公司 EQUIPMENT Co.,Ltd 压力容器计算书 计算书号Cal. No. Calculation Sheet For 版 次 Pressure Vessel Rev. No. JD-15-01 0 components >2.5mm for compressed steam 成形后封头的实际最小厚度 8.8mm – 2.0mm=6.8mm >4.78mm，而且> 2.5+2mm，也可。 Actual minimum thickness of heads after forming 8.8mm-2.0mm=6.8mm >4.78mm and > 2.5+2mm ,So it is OK。
2.3 接管最小厚度 Min. Required Thickness for Nozzles N1,N2，N3 (UG-45)
Symbols: 符号
t =管口要求最小壁厚，mm
t = minimum required thickness of nozzles, mm P =内部设计压力，1.3 MPa
P = internal design pressure, 1.3 MPa [see UG-21] R1 =管口内半径，24.61mm
R1= inside radius of the nozzle, 24.61 mm S =最大许用应力值，138 MPa
S = maximum allowable stress value, 138MPa [see ASME Code Section II
Part D Table 1A for material SA-105M ] 根据UG-45，管口要求最小厚度
According to UG-45, Min. required thickness of nozzle
[see UG-27]
[see UG-27]
tb3=3.42+Ca=3.42+2.0=5.42mm tb=min[tb3, tb31]=4.39mm t=max(ta,tb)=4.39mm
管壁的实际使用最小厚度： = 5.54mm >4.39mm
Actual min. used thickness of tube wall: = 5.54mm > 4.39mm, so it is satisfactory.
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公司 EQUIPMENT Co.,Ltd 压力容器计算书 计算书号Cal. No. Calculation Sheet For 版 次 Pressure Vessel Rev. No. JD-15-01 0 2.4 开孔和补强 Openings and Reinforcement (UG-36) 符号 Symbols: θ1=0°θ2=53°
d1=60.3mm d2=60.3mm d3=60.3mm
2.4.1 Nozzles N1,N2,N3. The finished diameter of circular opening is 49.22 mm, and minimum required thickness of shell is 4.81mm. According to UG-36(c)(3)(-a) openings in vessel not subject to rapid fluctuations in pressure do not require reinforcement other than that inherent in the construction under the following conditions: welded connections meeting the applicable and with a finished diameter of circular opening is not larger than 89mm diameter in vessel shell with a required minimum thickness of 10mm or less than 10mm,(-c)No two isolated unreinforced openings have their centers closer to each other than the sum of their diameter.(-d) Their centers closer to each other than the following:(1+1.5cosθ1)(d1+d2)=301.5mm＜1200mm. (1+1.5cosθ2)(d1+d3)=229.4mm＜1001mm. openings of Nozzle N1,N2,N3 shall be exempt from the reinforcement requirements.
2.5 接管与壳体连接焊缝的强度计算 Strength Calculation for Nozzle Attachment Weld ( UW-15)
According to UW-15(b)(2), strength calculation for nozzle attachment welds for pressure loading are not required for openings that are exempt from the reinforcement requirements by UG-36(c)(3).
2.6 接管与壳体连接焊缝高度核算 Verify the Fillet Weld Size of Nozzles according to UW-16(a)(2)(b) and Fig.UW-16.1(c) 2.6.1 FOR NOZZLE N1，N2，N3
tmin = 小于19mm或者由角焊，单坡口焊接或单J形焊接连接部分的较薄处的厚度= 5.54mm;
tmin = the smaller of 19mm or the thickness of the thinner of the parts jointed by a fillet, single-bevel, or single-J weld = 5.54mm tc =不小于6mm，或0.7 tmin = 3.87mm
tc= not less than the smaller of 6mm or 0.7tmin = 3.87mm 角焊的实际焊喉尺寸= 6.0×sin45°=4.24mm > 3.87mm
Actual throat size of fillet weld = 4.24mm >3.87mm, so it is satisfactory.
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公司 EQUIPMENT Co.,Ltd 压力容器计算书 计算书号Cal. No. Calculation Sheet For 版 次 Pressure Vessel Rev. No. JD-15-01 0 2.7检查孔 Inspection Openings 设备设有三个DN50的管口（N1/N2/N3），与之相连附件是可拆卸的，因此依据UG-46(f)可不另设检查孔。
There are three DN50（N1/N2/N3）nozzles with removable attachments.Therefore,no inspection openings will be provided based on UG-46 (f) .
3. 热处理 Heat treatment
3.1 制造后热处理 Post Fabrication Heat Treatment ( UCS-79)
According to UCS-79 Forming strains for the shell shall be calculated as follows
钢板形成的圆筒
cylinders formed from plate:
其中，
R f= 成形后的平均半径 = 255 mm
Ro= 原始半径(等于于钢板平面的正无穷)= 无穷大 t =成形前钢板的正常厚度 =10 mm Where
Rf= mean radius after forming=255 mm
Ro= original radius(equal to infinity for a flat plate)= 无穷大 t = nominal thickness of the plate before forming=10 mm
According to UCS-79(d) For P-No.1 group No.1 materials the extreme fiber elongation is less than 5%
No post fabrication heat treatment is required.
3.2 焊后热处理 Post Weld Heat Treatment ( UCS-56 )
Shell and head material SA-516 Gr.485belongs to P-No.1,nozzle and flange material SA-105M belongs to P-No.1 (see Section Ⅸ P-Number material groupings of base metals for qualification of QW-422).All the welded joints not over 38mm thickness, In according to Table UCS-56 note (b), the post weld heat treatment is not required.
4. 最低设计金属温度和冲击试验 MDMT and Impact Testing (UCS-66)
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公司 EQUIPMENT Co.,Ltd 压力容器计算书 计算书号Cal. No. Calculation Sheet For 版 次 Pressure Vessel Rev. No. JD-15-01 0 4.1 最低设计金属温度 MDMT
根据“客户设计条件”，最低设计金属温度为0℃。
The minimum design metal temperature(MDMT) is 0℃ per “Gustomer’s Design Specification”.
4.2 冲击试验 Impact Testing UG-20(f)
根据UG-20(f)，压力容器材料满足下列要求时，按UG-84的冲击试验不是 强制性的：
According to UG-20(f), impact testing per UG-84 is not mandatory for pressure vessel materials that satisfy all of following:
(1) 材料(SA105M)为P-No1，Gr. No.1 ，厚度不超过下面(a)条的规定： (a)对于图UCS-66曲线B的材料25mm；
The material is P-No1，Gr.No1 (SA105M), and the thickness is not exceed that given in (b) below:
(a) 25mm for materials listed in Curve B of Fig. UCS-66; 材料(SA-516M Gr.485)为P-No1，Gr. No.1 ，厚度不超过下面(b)条的规定： (b)对于图UCS-66曲线D的材料25mm；
The material is P-No1，Gr.No1 (SA-516M Gr485), and the thickness is not exceed that given in (b) below:
(b) 25mm for materials listed in Curve D of Fig. UCS-66; (2) 按UG-99，对完工的容器进行液压试验；
The completed vessel shall be hydrostatically tested per UG-99; (3) 设计温度为60℃，不高于345℃，且不低于-29℃；
Design temperature is 60℃ , it is no warmer than 345℃ nor colder than -29℃;
(4) 热冲击或机械冲击载荷不作为控制性的设计要求；
The thermal or mechanical shock loadings are not a controlling design requirement ;
(5) 循环载荷不作为控制性的设计要求；
Cyclical loading is not a controlling design requirement. 因此实际最低设计金属温度0℃应免于冲击试验。
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公司 EQUIPMENT Co.,Ltd 压力容器计算书 计算书号Cal. No. Calculation Sheet For 版 次 Pressure Vessel Rev. No. JD-15-01 0 So actual MDMT is 0℃ shall be exempt from impact testing.
5. 水压试验压力 Hydrostatic Testing Pressure ( UG-99) St 压力试验条件下封头、筒体、接管、法兰的许用应力
The allowable stress of the head, cylinder, nozzle and flange in the pressure test
Sd设计条件下封头、筒体、接管、法兰的许用应力
The allowable stress of the head, cylinder, nozzle and flange in the design conditions
According to UG-99 (b) and Sec.Ⅱ, Part D Table 1A
The stress value St for the test temperature is 138 MPa, the stress value Sd for the design temperature is 138 MPa, so the hydrostatic testing pressure is
ptest?1.3?St138?MAWP?1.3??1.3?1.69MPa Sd1386.法兰的校核计算 Verify For Flanges
According to ASME B16.5-2009 ANNEX B Table B1, the maximum allowable working pressure for the flanges of class150 at 60℃ is 1.91Mpa, and the design pressure of the air storage tank is 1.3Mpa, so the flanges is satisfactory.
7. 鞍式支座的校核计算 Verify For Saddle Support (JB/T 4712.1-2007) 鞍式支座允许载荷：
Allowable loadings for Saddle Support： A--一支座的横截面积，mm2。
Ae--承受水平分力的腹板和垫板有效截面积，mm2。
f--摩擦系数，取鞍座与基础垫板之间钢对钢的静摩擦系数f=0.3 h--圆筒最低表面至基础表面的距离，mm K9--系数=0.204
W--鞍座有效断面抗弯模量，mm3 [σ]—鞍座材料许用应力，MPa [Q]=min{
}=min{
}=133KN
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公司 EQUIPMENT Co.,Ltd 压力容器计算书 计算书号Cal. No. Calculation Sheet For 版 次 Pressure Vessel Rev. No. JD-15-01 0
空气储罐空重：M=298Kg
The Air Storage Tank empty weight：M=298Kg 空气储罐充满水重量：M1=598Kg When it is full of water：M1=598Kg
空气储罐操作条件下重：M2=303Kg
Weight of Normal Contents Under Operating Conditions : M2=303Kg 空气储罐载荷：
Air Storage Tank loadings： When it is empty：
G=M×g=298Kg×9.8N/ Kg=2920.4N=2.9204KN＜[Q]=133KN When it is full of water：
G1= M1×g =598Kg×9.8N/ Kg=5860.4N=5.8604KN ＜[Q]=133KN When it is operating:
G2=M2×g=303Kg×9.8N/Kg=2969.4N=2.969KN＜[Q]=133KN 因此，鞍式支座满足要求. So Saddle Support is satisfactory.
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