ASME取证用储罐强度计算书Word文档下载推荐.docx

1、ASME Section，Div.1, 20132） 设计压力（p） : 内部1.3Mpa Design Pressure （p）: Internal 1.3 MPa3） 设计温度: 60 Design Temperature: 604） 焊接接头系数（E）: 壳体为0.85，封头为0.85（无缝） Joint Efficiency （E）: 0.85 for Shell and 0.85 for Heads（ seamless）5） 材料最大许用应力 Material Max. Allowable Stress:Based on ASME Code Sec., Part D Table 1A

2、 壳体和封头: SA516 Gr. 485，60时为138MPaShell & Heads: SA516 Gr. 485 Material Max. Allowable Stress is 138MPa at 60；接管: SA105M钢，60时为138MPa Nozzles：SA105M Steel Material Max. Allowable Stress 138 MPa at 60；6） 媒介: 空气 Medium: Air （Non lethal） 7） 封头类型: 2:1椭圆封头 Head type:1Ellipsoidal Head；8） 其他载荷: 依据“客户设计说明书”（Do

3、c. No. TS-15-01 Rev.0）Others Loadings: As Shown in“Customers Design Specification” （Doc. No. TS-15-01 Rev. 0）9） 腐蚀余度:2.0 mm Corrosion Allowance: 2.0 mm 10） 容器外形和尺寸：依据“客户设计说明书”（Doc. No. TS-15-01 Rev.0） Layout of Vessel and Dimension:As Shown in“Customers Design Specification” （Doc. No. TS-15-01 Rev.

4、0）11） 钢印要求: 要求ASME标识 Stamp required: ASME Certification Mark required 12） NB要求: 不要求NB钢印NB stamp required: NO “NB” stamp required.2. 计算 Calculation:Verify for UG-22 LoadingYesNo1. Internal Design Pressure 内压设计压力2. External Design Pressure 外压设计压力3. Weight of the Vessel 容器重量4. Weight of Normal Contents

5、 Under Operating Conditions 在操作状态下容器内部正常介质的重量5. Weight of Normal Contents Under Test Conditions 在试验状态下容器内部正常介质的重量6. Superimposed Static Loadings From Weight of Attached Equipment 附属设备的重量产生的附加静载荷7. The Attachment of Internals 内部附件8. The Attachment of Lifting Lugs 吊耳9. The Attachment of Vessel of Vess

6、el Support （Skirt, Legs, Saddles, Etc.） 容器的支座（裙座、支架、鞍座等）10. Cyclic and Dynamic reactions due to Pressure or thermal variations,or from equipment mounted on a vessel,and mechanical loading.由压力或温度变化而引起的，或由容器上的设备引起的周期性和动荷反作用力以及机械载荷。11. Wind Loadings 风负荷12. Snow Loadings 雪负荷13. Seismic Loadings 地震负荷14.

7、Impact Loadings Such As Those Due to fluid shock冲击载荷，例如由流体冲击而引起的等15. Temperature Gradients and Differential Thermal Expansion 温度梯度及不同的热膨胀16. Abnormal pressures,such as those caused by deflagration例如由爆燃引起的各种异常压力17. Test pressure coincident static head acting during the test.在试验期间所作用的试验压力和共同作用的静压头2.1

8、内压壳体最小厚度 Min. Required Thickness of Shell under Internal Pressure符号 Symbols:t= 壳体要求最小厚度，mmt = minimum required thickness of shell, mmP = 内部设计压力, 1.3MPa P = internal design pressure, 1.3 MPa see UG-21R = 预计容器筒内半径， 250mmR = inside radius of the shell course under consideration, 250mmS = 最大许用应力值，138MPa

9、S = maximum allowable stress value, 138MPa see ASME Code Part II D Table 1A for material SA-516 Gr.485E = 焊接接头系数，0.85E = joint efficiency, 0.85 see Table UW-12（1）Since P=1.3MPa is less than 0.385SE=45.16MPa, Formula UG-27（c）（1） is used:考虑腐蚀裕量：Consider of corrosion allowable: tr= t + Ca = 2.81 + 2.0

10、= 4.81mm These formulas will govern only when the circumferential joint efficiency is less than one-half the longitudinal joint efficiency, according to UG-27（c） （2） note 20, the formula UG-27（c） （2） for longitudinal stress neednt considered.公称钢板规则厚度=10mmNominal Plate Thickness Ordered = 10 mm钢板厚度可允

11、许下偏差=0.25mmsee UG-16（c）Plate Under tolerance=0.25 mm see UG-16（c） UG-16 （b）（4） the minimum thickness of pressure retaining components 2.5mm for air service（exclusive any corrosion allowance）. 实际使用厚度=10-0.25=9.75 4.81mm，并且也2.5+2mm,可以。Actual Used Thickness = 10 -0.25=9.754.81 mm, and 2.5+2 mm（Ca）So it

12、 is satisfactory.2.2 椭圆封头最小厚度 Min. Required Thickness of Ellipsoidal Headst = 封头成形后要求最小厚度，mmt = minimum required thickness of head after forming, mm.ts = 封头成形后规定的最小厚度，ts=8.8mmts = minimum specified thickness of head after forming , ts=8.8mm P = 内部设计压力, 1.3 MPaD =椭圆封头长轴内部长度，500+4mm（考虑腐蚀裕量）D = inside

13、length of major axis of the ellipsoidal head, 500+4mm（under corrosion condition）h =椭圆封头短轴长度的一半，125+2mm（考虑腐蚀裕量）h = one-half of the length of the minor axis of the ellipsoidal head, 125+2mm（under corrosion condition）S =最大安全允许应力值，138 MPaS = maximum allowable stress value, 138MPa see ASME Code Part II D

14、, Table 1A for material SA516 Gr.485,E =焊接接头系数，0.85 E = joint efficiency, 0.85 for Seamless Head and see UW-12（d） .E1 =筒体与封头的焊接接头系数，0.85 E1 = joint efficiency of shell and head,0.85Ca=腐蚀裕量，2mmCa=corrosion allowance, 2mmK1 = 球半径系数，0.9K1 = 0.9 see Table UG-37, D/2h=2L =当量球半径 K1D = 0.9504 = 453.6mmL =

15、K1D = 0.9504=453.6mm see 1-4（b）Since ts /L=7.1450=0.015 More Than 0.002, Formula UG-32（d）（1） to Be Used:考虑允许的腐蚀裕量：t= t+Ca=2.78+Ca=2.78+2.00=4.78mm t = t+Ca=2.78+Ca=2.78+2.00=4.78mm2.5mm for compressed steam成形后封头的实际最小厚度 8.8mm 2.0mm=6.8mm 4.78mm，而且 2.5+2mm，也可。Actual minimum thickness of heads after fo

16、rming 8.8mm-2.0mm=6.8mm 4.78mm and 2.5+2mm ,So it is OK。2.3 接管最小厚度 Min. Required Thickness for Nozzles N1,N2，N3 （UG-45）Symbols: 符号t =管口要求最小壁厚，mmt = minimum required thickness of nozzles, mmP =内部设计压力，1.3 MPaR1 =管口内半径，24.61mmR1= inside radius of the nozzle, 24.61 mmS =最大许用应力值，138 MPaS = maximum allowa

17、ble stress value, 138MPa see ASME Code Section II Part D Table 1A for material SA-105M 根据UG-45，管口要求最小厚度According to UG-45, Min. required thickness of nozzle see UG-27see UG-27tb3=3.42+Ca=3.42+2.0=5.42mmtb=mintb3, tb31=4.39mmt=max（ta,tb）=4.39mm管壁的实际使用最小厚度：= 5.54mm 4.39mmActual min. used thickness of

18、tube wall: 4.39mm, so it is satisfactory.2.4 开孔和补强 Openings and Reinforcement （UG-36）1=02=53d1=60.3mm d2=60.3mm d3=60.3mm2.4.1 Nozzles N1,N2,N3. The finished diameter of circular opening is 49.22 mm, and minimum required thickness of shell is 4.81mm. According to UG-36（c）（3）（-a） openings in vessel n

19、ot subject to rapid fluctuations in pressure do not require reinforcement other than that inherent in the construction under the following conditions: welded connections meeting the applicable and with a finished diameter of circular opening is not larger than 89mm diameter in vessel shell with a re

20、quired minimum thickness of 10mm or less than 10mm,（-c）No two isolated unreinforced openings have their centers closer to each other than the sum of their diameter.（-d） Their centers closer to each other than the following:（1+1.5cos1）（d1+d2）=301.5mm1200mm. （1+1.5cos2）（d1+d3）=229.4mm1001mm. openings

21、of Nozzle N1,N2,N3 shall be exempt from the reinforcement requirements.2.5 接管与壳体连接焊缝的强度计算 Strength Calculation for Nozzle Attachment Weld （ UW-15）According to UW-15（b）（2）, strength calculation for nozzle attachment welds for pressure loading are not required for openings that are exempt from the rei

22、nforcement requirements by UG-36（c）（3）.2.6 接管与壳体连接焊缝高度核算 Verify the Fillet Weld Size of Nozzles according to UW-16（a）（2）（b） and Fig.UW-16.1（c）2.6.1 FOR NOZZLE N1，N2，N3tmin = 小于19mm或者由角焊，单坡口焊接或单J形焊接连接部分的较薄处的厚度= 5.54mm;tmin = the smaller of 19mm or the thickness of the thinner of the parts jointed by

23、a fillet, single-bevel, or single-J weld = 5.54mmtc =不小于6mm，或0.7 tmin = 3.87mmtc= not less than the smaller of 6mm or 0.7tmin = 3.87mm 角焊的实际焊喉尺寸= 6.0sin45=4.24mm 3.87mmActual throat size of fillet weld = 4.24mm 3.87mm, so it is satisfactory.2.7检查孔 Inspection Openings设备设有三个DN50的管口（N1/N2/N3），与之相连附件是可拆

24、卸的，因此依据UG-46（f）可不另设检查孔。There are three DN50（N1/N2/N3）nozzles with removable attachments.Therefore,no inspection openings will be provided based on UG-46 （f） .3. 热处理 Heat treatment3.1 制造后热处理 Post Fabrication Heat Treatment （ UCS-79）According to UCS-79 Forming strains for the shell shall be calculated

25、 as follows 钢板形成的圆筒cylinders formed from plate:其中，R f= 成形后的平均半径 = 255 mmRo= 原始半径（等于于钢板平面的正无穷）= 无穷大t =成形前钢板的正常厚度 =10 mmWhere Rf= mean radius after forming=255 mmRo= original radius（equal to infinity for a flat plate）= 无穷大t = nominal thickness of the plate before forming=10 mmAccording to UCS-79（d） Fo

26、r P-No.1 group No.1 materials the extreme fiber elongation is less than 5% No post fabrication heat treatment is required.3.2 焊后热处理 Post Weld Heat Treatment （ UCS-56 ）Shell and head material SA-516 Gr.485belongs to P-No.1,nozzle and flange material SA-105M belongs to P-No.1 （see Section P-Number mat

27、erial groupings of base metals for qualification of QW-422）.All the welded joints not over 38mm thickness, In according to Table UCS-56 note （b）, the post weld heat treatment is not required.4. 最低设计金属温度和冲击试验 MDMT and Impact Testing （UCS-66）4.1 最低设计金属温度 MDMT 根据“客户设计条件”，最低设计金属温度为0。The minimum design m

28、etal temperature（MDMT） is 0 per “Gustomers Design Specification”.4.2 冲击试验 Impact Testing UG-20（f）根据UG-20（f），压力容器材料满足下列要求时，按UG-84的冲击试验不是强制性的：According to UG-20（f）, impact testing per UG-84 is not mandatory for pressure vessel materials that satisfy all of following:（1） 材料（SA105M）为P-No1，Gr. No.1 ，厚度不超

29、过下面（a）条的规定： （a）对于图UCS-66曲线B的材料25mm；The material is P-No1，Gr.No1 （SA105M）, and the thickness is not exceed that given in （b） below:（a） 25mm for materials listed in Curve B of Fig. UCS-66;材料（SA-516M Gr.485）为P-No1，Gr. No.1 ，厚度不超过下面（b）条的规定： （b）对于图UCS-66曲线D的材料25mm；The material is P-No1，Gr.No1 （SA-516M Gr485）, and the thickness is not exceed that given in （b） below:（b） 25mm for materials listed in Curve D of Fig. UCS-66;（2） 按UG-99，对完工的容器进