ASME计算书201413

ASME计算书201413 江苏星瑞化工工程科技有限公司 Rev. No. : 0 Jiangsu Sunrise Chemical Document No. DC-A14-001 Page : 1 of 30 Engineering Technology Co., Ltd. 压缩空气罐的设计计算 DESIGN CALCULATIONS OF COMPRESSED AIR STORAGE TANK 设计 规范 编程规范下载gsp规范下载钢格栅规范下载警徽规范下载建设厅规范下载 :ASME规范第?卷第1册，2013年版 Design Code: ASME Code Section ? Division 1,2013 Edition 工作令号: Work Number: 图号:ASME14-001 Rev.0 Drawing No.:ASME14-001 Rev.0 3 2 1 0 计算 审核 批准 Rev. Prepared / Date Reviewed /Date Approved /Date 江苏星瑞化工工程科技有限公司 Jiangsu Sunrise Chemical Engineering Technology Co.,Ltd 1 江苏星瑞化工工程科技有限公司 Rev. No. : 0 Jiangsu Sunrise Chemical Document No. DC-A14-001 Page : 2 of 30 Engineering Technology Co., Ltd. 目 录 Content 封面 1 Cover 目录 2 Content A( 设计参数和条件 3 Design parameters and the condition B(基本材料许用应力的选取及其依据 4 Selection of base material, allowable stresses and its basis C(强度计算 4 Strength Calculations 1(壳体壁厚的计算列表 4 Calculation Tabulation of cylindrical shell wall thickness 2(椭圆形封头的壁厚计算 5 Wall thickness calculations for ellipsoidal heads 3(人孔圈的计算 7 Calculation of manhole ring 4(接管计算(依照UG-45) 8 Calculation of nozzles(according to UG-45) 5(开孔补强计算 10 Calculation of opening reinforcement 6(接管角焊缝尺寸计算 13 Calculation for fillet welding size of nozzles 7. 法兰与接管颈部的焊缝计算 14 Calculation for flange to nozzle neck welds 8(人孔附件焊接强度 16 Checking of welding joint strength of the attachment of manhole D( 标准 excel标准偏差excel标准偏差函数exl标准差函数国标检验抽样标准表免费下载红头文件格式标准下载 件的选取 17 Selection of standard parts E(液压试验压力及校核 17 Hydrotest pressure and stress checking F(判定对冲击试验的要求 18 Judgements whether the impact test is required G(判定对冷作成型后热处理的要求 19 Judgement for whether heat treatment shall be carried out after cold forming H(焊后热处理检测 20 Check of post weld heat treatment I(无损检测要求 21 Required NDE 附录: 21 Appendix 2 江苏星瑞化工工程科技有限公司 Rev. No. : 0 Jiangsu Sunrise Chemical Document No. DC-A14-001 Page : 3 of 30 Engineering Technology Co., Ltd. A 鞍座的计算 22 The calculation of saddle supports B 容器载荷要求(ASME-?-1 UG-22 & UG-54) 29-30 Vessel loading requirements (ASME sect.? Div. 1, UG-22&UG-54) A. 设计参数和条件: Design parameters and the condition 结构草案和设计 计划 项目进度计划表范例计划下载计划下载计划下载课程教学计划下载 参照用户设计技术条件ABC/2013 Rev.0 Structural sketch and design plan are referred to The Customer Design Specification And Drawings ABC/2013 Rev.0 工作令号:@@@ 图号:ASME13-001 ，Rev.0 Work No:@@@@ Dwg. No:ASME13-001 ，Rev.0 设计规范:ASME 规范第?卷第1册(2013年版) Design code: ASME Code Sect.?.Div.1(2013.Ed) 容器载荷依据UG-22 Vessel loadings per UG-22 操作压力: 0.5MPa Operating pressure: 0.5MPa 操作温度:0,40? Operating temperature:0,40? 介质:压缩空气(非致命性) Service Fluid: Compressed air (Non-lethal) 射线检测要求:抽样射线检测(A、B类，其他按标准) NDE requirements: spot RT(A、B category，other per Code) 焊接接头系数: 0.85 for shell & head Joint efficiency: 0.85 for shell & head 设计压力:0.6MPa Design pressure:0.6MPa 设计温度: 50? Design temperature:50? 最小设计金属温度: 0? at 1.2MPa Min. design metal temperature(MDMT):0? at 1.2MPa 最大许用工作压力:1.2MPa at 50? MAWP: 1.2MPa at 50? 腐蚀裕量:1.0mm Corrosion allowance:1.0mm 水压试验压力:1.56Mpa Hydrostatic test pressure:1.56Mpa 焊后热处理:NO,per UCS-56 Postweld heat treatment:NO,per UCS-56 冲击要求:NO,per UG-20(f) AND UCS-66 IMPact require:NO,per UG-20(f) AND UCS-66 3名义容积:1.48m 3Nominal volume:1.48m 3 江苏星瑞化工工程科技有限公司 Rev. No. : 0 Jiangsu Sunrise Chemical Document No. DC-A14-001 Page : 4 of 30 Engineering Technology Co., Ltd. 基本材料: SA-516M Gr.485 筒体和封头板(Shell and Head plate) Base material: SA-106M Gr.B接管(Pipe) SA-105M 法兰(Flange) B. 基本材料，许用应力的选取及其依据 Selection of base material, allowable stresses and its basis (a)壳体，封头和人孔圈(由钢板轧制而成)的材料:SA-516M Gr.485 Material of shell course, head and manhole ring(rolled with plate): SA-516M Gr.485 它在设计温度下的最大许用应力为: Its max. allowable stresses at the design temperature is: S=138MPa (b)对于作为承压元件的接管材料，采用SA-106M Gr.B。 For nozzles as pressurized parts, material SA-106M Gr.B is adopted 它在设计温度下的最大许用应力为:(摘自:ASME第?卷，D 篇，表1A) Its max. allowable stresses(abstracted from:ASME Sect.?.part D,Table 1 A) at the design temperature is: S=118MPa C.强度计算 Strength Calculations 1. 壳体壁厚计算列表 Calculation Tabulation of cylindrical shell thickness 设计公式Design formula: 环向应力Circumferential Stress: tr= PR/(SE-0.6P) UG-27(c) (1) (P=1.2Mpa,0.385SE=45.16 Mpa); 1 纵向应力Longitudinal Stress: tr= PR/(2SE+0.4P) UG-27(c) (2) (P=1.2 Mpa,1.25SE=146.625 Mpa) 2 计算公式及结参数 符号数值单位果Calc.formulae 备注Remarks parameter symbol Value Unit & results 设计压力 P 1.2 MPa Design press 设计温度 t 50 ? Design temp 腐蚀裕量 c 1.0 mm Corr. allow 基本材料 SA-516M Gr.485 4 江苏星瑞化工工程科技有限公司 Rev. No. : 0 Jiangsu Sunrise Chemical Document No. DC-A14-001 Page : 5 of 30 Engineering Technology Co., Ltd. Base material 焊接接头系数 E 0.85 joint effic. 许用应力 S 138 MPa Allow. stress 壳体半径 R 500+1 mm Cylind.radius UG-27(c) (1) tr=1.2×501/(138×0.85-0.6×1.2)=5.16mm 1计算厚度 tr UG-27(c) (2) Calc. thick tr=1.2×501/(2×138×0.85，0.4×1.2)=2.56mm 2 tr取较大值5.16mm 最小厚度加腐蚀 裕量 UG-16(b)(4) Min.wall.thick.plus 2.5+1.0=3.5mm corr.Allow 设计厚度 tr+c=5.16+1.0=6.16mm Design thick 最小需要厚度 tm 6.16 Req.min.thick 名义厚度 tn 8mm(under-tolerance considered公差考虑在内) Nominal thick 结论 8mm, 6.16mm OK Conclusion 2椭圆形封头的壁厚计算 Wall thickness calculations for ellipsoidal heads (1) 内压椭圆形封头厚度计算 Calculations of thickness of 2:1 ellipsoidal head under internal pressure 选取长轴与短轴比值为2:1 的椭圆形封头。 Select ellipsoidal head with the ratio of major axis to minor axis of 2:1. 设计公式Design formula: tr = PD/(2SE-0.2P) UG-32 (d) (1) (t=7.2mm t/L=7.2/901.8=0.00798?0.002) 1ss 计算公式及结果参数 符号数值单位备注Calc.formulae & parameter symbol Value Unit Remarks results 腐蚀裕量 c 1.0 mm Corr. allow 5 江苏星瑞化工工程科技有限公司 Rev. No. : 0 Jiangsu Sunrise Chemical Document No. DC-A14-001 Page : 6 of 30 Engineering Technology Co., Ltd. 基本材料 SA-516M Gr.485 Base material 焊接接头系数 E 0.85 joint effic. 许用应力 S 138 MPa Allow. stress 壳体内径 D 1000+2 mm Cylind.radius 计算厚度 =1.2×1002/(2×138×0.85-0.2×1.2) =5.13mm trtr 11Calc. thick Take tr =tr=5.13mm 1 最小厚度加腐蚀 裕量 UG-16(b)(4) 2.5+1.0=3.5mm Min.wall.thick.plus corr.Allow 设计厚度 tr+c=5.13+1.0=6.13mm,3.5mm Design thick 最小需要厚度 5.13+1.0=6.13mm tm Req.min.thick (under-tolerance considered公差考虑在内) 成型后最小厚度 After forming tn 7.2mm thickness(mm) 结论 7.2mm ,6.13mm ?OK Conclusion (2) 内压椭圆形封头直边段厚度计算 Calculations of thickness for skirt of ellipsoidal heads 设计公式Design formula: R/(SE-0.6P) UG-27(c) (1) t= P = 1.2×501/(138×0.85-0.6×1.2) =5.16mm 据 UG-32(l) ，封头直边段实际取值厚度8mm大于相同内径无缝壳体要求厚度5.16mm，满足要求。 According UG-32(l),the thickness 8mm of skirt is greater than 5.16mm that required for a seamless shell of the same inside diameter, It’s OK. 3.人孔圈的计算 Calculation of manhole ring 6 江苏星瑞化工工程科技有限公司 Rev. No. : 0 Jiangsu Sunrise Chemical Document No. DC-A14-001 Page : 7 of 30 Engineering Technology Co., Ltd. 人孔是依照UG-46(f)(3)准备的，人孔圈是用名义直径为450mm的SA-516M Gr.485钢板卷制而成的，以便于人孔圈与标准法兰的连接。 Manhole is provided in accordance with UG-46(f)(3),Its ring is formed by rolling using SA-516M Gr.485 plate with a nominal diameter of DN450 in order to joint the std.flange with the manhole ring. 设计公式Design formula: tr = PRo/(SE+0.4P) 附录Appendix 1,1-1(a)(1) 计算公式及结果参数 符号数值单位备注Calc.formulae & parameter symbol Value Unit Remarks results 设计压力 P 1.2 MPa Design press 设计温度 t 50 ? Design temp 腐蚀裕量 c 1.0 mm Corr. allow 基本材料 SA-516M Gr.485 Base material 焊接接头系数 E 0.85 joint effic. 许用应力 S 138 MPa Allow. stress 壳体半径 Ro 228.5 mm Cylind.diameter 计算厚度 tr tr = 1.2×228.5/(138×0.85+0.4×1.2) =2.33mm Calc. thick 最小厚度加腐蚀 裕量 UG-16(b)(4) 2.5+1.0=3.5mm Min.wall.thick.plus corr.Allow 设计厚度 tr+c=2.33+1.0=3.33mm Design thick 最小需要厚度 tm 3.5mm Req.min.thick 名义厚度 tn 8mm Nominal thick 结论 8mm,3.5mm ?OK Conclusion 7 江苏星瑞化工工程科技有限公司 Rev. No. : 0 Jiangsu Sunrise Chemical Document No. DC-A14-001 Page : 8 of 30 Engineering Technology Co., Ltd. 4.接管计算(依照UG-45) Calculation of nozzles(according to UG-45) 接管类型及尺寸如下: The types & sizes of nozzles as follow: 公称壁厚符号公称尺寸Noml.Th 用途Service 标准号Specifi Symbol Noml.Size (mm) 进口 N1 DN50 5.54 ASME B36.10M-2004 Inlet 出口 N2 DN50 5.54 ASME B36.10M-2004 Outlet 压力指示N3 DN25 4.55 ASME B36.10M-2004 Press.Ind. 排水 N4 DN25 4.55 ASME B36.10M-2004 Drain 接管设计公式Design formula for nozzles: tr = PRo/(SE+0.4P) 附录Appendix 1,1-1(a)(1) n 壳体设计公式Design formula for cylindrical shell: tr = PR/(SE-0.6P) UG-27(c)(1) s (4-1) DN50接管颈部厚度计算列表 Calculation Tubulation For DN50 Nozzle Neck 依照ASME B36.10M，此接管参数如下: According to ASME B36.10M,this nozzle parameter are as follow: 外径outer diameter(O.D): 60.3mm 壁厚Wall thickness:: 5.54mm 计算公式及结果参数 符号数值单位备注Calc.formulae & parameter symbol Value Unit Remarks results 设计压力 P 1.2 MPa Design press 设计温度 t 50 ? Design temp 腐蚀裕量 c 1.0 mm Corr. allow 基本材料 SA-106M Gr.B Base material 焊接接头系数 E 0.85 joint effic. 8 江苏星瑞化工工程科技有限公司 Rev. No. : 0 Jiangsu Sunrise Chemical Document No. DC-A14-001 Page : 9 of 30 Engineering Technology Co., Ltd. 许用应力 S 118 MPa Allow. stress 接管外半径 Outer radius of Ro 30.15 mm nozzle 设计厚度 t t = 1.2×30.15/(118×0.85+0.4×1.2)+1.0 =1.36mm aaDesign thick 2.5+1.0=3.5 mm UG-16(b)(4) t=Max, b1 t =1.2×501/(138×1-0.6×1.2) +1=5.38mm rs 最小厚度t=5.38mm b1 Min.thick. of t=5.38mm b1 t=Min, b t=3.42+1.0=4.42mm Table UG-45(DN50) b3 tb =4.42mm t=1.36mm a 最小需要厚度 t=Max, UG-45 Req.min.thick t=4.42mm b t=4.42mm UG-45 接管厚度 tn 5.54mm Nozzle thick 结论 5.54*0.875mm=4.85mm>4.42mm ,OK Conclusion (4-2) DN25接管颈部厚度计算列表 Calculation Tubulation For DN25 Nozzle Neck 依照ASME B36.10M，此接管参数如下: According to ASME B36.10M,this nozzle parameter are as follow: 外径outer diameter(O.D): 33.4mm 壁厚Wall thickness: 4.55mm 计算公式及结果参数 符号数值单位备注Calc.formulae & parameter symbol Value Unit Remarks results 设计压力Design P 1.2 MPa press 设计温度 t 50 ? Design temp 腐蚀裕量 c 1.0 mm Corr. allow 基本材料 SA-106M Gr.B Base material 9 江苏星瑞化工工程科技有限公司 Rev. No. : 0 Jiangsu Sunrise Chemical Document No. DC-A14-001 Page : 10 of 30 Engineering Technology Co., Ltd. 焊接接头系数 E 0.85 joint effic. 许用应力 S 118 MPa Allow. stress 壳体半径 Ro 16.7 mm Cylind.radius 设计厚度 t t = 1.2×16.7/(118×0.85+0.4×1.2)+1.0 =1.20mm aaDesign thick 2.5+1.0=3.5 mm UG-16(b)(4) t=Max, b1 t=1.2×501/(138×1-0.6×1.2) +1=5.38mm rs 最小厚度t=5.38mm b1 Min.thick. of t=5.38mm b1 t=Min, b t=2.96+1.0=3.96mm Table UG-45 b3 t =3.96mm b t=1.20mm a 最小需要厚度 t=Max, UG-45 Req.min.thick t =3.96mm b t=3.96mm UG-45 接管厚度 tn 4.55 mm Nozzle thick 结论 4.55*0.875mm=3.98mm>3.96mm,?OK Conclusion 5.开孔补强计算: Calculation of opening reinforcement: (5-1).依照UG-36(c)(3)(a),壳体名义厚度为8mm, 接管(除人孔接管 外)不需要另行补强。 Nominal thickness of the shell is 8mm according to UG-36(c)(3)(a), the nozzles other than manhole nozzle are not required for additional reinforcement. (5-2).人孔补强: manhole reinforcement: (5-2-1).参数: Parameters: 接管许用应力Allowable stress in nozzle: Sn = 138(MPa) 壳体许用应力Allowable stress in shell: Sv = 138(MPa) 10 江苏星瑞化工工程科技有限公司 Rev. No. : 0 Jiangsu Sunrise Chemical Document No. DC-A14-001 Page : 11 of 30 Engineering Technology Co., Ltd. 补强板的许用应力Allowable stress in reinforcement plate: Sp = 138(MPa): 接管壁厚Thickness of nozzle wall: tn = 8-1.0=7mm : 接管计算厚度Calculated thickness of nozzle wall: trn = 1.2×228.5/(138×1+0.4×1.2) =1.98mm (E=1): 接管计算半径Calculated radius of nozzle: Rn = (457-2×7)/2=221.5mm 壳体计算厚度Calculated thickness of shell: tr = 1.2×501/(138×1-0.6×1.2) =4.38mm (E=1) 开孔直径Opening diameter: d =2×Rn =443mm: 补强板厚度Thickness of reinforcing plate: te = 8mm 外伸高度Height of outward extension: h1 = min{2.5t,2.5tn+te} = min{17.5mm,25.5mm} =17.5mm 人孔圈外伸高度Height of outward extension of ring: h = 191mm >17.5mm 内伸高度Height of inward extension: h2 = 0 系数Factor: E1 = 1; F = 1 强度削弱系数Strength reduction factor:: fr1 = 1 fr2 = 1 fr3 = min{Sn,Sp}/Sv = 1 fr4 = Sp/Sv = 1 (5-2-2)补强范围检验: Check for limits of reinforcement: (a) 平行于容器壁的范围:UG-40(b) Limit parallel to the vessel wall: UG-40(b) d=443mm Rn+tn+t=221.5mm+7mm+7mm=235.5mm large of 二者中较大值 取443mm use 443mm (b)垂直于容器壁的范围:UG-40(c) Limit vertical to the vessel wall: UG-40(c) 2.5t=2.5x7mm=17.5mm 2.5tn+te=2.5x7mm+8mm=25.5mm smaller of 二者中较小值 11 江苏星瑞化工工程科技有限公司 Rev. No. : 0 Jiangsu Sunrise Chemical Document No. DC-A14-001 Page : 12 of 30 Engineering Technology Co., Ltd. 取17.5mm use17.5mm 所需补强面积:UG-37(c)、图UG-37.1 Reinforcement area required: UG-37(c)、Drawing UG-37.1 2 A = dtrF+2tntrF(1-fr1) = 443×4.38×1+0 =1940.34(mm) 壳体补强面积:图UG-37.1 Area for the reinforcement of the shell: Drawing UG-37.1 d(E1t-Ftr)-2tn(E1t-Ftr)(1-fr1) A1=Max{ 2(t+tn)(E1t-Ftr)-2tn(E1t-Ftr)(1-fr1) 2443×(1×7-1×4.38) = 1160.66(mm) = Max{ 2 2×(7+7)(1×7-1×4.38) =73.36(mm) 2 = 1160.66(mm) 接管有效补强面积:图UG-37.1 Area for the reinforcement of the nozzle: Drawing UG-37.1 5(tn-trn)fr2t A=Min{ 2 2(tn-trn)(2.5tn+te)fr 225×(7-1.98)×7= 175.7(mm) =Min{ 2 2×(7-1.98)×(2.5×7+8)×1=256.02(mm) 2=175.7(mm) 内伸接管补强面积:图UG-37.1 Area for the reinforcement of the inward extended nozzle:DrawingUG-37.1 A3 = 0 焊缝区补强面积:图UG-37.1 Area for the reinforcement of the join: Drawing UG-37.1 222A41=fillet height焊脚高度xfr=8x1=64(mm) 3222A42=fillet height焊脚高度xfr=7x1=49(mm) 4 补强元件外径:Dp = 760mm Outside diameter of reinforcing member: 补强板补强面积: Area for the reinforcement of the reinforcing plate: A5 = (Dp-d-2tn)tefr4 = (760-443-2×7)×8×1 2=2424(mm) 12 江苏星瑞化工工程科技有限公司 Rev. No. : 0 Jiangsu Sunrise Chemical Document No. DC-A14-001 Page : 13 of 30 Engineering Technology Co., Ltd. A1+A2+A3+A41+A42+A5 =1160.66+175.7+0+64+49+2424 22=3873.36(mm) > A = 1940.34(mm) 满足补强要求。 Reinforcement requirements are satisfied. (5-2-3)焊缝强度校核: Checking of welding joint strength: 依照UW-15(b)，DN450、DN50和DN25接管M,N1,N2,N3,N4 强度计算免 除[图UW-16.1(c)(d)]。 According toUW-15(b),the strength calculations for 450mm、 50mm and 25mm nozzles M,N1,N2,N3,N4 are exempted [Fig.UW-16.1(c)(d)] 。 6.接管角焊缝尺寸计算 Calculation for fillet welding size of nozzles 此节是以规范UW-16 为基础的。 this paragraph is based on Code UW-16. (a)人孔角焊缝尺寸计算: Calculation for fillet welding size of manhole t =8mm (依照UW-16，图UW-16.1(d)) min (in accordance with UW-16，Fig.UW-16.1(d)) 1/2tmin =1/2×8mm=4mm 1?Actual weld throat size(实际焊缝厚度) = 7mm×0.7 = 4.9mm > 1/2tmin =4mm O.K. 6mm,mintc,, 0.70.7*85.6t,,mmmin, ,5.6mm 2?Actual weld throat size(实际焊缝厚度)=8mm×0.7=5.6mm=tc=5.6mm O.K. (b)接管角焊缝尺寸计算: N1,N2尺寸:OD60.3X5.54,名义厚度是5.54mm。依图UW-16.1(c),角焊缝尺寸: The nozzleN1,N2 size: OD60.3X5.54,nominal wall thickness is 5.54mm. According to Fig UW-16.1(c),fillet welding size: 13 江苏星瑞化工工程科技有限公司 Rev. No. : 0 Jiangsu Sunrise Chemical Document No. DC-A14-001 Page : 14 of 30 Engineering Technology Co., Ltd. tc = 6mm或0.7tmin，取较小值。 tc = 6mm or 0.7tmin, whichever is smaller. = min{6mm ;0.7×5.54mm} = 3.88mm Actual tc = 6×0.7 = 4.2mm > 3.88mm O.K. N3,N4尺寸:OD33.4×4.55,名义厚度4.55mm,依图UW-16.1(c),角焊缝尺寸: The nozzleN3,N4 size: OD33.4×4.55,nominal wall thickness is 4.55mm. According to Fig UW-16.1(c),fillet welding size: tc = 6mm或0.7tmin，取较小值。 tc = 6mmor 0.7tmin, whichever is smaller. = min{6mm ;0.7×4.55mm } = 3.19mm Actual tc = 6×0.7 = 4.2mm > 3.19mm O.K. 7. 法兰与接管颈部的焊缝计算 Calculation for flange to nozzle neck welds 此节按 UW-21要求 this paragraph is based on UW-21 GENERAL NOTE: X pthe lesser of 1.4tn or the thickness of the hub min 7.1 the nozzle size接管尺寸规格: DN450(M) nominal wall thickness is 8mm 公称厚度是8mm According to UW-21(b) and Fig. UW-21 , fillet weld leg size: 依照UW-21(b)及 图UW-21，角焊缝焊脚尺寸: 1) 取小者 nozzle thickness t=8mm 接管公称厚度 n smaller 6 mm take 6mm 取6mm Actual : 6mm OK 实际为6mm 满足要求 2)取小者 X= 1.4×nozzle thickness 1.4t=11.2mm 1.4倍接管公称厚度 nmin 14 江苏星瑞化工工程科技有限公司 Rev. No. : 0 Jiangsu Sunrise Chemical Document No. DC-A14-001 Page : 15 of 30 Engineering Technology Co., Ltd. smaller 21.6mm 法兰颈箍厚度 take 11.2 mm 取11.2mm Actual : 11.5mm OK 实际为11.5mm 满足要求 7.2 the nozzle size接管尺寸规格: DN50(N1,N2) nominal wall thickness is 5.54mm 公称厚度是5.54mm According to UW-21(b) and Fig. UW-21 , fillet weld leg size: 依照UW-21(b)及图UW-21，角焊缝焊脚尺寸: 1) 取小者 nozzle thickness t=5.54mm 接管公称厚度 n smaller 6 mm take 5.54mm 取5.54mm Actual : 5.6mm OK 实际为5.6mm 满足要求 2)取小者 X= 1.4×nozzle thickness 1.4t=7.756mm 1.4倍接管公称厚度 nmin smaller 8.05mm 法兰颈箍厚度 take 7.756 mm 取7.756mm Actual : 7.8mm OK 实际为7.8mm 满足要求 7.3 the nozzle size接管尺寸规格: DN25(N3,N4) nominal wall thickness is 4.55mm 公称厚度是4.55mm According to UW-21(b) and Fig. UW-21 , fillet weld leg size: 依照UW-21(b)及图UW-21，角焊缝焊脚尺寸: 1) 取小者 nozzle thickness t=4.55mm 接管公称厚度 n smaller 6 mm take 4.55 mm 取4.55 mm Actual : 4.6 mm OK 实际为4.6 mm 满足要求 2)取小者 X= 1.4×nozzle thickness 1.4t=6.37mm 1.4倍接管公称厚度 nmin smaller 7.25mm 法兰颈箍厚度 take 6.37 mm 取6.37mm Actual : 6.4mm OK 实际为6.4mm 满足要求 8.人孔附件焊接强度计算 Checking of welding joint strength of the attachment of manhole 人孔盖轴耳焊接简图 15 江苏星瑞化工工程科技有限公司 Rev. No. : 0 Jiangsu Sunrise Chemical Document No. DC-A14-001 Page : 16 of 30 Engineering Technology Co., Ltd. Weld corner strength calculation is selected per Chinese standards YZB250-89 角焊缝强度计算按中国标准YZB250-89 Parameters:参数 Material SA-516 Gr.485 Allowable T ensile Stress 许用拉伸应力 [σ]=138MPa Tensile strength of the fillet –weld (Flange Cover Axis Plate)法兰盖轴耳角焊缝拉伸强度校核 Flange Cover weight 法兰盖质量 m=94kg 2 Area of welding 焊缝面积 A=10×0.7×30=210mm [σ]w =0.7[σ]= 0.7×138=96.6 MPa Stress 应力 σ=mg/ A=94x9.8/(2×210)=2.19MPa<[σ] [σ]w Shear strength of the fillet –weld (Flange Axis Plate)法兰轴耳角焊缝剪切强度校核 2τ=m gl/(αhb) 2 mFlange Cover weight 法兰盖重量 94kg 2: l:Length between the center of the boom and the welding neck 法兰盖中心到焊缝距离402mm α:Torsion Factor 扭转系数 0.31 h:Width of the supporting plate 支撑宽度 24mm b: Length of the supporting plat支撑长度 30mm 2τ=94×9.8×402/(0.31×24×30)=55.31 [τ]w =0.49[σ]= 0.49×138=67.62 MPa τ< [τ]w OK D.标准件的选取 Selection of standard parts 16 江苏星瑞化工工程科技有限公司 Rev. No. : 0 Jiangsu Sunrise Chemical Document No. DC-A14-001 Page : 17 of 30 Engineering Technology Co., Ltd. 法兰/法兰盖:依照ASME B16.5-2009选取SA-105M, CLASS150(在设计温度 50?下，压力 等级最少可达1.92MPa)。 Flange/Flange Cover: selected in accordance with ASME B16.5-2009 SA-105M, CLASS 150(Pressure Rating can be at least 1.92MPa at design temperature 50?). E.液压试验压力及应力较核:(依照UG-99(b)) Hydrotest pressure and stress checking:(in accordance with UG-99(b)) Pt = 1.3×最大许用工作压力×容器在试验温度下材料的许用应力/容器在设 计温度下材料的许用应力 Pt = 1.3×MAWP×allowable stress at test temp. of vessel/allowable stress at design temp. of vessel 容器在试验温度下各材料的许用应力/容器在设计温度下各材料的许用应力 = 1 where:allowable stress at test temp.of vessel/allowable stress at design temp. of vessel =1(LSR=138/138=1 LSR=138/138=1 LSR=118/118=1) (SA-516M)(SA105M)(SA106M Gr.B) LSR=172/172=1) (SA193M B7) ?1.3×LSR ×172=1.3×1×172=224 Mpa?0.9×Sy=0.9×724=651.6Mpa (SA193M B7) ?螺栓不参与LSR的确定。 Bolting shall not be included in the determination of the LSR. Pt = 1.3×MAWP×MinLSR= 1.3×1.2×1 = 1.56Mpa E.1用公式校核筒体的应力 The stress of shell shall is checked in accordance with the formula prior to static pressure test: Te= 8 - 1 =7mm 1 P= 1.56 + 0.012= 1.572 MPa T1 Ss = P(R+0.6Te) / TeE=1.572×(501+0.6×7)/(7×0.85)=133.47 Mpa,0.9Sy= 0.9×T 262=235.8Mpa 因此通过校核So it’s OK E.2用公式校核封头的应力 The stress of head is checked in accordance with the formula prior to static pressure test. Te = 7.2 - 1 =6.2mm 2 P =1.56 + 0.012= 1.572 Mpa T2 S = P(D+0.2Te)/2TeE=1.572×(1002+0.2×6.2)/(2×6.2×0.85)=149.63 Mpa hT S==149.63 Mpa,0.9 Sy= 0.9×262=235.8 Mpa h 因此通过校核So it’s OK E.3用公式校核接管的应力 The stress of nozzle is checked in accordance with the formula prior to static 17 江苏星瑞化工工程科技有限公司 Rev. No. : 0 Jiangsu Sunrise Chemical Document No. DC-A14-001 Page : 18 of 30 Engineering Technology Co., Ltd. pressure test. Te =5.54 - 1 =4.54mm 31 P =1.56 + 0= 1.56MPa T31 Te =4.55 - 1 =3.55mm 32 P =1.56 + 0.012= 1.572MPa T32 Te=8 - 1 =7mm 33 P =1.56 + 0= 1.56MPa T33 Ss = P(R-0.4Te) / TeE=1.56×(30.15-0.4×4.54)/(4.54×0.85)=11.45 Mpa 1TO Ss=11.45 Mpa,0.9Sy= 0.9×241=216.9MPa 1 Ss = P(R-0.4Te) / TeE=1.572×(16.7-0.4×3.55)/(3.55×0.85)=7.96Mpa 2TO Ss =7.96Mpa,0.9 Sy= 0.9×241= 216.9 Mpa 2 Ss = P(R-0.4Te) / TeE=1.56×(228.5-0.4×7)/(7×0.85)=59.18 Mpa 3TO Ss =59.18 Mpa,0.9 Sy= 0.9×262= 235.8MPa 3 因此通过校核So it’s OK E.4 校核法兰材料压力-温度额定值大于水压试验压力。 The Pressure-Temperature Rating of flange is checked that is greater than hydrostatic test pressure. 根据ASME B16.5-2009中1.1组材料压力-温度额定值表， 30?时为1.96 MPa ,1.56MPa。 According to Table 2-1.1 Pressure-Temperature Rating for Group 1.1 Materials ASME B16.5-2009，Working Pressure of 30? is 1.96MPa ,1.56MPa. 因此通过校核。So it’s OK. F.当容器部件材料在最小设计金属温度0?下工作时，判定对冲击试验的要求。 Judgements whether the impact test is required when materials of vessel elements are working at minimum design metal temperature of 0?. 确定无冲击试验容器的金属最小设计温度(用UG- 20(f)，UCS- 66规范) Determining the minimum desing metal temperature of vessel without impact testing(using UG-20(f),UCS-66 rules) MDMT Material 材料 Thick Figucs-66 Without impact Governing Elements & (mm) Remarks Thickness test(?) 零件名称 H.T.Condition 热处理条厚度 备注 Curve 控制厚度 免冲击试验 件 曲线 最低金属温度 壳体 SA-516M Gr485 8 8 B -29 UG-20(f) shell As rolled 轧制 封头 SA-516M Gr485 8 8 B -29 UG-20(f) head As rolled 轧制 人孔圈 SA-516M Gr485 8 8 B -29 UG-20(f) 18 江苏星瑞化工工程科技有限公司 Rev. No. : 0 Jiangsu Sunrise Chemical Document No. DC-A14-001 Page : 19 of 30 Engineering Technology Co., Ltd. manhole As rolled 轧制 ring 补强圈 SA-516M Gr485 reinforcin8 8 B -29 UG-20(f) As rolled 轧制 g pad 鞍座垫板SA-516M Gr485 saddle 8 8 B -29 UG-20(f) As rolled 轧制 support 铭牌支架 SA-516M Gr485 nameplate 8 8 B -29 UG-20(f) As rolled 轧制 bracket 法兰/盖轴SA-516M Gr485 耳 12 12 B -29 UG-20(f) As rolled 轧制 PLATE 接管 SA106M GrB 5.54 5.54 B -29 UG-20(f) Nozzle Normalized 标准 接管 SA106M GrB 4.55 4.55 B -29 UG-20(f) Nozzle Normalized 标准 把手 SA105M 14 14 B -29 UG-20(f) HANDLE Normalized 标准 法兰 SA105M , , B -29 UCS-66(c) Flanges Normalized 标准 法兰盖 SA105M 40.1 10 B -29 UG-20(f) Blind Normalized 标准 UCS-66 螺栓 SA193-B7 , , , -48 general bolting Normalized 标准 note (c) UCS-66 螺母 SA194-2H , , , -48 general nuts Normalized 标准 note (c) According toUG- 20(f)，UCS- 66(c)，Impact test don't need. 冲击试验可免除。 G. 判定对冷作成型后热处理的要求 Judgement for whether heat treatment shall be carried out after cold forming 根据ASME 规范第?卷第?册UCS-79(d),当因冷作成型而发生的最大纤维伸长率比轧制状态后的大5%时，以及存在UCS-79(d)(1),(5)所列附加条件者都要求进行冷作成型后热处理。 According to ASME Code Sect.?,Div?UCS-79(d),the requirement that heat treatment shall be carried out after cold forming is that the resulting extreme fiber elangation is more than 5% from the as-rolled condition and any of the addtional conditons in UCS-79(d)(1),(5) exits. 19 江苏星瑞化工工程科技有限公司 Rev. No. : 0 Jiangsu Sunrise Chemical Document No. DC-A14-001 Page : 20 of 30 Engineering Technology Co., Ltd. (a)椭圆形封头: Ellipsoidal head: 最大纤维伸长率的公式: 75t(1-R/R)/R fof the formula for % extreme fiber elongation: 对于封头:t=8mm; UG-32(d) R=min{0.9Di+t/2,0.17Di+t/2} f = min{0.9 x 1000+8/2,0.17 x 1000+8/2}=174mm; R=? o 因而发生的纤维伸长率(%) = 75x8(1-0)/174=3.4% < 5% for head: the resulting fiber elongation (%) = 75x8(1-0)/174= 3.4% < 5% (b)壳体，人孔圈，补强板: shell, manhole ring，reinforcing plate: 最大纤维伸长率的公式: 50t(1-R/R)/R fof the formula for % extreme fiber elongation: 对于壳体，人孔圈，补强板:t = 8mm; R= min{504,224.5,512} = 224.5mm; f R = ? o for shell,manhole ring，reinforcing plate: 因而发生的纤维伸长率 (%)=50x8(1-0)/224.5=1.78% < 5% the resulting fiber elongation (%)=50x8(1-0)/224.5= 1.78% < 5% 依照以上计算结果，不需要在冷作成型后进行热处理。 According to above calculation results,the heat treatment after cold forming is not required. H.焊后热处理检测 Check of postweld heat treatment 壳体和封头的材料是SA-516M Gr.485，厚度为8mm。依照UW-2，表UCS-56(注解2)，壳体和封头的厚度(=8mm)小于32mm ，所以不需要进行焊后热处理检测。 Material for shell and head is SA-516M Gr.485,8mm thick,according to UW-2，table UCS-56(note 2),the thickness of shell and head (=8mm) is less than 32mm, so postweld heat treatment is not needed. I.无损检测要求 Required NDE 20 江苏星瑞化工工程科技有限公司 Rev. No. : 0 Jiangsu Sunrise Chemical Document No. DC-A14-001 Page : 21 of 30 Engineering Technology Co., Ltd. (a)A,B类焊接接头: 压缩空气为无毒介质,并且壳体和封头的厚度为8mm,小于32mm.按照规范 UW-11(a)(1)、(2),UCS-57可以不必做全部射线检测。壳体及壳体与封头的 A，B类焊接接头型式按表UW-12中的(1)型选取，所以A，B类焊接接头可 以进行抽样射线检测。 Category A and B welded joints The compressed air is not lethal, and both the shell and head are 8mm thick, less than 32mm. according to ASME Code Sect.?，Div.?UW-11(a)(1)、(2), UCS-57full length radiography for the category A and B welded joints is not required. Joint types of the shell to shell and shell to head are adopted based on No.(1) of table UW-12. So the category A and B welded joints may be examined by spot radiography. 综上所述,壳体的焊接接头系数取0.85, 封头与筒体之间焊接接头系数取 0.85。 Accordingly, The joint efficiency of shell is 0.85, and Joint efficiency of the head to shell is 0.85. (b)C,D类焊接接头: C,D类焊接接头的MT,PT检测要求在用户设计技术条件中没有要求,且在规 范里也没有要求。 Category C and D welded joints On the condition that there are no requirements in the customer design specification or in the Code. The MT or PT for the category C and D welded joint is not required. 附录: Appendix: A. 鞍座的计算 The calculation of saddle supports 容器的结构尺寸如图1 所示。支座的应力计算依照中国标准 JB/T4731-2005。 21 江苏星瑞化工工程科技有限公司 Rev. No. : 0 Jiangsu Sunrise Chemical Document No. DC-A14-001 Page : 22 of 30 Engineering Technology Co., Ltd. Structure size of vessel as shown by Fig.1. Caculations of stress at supports are in accordance with chinese standards JB/T4731-2005。 其中: Where: Design Pressure P=1.2MPa Calculate Pressure Pc=1.2MPa Cylinder Material : SA-516M Gr.485 Head Material : SA-516M Gr.485 Material Designation of Saddle Support: Component Allowable Stress of Cylinder Material at Ambient Temperature. [, ] : 138MPa Allowable Stress of Head Material at Ambient Temperature. [, ] : 138MPa h tAllowable Stress of Cylinder Material at Design Temp. [, ] : 138MPa tAllowable Stress of Head Material at Design Temp. [ ] : 138MPa ,h Allowable Stress of Saddle Support Material [, ] : 146MPa sa Yield Strength of Cylinder Material at Ambient Temperature. ReL: 345MPa -6Density of Cylinder Material : γs= 7.85x10 kg/mm3 -6Density of Head Material : γh=7.85x10 kg/mm3 22 江苏星瑞化工工程科技有限公司 Rev. No. : 0 Jiangsu Sunrise Chemical Document No. DC-A14-001 Page : 23 of 30 Engineering Technology Co., Ltd. -10Density of Operating Substance: γo=12.94x10 kg/mm3 Filling Ratio : υo=1 -6Density of Testing Substance γT=1x10 kg/mm3 Inside Diameter of Cylindrical Shell Di: 1000mm Average Radius of Cylinder R(Ra): 504mm m Nominal Thickness of Cylindrical Shell δn=8mm ,rnNominal Thickness of Support Backing Plate =8mm Efficient Thickness of Cylinder δe=8-1=7mm Nominal Thickness of Head δhn=8mm Efficient Thickness of Head δhe=8-1-1.2=5.8mm Nominal Thickness of Support Backing Plate δrn=8mm Efficient Thickness of Support Backing Plate δre=8mm Nominal Thickness of Saddle Support Plate bo=8mm Distance Between Tangents of Two Heads L=1550mm Length of Cylindrical Shell Lc=1500mm Depth of Curved Suface of Head hi=250mm Width of Saddle Support b=170mm Contact Angle of Saddle Support θ=120? Distance from Support Centroid to Head Tanget A=250mm Joint Efficiency of Cylindrical Shell υ=0.85 Design Temp. 50? Test Pressure pT=1.56 MPa 1. Calculation for Support Reaction Mass of Cylindrical Shell (between Two Tangents) -6mDL,，,,,,,，，1inns π×(1000+8)×1550×8×7.85×10 =308.2kg Mass of Head(Curved Surface Portion) m2= 62.1kg Mass of Attachments m3=209.5kg Volume of Head VH=150500000mm3 2Volume of Vessel V=(π/4)DL+2 VH ic 29 =(π/4)×1000×1500+2×150500000=1.48×10 mm3 9 -10 Compressed air Weight m4=Vγoυo=1.48×10×12.94×10×1=1.92kg 9-6Hydrostatic Testing water Weight m 4’ =VγT ==1.48×10×1×10=1480kg 23 江苏星瑞化工工程科技有限公司 Rev. No. : 0 Jiangsu Sunrise Chemical Document No. DC-A14-001 Page : 24 of 30 Engineering Technology Co., Ltd. Mass of Insulation m5=0 Total Mass Under Operation Condition m=m1+m2+m3+m4+m5=308.2+62.1+209.5+1.92+0=581.72kg Under Hydrostatic Testing Condition m’= m1+m2+m3+m4’ +m5=308.2+62.1+209.5+1480+0=2059.8kg Support Reaction Force F 1) Under Operation Condition F’=mg/2= 0.5×581.72×9.81=2853.3N 2) Under Hydrostatic Testing Condition F’’ =m g/2 =0.5×2059.8×9.81=10103.3N F=max(F’ , F’’ )= 10103.3N 2. Calculation for Bending Moment of Shell 1) Bending Moment at Mid-Point of Span M1,MT1 Operation Condition ，，222,12，,,RhL/，，4FLAmi,,M,,14h4Li,,1，3L，， 222=(2853.3×1550/4) ×(1+2×(504-250)/1550/[1+(4/3) ×(250/1550)]-4×250/1550) = 388585.4 N.mm Test Condition ，，222,,,,12，，/4FL，R,hLAaiM,,,,T14h4Li,,1，,3L，， 222=(10103.3×1550/4) ×(1+2×(504-250)/1550/[1+(4/3) ×(250/1550)]-4× 250/1550) = 1375948.9 N.mm 24 江苏星瑞化工工程科技有限公司 Rev. No. : 0 Jiangsu Sunrise Chemical Document No. DC-A14-001 Page : 25 of 30 Engineering Technology Co., Ltd. 2) Bending Moment at Support M2,MT2 Operation Condition 22，，ARh,mi1,，,,L2ALMFA,,,1,,,24hi,,1，22,,3L，，-2853.3×250 ×(1-(1-250/1550+(504-250)/(2×250× 1550))/(1+(4/3) ×(250/1550))) = -366012.7 N.mm Test Condition 22，，AR,hai1,，,,2LAL,,M,,FA1,,,,T24hi,,1，22,,3L，，-10103.3×250 ×(1-(1-250/1550+(504-250)/(2×250× 1550))/(1+(4/3) ×(250/1550))) = -1296020.9 N.mm 3. Calculation for Axial Stress in Cylindrical Shell 1)Factor K1,K2 From Ra/2=504/2=252 , A=250 , θ=120? From Table 7-1, get K1=1.0 , k2=1.0 2) Operation Condition pRMcm1,,,,1222,,R,eme1.2×504/(2×7)-388585.4/(π×504×7)=43.1MPa pRMcm1,,，,2222,,R,eme1.2×504/(2×7)+388585.4/(π×504×7)=43.3 MPa pRMcm2,,,,3222,K,R,e1me1.2×504/(2×7)-( -366012.7 /(1.0×π×504×7))=43.3MPa pRMCa2,,，,4222,K,R,e2ae1.2×504/(2×7)+( -366012.7 /(1.0×π×504×7))=43.1 MPa 25 江苏星瑞化工工程科技有限公司 Rev. No. : 0 Jiangsu Sunrise Chemical Document No. DC-A14-001 Page : 26 of 30 Engineering Technology Co., Ltd. 3) Hydrostatic Testing Condition Full of Water and not Implement Pressure Status MT1,,,,T122,R,me -1375948.9 /(π×504×7)= -0.25MPa MT2,,,T422K,R,2me -1296020.9 /(π×1.0×504×7)=-0.23MPa Full of Water and Pressure Implement Status 4)Stress Calibration pRMTm1T,,，,2T222,,R,eme1.56×504/(2×7)+1375948.9 /(π×504×7)=56.4 MPa pRMTTa2,,,,T3222,K,R,e1ae1.56×504/(2×7)-1296020.9 /(π×1.0×504×7)=56.4 MPa Allowable compressed Stress [σ] ac A=0.188×7/1000=0.001316 Using B Value According to Cylindrical Shell Material,See GB150 Fig6-5 -Status at Operating tt，，,,,,,,min,,B,acB=142 MPa 142MPa -Status at Full of Water and not Implement Pressure ,,,,min(0.9R,B),aceLB0=146MPa 146MPa Operating Status tMax(,1, ,2, ,3, ,4)=43.3,υ[, ] =0.85×146=124.1 t,,,,ac|Min(,1, ,2, ,3, ,4)|=43.1, 142MPa Status at Full of Water and not Implement Pressure |Min(,T1, ,T3)|=0.23,[σ] ac =146MPa 26 江苏星瑞化工工程科技有限公司 Rev. No. : 0 Jiangsu Sunrise Chemical Document No. DC-A14-001 Page : 27 of 30 Engineering Technology Co., Ltd. Status at Pressure Implementing Max(,T2, ,T4)=56.4,0.9υReL =0.9×0.85×345=264 MPa 4.Tangential Shearing Stress Calculation 1)Modulus K3,K4 From Ra/2=504/2=252 , A=250 , θ=120? From Table 7-2, get K3= 0.880, K4=0.401 2)A