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项目号 ITEM NO. |
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Strength Check of Tailing Lug and Base Plate
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文件号 DOC. NO. |
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说明: |
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1. 本计算程序适用于与裙座筒体、底板和盖板圈相连接的尾部吊耳以及底板、盖板圈和相互间连接焊缝的强度校核。 |
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2. 黄色色单元格内的数据是需要输入的。 |
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3. 尾部吊耳与裙座筒体间的连接焊缝为全焊透焊缝加角焊缝，与底板及盖板圈之间采用角焊缝连接，所有角焊缝的焊脚高度为"a". |
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NOTES: |
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1. This calculation template is applicable to the strength check of tailing lug that is attached to skirt shell, base plate and top ring, and the strength check of the base plate, top ring and the welds attaching the tailing lug to the skirt shell, base plate and top ring. |
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2. The data in light blue cells shall be inputted. |
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3. The tailing lug is attached to the skirt shell by a penetration weld plus fillet welds, and attached to the base plate and top ring by fillet welds. The leg dimension of all the fillet welds is "a". |
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| 说明： |
尾部吊耳与裙座筒体间的连接焊缝为全焊透焊缝加角焊缝，与底板及盖板圈之间采用角焊缝连接，所有 |
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角焊缝的焊脚高度为"a". |
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| Note: |
The tailing lug is attached to skirt shell by a penetration weld plus fillet welds, and |
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载荷变化如下图： |
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attached to base plate and top ring by fillet welds. The leg dimension of all the fillet |
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welds is "a". |
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| 1. 输入数据 Input Data |
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| 设备质量 Weight of equipment |
W= |
62000 |
kg |
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| 综合影响系数 Dynamic factor |
k= |
1.65 |
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| 吊耳至设备质心的轴向距离 |
L1= |
11000 |
mm |
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| Axial distance from lifting lug to C.G of equipment |
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| 尾部吊耳孔中心至设备质心的轴向距离 |
L2= |
12000 |
mm |
| Axial distance from pin hole center of tailing lug to C.G of equipment |
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| 尾部吊耳孔中心至设备轴线的距离 |
L3= |
1400 |
mm |
| Distance from pin hole center of tailing lug to the axis of equipment |
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| 裙座底板的内径 Inside diameter of skirt base plate |
Di= |
2280 |
mm |
| 裙座底板的外径 Outside diameter of skirt base plate |
Do= |
2900 |
mm |
| 底板的有效厚度 Effective thickness of base plate |
Tb= |
29.7 |
mm |
| 盖板圈的外径 Outside diamter of top ring |
Dr= |
2980 |
mm |
| 盖板圈的有效厚度 Effective thickness of top ring |
Tr= |
29.7 |
mm |
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角度 |
0 |
10 |
20 |
30 |
40 |
50 |
60 |
70 |
80 |
85 |
| 裙座筒体的外径 Outside diameter of skirt shell |
Dsk= |
2700 |
mm |
系列1 |
σ |
48.9 |
72.8 |
93.9 |
111.7 |
125.2 |
134.0 |
136.9 |
132.3 |
113.6 |
88.6 |
| 裙座筒体的有效厚度 Effective thickness of skirt shell |
Tsk= |
11.7 |
mm |
系列2 |
τ |
63.03 |
62.36 |
61.67 |
60.89 |
59.97 |
58.77 |
57.02 |
54.00 |
46.86 |
37.17 |
| 吊耳的宽度 Width of tailing lug |
A= |
250 |
mm |
系列3 |
σp |
74.58 |
73.79 |
72.97 |
72.05 |
70.96 |
69.54 |
67.47 |
63.90 |
55.44 |
43.98 |
| 吊耳的有效厚度 Effective thickness of tailing lug |
Tt= |
39.7 |
mm |
系列4 |
τw |
18.26 |
32.51 |
46.92 |
59.92 |
70.79 |
78.89 |
83.53 |
83.36 |
73.86 |
58.54 |
| 尾部吊耳孔中心至裙座筒体外表面的距离 |
Lt= |
225 |
mm |
系列5 |
σ1 |
39.96 |
50.99 |
60.21 |
67.32 |
72.03 |
74.05 |
73.03 |
68.18 |
56.51 |
43.26 |
| Distance from pin hole center of tailing lug to skirt outside surface |
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系列6 |
σ2 |
-87.11 |
-101 |
-111.5 |
-118.2 |
-120.9 |
-119.3 |
-113 |
-101.1 |
-79.9787 |
-59.6332 |
| 吊耳孔直径 Pin hole diameter of lug |
D1= |
110 |
mm |
系列7 |
σ3 |
56.362 |
11.53 |
-32.68 |
-74.82 |
-113.4 |
-146.6 |
-172.3 |
-186.8 |
-177.598 |
-145.456 |
| 吊耳孔衬板的直径 Diameter of pin hole pad |
Dp= |
220 |
mm |
| 吊耳孔衬板的有效厚度 Effective thickness of pin hole pad |
Tp= |
9.7 |
mm |
| 吊耳材料 material of tailing lug |
Q345R |
| 裙座底板和盖板的材料 Material of base plate and top ring |
Q345R |
| 吊耳孔衬板材料 material of pin hole pad |
Q345R |
| 吊耳材料的屈服强度 Yield strength of lug material |
Syt= |
305 |
Mpa |
| 底板材料的屈服强度 Yield strength of base plate |
Syb= |
325 |
Mpa |
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| 盖板圈材料的屈服强度 Yield strength of top ring |
Syr= |
325 |
Mpa |
| 吊耳与裙座间连接焊缝的焊脚高度 |
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a= |
24 |
mm |
| Leg size of welds attaching tailing lug to skirt support |
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| 承载点数（见下图，输入1或2）Number of load point (input 1 or 2 ) |
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2 |
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| 如果承载点数为2,请输入以下数据: Input following data if number of load is 2: |
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| 支撑管的外径 Outside diameter of stay pipe |
Dso= |
168 |
mm |
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| 支撑管的有效厚度 Effective thickness of stay pipe |
Ts= |
9 |
mm |
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| 支撑管材料 Material of stay pipe |
20 |
| 支撑管材料的屈服强度 Yield strength of stay pipe material |
Sys= |
245 |
Mpa |
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| 一点承载（无拉撑件） |
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两点承载（即设置了拉撑件） |
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| 2. 计算 Calculation |
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| (1) 载荷与许用应力 Load and allowable stresses |
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| 垂直起吊总载荷 Total vertical lifting load |
WL=f*W*9.81 |
1013793 |
N |
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L=L1+L2 |
23000 |
mm |
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| 尾部吊耳的垂直起吊载荷 Vertical lifting load of tailing lug |
T=WL*cosθ*L1/(cosθ*L+sinθ*L3) |
见表1 See table 1 |
| 起吊载荷T的径向分量 Radial component of lifting load T |
fr=Tcosθ |
见表1 See table 1 |
| 起吊载荷T的径向分量 Longitudinal component of lifting load T |
fl=Tsinθ |
见表1 See table 1 |
| 吊耳的许用拉伸应力 Allowable tensile stress of lug |
［σ］t=Syt/1.5 |
203.333 |
Mpa |
| 吊耳的许用剪切应力 Allowable shear stress of lug |
［τ］=0.6［σ］t |
122 |
Mpa |
| 吊耳的许用挤压应力 Allowable bearing stress of lug |
［σp］=0.9Syt |
274.5 |
Mpa |
| 焊缝的许用剪切应力 Allowable shear stress of welds |
［τw］=0.7*［τ］ |
85.4 |
Mpa |
| 底板材料的许用应力 Allowable stress of base plate |
［σ］b=Syb/1.5 |
216.667 |
Mpa |
| 盖板圈材料的许用应力 Allowable stress top ring |
［σ］r=Syr/1.5 |
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216.667 |
Mpa |
| (2) 尾部吊耳的强度校核 Strength check of tailing lug |
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| 吊耳的横截面积 Cross sectional area of tailing lug |
Al=A*Tt |
9925 |
mm2 |
| 吊耳的拉伸应力 Tensile stress of tailing lug |
σt=fr/Al |
见表1 See table 1 |
| 尺寸E Dimension E |
E=MAX(Lt-(Do-Dsk)/2,Lt-(Dc-Dsk)/2) |
125 |
mm |
| 作用在吊耳上的弯矩 Bending moment on tailing lug |
M=fl*E |
见表1 See table 1 |
| 吊耳的抗弯断面模数 Section modulus of tailing lug |
Z=Tt*A2/6 |
413542 |
mm3 |
| 吊耳的弯曲应力 Bending stress of tailing lug |
σb=M/Z |
见表1 See table 1 |
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σ=σt+σb |
见表2 See table 2 |
| 吊耳孔处的横截面积 Cross sectional area at pin hole of lug |
At=(A-D1)*Tt+2(Dp-D1)*Tp |
7692 |
mm2 |
| 吊耳孔处的剪切应力 Shear stress at pin hole |
τ=T/At |
见表2 See table 2 |
| 吊耳孔处抗挤压的有效面积 Avaiable area at pin hole for bearing |
Ap=D1*(Tt+2Tp) |
6501 |
mm2 |
| 吊耳孔处的挤压应力 Bearing stress at pin hole |
σp=T/Ap |
见表2 See table 2 |
| (2) 尾吊与裙座连接焊缝的强度校核 Strength check of welds attaching tailing lug to skirt |
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Wb=(Do-Dsk)/2 |
100 |
mm |
| 盖板圈的宽度 Width of cover ring |
Wr=(Dr-Dsk)/2 |
140 |
mm |
| 连接焊缝的面积 Area of welds attaching lug to skirt |
Aw=2*(A+Wb+Wr)*0.707*a+A*Tt |
26553.6 |
mm2 |
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B=MIN(Wb,Wr) |
100 |
mm |
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Nt=B2/(A+2B) |
22.2222 |
mm |
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Mw=fl*(Lt-Nt) |
见表1 See table 1 |
| 单位宽度焊缝的极惯性矩 Polor moment of inertia |
Jw=(A+2B)3/12-B2(A+B)2/(A+2B) |
4871528 |
mm3 |
| fl引起的横向剪应力 Transverse shear stress due to fl |
f1=fl/Aw |
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见表1 See table 1 |
| Mw引起的横向剪应力 Transverse shear stress due to Mw |
f2=Mw*(B-Nt)/(Jw*2*0.707*a) |
见表1 See table 1 |
| fr引起的径向剪应力 Radial shear stress due to fr |
f3=fr/Aw |
见表1 See table 1 |
| Mw引起的径向剪应力 Radial shear stress due to Mw |
f4=0.5*Mw*A/(Jw*2*0.707*a) |
见表1 See table 1 |
| 尾部吊耳与裙座连接焊缝的剪应力 Shear stress of welds attaching tailing lug to skirt |
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见表2 See table 2 |
| (3) 裙座底板和盖板圈的强度校核 Strength Check of Base Plate and top ring |
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| ① 起吊载荷的径向分量所产生的应力 Stress caused by radial component of lifting load |
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| 系数 Coefficient |
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Kr= |
0.0795 |
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| 系数 Coefficient |
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Kt= |
-0.2387 |
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| 底板宽度 Width of base plate |
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Wb=(Do-Di)/2 |
310 |
mm |
| 底板的横截面积 Cross sectional area of base plate |
A1=Wb*Tb |
9207 |
mm2 |
| 面积A1的形心至底板外表面的距离 Distance from centroid of area A1 to outside surface of base plate |
Y1=Wb/2 |
155 |
mm |
| 底板的惯性矩 Moment of inertia of base plate |
I1=Tb*Wb3/12 |
7.4E+07 |
mm4 |
| 裙座筒体的平均半径 Mean radius of skirt shell |
Rms=(Dsk-Tsk)/2 |
1344.15 |
mm |
| 裙座筒体的有效长度 Effective length of skirt shell |
Le=W+Tr+0.5*SQR(Rms*Tsk) |
342.403 |
mm |
| 裙座筒体有效段的横截面积 Cross sectional area of effective skirt shell |
A2=Tsk*Le |
4006.11 |
mm2 |
| 面积A2的形心至底板外表面的距离 Distance from centroid of area A2 to outside surface of base plate |
y2=(Do-Dsk)/2+tsk/2 |
105.85 |
mm |
| 裙座筒体有效段的惯性矩 Moment of inertia of skirt shell |
I2=Le*Tsk3/12 |
45699.7 |
mm4 |
| 盖板圈的横截面积 Cross sectional of top ring |
A3=Tr*Wr |
4158 |
mm2 |
| 面积A3的形心至底板外表面的距离 Distance from centroid of area A3 to outside surface of base plate |
Y3=Do/2-(Dr/2-Wr/2) |
30 |
mm |
| 盖板圈的惯性矩 Moment of inertia of top ring |
I3=Tr*Wr3/12 |
6791400 |
mm4 |
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ΣAY=A1*Y1+A2*Y2+A3*Y3 |
1975872 |
mm3 |
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ΣAY2=A1*Y12+A2*Y22+A3*Y32 |
2.7E+08 |
mm4 |
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ΣA=A1+A2+A3 |
17371.1 |
mm2 |
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ΣI=I1+I2+I3 |
8.1E+07 |
mm4 |
| 面积ΣA的形心至底板外表面的距离 Distance from centroid of ΣA to outside surface of base plate |
C1=ΣAY/ΣA |
113.745 |
mm |
| 面积ΣA的形心至底板内表面的距离 Distance from centroid of ΣA to inside surface of base plate |
C2=Wb-C1 |
196.255 |
mm |
| 面积ΣA的形心至盖板圈外表面的距离 Distance from centroid of ΣA to outside surface of top ring |
C3=C1+(Dr/2-Do/2) |
153.745 |
mm |
| 组合惯性矩 Moment of inertia of ΣA |
I=ΣAY2+ΣI-C1*ΣAY |
1.3E+08 |
mm4 |
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R=Do/2-C1 |
1336.26 |
mm |
| 内力矩 Internal moment |
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Mb1=Kr*fr*R |
见表1 See table 1 |
| 周向内力 Internal circumferential force |
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F1=Kt*fr |
见表1 See table 1 |
| 底板外表面的应力 Stress at outside surface of base plate |
σ11=Mb1*C1/I+F1/ΣA |
见表1 See table 1 |
| 底板内表面的应力 Stress at inside surface of base plate |
σ21=-Mb1*C2/I+F1/ΣA |
见表1 See table 1 |
| 盖板圈外表面的应力 Stress at outside surface of top ring |
σ31=Mb1*C3/I+F1/ΣA |
见表1 See table 1 |
| ②起吊载荷的轴向分量所引起的应力 Stress caused by longitudinal component of lifting load |
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| fl 产生的弯矩 Bending moment caused by fl |
Ml=fl*Lt |
见表1 See table 1 |
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h=A+(Tb+Tr)/2 |
279.7 |
mm |
| 由Ml所引起的径向力 Radial force caused by Ml |
f=Ml/h |
见表1 See table 1 |
| a) 底板中的应力 Stress in base plate |
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| 底板的横截面积 Cross sectional area of base plate |
A1= |
9207 |
mm2 |
| 面积A1的形心至底板外表面的距离 Distance from centroid of area A1 to outside surface of base plate |
Y1= |
155 |
mm |
| 底板的惯性矩 Moment of inertia of base plate |
I1= |
7.4E+07 |
mm4 |
| 裙座筒体的有效长度 Effective length of skirt shell |
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97.8163 |
mm |
| 裙座筒体有效段的横截面积 Cross sectional area of effective skirt shell adjacent to base plate |
A21=Le1*Tsk |
1144.45 |
mm2 |
| 面积A21的形心至底板外表面的距离 Distance from centroid of area A21 to outside surface of base plate |
Y21= |
105.85 |
mm |
| 裙座筒体有效段的惯性矩 Moment of inertia of skirt shell |
I21=Le1*Tsk3/12 |
13055.3 |
mm4 |
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ΣA=A1+A21 |
10351.5 |
mm2 |
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ΣAY=A1*Y1+A21*Y21 |
1548225 |
mm3 |
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ΣAY2=A1*Y12+A21*Y212 |
2.3E+08 |
mm4 |
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ΣI=I1+I21 |
7.4E+07 |
mm4 |
| 面积ΣA的形心至底板外表面的距离 Distance from centroid of ΣA to outside surface of base plate |
C1=ΣAY/ΣA |
149.566 |
mm |
| 面积ΣA的形心至底板内表面的距离 Distance from centroid of ΣA to inside surface of base plate |
C2=Wb-C1 |
160.434 |
mm |
| 组合惯性矩 Moment of inertia of ΣA |
I=ΣAY2+ΣI-C1*ΣAY |
7.6E+07 |
mm4 |
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R=Do/2-C1 |
1300.43 |
mm |
| 内力矩 Internal moment |
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Mb2=Kr*f*R |
见表1 See table 1 |
| 周向内力 Internal circumferential force |
F2=Kt*f |
见表1 See table 1 |
| 底板外表面的应力 Stress at outside surface of base plate |
σ12=Mb2*C1/I+F2/ΣA |
见表1 See table 1 |
| 底板内表面的应力 Stress at inside surface of base plate |
σ22=-Mb2*C2/I+F2/ΣA |
见表1 See table 1 |
| 底板外表面的组合应力 Combined stress at outside surface of base plate |
σ1=σ11+σ12 |
见表2 See table 2 |
| 底板内表面的组合应力 Combined stress at inside surface of base plate |
σ2=σ21+σ22 |
见表2 See table 2 |
| b) 盖板圈的应力 Stress in top ring |
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| 盖板圈的横截面积 Cross sectional of top ring |
A3= |
4158 |
mm2 |
| 面积A3的形心至底盖板圈外表面的距离 Distance from centroid of area A3 to outside surface of top ring |
Y32=Wr/2 |
70 |
mm |
| 盖板圈的惯性矩 Moment of inertia of top ring |
I3= |
6791400 |
mm3 |
| 裙座筒体的有效长度 Effective length of skirt shell |
Le2=2*Le1+Tr |
225.333 |
mm |
| 裙座筒体有效段的横截面积 Cross sectional area of effective skirt shell adjacent to base plate |
A22=Le2*Tsk |
2636.39 |
mm2 |
| 面积A22的形心至盖板圈外表面的距离 Distance from centroid of area A22 to outside surface of top ring |
Y22=Wr+Tsk/2 |
145.85 |
mm |
| 裙座筒体有效段的惯性矩 Moment of inertia of skirt shell |
I22=Le2*Tsk3/12 |
30074.6 |
mm4 |
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ΣA=A3+A22 |
6794.39 |
mm2 |
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ΣAY=A3*Y32+A22*Y22 |
675578 |
mm3 |
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ΣAY2=A3*Y322+A22*Y222 |
7.6E+07 |
mm4 |
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ΣI=I3+I22 |
6821475 |
mm4 |
| 面积ΣA的形心至盖板圈外表面的距离 Distance from centroid of ΣA to outside surface of top ring |
C12=ΣAY/ΣA |
99.4317 |
mm |
| 面积ΣA的形心至裙座筒体内表面的距离 Distance from centroid of ΣA to inside surface of skirt shell |
C22=Wr+Tsk-C2 |
52.2683 |
mm |
| 组合惯性矩 Moment of inertia of ΣA |
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I=ΣAY2+ΣI-C12*ΣAY |
1.6E+07 |
mm4 |
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R=Dr/2-C12 |
1390.57 |
mm |
| 内力矩 Internal moment |
Mb3=-Kr*f*R |
见表1 See table 1 |
| 周向内力 Internal circumferential force |
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F3=-Kt*f |
见表1 See table 1 |
| 盖板圈外表面的应力 Stress at outside surface of top ring |
σ32=Mb3*C12/I+F3/ΣA |
见表1 See table 1 |
| 盖板圈外表面的组合应力 Combined stress at outside surface of top ring |
σ3=σ31+σ32 |
见表2 See table 2 |
| (4) 支撑管强度校核 Strength check of stay pipe (注: 只有在采用拉撑管时,才进行此项计算。Note: this part of cauculation shall be done only where a stay pipe is used.) |
| 尾部吊耳的最大垂直起吊载荷 Maximum vertical lifting load of tailing lug |
T'=WL*L1/L |
484858 |
N |
| 支撑管的拉伸载荷 Tensile load acting on stay pipe |
Fs=0.5*T' |
242429 |
N |
| 支撑管的横截面积 Cross sectional area of stay pipe |
As=π*(Ds02-(Dso-2Ts)2)/4 |
4495.62 |
mm2 |
| 支撑管的拉伸应力 Tensile stress in stay pipe |
σs=Fs/As |
53.9256 |
Mpa |
| 支撑管材料的许用应力 Allowable stress of stay pipe material |
［σ］s=Sys/1.6 |
153.125 |
Mpa |
| 表1 Table 1 |
| θ(deg) |
0 |
10 |
20 |
30 |
40 |
50 |
60 |
70 |
80 |
85 |
| T(N) |
484857.5 |
479708.8 |
474348.5 |
468396.6 |
461296.5 |
452064.1 |
438614.7 |
415388.8 |
360433 |
285926.4 |
| fr(N) |
484857.5 |
472421 |
445741.8 |
405643.4 |
353373.6 |
290581.2 |
219307.4 |
142071.3 |
62588.53 |
24920.13 |
| fl(N) |
0 |
83300.56 |
162236.7 |
234198.3 |
296515.7 |
346301.2 |
379851.5 |
390337.8 |
354957.2 |
284838.4 |
| M(N.mm) |
0 |
10412571 |
20279591 |
29274789 |
37064460 |
43287649 |
47481437 |
48792227 |
44369652 |
35604797 |
| σt(Mpa) |
48.85 |
47.60 |
44.91 |
40.87 |
35.60 |
29.28 |
22.10 |
14.31 |
6.31 |
2.51 |
| σb(Mpa) |
0.00 |
25.18 |
49.04 |
70.79 |
89.63 |
104.68 |
114.82 |
117.99 |
107.29 |
86.10 |
| Mw (N.mm) |
0 |
16891503 |
32898004 |
47490214 |
60126791 |
70222187 |
77025443 |
79151835 |
71977435 |
57758894 |
| f1(Mpa) |
0 |
3.137068 |
6.109774 |
8.81982 |
11.16667 |
13.04157 |
14.30506 |
14.69997 |
13.36755 |
10.72691 |
| f2(Mpa) |
0 |
7.946905 |
15.47744 |
22.34261 |
28.28771 |
33.03726 |
36.23797 |
37.23837 |
33.86305 |
27.17369 |
| f3(Mpa) |
18.25955 |
17.79119 |
16.78647 |
15.27638 |
13.30792 |
10.94318 |
8.259032 |
5.350353 |
2.35706 |
0.938483 |
| f4(Mpa) |
0 |
12.77181 |
24.87446 |
35.90776 |
45.46238 |
53.0956 |
58.2396 |
59.84738 |
54.42276 |
43.672 |
| Mb1 (N.mm) |
51507528 |
50186365 |
47352170 |
43092428 |
37539692 |
30869109 |
23297525 |
15092565 |
6648924 |
2647323 |
| F1(N) |
-115735 |
-112767 |
-106399 |
-96827.1 |
-84350.3 |
-69361.7 |
-52348.7 |
-33912.4 |
-14939.9 |
-5948.43 |
| σ11(Mpa) |
39.96446 |
38.93937 |
36.74033 |
33.43522 |
29.12688 |
23.9512 |
18.07644 |
11.71025 |
5.158869 |
2.054045 |
| σ21(Mpa) |
-87.1128 |
-84.8784 |
-80.085 |
-72.8806 |
-63.4895 |
-52.2078 |
-39.4023 |
-25.5255 |
-11.2451 |
-4.47732 |
| σ31(Mpa) |
56.36152 |
54.91585 |
51.81457 |
47.15339 |
41.07738 |
33.77817 |
25.49305 |
16.51487 |
7.275508 |
2.896802 |
| Ml(N.mm) |
0 |
18742627 |
36503265 |
52694621 |
66716029 |
77917769 |
85466587 |
87826008 |
79865373 |
64088635 |
| f(N) |
0 |
67009.75 |
130508.6 |
188396.9 |
238527.1 |
278576.2 |
305565.2 |
314000.7 |
285539.4 |
229133.5 |
| Mb2 (N.mm) |
0 |
6927770 |
13492570 |
19477323 |
24660005 |
28800464 |
31590707 |
32462811 |
29520350 |
23688851 |
| f2(N) |
0 |
-15995.2 |
-31152.4 |
-44970.3 |
-56936.4 |
-66496.1 |
-72938.4 |
-74952 |
-68158.3 |
-54694.2 |
| σ12(Mpa) |
0 |
12.05181 |
23.47219 |
33.8835 |
42.89949 |
50.10239 |
54.9564 |
56.47355 |
51.35473 |
41.21003 |
| σ22(Mpa) |
0 |
-16.1303 |
-31.4154 |
-45.35 |
-57.4171 |
-67.0575 |
-73.5541 |
-75.5847 |
-68.7336 |
-55.1559 |
| Mb3 (N.mm) |
0 |
-7407940 |
-1.4E+07 |
-2.1E+07 |
-2.6E+07 |
-3.1E+07 |
-3.4E+07 |
-3.5E+07 |
-3.2E+07 |
-2.5E+07 |
| F3(N) |
0 |
15995.23 |
31152.41 |
44970.35 |
56936.42 |
66496.14 |
72938.41 |
74951.98 |
68158.26 |
54694.16 |
| σ32(Mpa) |
0 |
-43.3857 |
-84.4982 |
-121.978 |
-154.435 |
-180.365 |
-197.839 |
-203.301 |
-184.873 |
-148.353 |
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| 表2 应力计算结果 |
|
| Table 2 Stress Calculation Results |
|
| θ(deg) |
0 |
10 |
20 |
30 |
40 |
50 |
60 |
70 |
80 |
85 |
| σ(Mpa) |
48.85 |
72.78 |
93.95 |
111.66 |
125.23 |
133.95 |
136.91 |
132.30 |
113.60 |
88.61 |
| ［σ］t(Mpa) |
|
|
|
|
203.33 |
|
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|
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|
|
σ<［σ］t, 合格， Acceptable. |
| τ(Mpa) |
63.03 |
62.36 |
61.67 |
60.89 |
59.97 |
58.77 |
57.02 |
54.00 |
46.86 |
37.17 |
| ［τ］(Mpa) |
|
|
122.00 |
|
|
τ<［τ］, 合格， Acceptable. |
| σp(Mpa) |
74.58 |
73.79 |
72.97 |
72.05 |
70.96 |
69.54 |
67.47 |
63.90 |
55.44 |
43.98 |
| ［σp］ |
|
274.50 |
|
|
σp<［σp］, 合格， Acceptable. |
| τw |
18.26 |
32.51 |
46.92 |
59.92 |
70.79 |
78.89 |
83.53 |
83.36 |
73.86 |
58.54 |
| ［τw］ |
|
85.40 |
|
|
τw<［τw］, 合格， Acceptable. |
|
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|
| σ1(Mpa) |
39.96 |
50.99 |
60.21 |
67.32 |
72.03 |
74.05 |
73.03 |
68.18 |
56.51 |
43.26 |
| σ2(Mpa) |
-87.113 |
-101.01 |
-111.5 |
-118.23 |
-120.91 |
-119.27 |
-112.96 |
-101.11 |
-79.979 |
-59.633 |
| ［σ］b |
|
216.67 |
|
|
σ1<［σ］b, 合格, Acceptable. |
|
｜σ2｜<［σ］b, 合格， Acceptable. |
| σ3(Mpa) |
56.3615 |
11.5302 |
-32.684 |
-74.825 |
-113.36 |
-146.59 |
-172.35 |
-186.79 |
-177.6 |
-145.46 |
| ［σ］r |
|
216.67 |
|
|
|
|
｜σ3｜<［σ］r, 合格， Acceptable. |
|
|
| σs |
53.93 |
σs<［σ］s, 合格， Acceptable. |
|
|
| ［σ］s |
153.13 |
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| 表中 Where |
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|
| θ— |
设备轴线与水平面的夹角 Included angle between equipment axis and horizontal plane |
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| σ— |
尾部吊耳拉伸应力与弯曲应力之和 Sum of tensile stress and bending stress of tailing lug |
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［σ］t—
|
尾部吊耳的许用拉伸应力 Allowable tensile stress of tailing lug |
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| τ— |
吊耳孔截面处的剪应力 Shear stress at cross section of pin hole |
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［τ］—
|
尾部吊耳的许用剪切应力 Allowable shear stress of tailing lug |
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σp—
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吊耳孔处的挤压应力 Bearing stress at pin hole |
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［σp］—
|
尾部吊耳的许用挤压应力 Allowable bearing stress of tailing lug |
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|
τw—
|
尾部吊耳与裙座连接焊缝的剪应力 Shear stress of welds attaching tailing lug to skirt |
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［τw］—
|
焊缝的许用剪切应力 Allowable shear stress of welds |
|
| σ1— |
底板外圆表面的应力 Stress at outside surface of base plate |
|
| σ2— |
底板内圆表面的应力 Stress at inside surface of base plate |
|
|
［σ］b—
|
底板的许用应力 Allowable stress of base plate |
|
| σ3— |
盖板圈外圆表面的应力 Stress at outside surface of top ring |
|
|
［σ］r—
|
盖板圈的许用应力 Allowable stress of top ring |
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σs—
|
拉撑管的拉伸应力 Tensile stress in stay pipe |
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［σ］s—
|
拉撑管材料的许用应力 Allowable stress of stay pipe material |
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