三鞍座容器计算 文件号 /Doc. Calculation of a Vessel on Three Saddles
计算依据： HG/T20582-1998 HG/T20582-1998，JB/T4731-2005。
This calculation calculation sheet is prepared prepared in accordance accordance with with HG/T20582-1998 HG/T20582-1998 and JB/T4731-2005.
计算压力 Calculation pressure
P=
设计温度Design temperature
0.5
Mpa
40
℃
液压试验压力 Hy Hydrostatic test pressure
Pt=
0.27
Mpa
容器内径 In Inside diameter of vessel
Di=
8200
mm
筒体名义厚度 Nominal wall thickness of shell
δn=
30
mm
封头名义厚度 Nominal wall thickness of head
30
mm
筒体的有效厚度 Effective thickness of shell
δH= δe=
29
mm
封头的有效厚度 Effective thickness of head
δhe=
29
mm
Ri=
4100
mm
Rm=Ri+0.5δn=
4115
mm
筒体内半径 Inside diameter of shell 筒体平均半径 Mean diameter of shell 筒体长度（切线至切线 ) Length of shell (T.L to T.L)
L=
12200
mm
封头内壁曲面深度 De Depth of curved surface of head
H=
1070
mm
边支座中心线到近端部封头切线的距离 Diatance of side support's center line to nearest head's tangent line
A=
1750
mm
容器操作时的总重量 Total weight of vessel at operating condition 容器液压试验时的总重量 Total weight of vessel at hydrostatic test condition 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
W= 1059355.8 N Wt= 105935 59355. 5.8 8 N mm
Ls=
1620
鞍座包角 Saddle included angle
θ=
150
°
鞍座垫板的包角 Included angle of saddle pad
θ'=
162
°
鞍座垫板有效厚度 Effictive thickness of saddle pad
δPe=
29
mm
鞍座垫板的宽度 Width of saddle pad
Bp=
1000
mm
鞍座腹板的有效厚度 Effective thickness of web
bo=
29
mm
800
mm
支座的轴向宽度 Ax A xial width of supports
b=
圆筒有效宽度 Effective width of shell
0.5
b2=b+1.56× （Rmδn）
=
1348.11
mm
设计温度下筒体材料的许用应力 Allowable stress of shell material at design temperature
[σ]t=
181
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=
181
Mpa
[σ]crt=
141
Mpa
容器材料在常温的轴向许用压缩应力 Allowable axial compressive stress [σ]cr= of vessel material at ambient temperature
141
Mpa
筒体材料常温屈服强度 Yield strength of shell material at ambient temperature.
315
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
ReL=
鞍座腹板的材料 Material of web
Q235-B
鞍座腹板的许用应力 Allowable stress of web material
[σ]sa=
108
容器的焊接接头系数 Joint efficiency of vessel
Φ=
1
系数 Coefficient
k=
0.1
Mpa
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 NO stiffening rings used? Input "YES" or "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=
mm
组合截面对 X-X轴的惯性矩 Moment of inertia of composite section
Io=
尺寸d （见下图） Dimension d (see sketch below)
d=
mm 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=
2 4
1. calculation of shell longitudinal moment (1) 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=W/(L+4H/3)
77.74
N/mm
边支座处弯矩 Moment at the side supports 中间支座处弯矩 Moment at the center support
M A
M C
M B
q(
L 2
q 2
( A
2
A) 2 8
2 4 HA Rm
3
H 2
2
)
M A
90762896 N.mm
-229264101 N.mm
2 2
跨距中点弯矩 Moment at Mid-span
1 L M B M A M p M A q ( A) / 2q L 2 2 ( A) 2
149442729 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 边支座处弯矩 Moment at the side supports 中间支座处弯矩 Moment at the center support
跨距中点弯矩 Moment at Mid-span
M TA
M TC
M T B
M T p
qT=Wt/(L+4H/3)
qT
2
qT (
( A
2
2 4 HA Rm
3
77.74
H 2 2
)
L A) 2 M T A 2 8 2
1 L M T B M T A M T A qT ( A) L 2 2 ( A) 2
N.mm
90762896 N.mm
-229264101 N.mm
2
/ 2qT
149442729 N.mm
2. calculation of reactor force on the support (1) 操作工况 Operating condition 边支座反力 Reaction of side supports
2 L A M B M A F A F C q ( H ) 1.2 L 4 2 3 ( A) 2
中间支座反力 Reaction of center support
L 2( M A M B ) 1 .2 F B q ( A) 2 L A 2
344425.2
N
582376.61 N
(2) 液压试验工况 Hydrostatic test condition 边支座反力 Reaction of side supports
中间支座反力 Reaction of center support
F T A
2 L A M T B M T A F T C qT ( H ) 1.2 L 4 2 3 ( A) 2
344425.2 N
F TB
2 M M L TA TB 1.2 qT A L 2 A 2
582376.61 N
3. calculation of longitudinal stress in the shell (1) 操作工况 Operating condition 1）两支座中间处的横截面上 Cross-section in the middle of two supports
最高点 The highest point
1
最低点 the lowest point
PR
2 e
PR
2
m
m
2 e
M P R
2 m
e
M P R
2 m
e
35.38
Mpa
35.57
Mpa
2）边支座处横截面上 Cross-section at side supports A/Rm=
0.425
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 on the shell when reinforced or the point close to the middle hotizontal plane when not reinforced 查JB/T4731 ，得系数K1=
Refer to JB/T4731, coefficient K1= 3 A
查JB/T4731 ，得系数K2= 最低点 The lowest point
3C
PR m 2 e
1
M A K 1 R m2 e
Refer to JB/T4731 , coefficient K2= 4 A
4C
PRm
2 e
Mpa
1
M A
35.42
2
K 2 Rm e
35.53
Mpa
3）中间支座处横截面上 Cross-section at center support 0.5L/Rm=
1.482
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 on the shell when reinforced or the point close to the middle hotizontal plane when not reinforced 查JB/T4731 ，得系数K1=
Refer to JB/T4731, coefficient K1= 3 B
查JB/T4731 ，得系数K2= 最低点 The lowest point
PR m
2 e
M B K 1 R m2 e
Refer to JB/T4731 , coefficient K2= 4 B
PR m 2 e
M B K 2 R m2 e
0.161 36.40
Mpa
0.279 34.94
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{σ1,σ2,σ3A,σ3B,σ4A,σ4B}= Φ*[σ]t= σmt<Φ[σ]t ,
36.40
Mpa
181.00
Mpa
Acceptable.
取出上述轴向应力中的最大压应力（最小负值）T ake out the maximum compressive stress (the maximum negative) from the above calculated longitudinal stresses
σmc=|min{σ1,σ2,σ3A,σ3B,σ4A,σ4B}|= σmc<[σ]crt ,
0
Mpa
Acceptable.
(1) 液压试验工况 Hydrostatic test condition 分别以P=Pt和P=0代入上述σ1、σ2、σ3A、σ3B、σ4A和σ4B的计算式中并以 MTA、MTB和MTP代替式 中的MA、MB和MP，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σ T1、σT2、σT3A、 σT3B、σT4A、和σT4B，计算结果见下表。
Let P=Pt and P=0 respectively in the calculation formulas for σ1,σ2,σ3A,σ3B,σ4A, and σ4B, and use MTA, MTB, MTP instead of MA, MB and MP, the longitudinal stresses under hydrostatic test condition σT1,σT2,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
σT1
19.06
-0.10
σT2
19.25
0.10
边支座处横截面上 Cross-section at side supports
σT3A
19.10
-0.06
σT4A
19.21
0.06
中间支座处横截面上 Cross-section at center support
σT3B
19.30
0.15
σT4B
19.01
-0.15
两支座中间处的横截面上 Crosssection in the middle of two supports
液压试验工况 Hydrotest condition
σMT=max(σT1,σT2,σT3A,σT3B,σT4A,σT4B)=
19.30
Mpa
0.9ΦReL=
283.5
Mpa
Acceptable.
σMT<0.9ΦReL, 充满水但未加压 Full of water but no pressure
σMC=|min(σT1,σT2,σT3A,σT3B,σT4A,σT4B)|= Acceptable.
σMC<[σ]cr,
4.
0.15 Mpa
calculation of tangential shearing stress
(1)边支座处横截面上 Ccross-section at side supports 筒体中：查 JB/T4731 ，得系数K3= For shell, refer to JB/T4731, coefficient K3=
A
0.485
C
K 3 F A R m e
1.40
封头中：查 JB/T4731 ，得系数K4= For head, refer to JB/T4731, coefficient K4= H
0.295
K 4 F A
R m he
0.85
(2)中间支座处横截面上 Cross-section at center support 查JB/T4731 ，得系数K3= Refer to JB/T4731, coefficient K3=
B
Mpa
0.799 291188.31 N
Q=FB /2=
Mpa
K 3 Q R
m
e
1.95
Mpa
(3)切向剪应力验算 Check of tangential shearing stress 对椭圆封头 For ellipsoidal head 封头形状系数 Shape factor of ellipsoidal head H
Kp c Di 2 he
K=
1 70.69
Mpa
max{τA,τB}=
1.95
Mpa
0.8[σ]t=
144.8
Mpa
max{τA,τB}<0.8[σ]t ,
1.25[σ]ht=
Acceptable.
226.25
Mpa
71.54
τH+σH=
Mpa
Acceptable.
τH+σH<1.25[σ]t ,
calculation of shell circumference stress
5.
(1) 无加强圈的圆筒或加强圈位于靠近鞍座处 For shells without stiffening rings or with stiffening rings adjacent to the saddles 垫板是否起加强作用 ? Does the pad play a part in stiffening?
NO
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=
0.673
σ5A=σ5C=-k*K5*FA/(δe*b2)
-0.59 σ5A
=
σ5C
Acceptable.
<[σ]t ,
-1.00
σ5B=-k*K5*FB/(δe*b2) σ5B
Mpa
Mpa
Acceptable.
<[σ]t ,
2) 边鞍座边角处 At horn of side supports 查JB/T4731 ，得系数K6=
Refer to JB/T4731, coefficient K6=
0.008
(0.5L+A)/Rm=
1.91
(0.5L+A)/Rm≥8时: Mpa
σ6A=σ6C=-FA/(4δe*b2)-3*K6*FA/(2*δe^2)
(0.5L+A)/Rm<8时: σ6A=σ6C=-FA/(4*δe*b2)-12*K6*FA*Rm/((0.5L+A)*δe^2) σ8A=σ8C= σ6A
=
σ6C
<1.25[σ]t,
-22.81
Mpa
-22.81
Mpa
Acceptable.
3) 中间鞍座边角处 At horn of central support 查JB/T4731 ，得系数K6b=
Refer to JB/T4731, coefficient K6b=
0.032 2.11
(L-2A)/Rm= (L-2A)/Rm≥8时:
Mpa
σ6B=-FB/(4*δe*b2)-3*K6b*FB/(2*δe^2)
(L-2A)/Rm<8时: σ6B=-FB/(4*δe*b2)-12*K6b*FB*Rm/((L-2A)*δe^2) σ6B= σ6B
<1.25[σ]t,
-129.50
Mpa
-129.50
Mpa
Acceptable.
4) 边鞍座垫板边角处 At horn of side s upport pad 根据A/Rm和θ'=θ+12°的数值，由 JB/T4731 查得K6' Based on the values of A/Rm and θ'=θ+12°, obtain K6' from JB/T4731
K6'=
0.006 Mpa
σ6A'=σ6C'=-FA/(4*δe*b2)-12*K6'*FA*Rm/((0.5L+A)*δe^2) ####
5) 中间鞍座垫板边角处 At horn of central support pad 根据0.5L/Rm和θ'=θ+12°的数值，由JB/T4731查得K6b' Based on the values of 0.5L/Rm and θ'=θ+12°, obtain K6b' from JB/T4731
σ6B'=-FB/(4*δe*b2)-12*K6b'*FB*Rm/((L-2A)*δe^2) ####
K6b'=
0.025 Mpa
(2) 有加强圈的圆筒 For shells with stiffening rings 1) 边鞍座边角处圆筒的周向应力 stress in the shell at corner of side support
Circumferential
7 A 7 C
K 8 F A Ao
C 4 K 7 F A Rm
2) 中间鞍座边角处圆筒的周向应力 stress in the shell at corner of central support 7 B
K 8 F B Ao
Mpa
I o
Circumferential
C 4 K 7 F B Rm
Mpa
I o
3) 边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 corner of side support 8 A 8 C
K 8 F A Ao
C 5 K 7 F A Rm
Mpa
I o
4) 中间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 corner of central support 8 B
6.
K 8 F B Ao
C 5 K 7 F B Rm
Mpa
I o
calculation of tensile stress in web F=max(FA,FB)
582376.61 N
K9=
0.259
Fs=F9*F
150835.54 N
Hs=min(Ls,Rm/3)
1371.6667 mm 3.79
σ9=Fs/(Hs*bo) σ9<[σ]sa,
Acceptable.
Mpa
