压力容器计算书.doc

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1、 产 品 名 称：空气储罐Product Name : Air storage tank施 工 图 号：xxxxxxxDrawing. No. 版 次：0Rev.： 0版 次Rev.编 制Prepared By批 准Approved By授权检验师Authorized Inspector设 计 计 算 书Design Calculation Sheet1. 设计参数和条件 Design Data and Condition:1) 设计所遵循的规范 Applicable Code: ASME Section，Div.1, 2013 Edition;2) 设计压力(p) : 内部1.2兆帕 Des

2、ign Pressure (p):Internal 1.2 Mpa; 3) 设计温度: 0摄氏度到60摄氏度 Design Temperature: 060; 4) 最低设计金属温度：-29； MDMT: -295) 焊缝系数(E): 壳体为0.85，封头为0.85(无缝)， Joint Efficiency (E): 0.85 for Shell and 1.0 for Heads（seamless）； 6) 材料最大许用应力 Material Max. Allowable Stress:Based on ASME Code Sec., Part D Table 1A 壳体和封头: SA51

3、6M Gr. 485，60摄氏度时为138兆帕Shell & Heads: SA516M Gr. 485 Material Max. Allowable Stress is 138MPa at 60；接管: SA106M Gr. B，60摄氏度时为118兆帕 Nozzles：SA106M Gr. B Steel Material Max. Allowable Stress 118 Mpa at 60；7) 媒介: 空气 Medium: Air ; 8) 封头类型: 2:1椭圆封头 Head type: 2:1Ellipsoidal Head； 9) 其他载荷: Others Loadings:

4、See verify for UG-22 loading;10) 腐蚀余度: 2.0毫米 Corrosion Allowance: 2.0 mm 11) 容器外形和尺寸 (见图纸 空气储罐 U-1110-1 ) Layout of Vessel and Dimension: As Shown in Air storage tank Specification (Dwg. No. U-1110-1)12) ASME 认证钢印及标志符: 要求”ASME”钢印及”U” 标志符 Stamp of ASME Ceretification Mark and U Designator: Stamp of A

5、SME Ceretification Mark and U Designator required. 2. 计算 Calculation:Verify for UG-22 LoadingYesNo1. Internal Pressure 内部压力2. External Pressure 外部压力3. Weight of the Vessel 容器重量4. Weight of Normal Contents Under Operating Conditions (Static Head) 在运行条件下正常容量的重量（落差）5. Weight of Normal Contents Under Te

6、st Conditions (Static Head) 在测试条件下正常容量的重量（落差）6. Superimposed Static Loadings From Weight of Attached Equipment 从附加设备重量产生的叠加静负荷7. The Attachment of Internals 内部附件8. The Attachment of Lifting Lugs 吊耳9. The Attachment of Vessel of Vessel Support (Skirt, Legs, Saddles, Etc.) 容器支撑上的附件（裙座、支架、鞍座等）10. Cycli

7、c and Dynamic Loadings Due to Pressure由于压力产生的旋转和动力载荷11. Cyclic and Dynamic Loadings Due to Thermal Variations由于热变化产生的旋转和动力载荷12. Cyclic and Dynamic Loadings Due to Equipment mounted on Vessel 由安装在容器上的设备产生的旋转和动力载荷13. Cyclic and Dynamic Loadings Due to Mechanical Loadings由机械负荷产生的旋转和动力载荷14. Wind Loading

8、s 风负荷15. Snow Loadings 雪负荷16. Seismic Loadings 地震负荷17. Impact Loadings Such As Those Due to Thermal Shock碰撞负荷，例如由于热冲击产生的负荷18. Temperature Gradients 温度梯度19. Differential Thermal Expansion 局部热膨胀20. Minimum Design Metal Temperature 最小设计金属温度21. Test pressure and the joint effect of static head 试验压力和共同作用

9、的静压头2.1 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，毫米t = minimum required thickness of shell, mmP = 内部设计压力, 1.2兆帕 P = internal design pressure, 1.2MPa see UG-21R = 容器筒内半径， 402毫米 (考虑腐蚀余量)R = inside radius of the shell course under consideration, 402mmS =

10、最大许用应力值，138兆帕S = maximum allowable stress value, 138MPa see ASME Code Part II D Table 1A for material SA516M Gr.485E = 焊缝系数，0.85E = joint efficiency, 0.85 see Table UW-12(1)Since P=1.2MPa 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 =

11、4.14 + 2.0 = 6.14mm ；这些公式只有在环向接头系数小于纵向接头系数一半时才起作用，根据UG-27(c) (2)的注释16，用于纵向应力的UG-27(c) (2)公式不用考虑。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 16, the formula UG-27(c) (2) for longitudi

12、nal stress neednt considered.钢板公称厚度=13.0毫米Nominal Plate Thickness Ordered = 13.0 mm钢板厚度可允许下偏差=0.25毫米见 UG16(c)Plate Under tolerance=0.25 mm see UG16(c) 对于介质是压缩空气（不含任何腐蚀余量），UG-16 (b)(4)中的受压件最小厚度应大于2.5mm；UG-16 (b)(4) the minimum thickness of pressure retaining components 2.5mm for compressed air servic

13、e(exclusive any corrosion allowance). 实际使用厚度=13.0-0.25=12.75 6.14毫米，并且也2.5+2毫米=4.5毫米,所以满足要求。Actual Used Thickness =13.0 -0.25-=12.75 6.14 mm, and 2.5+2 mm=4.5mmSo it is satisfactory.2.2 椭圆封头最小厚度 Min. Required Thickness of Ellipsoidal Heads符号 Symbols:t = 封头成形后要求最小厚度，毫米t = minimum required thickness o

14、f head after forming, mm.ts = 封头成形后规定的最小厚度，ts=11.5毫米ts = minimum specified thickness of head after forming , ts=11.5 mm P = 内部设计压力, 1.2兆帕 P = internal design pressure, 1.2 MPa see UG-21D =椭圆封头长轴内部长度，804毫米 (考虑腐蚀余量)D = inside length of major axis of the ellipsoidal head under consideration, 804mmh =椭圆

15、封头短轴长度的一半，202毫米(考虑腐蚀余量)h = one-half of the length of the minor axis of the ellipsoidal head under consideration, 202mmS =最大允许应力值，138兆帕S = maximum allowable stress value, 138MPa see ASME Code Part II D, Table 1A for material SA516M Gr.485,E =封头焊缝系数，0.85(对无缝封头见UW-12(1)E = joint efficiency, 0.85 for Se

16、amless Head and see UW-12(1) .E1 =筒体与封头的焊缝系数，0.85 E1 = joint efficiency of shell and head, 0.85Ca=腐蚀裕量，2毫米Ca=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 = 0.9(804) = 723.6毫米L = K1D = 0.9(800+4) = 723.6mm see 1-4(b)Since ts /L=11.3723.6=0.016 More Than 0.002, Fo

17、rmula UG-32(d)(1) to Be Used:According to UG-32(b) & UG-32(f) t=larger of t2 and t1,t=4.36考虑允许的腐蚀裕量：t= t+Ca=4.36+Ca=4.36+2.00=6.36mmConsider of corrosion allowable: t = t+Ca=4.36+Ca=4.36+2.00=6.36mm对于介质是压缩蒸汽，UG-16 (b)(4)中的受压件最小厚度应大于2.5mm；UG-16 (b)(4) the minimum thickness of pressure retaining compo

18、nents 2.5mm for compressed steam；成形后封头的实际最小厚度 11.5毫米 2.0毫米=9.5毫米 6.36毫米，而且 4.5毫米，也可。Actual minimum thickness of heads after forming 11.5mm-2.0mm=9.5mm 5.73mm and 4.5mm ,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，毫米t = minimum required thickn

19、ess of nozzles, mmP =内部设计压力，1.2兆帕P = internal design pressure, 1.2 MPa see UG-21R =管口内半径，36.83+2毫米R = inside radius of the nozzle, 36.83+2 mmS =最大许用应力值，118兆帕S = maximum allowable stress value, 118 MPa see ASME Code Section II Part D Table 1A for material SA106M Gr. B E =焊缝系数，1.0 E = joint efficiency

20、, 1.0 Seamless shell see Table UW-12(1) 根据UG-45，管口要求最小厚度According to UG-45, Min. required thickness of nozzle : ta =0.40+2=2.40mmSee Formula UG-27(c)(1)tb =mintb3，max(tb1，tb2) where 在此：tb1 =对于仅受内压容器,在压力(假设E=1.0)下壳体或封头在接管颈或其它连接件在容器连接处所 需的最小厚度(加上复腐蚀余量),但在任何情况下不得小于UG-16(b)中所规定的材料最小厚度.tb1 = for vessels

21、under internal pressure, the thickness (plus corrosion allowance) required for pressure (assuming E=1.0) for the shell or head at the location where the nozzle neck or other connection attaches to the vessel but in no case less than the minimum thickness specified for the material in UG-16(b). tb1 =

22、 对于介质是压缩空气(不含任何腐蚀余量)，UG-16 (b)(4)中的受压件最小厚度应大于2.5mm；UG-16 (b)(4) the minimum thickness of pressure retaining components 2.5mm for compressed air service(exclusive any corrosion allowance). tb2 = 0 mm: 对于仅受外压容器,壳体或封头在接管颈或其它连接件在容器连接处，将外压设计压力(假 设E=1.0)，代入公式所得的厚度(加上复腐蚀余量),但在任何情况下不得小于UG-16(b)中 所规定的材料最小厚度.

23、tb2 = 0 mm for vessels under external pressure, the thickness (plus corrosion allowance) obtained by using the external design pressure as an equivalent internal design pressure (assuming E =1.0) in the formula for the shell or head at the location where the nozzle neck or other connection attaches

24、to the vessel but in no case less than the minimum thickness specified for the material in UG-16(b).tb3= 在表UG-45中所给出的厚度应加上腐蚀余量。tb3 = the thickness given in Table UG-45 plus the thickness added for corrosion allowance.= 4.80+2=6.80mm (见表 UG-45)Therefore 所以:tb =mintb3，max(tb1，tb2)= min6.8，max(5.51，0)

25、= 5.51mmTUG-45 = max(ta，tb) = max(2.40，5.51) =5.51mm接管要求的最小厚度：Actual used thickness of tube wall:= 7.62mm*0.875=6.67 5.51mm, so it is satisfactory.实际使用的管厚度为7.62*0.875=6.67 5.51毫米,满足要求.2.4 人孔的最小厚度 Min. Required Thickness for Manhole (N4) (UG-45)Symbols: 符号t =管口要求最小壁厚，毫米t = minimum required thickness

26、of nozzles, mmP =内部设计压力，1.2兆帕P = internal design pressure, 1.2 MPa see UG-21R =管口内半径，190.5+2毫米R = inside radius of the nozzle, 190.5+2 mmS =最大许用应力值，118兆帕（见asme规范第二卷D 分册的表1A材料SA106 Gr. B）S = maximum allowable stress value, 118 MPa see ASME Code Section II Part D Table 1A for material SA106 Gr. B E =焊

27、缝系数，1.0 无缝壳体见表UW-12(1)E = joint efficiency, 1.0 Seamless shell see Table UW-12(1) 根据UG-45，接管颈要求最小厚度：According to UG-45, Min. required thickness of nozzle neck ta= 适用时，适用于UG-27 和 UG- 28的内压与外压的接管颈所要求最小厚度（加上腐蚀余量）ta = minimum neck thickness required for internal and external pressure using UG-27 and UG-

28、 28 (plus corrosion allowance), as applicable.=tUG-45 = ta = 3.97mm管壁的实际使用最小厚度：Actual min. used thickness of tube wall:实际使用的接管为12.70.875=11.11毫米3.97毫米,满足要求.= 12.70.875=11.11mm 3.97mm, so it is satisfactory.2.5 开孔和补强 Openings and Reinforcement (UG-36)2.5.1 用于接管N1,N2和N3 For nozzles N1,N2,N3. 最终的开孔直为88

29、.9mm，壳体所要求的最小厚度为5.51mm。根据UG36(c)(3)(a)压力无剧烈波动的容器上的开孔，在下述情况下，不需要结构自补强以外的补强: The finished diameter of circular opening is 88.9mm, and minimum required thickness of shell is 5.51mm. According to UG36(c)(3)(a) openings in vessel not subject to rapid fluctuations in pressure do not require reinforcement

30、other than that inherent in the construction under the following conditions: a) 焊接连接件满足相关规范要求，且其已经完成的开孔（直径不大于88.9mm）在最小需要厚 度为10mm或更小的容器壳体上。a) welded connections meeting the applicable，and with a finished diameter of circular opening is not larger than 89mm diameter in vessel shell with a required mi

31、nimum thickness of 10mm or less than 10mm.因此，接管N1,N2和N3的开孔不需要进行补强。So openings of Nozzle N1,N2,N3 shall be exempt from the reinforcement requirements.2.5.2 For Manhole N4 对于人孔: ( UG-37). Symbols: 符号A= total cross-sectional area of reinforcement required in the plane under consideration总的要求补强所需面积A1= a

32、rea in excess thickness in the head wall available for reinforcement封头的有效补强面积A2= area in excess thickness in the nozzle wall available for reinforcement接管的有效补强面积A3= area available for reinforcement when the nozzle extends inside the vessel wall内伸接管的补强面积,0平方毫米A41 = cross-sectional area of various wel

33、ds available for reinforcement焊缝的有效补强面积A5= cross-sectional area of material added as reinforcement 外加补强圈的有效补强面积c= corrosion allowance 腐蚀余量，2毫米D= inside shell diameter 封头内径，800+4毫米Dp= outside diameter of reinforcing element补强圈的外径d= finished diameter of circular opening or finished dimension 圆形开孔工的直径，

34、= 381+4毫米E1=值为1F=correction factor that compensates for the variation in internal pressure stresses on different planes with respect to the axis of a vessel修正系数值为= 1fr1= for nozzle wall inserted through the vessel wall Sn/ Sv= 118MPa/138MPa=0.855fr 2 = Sn /Sv =118MPa/138MPa=0.855h=distance nozzle pr

35、ojects beyond the inner surface of the head wall.接管在封头内壁的伸出高度，0毫米L=length of projection defining the thickened portion of integral reinforcement of a nozzle neck beyond the outside surface of the head wall接管颈座伸出封头壁外表面整体补强加厚部分的高度R= inside radius of the shell course under consideration考虑腐蚀余量后封头内半径，= 4

36、02毫米Rn= inside radius of the nozzle under consideration 考虑腐蚀余量后接管内半径= 192.5毫米 P = 内部设计压力，1.2兆帕P = internal design pressure, 1.2 MPa see UG-21Sp = allowable stress in reinforcing element (plate) 补强圈许用应力值=138兆帕 ( SA516M Gr.485)Sn=allowable stress in nozzle,接管许用应力值，118 MPa 兆帕 (SA106M Gr.B) Sv = allowab

37、le stress in head, 封头许用应力值=138 MPa兆帕 ( SA516M Gr.485 )t =specified head wall thickness 封头壁厚=13毫米-下偏差-c=13-0.25-2 = 10.75mmtn = nozzle wall thickness 接管壁厚度=12.7mmCa =12.7- 2=10.7 mmtr = required thickness a formed head, computed by the rules of this Division for the designated pressure, using E=1,封头所

38、需厚度te = thickness or height of reinforcing element补强圈的厚度trn = required thickness of a seamless nozzle wall 无缝接管管壁所需厚度， = 3.97mm1) The total cross sectional area of reinforcement in according to Fig. UG-37.1根据图UG-37.1，所需总的补强面积A= d tr F+2 tn tr F(1- fr1= (381+4)5.501+210.75.501(1-118/138)=2134.552) Ar

39、ea available in shell; use larger value:A1=d(E1 t-F tr-2 tn(E1 t-F tr(1- fr1 =(381+4)(110.75-15.50-210.7 (110.75-15.50(1- 118/138 =2004.97A1=取大的 A1=2(t+ tn(E1 t-F tr-2 tn(E1 t-F tr(1- fr1Use larger =2(10.75+10.7(110.75-15.50-210.7(110.75-15.50(1- 118/138=208.97A1=2004.973) Area available in nozzle p

40、rojecting, outward; use smaller value: A2=5(tn - trnfr2 t =5(10.7 -3.97118/13810.75=309.28A2=取小值Use smaller A2=5(tn - trnfr2 tn =5(10.7 -3.97118/13810.7=307.84A2=307.844) Area available for inward nozzle : A3 =05) Area available for outward weld A41=Leg焊脚高Leg焊脚高fr2 = 99118/138=69.266) Area available

41、 for inward weld A43= 0If A1+ A2+ A3+ A41+ A43A，Opening is adequately reinforced.则说明开孔补强足够。 A1+ A2+ A3+ A41+ A43=2004.97+307.84+0+69.26+0=2382.07平方毫米A=2134.55所以N4无需补强。2.6 接管与壳体连接焊缝的强度计算 Strength Calculation for Nozzle Attachment Weld ( UW-15)根据UW15(b)(1)，以下（1）所述的是不需要进行接管连接到收押件的强度计算。 According to UW1

42、5(b)(1), Strength calculations for nozzle attachment welds for pressure loading are not required for the following:(1)图UW-16.1的图示(a), (b), (c), (d), (e), (f-1), (f-2), (f-3), (f-4), (g), (x-1), (y-1)。 Figure UW-16.1 sketches (a), (b), (c), (d), (e), (f-1), (f-2), (f-3), (f-4), (g), (x-1), (y-1).2.7

43、接管与壳体连接焊缝高度核算 Verify the Fillet Weld Size of Nozzles according to UW16(a)(2)(b) and Fig.UW16.1(C)2.7.1 For Nozzle N1,N2,N3tmin =小于19毫米或者由角焊，单坡口焊接或单J形焊接连接部分的较薄处的厚度= 7.62毫米;tmin =the smaller of 19mm or the thickness of the thinner of the parts jointed by a fillet, single-bevel, or single-J weld = 7.62

44、mmtc 6毫米，并且0.7 tmin = 5.33毫米tc smaller of 6mm and 0.7tmin = 5.33mm 角焊的实际焊喉尺寸= 6.0毫米 5.33毫米Actual throat size of fillet weld = 6.0mm 5.33mm, so it is satisfactory.2.7.2 For Nozzle N4tmin = 小于19毫米或者由角焊，单坡口焊接或单J形焊接连接部分的较薄处的厚度= 12.7毫米;tmin = the smaller of 19mm or the thickness of the thinner of the par

45、ts jointed by a fillet, single-bevel, or single-J weld = 12.7mmtc 6毫米，并且0.7 tmin =8.89毫米tc smaller of 6mm and 0.7tmin = 6 mm 角焊的实际焊喉尺寸= 9毫米6.0毫米Actual throat size of fillet weld =9 mm6.0mm, so it is satisfactory.3. 热处理 Heat treatment3.1 制造后热处理 Post Fabrication Heat Treatment ( UG-79)3.2 焊后热处理 Post W

46、eld Heat Treatment ( UCS-56 )壳体和封头的材料SA-516M Gr.485属于P-No.1（见第九卷的QW-422所规定的母材P-No.分组）。根据表UCS-56注释2，不需要进行热处理。Shell and head material SA-516M Gr.485 belongs to P-No.1 (see Section P-Number material groupings of base metals for qualification of QW-422). In accordance with Table UCS-56 note 2, 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 ( UCS-66)4.2 冲击试验 Impact Testing UG20(f)根据U