Design Calculation
ITEM NAME:xxxxxxxxxxxxxx xxxxxxxx REVISION:x
Date:Date:Date:
PREPARED BY ：REVIEWED BY ：APPROVED BY ：
CONTENT
1Loadings Considered3 2Vesl 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 15
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气馁是什么意思APPLIES ITEM YES (a) External pressure NO (b) Weight of the vesl
YES (b) Weight of normal condition under operating condition YES (b) Weight of normal condition under test condition
YES (c) Superimpod static reactions from weight of attached equipment NO (d) The attachment of internals
NO (d) The attachment of vesl 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 vesl NO (e) Cyclic and dynamic reactions due to mechanical loadings NO (f) Wind reactions NO (f) Snow reactions NO (f) Seismic reactions
NO (g) Impact reactions such as tho due to fluid shock NO (h) Temperature gradients NO (h) Differential thermal expansions NO (i) Abnormal pressure
NO (j) Test pressure and coincident static head acting during the test
YES
不倒翁玩具1. Loadings Considered
◆ AS PER ASME CODE SECTION VIII , DIV.1,2015 UG-22 ◆ General Arrangement Drawing NO. (a) Internal pressure
2. Vesl Technology Parameters
关于诗的名言Item Symbol Parameter Unit Remark Medium Compresd Air
MAWP MAWP1MPa
Static Head of Liquids0.02MPa For hydrostatic test Design Pressure P 1MPa
Hydrostatic test#NAME?MPa
Working temperature0~90℃
Design temperature Temp 93℃
MDMT MDMT-20℃
Shell Nominal thickness t3mm
Shell Inside Dimmeter D 400mm
Shell Material SA-240M 304
Shell Allowable Stress at design Temperature S 137MPa
Shell Allowable Stress At Ambient Sa 138MPa
Joint Efficiency of Shell,Shell to Head E1 0.85 Shell
E20.85 Shell to Head Joint NDT SPOT RT : A1,B1,B2UW-52 Corrosion Allowance C0 mm
Total Volume0.20m3
形容贫穷的成语
Vesl fully loading mass m270 kg
3. Design Data
3.1 Nozzle list
Line Size Schedule tn O.D.Material UNS TYPE Sn Function N1DN100/NPS410S 3.05 114.3SA-312
M 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
爱尔兰和英国
◆ The thickness of threading port N3~N4 is larger than schedules 10S, meet the requirement of SA-312M appendix.
3.2Main Material
Part Material
Shell&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 Head
DESCRIPTION Symbol DATA Unit
Design Pressure P 1MPa
Inside Diameter of Head Di400 mm
Head Nominal thickness tn3mm
Head Finished (Minimum) Thickness t 2.4mm
Allowable Stress at design Temperature S 137MPa
Head Ratio D/2h Ar 2
Joint Effiency of Head E0.85
◆ Minimum thickness per UG-16 (b)
1.5mm
t= 2.4L=360t/L=0.01≳0.002= 1.72mm
t= 2.4it is customary to u 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:
Satisfactory
5. Required Thickness of Shell DESCRIPTION Symbol
DATA Unit Design Pressure P 1MPa Radius of Shell
R 200 mm Allowable Stress at design Temperature S 137MPa
英雄联盟重开
Joint Effiency of Shell
0.85 Joint Effiency of Shell&Head
E20.85
1.5mm
Design 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 2.70mm
小拇指长痣
P=1145.56=0.86mm
踏征程
t= 2.70Conclusion:
Satisfactory
6. Opening Reinforcement Calculation
t 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 u design thickness(Req. min. thickness)mm > larger of t1， t2
In 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 u design thickness(Req. min. thickness) mm ＞ larger of t1，t2,t3
