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侧壁式吊耳计算

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侧壁式吊耳的计算（1） 项目号 ITEM NO.
Calculation of Lifting Lug（1） 文件号 DOC. NO.
说明：本计算书是依据Dennis Moss编著的《Pressure Vessel Design Manual》中的计算方法编制的。 说明：
          计算中将吊耳与垫板的连接简化为仅在端部（宽度为A）和两侧（每侧长度为B）与垫板焊接。 1. 本计算程序适用于HG/T21574-2008中的标准侧壁式吊耳，只要在输入数据的“吊耳类型” 栏内输入HG/T21574标准中的吊耳型号，程序就会自动输入吊耳的有关尺寸。
Note: This calculation sheet is prepared based on 《Pressure Vessel Design Manual》 
        written by Dennis Moss.  In the calculation , the lug to pad connection is simplified as   2.  黄色单元格内的数据是需要输入的。 
        only welded at the bottom end (the width is A) and two sides (the length of each side 3. 由于标准的侧壁式吊耳一般比较细长，不宜用于起吊质量较大的设备。对于质量较大的设备，建议增加吊耳的宽度和厚度，尽可能缩短吊耳的长度，此时可采用“half standard" 或 "un-standard" 吊耳的程序进行计算。
        is B) of the lifting lug.
1 NOTES:
1 1. This calculation template is applicable to the strength check of standard top head lifting lug listed in HG/T21574-2008, as long as the type number of the lifting lug listed in HG/T21574-2008 is inputted into the cell for "Type of lifting lug", the program will automatically input the relevant dimensions of the lug. 
2. The data in light blue cells shall be inputted.
3. Using the standard top head lifting lugs to lift very heavy equipment is not recommended, because the lugs are usually long and narrow. For lifting heavy equipment, it is recmended that the width and thickness of the lug be increased, and the length of the lug be as short as possible, in this case, the calculation programs for "half standard" and "un-standard" lifting lugs can be used. 
⑴ 输入数据 Input Data
设备的最大吊装质量 Maximum lifting weight G= 10000 kg SP-3 SP-5 SP-8 SP-10 SP-15 SP-20 SP-25 SP-35 SP-50 SP-75 SP-100 SP-150 SP-200
动载系数 Dynamic factor f= 1.65 S = 8 10 10 12 16 20 24 30 40 60 70 95 120
吊耳类型 Type of lifting lug                    SP-100 H = 100 120 150 200 220 230 240 260 280 320 350 400 450
侧壁式吊耳孔中心至设备重心的轴向距离                                                                   Axial distance of lifting lug hole to C.G. of equipment            L1= 14347 mm D = 50 50 50 80 80 80 90 100 110 120 140 160 180
尾部吊耳孔中心至设备重心的轴向距离                                                                      Axial distance of tailing lug hole to C.G. of equipment                   L2= 9048 mm F = 40 40 50 70 80 80 80 90 100 100 130 150 160
尾部吊耳孔中心至设备轴线的距离                                                     Distance between tailing lug hole and axis of equipment  L3= 1284 mm G = 15 15 15 25 25 30 35 40 50 60 65 65 75
吊耳的材料 Lifting lug material Q345R L1 = 60 60 80 140 140 140 140 160 160 160 180 220 250
吊耳的名义厚度 Nominal thickness of lifting lug S= 70 mm L3 = 80 80 80 110 110 110 120 145 200 280 320 380 450
吊耳的厚度负偏差 Thickness under tolerance of lifting lug  C1= 0.3 mm Hsp= 130 150 180 250 270 290 310 340 380 440 480 530 600
吊耳材料的屈服强度 Yield strength of lug material σs1= 345 Mpa Lsp= 110 110 135 225 230 240 250 285 310 330 365 410 480
吊耳的宽度 Width of lug A= 350 mm r = 10 10 10 20 20 20 20 20 30 30 40 40 40
吊耳两侧连接焊缝的长度（指单侧长度）                                                                  Length of welds of each side of lifting lug B= 300 mm a = 6 7 7 8 12 14 18 20 30 36 40 50 60
吊耳上起吊孔的直径 Pin hole diameter of lifting lug D= 140 mm S1= 8 8 8 10 12 16 20 24 30 40 40 40 40
吊耳孔中心至垫板边缘的距离 Distance of pin hole center to pad edge L= 342 mm S2= 6 6 8 8 10 10 10 12 16 16 28 30 36
吊耳与垫板间连接焊缝的焊脚高度 Leg size of welds connecting lug to pad          h1= 40 mm D1= 100 100 100 160 160 160 180 200 220 240 280 320 360
垫板材料 Pad material 316L
垫板的名义厚度 Nominal thickness of pad S1= 40 mm
垫板材料的屈服强度 Yield strength of pad material σs2= 170 MPa
垫板与筒体连接焊缝的焊脚高度  Leg size of welds connecting pad to shell             h2= 32 MM
垫板沿筒体周向的长度 Circumferential length of pad A1= 480 mm
垫板沿筒体轴向的宽度 Longitudinal length of pad B1= 365 mm
吊耳起吊孔处衬板的材料 Material of pin hole re-pad Q345R
衬板的名义厚度 Nominal thickness of pin hole re-pad  Tp= 28 mm
衬板的厚度负偏差 Thickness under tolerance of pin hole re-pad C1'= 0.3 mm
衬板的外径 Outside diameter of pin hole re-pad D1= 280 mm
衬板与吊耳连接焊缝的焊脚高度                                                                                Leg size of welds attaching pin hole re-pad to lifting lug                          h3= 8 mm
角焊缝系数 Fillet weld factor φ= 0.7
⑵ 载荷计算和许用应力  Load and Allowable Stresses 
侧壁式吊耳孔与尾吊孔之间的轴向距离         Axial distance of lifting lug hole to tailing lug hole Lo=L1+L2 23395 mm
侧壁式吊耳与尾部吊耳的起吊总载荷     Total lifting load of lifting lugs and tailing lug F=f*G*9.81 161865 N
侧壁式吊耳的起吊载荷                          Lifting load of lifting lugs P=F*(1-L1*cosθ/(Lo*cosθ+L3*sinθ)) 见表1                       SeeTable 1
单个侧壁式吊耳在竖直方向的起吊载荷Vertical load of each lifting lug Fv=P/2 见表1                    SeeTable 1
起吊载荷在设备轴向的分力                  Axial component of lifting load of each lifting lug Fl=Fv*sinθ 见表1                    SeeTable 1
起吊载荷在设备切向的分力             Tangential component of lifting load of each lifting lug Ft=Fv*cosθ 见表1                       SeeTable 1
吊耳材料拉伸和弯曲的许用应力       Allowable tensile and bending stress of lug material ［σ］=σs1/1.5 230 Mpa
吊耳材料的许用剪切应力 Allowable shear stress of lug material ［τ］=0.6［σ］ 138 Mpa
吊耳材料的许用挤压应力 Allowable bearing stress of lug material ［σp］=0.9σs1 310.5 Mpa
吊耳与垫板间角焊缝的许用剪应力                   Allowable shear stress of fillet welds attaching lug to pad  ［τw1］=φ*MIN(［τ］,0.6*σs2/1.5) 47.6 Mpa
垫板与筒体间角焊缝的许用剪应力                   Allowable shear stress of fillet welds attaching pad to shell ［τw2］=φ*0.6*σs2/1.5 47.6 Mpa
衬板与吊耳间角焊缝的许用剪应力        Allowable shear stress of fillet welds attaching lifting lug to pin hole re-pad ［τw3］=φ*［τ］ 96.6 MPa
⑶ 吊耳的强度计算 Strength Calculation for Lifting Lugs
吊耳的有效厚度                                          Effective thickness of lifting lug Se=S=C1 69.7 mm
衬板的有效厚度                                            Effective thickness of pin hole re-pad Te=Tp-C1' 27.7 mm
连接焊缝形心至吊耳端部的距离         Distance between C.G. of weld group and end of lug Nt=B2/(A+2B) 94.74 mm
起吊力Ft至连接焊缝形心的距离                 Distance of lifting force Ft to C.G. of weld group Lt=L+B-Nt 547.26 mm
吊耳所承受的最大弯矩 Maximum bending moment acting on lifting lug M=Ft*L 见表1                       See Table 1
吊耳与垫板连接焊缝所承受的扭矩       Moment acting on welds attaching lifting lug to pad Mt1=Ft*Lt 见表1                       See Table 1
吊耳的抗弯断面模数                          Section modulus of lifting lug W=A2*Se/6 1423042 mm3
吊耳与垫板连接处的轴向拉伸应力 Tensile stress at cross section of lifting lug σt=Fl/(A*Se) 见表1                       See Table 1
吊耳的弯曲应力                               Bending stress of lifting lug σb=M/W 见表1                       See Table 1
σ=σt+σb 见表1                       See Table 1
吊耳在起吊孔中心处的横截面积                 Net section at pin hole of lifting lug Ap=(A-D)*Se+2Te*(D1-D) 22393 mm2
该截面的剪应力 Shear stress at the net section at pin hole τ1=Ft/Ap 见表1                       See Table 1
吊耳顶部的截面积                                Net section at top of lifting lug Au=Se*(A/2-D/2)+Te*(D1-D) 11196.5 mm2
吊耳顶部截面的剪应力                         Shear stress at that net section τ2=Fl/Au 见表1                       See Table 1
起吊孔中销轴的挤压应力                      Bearing stress at pin hole σp=Fv/(D*(Se+2Te)) 见表1                       See Table 1
⑷ 吊耳与垫板间连接焊缝的应力计算 Stress Calculation for Welds Attaching Lifting Lug to Pad                                                                                                                                         
单位宽度焊缝的极惯性矩                                           Polar moment of inertia Jw1=(A+2B)3/12-B2*(A+B)2/(A+2B) 3.1E+07 mm3
Ft引起的横向剪力                                     Transverse shear due to Ft f1=Ft/(A+2B) 见表1                       See Table 1
Mt引起的横向剪力                               transverse shear due to Mt f2=Mt1*(B-Nt)/Jw1 见表1                       See Table 1
F1引起的纵向剪力                                 Longitudinal shear due to Fl f3=Fl/(A+2B) 见表1                       See Table 1
Mt引起的纵向剪力                              Longitudinal shear due to Mt f4=Mt1*0.5*A/Jw1 见表1                       See Table 1
组合剪力                                      Combined shear load fr1=SQRT((f1+f2)2+(f3+f4)2) 见表1                       See Table 1
吊耳与垫板间连接焊缝的剪应力                Shear stress of welds attaching lifting lug to pad τw1=fr/(0.707*h1) 见表1                       See Table 1
⑸垫板与筒体间连接焊缝的应力计算 Stress Calculation for Welds Attaching Pad to Shell                                                                                                       
垫板与筒体的连接焊缝所承受的扭矩Moment acting on welds attaching pad to shell Mt2=Ft*(L+B1/2) 见表1                       See Table 1
单位宽度焊缝的极惯性矩                                             Polor moment of inertia Jw2=(A1+B1)3/6 1E+08 mm3
Ft引起的横向剪力                                Transverse shear due to Ft fa=Ft/(2A1+2B1) 见表1                       See Table 1
Mt1引起的横向剪力                             Transverse shear due to Mt1 fb=0.5*Mt2*B1/Jw2 见表1                       See Table 1
F1引起的纵向剪力                                     Longitudinal shear due Fl fc=Fl/(2A1+2B1) 见表1                       See Table 1
Mt1引起的纵向剪力                           Longitudinal shear due Mt1 fd=0.5*Mt2*A1/Jw2 见表1                       See Table 1
组合剪力                                       Combined shear load fr2=SQRT((fa+fb)2+(fc+fd)2) 见表1                       See Table 1
垫板与筒体间连接焊缝的剪应力                Shear stress of welds attaching pad to shell τw2=fr/(0.707*h2) 见表1                       See Table 1
(6)衬板与吊耳连接焊缝的强度校核 Stress Calculation for Welds Attaching pin hole re-pad to lifting lug                                                                                                                      
fr3=Fv*Te/(n*D1*(2*Te+Se)) 见表1                       See Table 1
衬板与吊耳间连接焊缝的剪应力                                              Shear stress of welds attaching pin hole re-pad to lifting lug τw3=fr3/(0.707*h3) 见表1                       See Table 1
表1 载荷和应力的计算结果
Table 1 Calculation Results of Load and Stress
θ(deg) 0 10 20 30 40 50 60 70 80 90
P(N) 62601.18 63552.59 64545.23 65649.94 66971.29 68695.19 71218.16 75607.98 86163.9 161865
Fv(N) 31300.59 31776.29 32272.62 32824.97 33485.65 34347.6 35609.08 37803.99 43081.95 80932.5
Fl(N) 0 5517.896 11037.88 16412.49 21524.16 26311.79 30838.37 35524.13 42427.44 80932.5
Ft(N) 31300.59 31293.54 30326.34 28427.26 25651.49 22078.21 17804.54 12929.73 7481.102 4.96E-12
M(N.mm) 10704801 10702391 10371608 9722123 8772811 7550748 6089153 4421966 2558537 0.00 
Mt1(N.mm) 17129560 17125703 16596393 15557102 14038036 12082521 9743713 7075922 4094108 0.00 
σt(Mpa) 0.00  0.23  0.45  0.67  0.88  1.08  1.26  1.46  1.74  3.32 
σb(Mpa) 7.52  7.52  7.29  6.83  6.16  5.31  4.28  3.11  1.80  0.00 
f1(N/mm) 32.95  32.94  31.92  29.92  27.00  23.24  18.74  13.61  7.87  0.00 
f2(N/mm) 111.90  111.87  108.42  101.63  91.70  78.93  63.65  46.22  26.74  0.00 
f3(N/mm) 0.00  5.81  11.62  17.28  22.66  27.70  32.46  37.39  44.66  85.19 
f4(N/mm) 95.40  95.38  92.43  86.64  78.18  67.29  54.27  39.41  22.80  0.00 
fr1(N/mm) 173.44  176.66  174.70  167.64  155.75  139.50  119.63  97.36  75.83  85.19 
Mt2(N.mm) 16417158 16413462 15906165 14910098 13454208 11580021 9338481 6781641 3923838 0.00 
fa(N/mm) 18.52  18.52  17.94  16.82  15.18  13.06  10.54  7.65  4.43  0.00 
fb(N/mm) 29.79  29.79  28.87  27.06  24.42  21.02  16.95  12.31  7.12  0.00 
fc(N/mm) 0.00  3.27  6.53  9.71  12.74  15.57  18.25  21.02  25.10  47.89 
fd(N/mm) 39.18  39.17  37.96  35.59  32.11  27.64  22.29  16.19  9.36  0.00 
fr2(N/mm) 62.21  64.30  64.58  63.07  59.83  55.03  48.97  42.22  36.35  47.89 
fr3(N/mm) 7.88  8.00  8.12  8.26  8.43  8.65  8.96  9.52  10.84  20.37 
应力计算结果与判断 Stress Calculation Results and Judgement
θ(deg) 0 10 20 30 40 50 60 70 80 90
σ(Mpa) 7.52  7.75  7.74  7.50  7.05  6.38  5.54  4.56  3.54  3.32 
［σ］(Mpa) 230.00 
σ<［σ］,  合格，  Acceptable.
τ1(Mpa) 1.40  1.40  1.35  1.27  1.15  0.99  0.80  0.58  0.33  0.00 
τ2(Mpa) 0.00  0.49  0.99  1.47  1.92  2.35  2.75  3.17  3.79  7.23 
［τ］(Mpa) 138
τ1<［τ］,  合格，  Acceptable.
τ2<［τ］,  合格，  Acceptable.
σp(Mpa) 1.79  1.81  1.84  1.87  1.91  1.96  2.03  2.16  2.46  4.62 
［σp］(Mpa) 310.5
σp<［σp］,  合格，  Acceptable.
τw1(Mpa) 6.13  6.25  6.18  5.93  5.51  4.93  4.23  3.44  2.68  3.01 
［τw1］(Mpa) 47.6
τw1<［τw1］,  合格，  Acceptable.
τw2(Mpa) 2.75  2.84  2.85  2.79  2.64  2.43  2.16  1.87  1.61  2.12 
［τw2］(Mpa) 47.6
τw2<［τw2］,  合格，  Acceptable.
τw3(Mpa) 1.39  1.41  1.44  1.46  1.49  1.53  1.58  1.68  1.92  3.60 
［τw3］(Mpa) 96.6
τw3<［τw3］,  合格，  Acceptable.
      表中 Where
θ— 设备轴线与水平面的夹角 Included angle between equipment axis and horizontal plane
σ— 吊耳拉伸应力与弯曲应力之和 Sum of tensile stress and bending stress of lifting lug
［σ］—
吊耳的许用拉伸应力 Allowable tensile stress of lifting lug
τ1— 吊耳起吊孔截面的剪应力 Shear stress at the section of pin hole
τ2— 吊耳顶部截面的剪应力 Shear stress at the section of top of lifting lug
［τ］—
吊耳的许用剪应力 Allowable shear stress of lifting lug
σp—
吊耳起吊孔处的挤压应力 Bearing stress at pin hole
［σp］—
吊耳的许用挤压应力 Allowable bearing stress of lifting lug
τw1—
吊耳与垫板连接焊缝的剪应力 Shear stress of welds attaching lifting lug to pad
［τw1］—
吊耳与垫板连接焊缝的许用剪应力 Allowable shear stress of welds attaching lifting lug to pad
τw2—
垫板与壳体连接焊缝的剪应力 Shear stress of welds attaching pad to shell
［τw2］—
垫板与壳体连接焊缝的许用剪应力 Allowable shear stress of welds of attaching pad to shell
τw—
衬板与吊耳连接焊缝的剪应力 Shear stress of welds attaching re-pad to lifting lug
［τw］—
衬板与吊耳连接焊缝的许用剪应力 Allowable shear stress attaching re-pad to lifting lug
侧壁式吊耳的计算（2） 项目号 ITEM NO.
Calculation of Lifting Lug（2） 文件号 DOC. NO.
1
说明: 本计算书系参照HG/T21574-2008标准编制,仅适用 说明：
     于设备已起吊至其轴线与水平面垂直的状态。 1. 本计算书系参照HG/T21574-2008标准编制,仅适用于设备已起吊至其轴线与水平面垂直的状态。
Note: This calculation sheet is prepared referring         
        to Chinese standard HG/T21574-2008, and  2. 黄色单元格内的数据是需要输入的。
        is only appliable to the equipment which has  NOTES:
        been lifted to a vertical position. 1. This calculation template is prepared per Chinese standard HG/T21574-2008, and is only appliable to the equipment which has been lifted to a vertical position.  
2. The data in light blue cells shall be inputted.
⑴输入数据 Input Data
设备的最大吊装质量 Maximum lifting weight W= 10000 kg
动载系数 Dynamic factor f= 1.65
吊耳的材料 Material of lifting lug Q345R
吊耳的有效厚度 Effective thickness of lifting lug S= 70 mm
吊耳材料的屈服强度 Yield strength of lug material  σs1= 345 Mpa
吊耳的宽度 Width of lifting lug  H= 350 mm
吊耳上起吊孔的直径 Pin hole diameter of lifting lug D= 140 mm
垫板的材料 Pad material 316L
垫板的名义厚度 Nominal thickness of pad 40 mm
垫板材料的屈服强度 Yield strength of pad material σs2= 170 Mpa
垫板沿筒体周向的长度 Circumferential length of pad Hsp= 480 mm
垫板沿筒体轴向的宽度 Longitudinal length of pad Lsp= 365 mm
垫板四角的圆角半径 Corner radius of pad R= 20 mm
吊耳起吊孔处衬板的材料 Material of re-pad at pin hole Q345R
吊耳起吊孔处衬板的有效厚度 Effective thickness of re-pad at pin hole S2= 28 mm
吊耳衬板的外径 Outside diameter of re-pad D1= 280 mm
吊耳端部与垫板边缘的距离 Distance of lug end to pad edge G= 65 mm
吊耳端部的圆角半径 Corner radius of lifting lug r= 40 mm
吊耳中央部位焊缝长度尺寸 Length of welds in the middle of lug  L1= 180 mm
吊耳端部缺口部位的宽度 Dimention            F= 130 mm
吊耳与垫板间连接焊缝的焊脚高度 Leg size of welds attaching lug to pad h= 40 mm
垫板与筒体连接焊缝的焊脚高度 Leg size of welds attaching pad to shell h1= 32 mm
角焊缝系数 Fillet weld factor φ= 0.7
⑵载荷计算和许用应力 Load and allowable stresses
单个吊耳在竖直方向的起吊载荷                    Vertical lifting load of each lug Fv=f*W*9.81/2 80932.5 N
吊耳材料的许用拉伸应力 Allowable tensile stress of lug material ［σ］=σs1/1.5 230 Mpa
吊耳材料的许用剪切应力 Allowable shear stress of lug material ［τ］=0.6［σ］ 138 Mpa
吊耳与垫板连接焊缝的许用剪应力                                    Allowable shear stress of welds attaching lug to pad ［τw1］=φ*MIN(［τ］,0.6*σs2/1.5) 47.6 Mpa
垫板与筒体连接焊缝的许用剪应力                             Allowable shear stress of welds attaching pad to shell ［τw2］=φ*0.6*σs2/1.5 47.6 Mpa
⑶吊耳的强度校核 Stresses in Lifting Lug
吊耳A-A截面的轴向拉伸应力               Tensile stress at A-A section of lug σ=Fv/(S*(H-D)+2*S2*(D1-D)) 3.59 Mpa
吊耳B-B截面的剪应力                          Shear stress at B-B section of lug τ=0.5*Fv/(S*(H-D)/2+S2*(D1-D)) 3.59 Mpa
σ < ［σ］ 合格,  Acceptable.
τ < ［τ］ 合格,  Acceptable.
⑷垫板与筒体连接焊缝的强度校核 Stress in Welds Attaching Pad to Shell
垫板与筒体连接焊缝的总长度                         Total length of welds attaching pad to shell Lw1=2*(Hsp+Lsp)-8*R+2π*R 1655.66 mm
垫板与筒体连接焊缝的剪应力                 Shear stress of welds attaching pad to shell τw2=Fv/(0.707*h1*Lw1) 2.16 Mpa
τw2
< ［τw2］ 合格,  Acceptable.
⑸吊耳与垫板间连接焊缝的强度校核  Shear Stress in Welds of Lug to Pad
吊耳与垫板连接焊缝的总长度 Total length of welds attaching lug to pad Lw=2(Lsp-G+L1)+0.5πF+H-F-8r+2πr 1315.53 mm
吊耳与垫板连接焊缝中的剪应力                 Shear stress in welds of lug to pad τw1=Fv/(0.707*h*Lw) 2.18 Mpa
τw1
< ［τw1］ 合格,  Acceptable.
结论:吊耳及连接焊缝的强度满足要求。
Conclusion：The strength of lifting lugs and connecting welds is satisfactory.

侧壁式吊耳的计算（1） 项目号 ITEM NO.
Calculation of Lifting Lug（1） 文件号 DOC. NO.
说明：本计算书是依据Dennis Moss编著的《Pressure Vessel Design Manual》中的计算方法编制的。 说明：
          计算中将吊耳与垫板的连接简化为仅在端部（宽度为A）和两侧（每侧长度为B）与垫板焊接。 1. 采用本计算程序时，吊耳的尺寸可不受HG/T21574-2008的限制。可以通过增加吊耳的宽度和厚度，尽可能减小吊耳的长度来提高吊耳的起吊能力，但应注意吊耳上端的半径尺寸（即A/2）不应过大以致不能与相应的卸扣的尺寸相适应。
Note: This calculation sheet is prepared based on 《Pressure Vessel Design Manual》 
        written by Dennis Moss.  In the calculation , the lug to pad connection is simplified as  
        only welded at the bottom end (the width is A) and two sides (the length of each side 2. 黄色单元格内的数据是需要输入的。
        is B) of the lifting lug. NOTES:
1. When using this calculation template, the dimensions of lifting lugs need not be limitted to that specified in HG/T21574-2008. The lifting capasity of the lug can be enlarged by increasing the width and thickness of the lug and  making the length of the lug as short as possible, but it should be noticed that the dimension of top end radius of the lug (i.e. A/2) shall not be too large to match the corresponding shackle. 
1
1
2. The data in light blue cells shall be inputted.
1
⑴ 输入数据 Input Data SP-5 SP-8 SP-100 SP-150 SP-200
设备的最大吊装质量 Maximum lifting weight G= 10000 kg
动载系数 Dynamic factor f= 1.65
侧壁式吊耳孔中心至设备重心的轴向距离                                                                     Axal distance of lifting lug hole to C.G. of equipment            L1= 14347 mm
尾部吊耳孔中心至设备重心的轴向距离                                                                       Axial distance of tailing lug hole to C.G. of equipment               L2= 9048 mm
尾部吊耳孔中心至设备轴线的距离                                                                            Distance between tailing lug hole and axis of equipment               L3= 1284 mm
吊耳的材料 Lifting lug material Q345R
吊耳的有效厚度（扣除材料的厚度负偏差）                                                                  Effective thickness of lifting lug (exclusive under tolerance) S= 15.7 mm
吊耳材料的屈服强度 Yield strength of lug material  σs1= 345 Mpa
吊耳的宽度 Width of lug A= 220 mm
吊耳两侧连接焊缝的长度（指单侧长度）                                                                     Length of welds of each side of lifting lug B= 205 mm
吊耳上起吊孔的直径 Pin hole diameter of lifting lug D= 80 mm
吊耳孔中心至垫板边缘的距离 Distance of pin hole to pad edge L= 342 mm
吊耳与垫板间连接焊缝的焊脚高度 Leg size of welds connecting lug to pad         h= 12 mm
垫板材料 Pad material 316L
垫板的名义厚度 Nominal thickness of pad S1= 12 mm
垫板材料的屈服强度 Yield strength of pad material σs2= 170 MPa
垫板与筒体连接焊缝的焊脚高度 Leg size of welds connecting pad to shell               h1= 9.6 MM
垫板沿筒体周向的长度 Circumferential length of pad A1= 270 mm
垫板沿筒体轴向的宽度 Longitudinal length of pad B1= 230 mm
吊耳起吊孔处衬板的材料 Material of pin hole re-pad Q345R
衬板的有效厚度（扣除材料的厚度负偏差）                                                                       Effective thickness of pin hole re-pad (exclusive under tolerance) Tp= 9.7 mm
衬板的外径 Outside diameter of pin hole re-pad D1= 160 mm
衬板与吊耳连接焊缝的焊脚高度                                                                                  Leg size of welds attaching pin hole re-pad to lifting lug                       h3= 8 mm
角焊缝系数 Fillet weld factor φ= 0.7
⑵ 载荷计算和许用应力  Load and Allowable Stresses 
侧壁式吊耳孔与尾吊孔之间的轴向距离 Axial distance of lifting lug hole to tailing lug hole Lo=L1+L2 23395 mm
侧壁式吊耳与尾部吊耳的起吊总载荷                               Total lifting load of lifting lugs and tailing lug F=f*G*9.81 161865 N
侧壁式吊耳的起吊载荷 Lifting load of lifting lugs P=F(1-L1cosθ/(Locosθ+L3sinθ))
单个侧壁式吊耳在竖直方向的起吊载荷                            Vertical load of each lifting lug Fv=P/2
起吊载荷在设备轴向的分力 Axial component of lifting load of each lifting lug Fl=Fv*sinθ
起吊载荷在设备切向的分力 Tangential component of lifting load of each lifting lug Ft=Fv*cosθ
吊耳材料拉伸和弯曲的许用应力 Allowable tensile and bending stress of lug material ［σ］=σs1/1.5 230.00  Mpa
吊耳材料的许用剪切应力                                               Allowable shear stress of lug material ［τ］=0.6［σ］ 138.00  Mpa
吊耳材料的许用挤压应力                                              Allowable bearing stress of lug material ［σp］=0.9σs1 310.50  Mpa
吊耳与垫板连接焊缝的许用剪应力 Allowable shear stress of welds attaching lug to pad ［τw1］=φ*MIN(［τ］,0.6*σs2/1.5) 47.60  Mpa
垫板与筒体连接焊缝的许用剪应力 Allowable shear stress of welds attaching pad to shell ［τw2］=φ*0.6*σs2/1.5 47.60  Mpa
衬板与吊耳间角焊缝的许用剪应力 Allowable shear stress of fillet welds attaching lifting lug to pin hole re-pad ［τw3］=φ*［τ］ 96.60  MPa
⑶ 吊耳的强度校核 Strength Calculation for Lifting Lugs
连接焊缝形心至吊耳端部的距离 Distance between C.G. of weld group and end of lug Nt=B2/(A+2B) 66.71 mm
起吊力Ft至连接焊缝形心的距离 Distance of lifting force Ft to C.G. of weld group Lt=L+B-Nt 480.29 mm
吊耳所承受的最大弯矩                                    Maximum bending moment acting on lifting lug M=Ft*L 见表1                         See Table 1
吊耳与垫板连接焊缝所承受的扭矩 Moment acting on welds attaching lifting lug to pad Mt1=Ft*Lt 见表1                         See Table 1
吊耳的抗弯断面模数                                                      Section modulus of lifting lug W=A2*S/6 126647 mm3
吊耳与垫板连接处的轴向拉伸应力                                   Tensile stress at cross section of lifting lug σt=Fl/(A*S) 见表1                         See Table 1
吊耳的弯曲应力 Bending stress of lifting lug σb=M/W 见表1                         See Table 1
吊耳拉伸应力与弯曲应力之和 Sum of tensile stress and bending stress of lifting lug σ=σt+σb 见表1                         See Table 1
吊耳在起吊孔中心处的横截面积                                    Net section at pin hole of lifting lug Ap=(A-D)*S+2Tp*(D1-D) 3750 mm2
该截面的剪应力                                                          Shear stress at the net section at pin hole τ1=Ft/Ap 见表1                         See Table 1
吊耳顶部的截面积 Net section at top of lifting lug Au=S*(A/2-D/2)+Tp*(D1-D) 1875 mm2
吊耳顶部截面的剪应力                                                Shear stress at that net section τ2=Fl/Au 见表1                         See Table 1
起吊孔中销轴的挤压应力                                              Bearing stress at pin hole σp=Fv/(D*(S+2Tp)) 见表1                         See Table 1
⑷ 吊耳与垫板间连接焊缝的强度校核 Stress Calculation for Welds Attaching Lifting Lug to Pad                                                                                                                                        
单位宽度焊缝的极惯性矩 Polar moment of inertia Jw1=(A+2B)3/12-B2*(A+B)2/(A+2B) 8788416 mm3
Ft引起的横向剪力                                 Transverse shear due to Ft f1=Ft/(A+2B) 见表1                         See Table 1
Mt引起的横向剪力                               Transverse shear due to Mt f2=Mt1*(B-Nt)/Jw1 见表1                         See Table 1
Fl引起的纵向剪力                                                      Longitudinal shear due to Fl f3=Fl/(A+2B) 见表1                         See Table 1
Mt引起的纵向剪力                              Longitudinal shear due to Mt f4=Mt1*0.5A/Jw1 见表1                         See Table 1
组合剪力                                                                    Combined shear load fr1=SQRT((f1+f2)2+(f3+f4)2) 见表1                         See Table 1
吊耳与垫板间连接焊缝的剪应力 Shear stress of welds attaching lifting lug to pad τw1=fr1/(0.707*h) 见表1                         See Table 1
⑸垫板与筒体间连接焊缝的强度校核 Stress Calculation for Welds Attaching Pad to Shell                                                                                                          
垫板与筒体的连接焊缝所承受的扭矩 Moment acting on welds attaching pad to shell Mt2=Ft*(L+B1/2) 见表1                         See Table 1
单位宽度焊缝的极惯性矩 Polor moment of inertia Jw2=(A1+B1)3/6 2.1E+07 mm3
Ft引起的横向剪力                                                      Transverse shear due to Ft fa=Ft/(2A1+2B1) 见表1                         See Table 1
Mt1引起的横向剪力                                                    Transverse shear due to Mt1 fb=0.5*Mt2*B1/Jw2 见表1                         See Table 1
Fl引起的纵向剪力                                                       Longitudinal shear due Fl fc=Fl/(2A1+2B1) 见表1                         See Table 1
Mt1引起的纵向剪力                           Longitudinal shear due Mt1 fd=Mt2*0.5*A1/Jw2 见表1                         See Table 1
组合剪力                                                                    Combined shear load fr2=SQRT((fa+fb)2+(fc+fd)2) 见表1                         See Table 1
垫板与筒体间连接焊缝的剪应力                                Shear stress of welds attaching pad to shell τw2=fr2/(0.707*h1) 见表1                         See Table 1
(6)衬板与吊耳连接焊缝的强度校核 Stress Calculation for Welds Attaching pin hole re-pad to lifting lug                                                                                                                     
fr3=Fv*Tp/(n*D1*(2*Tp+S)) 见表1                         See Table 1
衬板与吊耳间连接焊缝的剪应力 Shear stress of welds attaching pin hole re-pad to lifting lug τw3=fr3/(0.707*h3) 见表1                         See Table 1
表1 载荷和应力计算结果
Table 1 Calculation aresults of Load and Stress
θ(deg) 0 10 20 30 40 50 60 70 80 90
P(N) 62601.18 63552.59 64545.23 65649.94 66971.29 68695.19 71218.16 75607.98 86163.9 161865
Fv(N) 31300.59 31776.29 32272.62 32824.97 33485.65 34347.6 35609.08 37803.99 43081.95 80932.5
Fl(N) 0 5517.89 11037.89 16412.49 21524.16 26311.79 30838.37 35524.13 42427.44 80932.5
Ft(N) 31300.59 31293.54 30326.34 28427.26 25651.5 22078.21 17804.54 12929.73 7481.1 0
M(N.mm) 10704802 10702391 10371608 9722123 8772813 7550748 6089153 4421968 2558536 0
Mt1(N.mm) 15033360 15029974 14565438 13653329 12320159 10603943 8551343 6210020 3593098 0
σt(Mpa) 0 1.6 3.2 4.75 6.23 7.62 8.93 10.28 12.28 23.43
σb(Mpa) 84.52 84.51 81.89 76.77 69.27 59.62 48.08 34.92 20.2 0
f1(N/mm) 49.68 49.67 48.14 45.12 40.72 35.04 28.26 20.52 11.87 0
f2(N/mm) 236.56 236.5 229.19 214.84 193.86 166.86 134.56 97.72 56.54 0
f3(N/mm) 0 8.76 17.52 26.05 34.17 41.76 48.95 56.39 67.35 128.46
f4(N/mm) 188.16 188.12 182.31 170.89 154.2 132.72 107.03 77.73 44.97 0
fr1(N/mm) 342.55 347.35 341.82 326.14 300.85 266.85 225.48 178.8 131.51 128.46
Mt2N.mm) 14304370 14301148 13859137 12991258 11722736 10089742 8136675 5908887 3418863 0
fa(N/mm) 31.3 31.29 30.33 28.43 25.65 22.08 17.8 12.93 7.48 0
fb(N/mm) 78.96 78.94 76.5 71.71 64.71 55.7 44.91 32.62 18.87 0
fc(N/mm) 0 5.52 11.04 16.41 21.52 26.31 30.84 35.52 42.43 80.93
fd(N/mm) 92.69 92.67 89.81 84.18 75.96 65.38 52.73 38.29 22.15 0
fr2(N/mm) 144.04 147.62 146.91 141.94 132.92 120.24 104.48 86.73 69.75 80.93
fr3(N/mm) 17.21  17.47  17.74  18.05  18.41  18.88  19.58  20.78  23.69  44.50 
应力计算结果和判断 Stress Calculation Results and Judgement
θ(deg) 0 10 20 30 40 50 60 70 80 90
σ(Mpa) 84.52  86.11  85.09  81.52  75.50  67.24  57.01  45.20  32.48  23.43 
［σ］(Mpa) 138.00 
σ<［σ］,  合格，  Acceptable.
τ1(Mpa) 8.35  8.34  8.09  7.58  6.84  5.89  4.75  3.45  1.99  0.00 
τ2(Mpa) 0.00  2.94  5.89  8.75  11.48  14.03  16.45  18.95  22.63  43.16 
［τ］(Mpa) 138.00 
τ1<［τ］,  合格，  Acceptable.
τ2<［τ］,  合格，  Acceptable.
σp(Mpa) 11.15  11.32  11.49  11.69  11.93  12.23  12.68  13.46  15.34  28.82 
［σp］(Mpa) 227.70 
σp<［σp］,  合格，  Acceptable.
τw1(Mpa) 40.38  40.94  40.29  38.44  35.46  31.45  26.58  21.07  15.50  15.14 
［τw1］(Mpa) 44.63 
τw1<［τw1］,  合格，  Acceptable.
τw2(Mpa) 21.22  21.75  21.65  20.91  19.58  17.72  15.39  12.78  10.28  11.92 
［τw2］(Mpa) 44.63 
τw2<［τw2］,  合格，  Acceptable.
τw3(Mpa) 3.04  3.09  3.14  3.19  3.25  3.34  3.46  3.67  4.19  7.87 
［τw3］(Mpa) 96.60 
τw3<［τw3］,  合格，  Acceptable.
      表中 Where
θ— 设备轴线与水平面的夹角 Included angle between equipment axis and horizontal plane
σ— 吊耳拉伸应力与弯曲应力之和 Sum of tensile stress and bending stress of lifting lug
［σ］—
吊耳的许用拉伸应力 Allowable tensile stress of lifting lug
τ1— 吊耳起吊孔截面的剪应力 Shear stress at the section of pin hole
τ2— 吊耳顶部截面的剪应力 Shear stress at the section of top of lifting lug
［τ］—
吊耳的许用剪应力 Allowable shear stress of lifting lug
σp—
吊耳起吊孔处的挤压应力 Bearing stress at pin hole
［σp］—
吊耳的许用挤压应力 Allowable bearing stress of lifting lug
τw1—
吊耳与垫板连接焊缝的剪应力 Shear stress of welds attaching lifting lug to pad
［τw1］—
吊耳与垫板连接焊缝的许用剪应力 Allowable shear stress of welds attaching lifting lug to pad
τw2—
垫板与壳体连接焊缝的剪应力 Shear stress of welds attaching pad to shell
［τw2］—
垫板与壳体连接焊缝的许用剪应力 Allowable shear stress of welds of attaching pad to shell
τw—
衬板与吊耳连接焊缝的剪应力 Shear stress of welds attaching re-pad to lifting lug
［τw］—
衬板与吊耳连接焊缝的许用剪应力 Allowable shear stress attaching re-pad to lifting lug
1 侧壁式吊耳的计算（2） 项目号 ITEM NO. Contract number 合同号
job number 工作令号
Calculation of Lifting Lug（2） 文件号 DOC. NO. document number 文件号
revision 修订号
1
说明：
说明: 本计算书系参照HG/T21574-2008标准编制,仅适用 1. 本计算书系参照HG/T21574-2008标准编制,仅适用于设备已起吊至其轴线与水平面垂直的状态。
     于设备已起吊至其轴线与水平面垂直的状态。
Note: This calculation sheet is prepared referring 2. 黄色单元格内的数据是需要输入的。
        to Chinese standard HG/T21574-2008, and  NOTES:
        is only appliable to the equipment which has  1. This calculation template is prepared per Chinese standard HG/T21574-2008, and is only appliable to the equipment which has been lifted to a vertical position.  
        been lifted to a vertical position.
2. The data in light blue cells shall be inputted.
⑴输入数据 Input Data
设备的最大吊装质量 Maximum lifting weight W= 10000 kg
动载系数 Dynamic factor f= 1.65
吊耳的材料 Material of lifting lug Q345R
吊耳的厚度 Thickness of lifting lug S= 15.7
吊耳材料的屈服强度 Yield strength of lifting lug material  σs1= 345 Mpa
吊耳的宽度 Width of lifting lug H= 220 mm
吊耳上起吊孔的直径 Pin hole diameter of lifting lug D= 80 mm
垫板的材料 Pad material 316L
垫板材料的屈服强度 Yield strength of pad material  σs2= 170 Mpa
垫板的厚度 Thickness of pad 12 mm
垫板沿筒体周向的长度 Circumferential length of pad Hsp= 270 mm
垫板沿筒体轴向的宽度 Longitudinal length of pad Lsp= 230 mm
垫板四角的圆角半径 Corner radius of pad R= 20 mm
吊耳起吊孔处衬板的厚度 Thickness of re-pad at pin hole S2= 9.7 mm
吊耳衬板的外径 Outside diameter of re-pad D1= 160 mm
吊耳端部与垫板边缘的距离 Distance of lug end to pad edge G= 25 mm
吊耳端部的圆角半径 Corner radius of lifting lug r= 20 mm
吊耳中央部位焊缝长度尺寸 Length of welds in the middle of lug  L1= 140 mm
吊耳端部缺口部位的宽度 Dimention            F= 80 mm
吊耳与垫板间连接焊缝的焊脚高度 Leg size of welds attaching pad to shell h= 12 mm
垫板与筒体连接焊缝的焊脚高度 Leg size of welds attaching lug to pad h1= 9.6 mm
角焊缝系数 Fillet weld factor φ= 0.7
⑵载荷计算和许用应力 Load and allowable stresses
单个吊耳在竖直方向的起吊载荷                                     Vertical lifting load of each lug Fv=f*W*9.81/2 80932.5 N
吊耳材料的许用拉伸应力 Allowable tensile stress of lug material ［σ］=σs1/1.5 230 Mpa
吊耳材料的许用剪切应力 Allowable shear stress of lug material ［τ］=0.6［σ］ 138 Mpa
吊耳与垫板连接焊缝的许用剪应力 Allowable shear stress of welds attaching lug to pad ［τw1］=φ*MIN(［τ］,0.6*σs2/1.5) 47.60  Mpa
垫板与筒体连接焊缝的许用剪应力 Allowable shear stress of welds attaching pad to shell ［τw2］=φ*0.6*σs2/1.5 47.60  Mpa
⑶吊耳的强度校核Stresses in Lifting Lug
吊耳A-A截面的轴向拉伸应力                                        Tensile stress at A-A section of lug σ=Fv/(S*(H-D)+2*S2*(D1-D)) 21.58 Mpa
吊耳B-B截面的剪应力                                                Shear stress at B-B section of lug τ=0.5*Fv/(S*(H-D)/2+S2*(D1-D)) 21.58 Mpa
σ < ［σ］ 合格,  Acceptable.
τ < ［τ］ 合格,  Acceptable.
⑷垫板与筒体连接焊缝的强度校核Stress in Welds Attaching Lug to Pad
垫板与筒体连接焊缝的总长度 Total length of welds attaching lug to pad Lw1=2*(Hsp+Lsp)-8*R+2π*R 965.66 mm
垫板与筒体连接焊缝的剪应力                                       Shear stress at B-B section of lug τw2=Fv/(0.707*h1*Lw1) 12.35 Mpa
τw2
< ［τw2］ 合格,  Acceptable.
⑸吊耳与垫板间连接焊缝的强度校核Shear Stress in Welds of Pad to Shell
吊耳与垫板连接焊缝的总长度 Total length of welds attaching pad to shell Lw=2(Lsp-G+L1)+0.5πF+H-F-8r+2πr 921.33 mm
吊耳与垫板连接焊缝中的轴向剪应力                                Shear stress in welds of pad to shell τw1=Fv/(0.707*h*Lw) 10.35 Mpa
τw1
< ［τw1］ 合格,  Acceptable.
结论:吊耳及连接焊缝的强度满足要求。
Conclusion：The strength of lifting lugs and connecting welds is satisfactory.

侧壁式吊耳的计算（1） 项目号 ITEM NO.
Calculation of Lifting Lug（1） 文件号 DOC. NO.
说明：本计算书是依据Dennis Moss编著的《Pressure Vessel Design Manual》中的计算方法编制的。 说明：
          计算中将吊耳与垫板的连接简化为仅在端部（宽度为A）和两侧（每侧长度为B）与垫板焊接。 1. 采用本计算程序时，吊耳的尺寸可不受HG/T21574-2008的限制。可以通过增加吊耳的宽度和厚度，尽可能减小吊耳的长度来提高吊耳的起吊能力，但应注意吊耳上端的半径尺寸R不应过大以致不能与相应的卸扣的尺寸相适应。
Note: This calculation sheet is prepared based on 《Pressure Vessel Design Manual》 
        written by Dennis Moss.  In the calculation , the lug to pad connection is simplified as  
        only welded at the bottom end (the width is A) and two sides (the length of each side 2. 黄色单元格内的数据是需要输入的。
        is B) of the lifting lug. NOTES:
1. When using this calculation template, the dimensions of lifting lugs need not be limitted to that specified in HG/T21574-2008. The lifting capasity of the lug can be enlarged by increasing the width and thickness of the lug and  making the length of the lug as short as possible, but it should be noticed that the dimension of top end radius R of the lug shall not be too large to match the corresponding shackle. 
1
1
2. The data in light blue cells shall be inputted.
⑴ 输入数据 Input Data
设备的最大吊装质量 Maximum lifting weight G= 159000 kg
动载系数 Dynamic factor f= 1.65
侧壁式吊耳孔中心至设备重心的轴向距离                                                                      Axial distance of lifting lug hole to C.G. of equipment L1= 16449.5 mm
尾部吊耳孔中心至设备重心的轴向距离                                                                         Axial distance of tailing lug hole to C.G. of equipment L2= 16449.5 mm
尾部吊耳孔中心至设备轴线的距离                                                                             Distance between center of tailing lug hole and axis of equipment  L3= 2267 mm
吊耳的材料 Lifting lug material Q345R
吊耳的有效厚度（扣除材料的厚度负偏差）                                                                                                               Effective thickness of lifting lug (exclusive under tolerance) S= 79.7 mm
吊耳材料的屈服强度 Yield strength of lug material σs1= 285 Mpa
吊耳的宽度 Width of lug A= 720 mm
吊耳顶部圆弧部分的半径 Radius of circular portion of lifting lug R= 200 mm
吊耳两侧连接焊缝的长度（指单侧长度）                                                                   Length of welds of each side of lifting lug B= 600 mm
吊耳上起吊孔的直径 Pin hole diameter of lifting lug D= 160 mm
吊耳上起吊孔中心至垫板边缘的距离 Distance of pin hole center to pad edge L= 850 mm
吊耳孔中心至吊耳梯形部分底部的距离 Distance of pin hole center to the bottom of trapeziform portion of lifting lug La= 770 mm
吊耳与垫板间连接焊缝的焊脚高度 Leg size of welds connecting lug to pad h= 50 mm
垫板材料 Pad material Q345R
垫板的名义厚度 Nominal thickness of pad S1= 40 mm
垫板材料的屈服强度 Yield strength of pad material σs2= 305 MPa
垫板与筒体连接焊缝的焊脚高度 Leg size of welds connecting pad to shell h1= 30 mm
垫板沿筒体周向的长度 Circumferential length of pad A1= 870 mm
垫板沿筒体轴向的宽度 Longitudinal length of pad B1= 670 mm
吊耳起吊孔处衬板的材料 Material of pin hole re-pad Q345R
衬板的有效厚度（扣除材料的厚度负偏差）                                                                Effective thickness of pin hole re-pad (exclusive under tolerance) Tp= 29.7 mm
衬板的外径 Outside diameter of pin hole re-pad D1= 320 mm
衬板与吊耳连接焊缝的焊脚高度                                                                              Leg size of welds connecting pin hole re-pad to lug h3= 24 mm
角焊缝系数 Fillet weld factor φ= 0.7
⑵ 载荷计算和许用应力  Load and Allowable Stresses 
侧壁式吊耳孔与尾吊孔之间的轴向距离 Axial distance of lifting lug hole to tailing lug hole Lo=L1+L2 32899 mm
侧壁式吊耳与尾部吊耳的起吊总载荷 Total lifting load of lifting lugs and tailing lug F=f*G*9.81 2573654 N
侧壁式吊耳的起吊载荷 Lifting load of lifting lugs P=F(1-L1cosθ/(Locosθ+L3sinθ)) 见表1                     See Table 1
单个侧壁式吊耳在竖直方向的起吊载荷              Vertical load of each lifting lug Fv=P/2 见表1                     See Table 1
起吊载荷在设备轴向的分力 Axial component of lifting load of each lifting lug Fl=Fv*sinθ 见表1                     See Table 1
起吊载荷在设备切向的分力 Tangential component of lifting load of each lifting lug Ft=Fv*cosθ 见表1                     See Table 1
吊耳材料拉伸和弯曲的许用应力 Allowable tensile and bending stress of lug material ［σ］=σs1/1.5 190 Mpa
吊耳材料的许用剪切应力                                               Allowable shear stress of lug material ［τ］=0.6［σ］ 114 Mpa
吊耳材料的许用挤压应力                                              Allowable bearing stress of lug material ［σp］=0.9σs1 256.5 Mpa
吊耳与垫板间角焊缝的许用剪应力 Allowable shear stress of fillet welds attaching lug to pad  ［τw1］=φ*MIN(［τ］,0.6*σs2/1.5) 79.8 Mpa
垫板与筒体连接焊缝的许用剪应力 Allowable shear stress of welds attaching pad to shell ［τw2］=φ*0.6*σs2/1.5 85.4 Mpa
衬板与吊耳间角焊缝的许用剪应力                                  Allowable shear stress of welds attaching lifting lug to pin hole re-pad ［τw3］=φ*［τ］ 79.8 MPa
⑶ 吊耳的强度校核 Strength Calculation for Lifting Lugs
1 θ1=arctan(2La/A) 1.13  rad
Lb=La/sinθ1 850 mm
θ2=arcsin(R/Lb) 0.24  rad
θ3=θ1+θ2 1.37  rad
Lc=R/sinθ3 204.06  mm
Ld=A/2-(La-D1/2)/tanθ3 236.46  mm
连接焊缝形心至吊耳端部的距离 Distance between C.G. of weld group and end of lug Nt=B2/(A+2B) 187.5 mm
起吊力Ft至连接焊缝形心的距离 Distance of lifting force Ft to C.G. of weld group Lt=L+B-Nt 1262.5 mm
吊耳所承受的最大弯矩 Maximum bending moment acting on lifting lug M1=Ft*L 见表1                     See Table 1
吊耳C-C截面上的弯矩(见注) Bending moment in section C-C of lifting lug (see Note)  M2=Ft*D1/2 见表1                     See Table 1
注: C-C截面是吊耳在衬板最低处的横截面.                                                                                                Note: Section C-C is the cross section of lifting lug at the lowest point of pin hole re-pad. 
吊耳与垫板连接焊缝所承受的扭矩 Torsional moment acting on welds attaching lifting lug to pad Mt1=Ft*Lt 见表1                     See Table 1
吊耳的抗弯断面模数                                                      Section modulus of lifting lug W1=A2*S/6 6886080 mm3
吊耳C-C截面的抗弯断面模数                                        Section modulus of section C-C of lifting lug  W2=(2*Ld)2*S/6 2970944 mm3
吊耳与垫板连接处的轴向拉伸应力                                 Tensile stress at cross section of lifting lug σt1=Fl/(A*S) 见表1                     See Table 1
吊耳的弯曲应力 Bending stress of lifting lug σb1=M1/W1 见表1                     See Table 1
σ1=σt1+σb1 见表1                     See Table 1
吊耳C-C截面的拉伸应力                                              Tensile stress in section C-C of lifting lug  σt2=Fl/(2*Ld*S) 见表1                     See Table 1
吊耳C-C截面的弯曲应力                               Bending stress in section C-C of lifting lug σb2=M2/W2 见表1                     See Table 1
σ2=σt2+σb2 见表1                     See Table 1
吊耳在起吊孔中心处的横截面积                                      Net section at pin hole of lifting lug Ap=(2Lc-D)*S+2Tp*(D1-D) 29279.2 mm2
该截面的剪应力                                                         Shear stress at the net section at pin hole τ1=Ft/Ap 见表1                     See Table 1
吊耳顶部的截面积                                                         Net section at top of lifting lug Au=S*(R-D/2)+Tp*(D1-D) 14316 mm2
吊耳顶部截面的剪应力                                                  Shear stress at that net section τ2=Fl/Au 见表1                     See Table 1
起吊孔中销轴的挤压应力                                                Bearing stress at pin hole σp=Fv/(D*(S+2Tp)) 见表1                     See Table 1
⑷ 吊耳与垫板间连接焊缝的强度校核 Stress Calculation for Welds Attaching Lifting Lug to Pad                                                                                                                                         
单位宽度焊缝的极惯性矩                                             Polar moment of inertia Jw1=(A+2B)3/12-B2*(A+B)2/(A+2B) 2.6E+08 mm3
Ft引起的横向剪力                                 Transverse shear due to Ft f1=Ft/(A+2B) 见表1                     See Table 1
Mt引起的横向剪力                               Transverse shear due to Mt f2=Mt1*(B-Nt)/Jw1 见表1                     See Table 1
Fl引起的纵向剪力                               Longitudinal shear due to Fl f3=Fl/(A+2B) 见表1                     See Table 1
Mt引起的纵向剪力                              Longitudinal shear due to Mt f4=Mt1*0.5*A/Jw1 见表1                     See Table 1
组合剪力                                                                     Combined shear load fr1=SQRT((f1+f2)2+(f3+f4)2) 见表1                     See Table 1
吊耳与垫板间连接焊缝的剪应力 Shear stress of welds attaching lifting lug to pad τw1=fr1/(0.707*h) 见表1                     See Table 1
⑸垫板与筒体间连接焊缝的强度校核 Stress Calculation for Welds Attaching Pad to Shell                                                                                                         
垫板与筒体的连接焊缝所承受的扭矩                               Torsional moment acting on welds attaching pad to shell Mt2=Ft*(L+B1/2) 见表1                     See Table 1
单位宽度焊缝的极惯性矩                                            Polor moment of inertia Jw2=(A1+B1)3/6 6.1E+08 mm3
Ft引起的横向剪力                                                  Transverse shear due to Ft fa=Ft/(2A1+2B1) 见表1                     See Table 1
Mt1引起的横向剪力                             Transverse shear due to Mt1 fb=0.5*Mt2*B1/Jw2 见表1                     See Table 1
Fl引起的纵向剪力                                                        Longitudinal shear due Fl fc=Fl/(2A1+2B1) 见表1                     See Table 1
Mt1引起的纵向剪力                            Longitudinal shear due Mt1 fd=Mt2*0.5*A1/Jw2 见表1                     See Table 1
组合剪力                                                                      Combined shear load fr2=SQRT((f1+f2)2+(f3+f4)2) 见表1                     See Table 1
垫板与筒体连接焊缝要求的最小焊脚高度 Required minimum leg of welds attaching pad to shell h1r=fr/(0.707*［τw2］) 见表1                     See Table 1
垫板与筒体间连接焊缝的剪应力                                   Shear stress of welds attaching pad to shell τw2=fr2/(0.707*h1) 见表1                     See Table 1
(6) 衬板与吊耳连接焊缝的强度校核Stress Calculation of welds attaching pin hole re-pad to lifting lug
衬板处的组合剪切应力                                                    Unit shear load on re-pad fr3=Pv*Tp/(π*D1*(2*Tp+S)) 见表1                     See Table 1
衬板与吊耳间连接焊缝的剪应力                                      Shear stress of welds τw3=fw/(0.707*h3) 见表1                     See Table 1
表1 载荷和应力计算结果
Table 1 Calculation aresults of Load and Stress
θ(deg) 0 10 20 30 40 50 60 70 80 90
P(N) 1286827 1302274 1318311 1336063 1357165 1384483 1424036 1491671 1648409 2573653
Fv(N) 643413.4 651137.2 659155.6 668031.5 678582.4 692241.4 712017.9 745835.4 824204.3 1286827
Fl(N) 0 113068.8 225444.5 334015.8 436184.4 530287.7 616625.6 700856 811682.8 1286827
Ft(N) 643413.4 641245 619403.7 578532.3 519824.3 444964.2 356009 255090.7 143121.6 0
M1(N.mm) 5.47E+08 5.45E+08 5.26E+08 4.92E+08 4.42E+08 3.78E+08 3.03E+08 2.17E+08 1.22E+08 0
M2(N.mm) 1.03E+08 1.03E+08 99104589 92565162 83171885 71194275 56961434 40814515 22899453 0
Mt1(N.mm) 8.12E+08 8.1E+08 7.82E+08 7.3E+08 6.56E+08 5.62E+08 4.49E+08 3.22E+08 1.81E+08 0
σt1(Mpa) 0.00  1.97  3.93  5.82  7.60  9.24  10.75  12.21  14.14  22.42 
σb1(Mpa) 79.42  79.15  76.46  71.41  64.17  54.93  43.94  31.49  17.67  0.00 
σt2(Mpa) 0.00  3.00  5.98  8.86  11.57  14.07  16.36  18.59  21.53  34.14 
σb2(Mpa) 34.65  34.53  33.36  31.16  28.00  23.96  19.17  13.74  7.71  0.00 
f1(N/mm) 335.11 333.98 322.61 301.32 270.74 231.75 185.42 132.86 74.54 0
f2(N/mm) 1273.46 1269.17 1225.94 1145.04 1028.85 880.68 704.62 504.88 283.27 0
f3(N/mm) 0 58.89 117.42 173.97 227.18 276.19 321.16 365.03 422.75 670.22
f4(N/mm) 1111.38 1107.64 1069.91 999.31 897.9 768.6 614.94 440.62 247.22 0
fr1(N/mm) 1955.16 1982.65 1951.35 1862.4 1718.94 1526.13 1291.69 1027.51 759.53 670.22
Mt2N.mm) 7.62E+08 7.6E+08 7.34E+08 6.86E+08 6.16E+08 5.27E+08 4.22E+08 3.02E+08 1.7E+08 0
fa(N/mm) 208.9 208.2 201.11 187.84 168.77 144.47 115.59 82.82 46.47 0
fb(N/mm) 419.61 418.19 403.95 377.29 339.01 290.19 232.17 166.36 93.34 0
fc(N/mm) 0 36.71 73.2 108.45 141.62 172.17 200.2 227.55 263.53 417.8
fd(N/mm) 544.86 543.03 524.53 489.92 440.2 376.81 301.48 216.02 121.2 0
fr2(N/mm) 831.8 853.5 850.52 823.05 772.24 700.22 610.43 508.77 409.35 417.8
fr3(N/mm) 136.65 138.29 140 141.88 144.12 147.02 151.22 158.41 175.05 273.31
应力计算结果和判断 Stress Calculation Results and Judgement
θ(deg) 0 10 20 30 40 50 60 70 80 90
σ1(Mpa) 79.42  81.12  80.39  77.23  71.77  64.17  54.69  43.70  31.81  22.42 
σ2(Mpa) 34.65  37.53  39.34  40.02  39.57  38.03  35.53  32.33  29.24  34.14 
［σ］(Mpa) 178.13 
σ1<［σ］,  合格，  Acceptable.
σ2<［σ］,  合格，  Acceptable.
τ1(Mpa) 21.98  21.90  21.16  19.76  17.75  15.20  12.16  8.71  4.89  0.00 
τ2(Mpa) 0.00  7.90  15.75  23.33  30.47  37.04  43.07  48.96  56.70  89.89 
［τ］(Mpa) 114.00 
τ1<［τ］,  合格，  Acceptable.
τ2<［τ］,  合格，  Acceptable.
σp(Mpa) 28.91  29.26  29.62  30.02  30.49  31.10  31.99  33.51  37.03  57.82 
［σp］(Mpa) 188.10 
σp<［σp］,  合格，  Acceptable.
τw1(Mpa) 55.31  56.09  55.20  52.68  48.63  43.17  36.54  29.07  21.49  18.96 
［τw1］(Mpa) 79.80 
τw1<［τw1］,  合格，  Acceptable.
τw2(Mpa) 39.22  40.24  40.10  38.80  36.41  33.01  28.78  23.99  19.30  19.70 
［τw2］(Mpa) 80.06 
τw2<［τw2］,  合格，  Acceptable.
τw3(Mpa) 8.05  8.15  8.25  8.36  8.49  8.66  8.91  9.34  10.32  16.11 
［τw3］(Mpa) 79.80 
τw3<［τw3］,  合格，  Acceptable.
      表中 Where
θ— 设备轴线与水平面的夹角 Included angle between equipment axis and horizontal plane
σ1—
吊耳拉伸应力与弯曲应力之和 Sum of tensile stress and bending stress of lifting lug
σ2—
吊耳C-C截面的拉伸和弯曲应力 Tensile and bending stress at C-C cross section
［σ］—
吊耳的许用拉伸应力 Allowable tensile stress of lifting lug
τ1— 吊耳起吊孔截面的剪应力 Shear stress at the section of pin hole
τ2— 吊耳顶部截面的剪应力 Shear stress at the section of top of lifting lug
［τ］—
吊耳的许用剪应力 Allowable shear stress of lifting lug
σp—
吊耳起吊孔处的挤压应力 Bearing stress at pin hole
［σp］—
吊耳的许用挤压应力 Allowable bearing stress of lifting lug
τw1—
吊耳与垫板连接焊缝的剪应力 Shear stress of welds attaching lifting lug to pad
［τw1］—
吊耳与垫板连接焊缝的许用剪应力 Allowable shear stress of welds attaching lifting lug to pad
τw2—
垫板与壳体连接焊缝的剪应力 Shear stress of welds attaching pad to shell
［τw2］—
垫板与壳体连接焊缝的许用剪应力 Allowable shear stress of welds of attaching pad to shell
τw3—
衬板与吊耳连接焊缝的剪应力 Shear stress of welds attaching re-pad to lifting lug
［τw3］—
衬板与吊耳连接焊缝的许用剪应力 Allowable shear stress attaching re-pad to lifting lug
1 侧壁式吊耳的计算（2） 项目号 ITEM NO.
Calculation of Lifting Lug（2） 文件号 DOC. NO.
说明: 本计算书系参照HG/T21574-2008标准编制,仅适用于设备已起吊至其轴线与水平面垂直的状态。 说明：
Note: This calculation sheet is prepared referring to Chinese standard HG/T21574-2008, and  1. 本计算书系参照HG/T21574-2008标准编制,仅适用于设备已起吊至其轴线与水平面垂直的状态。
        is only appliable to the equipment which has been lifted to a vertical position.
2. 黄色单元格内的数据是需要输入的。
⑴输入数据 Input Data NOTES:
设备的最大吊装质量 Maximum lifting weight W= 159000 kg 1. This calculation template is prepared per Chinese standard HG/T21574-2008, and is only appliable to the equipment which has been lifted to a vertical position.  
动载系数 Dynamic factor f= 1.65
吊耳的材料 Material of lifting lug Q345R
吊耳的厚度 Thickness of lifting lug S= 79.7 2. The data in light blue cells shall be inputted.
吊耳材料的屈服强度 Yield strength of lug σs1= 285 Mpa
吊耳的宽度 Width of lifting lug A= 720 mm
吊耳顶部圆弧部分的半径 Radius of circular portion of lifting lug R= 200 mm
吊耳上起吊孔的直径 Pin hole diameter of lifting lug D= 160 mm
吊耳孔中心至吊耳梯形部分底部的距离 Distance of pin hole center to the bottom of trapeziform portion of lifting lug La= 770 mm
垫板的材料 Pad material Q345R
垫板的厚度 Thickness of pad 40 mm
垫板材料的屈服强度 Yield strength of pad material σs2= 305 Mpa
垫板沿筒体周向的长度 Circumferential length of pad A1= 870 mm
垫板沿筒体轴向的宽度 Longitudinal length of pad B1= 670 mm
垫板四角的圆角半径 Corner radius of pad R= 20 mm
吊耳起吊孔处衬板的厚度 Thickness of re-pad at pin hole S2= 29.7 mm
吊耳衬板的外径 Outside diameter of pin hole re-pad D1= 320 mm
吊耳端部与垫板边缘的距离 Distance of lug end to pad edge G= 70 mm
吊耳端部的圆角半径 Corner radius of lifting lug r= 20 mm
吊耳中央部位焊缝长度尺寸 Length of welds in the middle of lug  L1= 220 mm
吊耳端部缺口部位的宽度 Dimention            F= 150 mm
吊耳与垫板间连接焊缝的焊脚高度 Leg size of welds attaching pad to shell h= 50 mm
垫板与筒体连接焊缝的焊脚高度 Leg size of welds attaching lug to pad h1= 30 mm
角焊缝系数 Fillet weld factor φ= 0.7
⑵载荷计算和许用应力 Load and allowable stresses
单个吊耳在竖直方向的起吊载荷             Vertical lifting load of each lug Fv=f*W*9.81/2 1286827 N
吊耳材料的许用拉伸应力 Allowable tensile stress of lug material ［σ］=σs1/1.5 190 Mpa
吊耳材料的许用剪切应力 Allowable shear stress of lug material ［τ］=0.6［σ］ 114 Mpa
吊耳与垫板连接焊缝的许用剪应力                                    Allowable shear stress of welds attaching lug to pad ［τw1］=φ*MIN(［τ］,0.6*σs2/1.5) 79.8 Mpa
垫板与筒体连接焊缝的许用剪应力                             Allowable shear stress of welds attaching pad to shell ［τw2］=φ*0.6*σs2/1.5 85.4 Mpa
⑶吊耳的强度校核Stresses in Lifting Lug
1 θ1=arctan(2La/A) 1.13  rad
Lb=La/sinθ1 850 mm
θ2=arcsin(R/Lb) 0.24  rad
θ3=θ1+θ2 1.37  rad
Lc=R/sinθ3 204.06  mm
Ld=A/2-(La-D1/2)/tanθ3 236.46  mm
吊耳A-A截面的轴向拉伸应力               Tensile stress at A-A section of lug σ=Fv/(S*(2*Lc-D)+2*S2*(D1-D)) 43.95 Mpa
吊耳C-C截面上的弯矩(见注)               Bending moment in section C-C of lifting lug (see Note)  σ'=Fv/(S*2*Ld) 34.14  N.mm
注: C-C截面是吊耳在衬板最低处的横截面.                                                                                            Note: Section C-C is the cross section of lifting lug at the lowest point of pin hole re-pad. 
吊耳B-B截面的剪应力                          Shear stress at B-B section of lug τ=0.5*Fv/(S*(R-D/2)+S2*(D1-D)) 44.94 Mpa
σ < ［σ］ 合格,  Acceptable.
σ' < ［σ］ 合格，  Acceptable.
τ < ［τ］ 合格，  Acceptable.
⑷垫板与筒体连接焊缝的强度校核Stress in Welds Attaching Lug to Pad
垫板与筒体连接焊缝的总长度 Total length of welds attaching lug to pad Lw1=2*(A1+B1)-8*r1+2π*R 3045.66 mm
垫板与筒体连接焊缝的剪应力                 Shear stress at B-B section of lug τw2=Fv/(0.707*h1*Lw1) 19.92 Mpa
τw2
< ［τw2］ 合格，  Acceptable.
⑸吊耳与垫板间连接焊缝的强度校核Shear Stress in Welds of Pad to Shell
吊耳与垫板连接焊缝的总长度 Total length of welds attaching pad to shell Lw=2(B1-G+L1)+0.5πF+A-F-8r+2πr 2411.28 mm
吊耳与垫板连接焊缝中的轴向剪应力    Shear stress in welds of pad to shell τw1=Fv/(0.707*h*Lw) 15.1 Mpa
τw1
< ［τw1］ 合格，  Acceptable.
结论:吊耳及连接焊缝的强度满足要求。
Conclusion：The strength of lifting lugs and connecting welds is satisfactory.
标准standard
半标准half standard
非标准un-standard
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