|
非对称双鞍座容器计算 |
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Calculation of a Vessel on Two Saddles
|
文件号 DOC. NO. |
|
|
|
| 计算压力 Calculation pressure |
|
Pc=
|
0.6 |
Mpa |
说明： |
| 设计温度 Design temperature |
|
|
150 |
℃ |
(1) 本计算程序适用于支承在两个非对称布置鞍座上的卧式容器。本计算程序未包括风 |
| 液压试验压力 Hydrostatic test pressure |
|
Pt= |
0.75 |
Mpa |
载荷和地震载荷作用下鞍座的强度校核。 |
|
| 容器内径 Inside diameter of vessel |
|
Di= |
1200 |
mm |
|
(2) 浅蓝色单元格内的内容是需要输入的，并应确保输入数据的正确性。 |
|
| 筒体名义厚度 Nominal wall thickness of shell |
|
δn= |
12 |
mm |
(3) 只有当容器在鞍座平面或靠近鞍座处设置加强圈时，才需要对J44至J54的单元格的 |
| 封头名义厚度 Nominal wall thickness of head |
|
δH=
|
12 |
mm |
数据进行输入，不设加强圈时，这些单元格应为空白。 |
| 筒体的有效厚度 Effective thickness of shell |
|
δe=
|
10.7 |
mm |
| 封头的有效厚度 Effective thickness of head |
|
δhe=
|
9.4 |
mm |
| 筒体内半径 Inside diameter of shell |
|
Ri=
|
600 |
mm |
| 筒体平均半径 Mean diameter of shell |
|
Rm=Ri+0.5δn= |
606 |
mm |
| 筒体长度（切线至切线) Length of shell (T.L to T.L) |
L= |
9500 |
mm |
| 封头内壁曲面深度 Depth of curved surface of head |
|
H= |
300 |
mm |
| A支座的中心线到近端部封头切线的距离 Diatance from center line of support A to nearest head's tangent line |
A1=
|
1500 |
mm |
| B支座的中心线到近端部封头切线的距离 Diatance from center line of support B to nearest head's tangent line |
A2=
|
2000 |
|
| 容器操作时的总重量 Total weight of vessel at operating condition |
W= |
20000 |
kg |
| 容器液压试验时的总重量 Total weight of vessel at hydrostatic test condition |
Wt=
|
30000 |
kg |
| 鞍座垫板底面至底板底面之间的距离 Distance from bottom of support pad to bottom of base plate |
Ls= |
192 |
mm |
| 鞍座包角 Saddle included angle |
θ= |
120 |
° |
| 鞍座垫板的包角 Included angle of saddle pad |
θ'= |
132 |
° |
| 鞍座垫板有效厚度 Effictive thickness of saddle pad |
δPe=
|
7.2 |
mm |
| 鞍座垫板的宽度 Width of saddle pad |
|
Bp= |
350 |
mm |
| 鞍座腹板的有效厚度 Effective thickness of web |
bo= |
9.2 |
mm |
| 支座的轴向宽度 Axial width of supports |
|
b= |
210 |
mm |
| 圆筒有效宽度 Effective width of shell |
b2=b+1.56×（Rmδn）0.5= |
343.03 |
mm |
| 筒体和封头的材料 Material of shell and head |
Q345R |
|
|
| 设计温度下筒体材料的许用应力 Allowable stress of shell material at design temperature |
[σ]t=
|
170 |
Mpa |
| 设计温度下封头材料的许用应力 Allowable stress of head material at design temperature |
[σ]ht=
|
170 |
Mpa |
| 容器材料在设计温度的轴向许用压缩应力 Allowable axial compressive stress of vessel material at design temperature |
[σ]crt=
|
140 |
Mpa |
| 容器材料在常温的轴向许用压缩应力 Allowable axial compressive stress of vessel material at ambient temperature |
[σ]cr=
|
155 |
Mpa |
| 筒体材料常温屈服强度 Yield strength of shell material at ambient temperature. |
ReL=
|
345 |
Mpa |
| 鞍座腹板材料 Web material |
Q235-B |
|
| 鞍座腹板的许用应力 Allowable stress of web material |
[σ]sa=
|
147 |
Mpa |
| 容器的焊接接头系数 joint efficiency of vessel |
|
Φ= |
0.85 |
|
| 系数 Coefficient |
|
|
|
k= |
0.1 |
|
|
注:
|
容器不焊在鞍座上时取k=1，容器焊在鞍座上时取k=0.1 |
|
| Note: |
If the vessel isn't welded on the saddle support,then k=1;if not,k=0.1 |
|
| 鞍座是否设置加强圈？请输入“YES”或“NO”。 Are stiffening rings used? Input "YES" or "NO". |
NO |
|
| 如果鞍座设置加强圈，请输入以下数据。 Input the following data if the saddle has stiffening ring(s). |
| 加强圈的位置：在鞍座平面上时输入“1”，靠近鞍座时输入“2”。 Location of stiffening ging(s): input "1" if the ring is in the plane of saddle, and "2" if it is adjacent to the saddle. |
|
|
 |
|
| 加强圈的材料 Material of stiffening ring |
|
|
|
| 加强圈材料的许用应力 Allowable stress of stiffening ring material |
[σ]rt= |
|
Mpa |
| 加强圈与圆筒有效段的组合截面积 Area of composite section |
|
Ao=
|
|
mm2 |
| 组合截面对X-X轴的惯性矩 Moment of inertia of composite section |
Io=
|
|
mm4 |
| 尺寸d （见下图） Dimension d (see sketch below) |
|
d=
|
|
mm |
| 尺寸e （见下图） Dimension e (see sketch below) |
|
e=
|
|
mm |
| 由JB/T4731查得系数C4 Coefficient C4 from JB/T4731 |
|
C4=
|
|
|
| 由JB/T4731查得系数C5 Coefficient C5 from JB/T4731 |
|
C5=
|
|
|
| 由JB/T4731查得系数K7 Coefficient K7 from JB/T4731 |
|
K7=
|
|
|
| 由JB/T4731查得系数K8 Coefficient K8 from JB/T4731 |
|
K8=
|
|
|
|
|
 |
|
|
|
|
|
|
|
|
|
|
|
| 1.支座反力计算 calculation of reactor force on the support |
|
|
| 操作工况 Operating condition |
|
|
| 单位长度重量均布载荷 Uniform load per unit length due to the total weight of equipment |
q=9.81*W/(L+4H/3) |
19.82 |
N/mm |
| A支座的反力 Reaction of support A |
FA=q(L-2A2)(L/2+2H/3)/(L-A1-A2) |
89925 |
N |
|
| B支座的反力 Reaction of support B |
FB=q(L-2A1)(L/2+2H/3)/(L-A1-A2) |
106275 |
N |
|
|
| 2.筒体轴向弯矩计算 calculation of shell longitudinal moment |
|
| (1) 操作工况 Operating condition |
|
| A支座处弯矩 Moment at support A |
MA=q(Ri2/4-H2/4-2H*A1/3-A12/2) |
-26903182 |
N.mm |
| B支座处弯矩 Moment at support B |
MB=q(Ri2/4-H2/4-2H*A2/3-A22/2) |
-46225909 |
N.mm |
|
X=FA/q-A1-2H/3 |
|
2837.50 |
mm |
| 支座A、B间的弯矩 Moment between supports A and B |
MAB=MA+qX2/2 |
52878935 |
N.mm |
|
| (2) 液压试验工况 Hydrostatic test condition |
|
|
| 单位长度重量均布载荷 Uniform load per unit length due to the total weight of equipment |
qT=9.81*Wt/(L+4H/3) |
29.73 |
N.mm |
|
| A支座处弯矩 Moment at support A |
MTA=qT(Ri2/4-H2/4-2H*A1/3-A12/2) |
-40354773 |
N.mm |
|
| B支座处弯矩 Moment at support B |
MTB=qT(Ri2/4-H2/4-2H*A2/3-A22/2) |
-69338864 |
N.mm |
|
| 支座A、B间的弯矩 Moment between supports A and B |
MTAB=MTA+qT*X2/2 |
79318402 |
N.mm |
|
|
|
| 3.筒体轴向应力计算 calculation of longitudinal stress in the shell |
|
|
| (1) 操作工况 Operating condition |
|
|
| 1）支座A与B之间的横截面上 Cross-section between supports A and B |
|
| 最高点 The highest point |
|
σ1AB=PcRm/(2δe)-MAB/(πRm2δe) |
12.71 |
Mpa |
|
| 最低点 the lowest point |
|
σ2AB=PcRm/(2δe)+MAB/(πRm2δe) |
21.27 |
Mpa |
|
| 2）A支座横截面上 Cross-section at support A |
|
 |
|
|
A1/Rm= |
|
2.475 |
|
|
| 筒体被加强的最高点或筒体不被加强的靠近中间水平平面处 the toppest point of the reinforced shell or the point close to the middle hotizontal plane of the un-reinforced shell |
|
| 查JB/T4731，得系数K1= Refer to JB/T4731, coefficient K1= |
|
0.107 |
|
|
|
σ3A=PcRm/(2δe)-MA/(K1πRm2δe) |
37.36 |
Mpa |
|
| 查JB/T4731，得系数K2= Refer to JB/T4731 , coefficient K2= |
|
0.192 |
|
|
| 最低点 The lowest point |
|
σ4A=PcRm/(2δe)+MA/(K2πRm2δe) |
5.64 |
Mpa |
|
| 3）B支座横截面上 Cross-section at support B |
|
|
|
A2/Rm= |
|
3.300 |
|
|
A1/Rm= |
2.475 |
|
A2/Rm= |
3.300 |
|
| 筒体被加强的最高点或筒体不被加强的靠近中间水平平面处 The toppest point of the reinforced shell or the point close to the middle hotizontal plane of the un-reinforced shell |
|
| 查JB/T4731，得系数K1= Refer to JB/T4731, coefficient K1= |
|
0.107 |
|
|
|
σ3B=PcRm/(2δe)-MB/(K1πRm2δe) |
51.99 |
Mpa |
|
|
|
| 查JB/T4731，得系数K2= Refer to JB/T4731 , coefficient K2= |
|
0.192 |
|
|
| 最低点 The lowest point |
|
σ4B=PcRm/(2δe)+MB/(K2πRm2δe) |
-2.51 |
Mpa |
|
| 4）筒体轴向应力验算 Ceck of shell longitudinal stress |
|
|
| 取出上述轴向应力中的最大拉应力（最大正值）Take out the maximum tensile stress (the maximum positive) from the above calculated longitudinal stresses |
|
| σmt=max{σ1AB,σ2AB,σ3A,σ3B,σ4A,σ4B}= |
51.99 |
Mpa |
|
| Φ*[σ]t= |
144.50 |
Mpa |
|
|
σmt<Φ[σ]t , 合格， Acceptable. |
|
|
| 取出上述轴向应力中的最大压应力（最小负值）Take out the maximum compressive stress (the maximum negative) from the above calculated longitudinal stresses |
|
| σmc=|min{σ1AB,σ2AB,σ3A,σ3B,σ4A,σ4B}|= |
2.51 |
Mpa |
|
|
σmc<[σ]crt , 合格， Acceptable. |
|
|
|
| (2) 液压试验工况 Hydrostatic test condition |
|
|
| 分别以Pc=Pt和Pc=0代入上述σ1AB、σ2AB、σ3A、σ3B、σ4A、和σ4B的计算式中并以MTA、MTB、MTAB代替式中的MA、MB和MAB，就可以求得液压试验工况以及容器充满水但未加压时的轴向应力σT1AB、σT2AB、σT3A、σT3B、σT4A和σT4B，计算结果见下表。 |
|
| Let Pc=Pt and Pc=0 respectively in the calculation formulas for σ1AB,σ2AB,σ3A,σ3B,σ4A and σ4B, and use MTA, MTB, MTAB instead of MA, MB and MAB, the longitudinal stresses under hydrostatic test condition σT1AB,σT2AB,σT3A,σT3B,σT4A, and σT4B can be obtained as follows. |
|
| 筒体的轴向应力 Longitudinal stresses in shell, Mpa |
|
|
液压试验工况 Hydrotest condition |
充满水但未加压 Full of water but no pressure |
|
| 支座A、B中间处的横截面上 Cross-section in the middle of supports A and B |
σT1AB |
14.81 |
-6.43 |
|
| σT2AB |
27.66 |
6.43 |
|
| A支座横截面上 Cross-section at support A |
σT3A |
51.79 |
30.55 |
|
| σT4A |
4.21 |
-17.03 |
|
| B支座横截面上 Cross-section at support B |
σT3B |
73.73 |
52.49 |
|
| σT4B |
-8.02 |
-29.25 |
|
| 液压试验工况 Hydrotest condition |
|
| σMT=max(σT1AB,σT2AB,σT3A,σT3B,σT4A,σT4B)= |
|
73.73 |
Mpa |
|
| 0.9ΦReL= |
|
|
|
263.925 |
Mpa |
|
|
σMT<0.9ΦReL, 合格， Acceptable. |
|
|
| 充满水但未加压 Full of water but no pressure |
|
|
| σMC=|min(σT1AB,σT2AB,σT3A,σT3B,σT4A,σT4B)|= |
|
|
29.25 |
Mpa |
|
|
σMC<[σ]cr, 合格， Acceptable. |
|
|
|
|
| 4.切向剪应力计算 calculation of tangential shear stress |
|
|
| (1)A支座横截面上 Ccross-section at support A |
|
|
| 筒体中：查JB/T4731，得系数K3= For shell, refer to JB/T4731, coefficient K3= |
1.171 |
|
|
|
QA=max(q(A1+2H/3),FA-q(A1+2H/3)) |
56234.1 |
N |
 |
|
|
τA=K3*QA/(Rm*δe) |
|
10.16 |
Mpa |
|
|
0.8[σ]t= |
|
136 |
Mpa |
|
|
τA<0.8[σ]t, 合格， Acceptable. |
|
|
| 封头中：查JB/T4731，得系数K4= For head, refer to JB/T4731, coefficient K4= |
|
|
|
|
τH=K4*FA/(Rm*δe) |
|
|
Mpa |
|
| 对椭圆封头 For ellipsoidal head |
|
| 封头形状系数 Shape factor of ellipsoidal head |
K= |
1 |
|
|
σH=KPcDi/(2δhe) |
|
|
Mpa |
|
|
1.25[σ]ht= |
|
212.5 |
Mpa |
|
|
τH+σH=
|
|
|
Mpa |
|
|
|
|
|
|
|
|
|
| (2)B支座横截面上 Cross-section support B |
|
|
|
|
| 查JB/T4731，得系数K3= Refer to JB/T4731, coefficient K3= |
|
1.171 |
|
|
|
QB=max(q(A2+2H/3),FB-q(A2+2H/3)) |
62675.0 |
N |
|
A1/Rm= |
2.475 |
|
A2/Rm= |
3.300 |
|
|
τB=K3*QB/(Rm*δe) |
|
11.32 |
Mpa |
|
|
|
|
τB<0.8[σ]t, 合格， Acceptable. |
|
|
| 封头中：查JB/T4731，得系数K4= For head, refer to JB/T4731, coefficient K4= |
|
|
|
|
τH=K4*FB/(Rm*δe) |
|
|
Mpa |
|
|
τH+σH= |
|
|
Mpa |
|
|
|
|
|
|
|
|
| 5.筒体周向应力计算 calculation of shell circumferential stress |
|
|
| 垫板是否起加强作用? Does the pad play a part in stiffening? |
YES |
|
|
| (1) 无加强圈的圆筒或加强圈位于靠近鞍座处 For shells with stiffening rings adjacent to the saddles or without stiffening rings |
|
| 1) 支座处横截面最低点周向应力 |
|
|
| Circumference stress at the lowest point of the support's cross-section |
|
 |
|
| 查JB/T4731，得系数 K5= Refer to JB/T4731, coefficient K5= |
0.76 |
|
|
|
σ5A=-k*K5*FA/(δe+δpe)*b2) |
|
-1.11 |
Mpa |
|
|
｜σ5A｜<[σ]t , 合格， Acceptable. |
|
|
|
σ5B=-k*K5*FB/((δe+δpe)*b2) |
|
-1.32 |
Mpa |
|
|
｜σ5B｜<[σ]t , 合格， Acceptable. |
|
|
| 2) A鞍座边角处 At horn of support A |
|
| 查JB/T4731，得系数K6= Refer to JB/T4731, coefficient K6= |
|
0.053 |
|
|
|
(L+A1-A2)/Rm= |
|
|
14.85 |
|
|
|
(L+A1-A2)/Rm≥8时: |
|
|
|
| σ6A=-FA/(4(δe+δpe)b2)-3*K6*FA/(2(δe^2+δpe^2)) |
|
-46.64 |
Mpa |
|
|
(L+A1-A2)/Rm<8时: |
|
|
| σ6A=-FA/(4(δe+δpe)b2)-12K6*FA*Rm/((L+A1-A2)*(δe^2+δpe^2)) |
|
Mpa |
|
A1/Rm= |
2.475 |
|
A2/Rm= |
3.300 |
|
|
σ6A= |
|
-46.64 |
Mpa |
|
|
｜σ6A｜<1.25[σ]t, 合格， Acceptable. |
|
|
| 3) B鞍座边角处 At horn of support B |
|
|
|
| 查JB/T4731，得系数K6= Refer to JB/T4731, coefficient K6= |
|
0.053 |
|
|
|
(L-A1+A2)/Rm= |
|
16.50 |
|
|
|
(L-A1+A2)/Rm≥8时: |
|
|
| σ6B=-FB/(4(δe+δpe)*b2)-3*K6*FB/(2(δe^2+δpe^2)) |
|
-55.12 |
Mpa |
|
|
(L-A1+A2)/Rm<8时: |
|
|
| σ6B=-FB/(4(δe+δpe)*b2)-12*K6*FB*Rm/((L-A1+A2)(δe^2+δpe^2)) |
|
Mpa |
|
|
σ6B= |
|
-55.12 |
Mpa |
|
|
｜σ6B｜<1.25[σ]t, 合格， Acceptable. |
|
|
| 4) A鞍座垫板边角处 At horn of pad of support A |
|
|
| 根据A1/Rm和θ'=θ+12°的数值，由JB/T4731查得K6' Based on the values of A1/Rm and θ'=θ+12°, obtain K6' from JB/T4731 |
K6'= |
0.043 |
|
|
| σ6A'=-FA/(4*δe*b2)-3*K6'*FA/(2*δe^2) |
|
-56.79 |
Mpa |
|
|
｜σ6A'｜<1.25[σ]t, 合格， Acceptable. |
|
|
| 5) B鞍座垫板边角处 At horn of pad of support B |
|
| 根据A2/Rm和θ'=θ+12°的数值，由JB/T4731查得K6' Based on the values of A2/Rm and θ'=θ+12°, obtain K6' from JB/T4731 |
K6'= |
0.043 |
|
|
| σ6B'=-FB/(4*δe*b2)-3*K6'*FB/(2*δe^2) |
|
-67.11 |
Mpa |
|
|
｜σ6B'｜<1.25[σ]t, 合格， Acceptable. |
|
|
|
|
| (2) 有加强圈的圆筒 For shells with stiffening rings |
|
|
| 1) A鞍座边角处圆筒的周向应力 Circumferential stress in the shell at horn of support A |
|
| σ7A=-K8*FA/Ao+C4*K7*FA*Rm*e/Io |
|
|
Mpa |
|
|
|
|
|
|
| 2) B鞍座边角处圆筒的周向应力 Circumferential stress in the shell at horn of support B |
|
| σ7B=-K8*FB/Ao+C4*K7*FB*Rm*e/Io |
|
|
Mpa |
|
|
|
|
|
|
| 3) A鞍座边角处加强圈内缘或外缘表面的周向应力 Circumferential stress in the stiffening ring at horn of support A |
|
| σ8A=-K8*FA/Ao+C5*K7*FA*Rm*d/Io |
|
|
Mpa |
|
|
|
|
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| 4) B鞍座边角处加强圈内缘或外缘表面的周向应力 Circumferential stress in the stiffening ring at horn of support B |
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| σ8B=-K8*FB/Ao+C5*K7*FB*Rm*d/Io |
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Mpa |
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| 6.腹板拉伸应力计算 calculation of tensile stress in web |
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F=max(FA,FB) |
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106275 |
N |
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K9= |
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0.204 |
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Fs=F9*F |
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21680.1 |
N |
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Hs=min(Ls,Rm/3) |
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192 |
mm |
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| 腹板的拉伸应力 Tensile stress in web |
σ9=Fs/(Hs*bo+b2*δpe) |
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5.12 |
Mpa |
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σ9<[σ]sa, 合格， Acceptable. |
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