360t/L=0.01≳0.002= 1.72mmt= 2.4it is customary to use a thicker plate to take care of possible thinning during the process of forming.So, The Min. thickness of head after forming is 2.4 mm.Conclusion:Satisfactory5. Required Thickness of Shell DESCRIPTION SymbolDATA Unit Design Pressure P 1MPa Radius of ShellR 200 mm Allowable Stress at design Temperature S 137MPaJoint Effiency of Shell0.85 Joint Effiency of Shell&HeadE20.851.5mmDesign thickness for internal pressure, Ⅷ-1 UG-27(c)(1), P=1< 0.385SE1=44.83= 1.73mm UG-16 (c): Min. plate thickness Undertolerance, 3mm 0.30mm 2.70mmP=1145.56=0.86mmt= 2.70Conclusion:Satisfactory6. Opening Reinforcement Calculationt 1=t min + Corrosion =◆ Design thickness due to internal pressure per Ⅷ-1 UG-32(d）t 2=PD/(2SE-0.2P)+ Corrosion ◆ The head internal pressure actual use design thickness(Req. min. thickness)mm > larger of t1， t2In order to ensure that a finished head is not less than the minimum thickness required，E 1◆ Minimum thickness per UG-16 (b) ,t 1=t min + Corrosion= t 2= PR/(SE 1-0.6P)+ Corrosion t n =t u = t=t n -t u =◆ Design thickness for internal pressure, Ⅷ-1 UG-27(c)(2)< 1.25SE2=t 3= PR/(2SE 2+0.4P)+ Corrosion ◆ The shell internal pressure actual use design thickness(Req. min. thickness) mm ＞ larger of t1，t2,t3Opening in vessel not subject rapid fluctuation under the following condition:The nozzle N1, N2, do not conform to the condition mentioned above so reinforcement calculation is needed. Outside Projection ho 145mm Weld leg size between Nozzle and Pad/Shell Wo 3mm Inside Projection h 0mm Weld leg size, Inside Element to Shell Wi 0mm Shell thickness-corrosion t 2.70mm1.47mm 0.42mmtn 3.05mm Actual Outside Diameter Used in Calculation 114.3mm.= 1.47 mm= 0.42 mm UG-40, Limits of Reinforcement : [Internal Pressure]Parallel to Vessel Wall (Diameter Limit) Dl 216.40mm Parallel to Vessel Wall, opening length d 108.20mmWeld Strength Reduction Factor [fr1]:Weld Strength Reduction Factor [fr2]:= Sn/S = Sn/S = 1.00= 1.00Weld Strength Reduction Factor [fr3]:Weld Strength Reduction Factor [fr4]:= min( fr2, fr4 )= Sp/S = 1.00= 1.00Results of Nozzle Reinforcement Area Calculations:AREA AVAILABLE, A1 to A5 Symbol Without Rein Area Required Ar 158.65mm^2Area in Shell A1 133.49mm^2Area in Nozzle Wall A2 35.56mm^2Area in Inward Nozzle A3 0.00mm^2Area in Welds A41+A42+A43 9.00mm^2Area in Element A5 0.00mm^2TOTAL AREA AVAILABLE Atot 178.05mm^2The area available without a pad is sufficient.6.1 Checking exemption of reinforced opening UG-36(c)- (3)- (a)、(c) ---N3, N4◆ A finished opening not larger than 89mm diameter in vessel with a required minimum thickness of 10mm or less.◆ No two isolated unreinforced openings have their centers closer to each other than the sum of their diameter.The nozzle N3,N4 conform to the condition mentioned above so reinforcement for above openings is not needed.6.2 Opening Reinforcement Calculation for N1, N2（Insert Nozzle Without Pad, no Inside projection）Reqd thk per Ⅷ-1 UG-32(d） trReqd thk per UG-37(a)of Nozzle Wall, t rn trn Nozzle thickness(not including forming allowances)D0Required thickness per Ⅷ-1 UG-27(c）t r =PR/(SE-0.6P)+Corrosion Reqd thk per UG-37(a)of Nozzle Wall, t rn [Int. Press]t rn = (P*Ro)/(S*E+0.4*P) per Appendix 1-1 (a)(1)Area Required [A]:= ( d * tr*F + 2 * tn * tr*F * (1-fr1) ) UG-37(c)= 158.65mm^2Area Available in Shell [A1]:= max(d( E1*t - F*tr ) - 2 * tn( E1*t - F*tr ) * ( 1 - fr1 ), 2(t+tn)(E1t-Ftr)-2tn(E1t-Ftr)(1-fr1))= 133.49 mm^2Area Available in Nozzle Wall Projecting Outward [A2]: =min(5(tn-trn)fr2t,5(tn-trn)fr2tn)=35.56mm^2Area Available in Welds [A41 + A43]:= Wo^(2)*fr3+Wi^(2)*fr2= 9.00mm^23mm 2.1mmtc(actual) = 2.1mm UW-16 Weld Sizing Summary Weld description Required weld throat size (mm)Actual weld throat size (mm)Nozzle to shell fillet2.1 2.1Conclusion:SatisfactoryWeld strength calculations are not required as per UW-15(b) for this detail which conforms to Fig. UW-16.1, sketch (c).2.87mm 2.01mmtc(actual) = 2.1mm UW-16 Weld Sizing Summary Weld description Required weld throat size (mm)Actual weld throat size (mm)Nozzle to shell fillet2.01 2.1Conclusion:SatisfactoryWeld strength calculations are not required as per UW-15(b) for this detail which conforms to Fig. UW-16.1, sketch (c).6.4 FLANGE TO NOZZLE NECK WELDS6.4.1 Calculation for N1, N2As per Fig. UW-21, illustrations (1)Internal weld size:3.05mm 4mm > 3.05 mm OK6.3 UW-16(c) Weld Check for All nozzles 6.3.1 UW-16(c) Weld Check for N1&N2Fillet weld: t min = lesser of 19 mm or t n or t = tc(min) = lesser of 6 mm or 0.7*t min =6.3.2 UW-16(c) Weld Check for N3,N4Fillet weld: t min = lesser of 19 mm or t n or t = tc(min) = lesser of 6 mm or 0.7*t min =UW-21(b): ASME B16.5 slip-on flanges shall be welded to a nozzle neck using an internal and an external weld. t min =The lesser of tn or 6 mm=实际X(actual)=External weld size:= 4.27 mm 5mm > 4.27 mm OKX min =the lesser of 1.4tn or the thickness of the hub实际X(actual)=Schematic diagramAngle Radian α300.5236β60 1.0472γ200.3491SA-240M 30495.9MPa 67.13MPa0.7SA-240M 304137MPa 1.65Vessel fully loading mass,G:270KG 9.8140mm 25mm 25mm 8mm 14.14368.57N14.2Transverse loading2522.20N14.35044.39N14.414. Lifting Lug Design Calculation Per HG/T 21574-2008The material of lifting lug：Tensile stress in lifting lug ［σL ］:Shear stress in lifting lug ［τL ］:Joint efficiency for fillet weld：The material of head：Allowable stress in head：Composite influence factor,K：Gravitational acceleration,g,Type in：L-The distance between the centre of lifting lugs to head,R-The radius of lifting lug，D-The diameter of eye for lifting lug，S-The thickness of lifting lug，Vertical loadingComputational formula ：Fv=G×g×1.65F V =Computational formula ：F H = Fv •tanαF H =Lifting rope direction loadingComputational formula:F L =Fv/CosαF L =Bending moment for warp directionM=100887.87N*mm14.525.22MPaOK14.625.22MPaOK14.7A=643.806.79MPa3.92MPa12.09MPa20.44MPaσ=67.13MPaConclusion:OKComputational formula:M= F H •LThe max tensile stress for the lifting lug in the Lifting rope directionComputational formula:σL =F L /［（2R-D）*S］σL =σL ＜［σL ］The max shearing stress for the lifting lug in the Lifting rope directionComputational formula :σL =τLτL =σL =σL ＜［τL ］Check fillet weld for lifting lugThe area of fillet weld is conservative：Computational formula:A=2*（L*tanγ+R）*Smm 2The tensile stress for fillet weld：Computational formula:σa =F V /Aσa =The shearing stress for fillet weld：Computational formula:τa =F H /Aτa =Bending stress for fillet weld：Computational formula:σab =6M/（S*（2*（L*tanγ+R ）)2）σab =Combined stress：Computational formula:σab =((σa +σab )2+4τa 2)1/2σab =The allowable stress of fillet weld：Computational formula:σ=0.7*［σL ］Lug strength calculation：σab ＜σ。