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AX型轴式吊耳的计算 |
项目号 ITEM NO. |
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| Calculation of Type AX Trunnion Lug |
文件号 DOC. NO. |
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本计算书是参照HG/T21574-2018编制的。 |
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说明: |
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This calculation sheet is prepared referring to HG/T 21574-2018. |
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1. 本计算书是参照HG/T21574-2018编制的，主要不同之处是增加了管轴与壳体连接焊缝的强度校核。（垫板与筒体连接焊缝应力值比管轴处低，故略去）
2. 黄色单元格内的数据是需要输入的。
3. 管轴与壳体连接焊缝根部宽度a的输入值应为焊缝根部的名义宽度减去负偏差，举例来说，如果图纸上标注的焊缝宽度为10±1mm, 则a的输入值应为9mm。
4. 设计者应根据轴式吊耳作用在垫板和壳体上的力和力矩（即本计算书中的Fv、Fh、M和M1），采用SW6或PV Elite的局部应力计算程序，对垫板及壳体中的局部应力进行校核。 应注意: 设备起吊时吊耳在垫板和壳体中引起的局部应力属于一次应力, 因此校核时局部薄膜应力和最大表面应力均不应超过1.5倍的材料许用应力。 |
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输入数据 Input Data |
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设备起吊重量 Equipment lifting weight |
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Q = |
70000 |
kg |
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轴式吊耳的数量 Trunnion number |
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n = |
2 |
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管轴材料 Material of trunnion |
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20 |
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管轴的许用拉伸和弯曲应力Allowable tensile and compressive stress of trunnion material |
[σ]= |
150 |
MPa |
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管轴的许用剪应力 Allowable shear stress of trunnion |
[τ]= |
90 |
MPa |
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管轴外径 Diameter of trunnion |
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DO = |
426 |
mm |
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管轴有效厚度 Effective thickness of trunnion |
S = |
18 |
mm |
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管轴长度 Length of trunnion |
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L = |
248 |
mm |
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垫板厚度 Thickness of pad |
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S'= |
16 |
mm |
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壳体材料 Shell material |
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Q345 |
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管轴与壳体连接焊缝根部的宽度 Bottom width of groove |
a = |
18 |
mm |
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Weld attaching trunnion to shell |
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焊缝系数 weld coefficient |
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Φ= |
0.7 |
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钢丝绳与垂直面的夹角 Angle of sling |
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α = |
15 |
° |
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动载系数 Dynamic factor |
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c = |
1.65 |
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A |
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t |
5~10 |
5~10 |
5~20 |
10~25 |
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DN |
150 |
180 |
200 |
250 |
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S = |
10 |
12 |
14 |
14 |
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L = |
120 |
130 |
140 |
150 |
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| 2 |
管轴强度校核 Checking strength of trunnion: |
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垂直力 Vertical force |
Fv =Q / n×9.81×c= |
566527.5 |
N |
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水平力 Horizontal force |
Fh =Fv×tanα= |
151800.59 |
N |
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纵向弯矩 Longitudinal bending moment |
M =Fv×L= |
1.40E+08 |
N·mm |
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管轴横截面积 Cross-sectional area of trunnnion |
A =π×(DO-S)×S= |
23071.86 |
mm2 |
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管轴内外径比值 Ratio of inside diametr to outside diameter |
α=(DO-2S)/DO= |
0.92 |
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管轴的惯性矩 Moment of inertia |
J =π×DO4×(1-α4)/64= |
4.81E+08 |
mm4 |
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管轴的断面模数 Section modulus |
W =J / (0.5DO)= |
2.26E+06 |
mm3 |
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2258279.8 |
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拉伸应力 Tensile stress |
σLt =Fh / A= |
6.58 |
MPa |
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弯曲应力 Bending stress |
σLb =M / W= |
62.21 |
MPa |
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组合应力 Combined stress |
σL =|σLt| + σLb= |
68.79 |
MPa |
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σL ≤ [σ] , 管轴组合应力校核合格，the combined stress in trunnion is satisfactory. |
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剪切应力 Shear stress |
τ =Fv / A= |
24.55 |
MPa |
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组合应力 Combined stress |
σC=sqrt(σL 2+τ2)= |
73.05 |
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σC ≤ [σ] , 组合应力合格，it is satisfactory. |
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| 3 |
耳轴与端板连接角焊缝强度校核 Checking strength of weld of trunnion to end plate: |
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剪切应力 Shear stress |
τh =Fh / 1.76SDO= |
11.25 |
MPa |
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τh |
≤ |
0.7[τ] |
合格,It is safe |
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| 4 |
轴耳与筒节连接角焊缝强度校核 Checking strength of welds of trunnion to shell |
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焊缝底部的外径 Outside diameter of root of weld |
DO1=DO+2a= |
462 |
mm |
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焊缝根部的内外径比值Ratio of inside to outside diameter of weld root |
α1=DO/DO1= |
0.92 |
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焊缝根部的截面积 Sectional area of weld root |
A1=π×(DO1-a)×a= |
25107.61 |
mm2 |
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焊缝根部的惯性矩 Moment of inertia of weld root |
J1=π×DO14×(1-α14)/64= |
6.20E+08 |
mm4 |
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焊缝根部的断面模数 Section modulus of weld root |
W1=J1/(0.5DO1)= |
2.68E+06 |
mm3 |
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弯矩 Bending moment |
M1=Fv×(L+S')= |
1.50E+08 |
N.mm |
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焊缝的拉伸应力 Tensile stress of weld |
σwt=Fh/A1= |
6.05 |
Mpa |
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焊缝的弯曲应力 Bending stress of weld |
σwb=M1/W1 |
55.75 |
Mpa |
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焊缝的组合应力 Combined stress in weld |
σw=σwt+σwb= |
61.80 |
Mpa |
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σw |
≤ |
[σ] |
合格,It is safe |
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焊缝的剪切应力 Shear stress of weld |
τw =Fv/A1= |
22.56 |
MPa |
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组合应力 Combined stress |
σwc=sqrt(σw+τw)= |
65.79 |
MPa |
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σwc |
≤ |
[σ] |
合格,It is safe |
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