ASME取证用储罐强度计算书
ASME+核证的取证过程
&1 -./0 证书的分类
&> &1 授权证书 授权证书由 -./0 协会颁发， 有效期为 $ 年。 该证书核准授权工厂制造还是现场制造， 以及授 权的等级。工厂制造或现场制造要经受各自分开 的审查。产品认证包括采用焊接工艺， 使用规范 钢印及签发数据报告等方面。持证厂家要对压力 试验负责并由授权核检验师 （ -"O） 见证。 &> #
1 收稿日期： #))+ % &# % &, 1 作者简介： 杜宁， 工程师， &((+ 年毕业于哈尔滨船舶学院， 现从事锅炉及压力容器的制造工作。
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杜( 宁， 等： !"#$ 核证的取证过程
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ASME中国制造-中英文计算书-永业
用途
Spec
标准号
N1
80
6
Inlet进气口
ASME B16.5
N2
80
6
Outlet出气口
ASME B16.5
N3
80
6
DRAIN疏水口
ASME B16.5
Design formula forpipe:接管计算公式
Appendix附录1 1-1（a）(1)
Design formula for cylindrical shell :圆柱形壳体计算公式
ProductNo.产品编号:A2012001
Doc. No.:文件号：DCS-1201
1
REVISION
0
First issue
REV.
DESCRIPTION
PREPARED BY
REVIEWED BY
APPROVED BY
CONTENT
Cover封面1
Content目录2
1.Designparameters and the condition设计参数和条件3
注：摘自ASME第Ⅱ卷D篇2010版及2011增补，表1A。
3.Strength Calculations强度计算
3.1Calculationof shell wall thickness壳体壁厚计算
checking condition校核条件:UG-27 ( c )( 1 )
t=8mm< R/2 =300/2=150mm
Design formula:设计公式
ts/L=7.2/0.9D=7.2/0.9×600=0.015>0.002 (ts=7.2mm)
UG-32(d)(1)
ASME取证用储罐强度计算书汇总
设计计算书Design Calculation Sheet1. 设计参数和条件Design Data and Condition:1) 设计所遵循的规范Applicable Design Code:ASME SectionⅧ，Div.1, 20132) 设计压力(p) : 内部1.3MpaDesign Pressure (p): Internal 1.3 MPa3) 设计温度: 60℃Design Temperature: 60℃4) 焊接接头系数(E): 壳体为0.85，封头为0.85(无缝)Joint Efficiency (E): 0.85 for Shell and 0.85 for Heads（seamless）5) 材料最大许用应力Material Max. Allowable Stress:Based on ASME Code Sec.Ⅱ, Part D Table 1A壳体和封头: SA516 Gr. 485，60℃时为138MPaShell & Heads: SA516 Gr. 485 Material Max. Allowable Stress is 138MPa at 60℃；接管: SA105M钢，60℃时为138MPaNozzles：SA105M Steel Material Max. Allowable Stress 138 MPa at 60℃；6) 媒介: 空气Medium: Air (Non lethal)7) 封头类型: 2:1椭圆封头Head type: 2:1Ellipsoidal Head；8) 其他载荷: 依据“客户设计说明书”（Doc. No. TS-15-01 Rev.0）Others Loadings: As Shown in“Customer’s Design Specification”(Doc. No. TS-15-01 Rev. 0)9) 腐蚀余度:2.0 mmCorrosion Allowance: 2.0 mm10) 容器外形和尺寸：依据“客户设计说明书”（Doc. No. TS-15-01 Rev.0）Layout of Vessel and Dimension:As Shown in“Customer’s Design Specification”(Doc. No. TS-15-01 Rev. 0) 11) 钢印要求: 要求ASME标识Stamp required: ASME Certification Mark required12) NB要求: 不要求NB钢印NB stamp required: NO “NB” stamp required.Verify for UG-22 LoadingPressure符号 Symbols:t= 壳体要求最小厚度，mmt = minimum required thickness of shell, mm P = 内部设计压力, 1.3MPaP = internal design pressure, 1.3 MPa [see UG-21] R = 预计容器筒内半径， 250mmR = inside radius of the shell course under consideration, 250mm S = 最大许用应力值，138MPaS = maximum allowable stress value, 138MPa [ see ASME Code Part II DTable 1A for material SA-516 Gr.485] E = 焊接接头系数，0.85E = joint efficiency, 0.85 [see Table UW-12(1)]Since P=1.3MPa is less than 0.385SE=45.16MPa, Formula UG-27(c)(1) is used:)(2.811.36.085.0381)2025(3.16.0mm P SE PR t =⨯-⨯+⨯=-=考虑腐蚀裕量：Consider of corrosion allowable: tr= t + Ca = 2.81 + 2.0 = 4.81mmThese formulas will govern only when the circumferential joint efficiency is less than one-half the longitudinal joint efficiency, according to UG-27(c) (2) note 20, the formula UG-27(c) (2) for longitudinal stress needn’t considered. 公称钢板规则厚度=10mmNominal Plate Thickness Ordered = 10 mm钢板厚度可允许下偏差=0.25mm[see UG-16(c)] Plate Under tolerance=0.25 mm [ see UG-16(c)]UG-16 (b)(4) the minimum thickness of pressure retaining components >2.5mm for air service(exclusive any corrosion allowance). 实际使用厚度=10-0.25=9.75> 4.81mm ，并且也>2.5+2mm,可以。
压缩空气储罐计算书-ASMEU钢印
CALCULATION SHEET FOR COMPRESSED AIR STORAGE TANK(JOB NO.: SP09-U-001)(DRAWING NO.: SP09-001-1. REV. 1)SUZHOU PFAUDLER GLASS-LINED EQUIPMENT CO., LTD苏州法德尔搪玻璃设备有限公司.TABLE OF CONTENTS1. DESIGN DATA:(1) APPLICABLE CODECUSTOMER SPECIFICA TIONASME SEC.ⅧDIV. 1 2007EDITION AND2009 ADDENDA.DOC. NO. DC-09-1/Rev 0(2) DESIGN PRESSURE INTERNAL 1.3MPa(3) DESIGN TEMPERA TURE 50℃(4) TYPE OF JOINTS OF CA TEGORIES A AND B TYPE NO.1(5) RADIOGRAPHY SPOT per UW-11(b)(6) JOINT EFFICIENCY SHELL: 0.85, HEAD: 0.85, SHEEL to HEAD: 0.85(7) CORROSION ALLOWANCE 1 mm.(8) MA TERIAL SHELL & HEAD :SA-516M Gr.485NOZZLE: SA-106Gr.BFLANGE: SA-105MSUPPORT LEGS:20(GB/T8163-2008)SUPPORT PLA TE: SA-285M Gr.CLUG:SA-516M Gr.485(9) MAX. ALLOWABLE STRESS A T DESIGNTEMPERA TURE SA-285M Gr.C:108MPa at 50℃SA-105M: 138MPa at 50℃SA-106Gr.B: 118MPa at 50℃SA-516M Gr.485: 138MPa at 50℃(10) HEAD TYPE 2:1 Standard Ellipsoidal Head(11) TANK CAPACITY 1.5 m3(12) SERVICE FLUID COMPRESSED AIR (no lethal)(13) MIN. SERVICE TEMPERA TURE -10℃(14) THE LOADING CONSIDERED IN DESIGNING SEE TABLE 1-1(15) TANK DIMENSIONS SEE FIG. 1-1TABLE 1-1 LOADING CONSIDERED IN DESIGNINGItem Description Yes No1 Internal pressure [ √ ] [ ]2 External pressure [ ] [ √ ]3 Weight of vessel [ √ ] [ ]4 Weight of normal contents under operation conditions [ ] [√ ]5 Weight of normal contents under test conditions [ √ ] [ ]6 Superimposed static reactions from weight of attached equipment [ ] [ √ ]7 The attachments of internals[ ] [ √ ]8 The attachments of vessel supports (skirt, legs, saddles etc.) [ √ ] [ ]9 The attachments of lifting lugs [ √ ] [ ]10 Cyclic and dynamic reactions due to pressure [ ] [ √ ]11 Cyclic and dynamic reactions due to thermal variations [ ] [ √ ]12 Cyclic and dynamic reactions due to equipment mounted on the vessel [ ] [ √ ]13 Cyclic and dynamic reactions due to mechanical loadings [ ] [ √ ]14 Wind reactions [ ] [ √ ]15 Snow reactions [ ] [ √ ]16 Seismic reactions [ ] [ √ ]17 Impact reactions, such as those due to fluid shock [ ] [ √ ]18 Temperature gradients [ ] [ √ ]19 Differential thermal expansion [ ] [ √ ]20 Abnormal pressure, such as those caused by deflagration [ ] [ √ ]21 Test pressure and coincident static head acting during the test[√ ] [ ] (See UG-99)LIST OF NOZZLESFIG.1-1 Brief Drawing of Shell2. THICKNESS OF CYLINDRICAL SHELL UNDER INTERNAL PRESSUREASME SEC.Ⅷ DIV.1 UG-27 ● Part: Shell ● Design pressure P (MPa) : 1.3 ● Design temperature (℃):50● Material: SA-516M Gr.485● Maximum allowable stress value at design temperature S d (MPa) : 138 ● Maximum allowable stress value at test temperature S t (MPa) : 138 ● Height to point under considerationH (m) : 1.900 ● Density of test medium (water) at test temperature ρ (kg/m 3) : 1000 ● Type of welded joints in TABLE UW-12 : Type No. (1)● Radiographic examination:SPOT Per UW-11(b)● Joint efficiency (specified in UW-12) E : 0.85 ● Corrosion allowance (designated by customer) C (mm) : 1.0 ● N ominal shell thickness tn (mm) 10 ● Inside radius corroded R (mm) : 501 ● Final center line radiusR f (mm) : 505● Original center line radius (specified in UCS-79) R o (mm):∞（Infinity ）(1) Required minimum shell thickness excluding allowance (circumferential stress)0.385SE = 0.385×138×0.85=45.16> P according to UG-27(b)&(c) (a) For design conditionmm P E S PR t d 59.53.16.085.01385013.16.01min =⨯-⨯⨯=-=(b) For hydrostatic test conditionmmH E S R H P E S PR t t t 67.508.059.5)10/1000900.181.9(6.085.013850110/1000900.181.93.16.085.01385013.1)10/81.9(6.0)10/81.9(6.066662min =+=⨯⨯⨯-⨯⨯⨯⨯+⨯-⨯⨯=-+-=ρρ (2) Design thicknessRequired minimum shell thickness including allowance t=max(t min1,t min2)+C=5.67+1.0=6.67 mm (3) Provided thicknessNominal thickness (mm) 10 > t OK(4) Check minimum required thickness for paragraph UG-16 (b) (4)Minimum thickness required (including corrosion allowance) : 2.5+1=3.5mm, nominal thickness is 10mm>3.5mm, OK(5) Check extreme fiber elongation for paragraph UCS-79Maximum allowable fiber elongation without post weld heat treatment is based on the following formula: For single curvature%5%99.0%50515051050%1500<=⎪⎭⎫⎝⎛∞-⨯⨯=⎪⎪⎭⎫ ⎝⎛-=R R R t r ff None of the conditions in UCS-79 (1~5) apply, so no heat treatment after cold forming need to apply.3.THICKNESS OF ELLIPSOIDAL HEAD, PRESSURE ON CONCA VE SIDEASME SEC.ⅧDIV.1 UG-32●Part : heads●Design pressure P (MPa) : 1.3●Design temperature (℃) : 50●Material : SA-516M Gr.485 ●Maximum allowable stress value at design temperature S d(MPa) : 138●Maximum allowable stress value at test temperature S t(MPa) : 138●Height to point under consideration (bottom head) H (m) : 2.190●Height to point under consideration (top head) H (m) : 0.400●Density of test medium at test temperature ρ(kg/m3) : 1000●Type of welded joints in TABLE UW-12 : Seamless●Radiographic examination (A) : N.A●Weld joining heads to shell : Type No. (1)，SPOT Per UW-11(b)●Joint efficiency (specified in UW-12(d)) E : 0.85●Corrosion allowance (designated by customer) C (mm) : 1●Inside diameter of ellipsoidal head (corroded) D 1002●Inside spherical radius of hemispherical head L (mm) : 501R f (mm) : 905●Crown final centerline radius (specified in UG-32(d)and UCS-79)r f (mm): 174.25●Knuckle final centerline radius (specified in UG-32(d)and UCS-79)●Original center line radius (specified in UCS-79) R0 (mm): ∞（Infinity）(1) Required minimum head thicknessWithout joint, according to UW-12(d), E=0.85,L=0.9D=0.9×1002=901.8mm t s /L = 8.5/901.8=0.0094> 0.002 according to UG-32(d) (a) For the top head according to UG-32(d)(a-1) for design conditionRequired minimum head thickness excluding allowance t minmm P E S PD t d 56.53.12.085.0138210023.12.021min =⨯-⨯⨯⨯=-=(b) For the bottom head(b-1) for design conditionRequired minimum head thickness excluding allowance tminmm P E S PD t d 56.53.12.085.0138210023.12.022min =⨯-⨯⨯⨯=-=(b-2) for hydrostatic test condition(Due to same dimension for ellipsoidal heads, the bottom head will be applied forcalculation)mmH E S D H P E S PD t t t 65.509.056.5)10/1000190.281.9(2.085.01382100210/1000190.281.93.12.085.0138210023.1)10/81.9(2.02)10/81.9(2.0266663min =+=⨯⨯⨯-⨯⨯⨯⨯⨯+⨯-⨯⨯⨯=-+-=ρρ (2) Design thicknessRequired minimum head thickness including allowance t=max(t min1,t min2,t min3)+C=5.65+1.0=6.65 mm(3) Provided thicknessNominal thickness (mm) 10Minimum thickness after forming (mm) 8.5 ≥ t OK(4) Check minimum head thickness for hemispherical head from paragraph UG-32 (b) & (f)0.665SE = 0.665 × 138× 1=91.77 MPa >PRequired minimum hemispherical head thicknessmm P SE PL t h 36.23.12.0113825013.12.02min =⨯-⨯⨯⨯=-=tr=t minh /E=2.36/0.85=2.78 mm < 8.5 mm OK(5) Check minimum required thickness for paragraph UG-16(b)(4)Minimum thickness required (including corrosion allowance) : 2.5+1= 3.5mm,minimum thickness after forming is 8.5mm.>3.5mm OK (6) Check extreme fiber elongation for paragraph UCS-79Maximum allowable fiber elongation without heat treatment is based on the following formula: For double curvature Crown radius elongation%5%83.0%90519051075%1750<=⎪⎭⎫⎝⎛∞-⨯⨯=⎪⎪⎭⎫ ⎝⎛-=R R R t r ff Knuckle radius elongation%5%3.4%25.174125.1741075%1750<=⎪⎭⎫⎝⎛∞-⨯⨯=⎪⎪⎭⎫ ⎝⎛-=R r r t r f f None of the conditions listed in UCS-79(d)(1) through (5) exist, so no heat treatment of heads after cold forming need to apply for SA-516M Gr.485 (P-NO.1 Group NO.2).4. THICKNESS OF NOZZLE NECK INTERNAL PRESSURE 4-1 FOR NOZZLE aASME SEC.Ⅷ DIV .1 UG-45●Design pressure P (MPa) : 1.3 ●Design temperature T (℃) : 50●Material of nozzle neck: SA-106Gr.B ●Allowablestress of nozzle neck material at design temperatureS d (MPa):118 ●Allowablestress of nozzle neck material at test temperatureS t (MPa):118●Material of shell: SA-516M Gr.485 ●Allowable stress of shell (or head) at design temperatureS s (MPa):138 ●Height to point under considerationH (m) : 1.580 ●Density of test medium at test temperature (water) ρ(kg/m 3) : 1000 ●Typeof welded joints of nozzle neck in TABLEUW-12:Seamless●Joint efficiency of nozzle neckE : 1.0 ●Corrosion allowance (designated by customer) C (mm) : 1 ●Outside radius of nozzle neckR o (mm) : 30.15 ●Nominal thickness of the standard wall pipe(B36.10M ) t std (mm) : 3.91 ●Inside radius of shell corrodedR s (mm): 501(1) Minimum required thickness of nozzle neck for par. UG-45 (a)0.385SE = 0.385× 118 ×1.00 = 45.43 > P (a) under design condition A ppendix 1-1 Required minimum thickness including allowancemm C P E S PR t d o 33.113.14.0111815.303.14.01min =+⨯+⨯⨯=++=(b)under hydrostatic test conditionRequired minimum thickness including allowancemmC H E S R H P E S PR t t ot o 334.11004.033.01)10/1000580.181.9(4.0111815.3010/1000580.181.93.14.0111815.303.1)10/81.9(4.0)10/81.9(4.066662min =++=+⨯⨯⨯+⨯⨯⨯⨯+⨯+⨯⨯=++++=ρρ(2) Minimum required thickness of shell for par. UG-45 (b) (1),and UG-16 (b) (4), Es = 1.00mm3.512.575.5175.413.16.011385013.16.0=+>=+=+⨯-⨯⨯=+-=mm C P E S PR t s s s s(3) Minimum thickness of standard wall pipe including allowance for par. UG-45 (b) (4)t p = 0.875t std + C = 0.875 × 3.91 + 1 =4.42mm t = (the smaller value of t s or t p ) per UG-45(b) = 4.42mm. > t min1,t min2(4) Provided thicknessNominal thickness (mm) 5.54Minimum thickness (mm) 5.54×0.875 =4.8475 ≥ t OK 4-2 FOR NOZZLE bASME SEC.Ⅷ DIV .1 UG-45●Design pressure P (MPa) : 1.3 ●Design temperature T (℃) : 50●Material of nozzle neck: SA-106Gr.B ●Allowablestress of nozzle neck material at design temperatureS d (MPa):118 ●Allowablestress of nozzle neck material at test temperatureS t (MPa):118●Material of shell: SA-516M Gr.485 ●Allowable stress of shell (or head) at design temperatureS s (MPa):138 ●Height to point under considerationH (m) : 0.680 ●Density of test medium at test temperature (water)ρ(kg/m 3): 1000●Type of welded joints of nozzle neck in TABLE UW-12:Seamless●Joint efficiency of nozzle neckE : 1.0 ●Corrosion allowance (designated by customer) C (mm) : 1 ●Outside radius of nozzle neckR o (mm) : 30.15 ●Nominal thickness of the standard wall pipe(B36.10M ) t std (mm) : 3.91 ●Inside radius of shell corrodedR s (mm): 501(1) Minimum required thickness of nozzle neck for par. UG-45 (a)0.385SE = 0.385× 118 ×1.00 = 45.43 > P (a) under design condition A ppendix 1-1 Required minimum thickness including allowancemm C P E S PR t d o 33.113.14.0111815.303.14.01min =+⨯+⨯⨯=++=(b)under hydrostatic test conditionRequired minimum thickness including allowancemmC H E S R H P E S PR t t o t o 332.11002.033.01)10/1000680.081.9(4.0111815.3010/1000680.081.93.14.0111815.303.1)10/81.9(4.0)10/81.9(4.066662min =++=+⨯⨯⨯+⨯⨯⨯⨯+⨯+⨯⨯=++++=ρρ (2) Minimum required thickness of shell for par. UG-45 (b) (1),and UG-16 (b) (4), Es = 1.00mm3.512.575.5175.413.16.011385013.16.0=+>=+=+⨯-⨯⨯=+-=mm C P E S PR t s s s s(3) Minimum thickness of standard wall pipe including allowance for par. UG-45 (b) (4)t p = 0.875t std + C = 0.875 × 3.91 + 1 =4.42mm t = (the smaller value of t s or t p ) per UG-45(b) = 4.42mm. > t min1,t min2(4) Provided thicknessNominal thickness (mm) 5.54Minimum thickness (mm) 5.54×0.875 =4.8475 ≥ t OK4-3 FOR NOZZLE dASME SEC.Ⅷ DIV .1 UG-45●Design pressure P (MPa) : 1.3 ●Design temperature T (℃) : 50●Material of nozzle neck: SA-106Gr.B ●Allowablestress of nozzle neck material at design temperatureS d (MPa):118 ●Allowablestress of nozzle neck material at test temperatureS t (MPa):118●Material of shell: SA-516M Gr.485 ●Allowable stress of shell (or head) at design temperatureS s (MPa):138 ●Height to point under considerationH (m) : 0.11 ●Density of test medium at test temperature (water) ρ(k/m 3) : 1000 ●Typeof welded joints of nozzle neck in TABLEUW-12:Seamless●Joint efficiency of nozzle neckE : 1.0 ●Corrosion allowance (designated by customer) C (mm) : 1 ●Outside radius of nozzle neckR o (mm) : 24.15 ●Nominal thickness of the standard wall pipe(B36.10M ) t std (mm) : 3.68 ●Inside diameter of ellipsoidal head (corroded)D (mm): 1002(1) Minimum required thickness of nozzle neck for par. UG-45 (a)0.385SE = 0.385× 118 ×1.00 = 45.43 > P (a) under design condition A ppendix 1-1 Required minimum thickness including allowancemm C P E S PR t d o 265.113.14.0111815.243.14.01min =+⨯+⨯⨯=++=(b)under hydrostatic test conditionRequired minimum thickness including allowancemmC H E S R H P E S PR t t ot o 2752.110002.0275.01)10/1000110.081.9(4.0111815.2410/1000110.081.93.14.0111815.243.1)10/81.9(4.0)10/81.9(4.066662min =++=+⨯⨯⨯+⨯⨯⨯⨯+⨯+⨯⨯=++++=ρρ (2) Minimum required thickness of head for par. UG-45 (b) (1),and UG-16 (b) (4), Es = 1.00m m3.512.572.5172.413.12.01138210023.12.02=+>=+=+⨯-⨯⨯⨯=+-=mm C P E S PD t s s s(3) Minimum thickness of standard wall pipe including allowance for par. UG-45 (b) (4)t p = 0.875t std + C = 0.875 × 3.68 + 1 =4.22mm t = (the smaller value of t s or t p ) per UG-45(b) = 4.22mm. > t min1,t min2(4) Provided thicknessNominal thickness (mm) 5.08Minimum thickness (mm) 5.08×0.875 =4.445≥ t OK 4-4 FOR NOZZLE fASME SEC.Ⅷ DIV .1 UG-45●Design pressure P (MPa) : 1.3 ●Design temperature T (℃) : 50●Material of nozzle neck: SA-106Gr.B ●Allowablestress of nozzle neck material at design temperatureS d (MPa):118 ●Allowablestress of nozzle neck material at test temperatureS t (MPa):118●Material of shell: SA-516M Gr.485 ●Allowable stress of shell (or head) at design temperatureS s (MPa):138 ●Height to point under considerationH (m) : 2.300 ●Density of test medium at test temperature (water) ρ(kg/m 3) : 1000 ●Typeof welded joints of nozzle neck in TABLEUW-12: Seamless●Joint efficiency of nozzle neckE : 1.0 ●Corrosion allowance (designated by customer) C (mm) : 1 ●Outside radius of nozzle neckR o (mm) : 24.15 ●Nominal thickness of the standard wall pipe(B36.10M ) t std (mm) : 3.68 ●Inside diameter of ellipsoidal head (corroded)D (mm): 1002(1) Minimum required thickness of nozzle neck for par. UG-45 (a)0.385SE = 0.385× 118 ×1.00 =45.43 > P (a) under design condition A ppendix 1-1 Required minimum thickness including allowancemm C P E S PR t d o 265.113.14.0111815.243.14.01min =+⨯+⨯⨯=++=(b)under hydrostatic test conditionRequired minimum thickness including allowancemmC H E S R H P E S PR t t o t o 27.11005.0265.01)10/1000300.281.9(4.0111815.2410/1000300.281.93.14.0111815.243.1)10/81.9(4.0)10/81.9(4.066662min =++=+⨯⨯⨯+⨯⨯⨯⨯+⨯+⨯⨯=++++=ρρ (2) Minimum required thickness of head for par. UG-45 (b) (1),and UG-16 (b) (4), Es = 1.00m m3.512.572.5172.413.12.01138210023.12.02=+>=+=+⨯-⨯⨯⨯=+-=mm C P E S PD t s s s(3) Minimum thickness of standard wall pipe including allowance for par. UG-45 (b) (4)t p = 0.875t std + C = 0.875 × 3.68 + 1 =4.22mm t = (the smaller value of t s or t p ) per UG-45(b) = 4.22mm. > t min1,t min2(4) Provided thicknessNominal thickness (mm) 5.08Minimum thickness (mm) 5.08×0.875 =4.445 ≥ t OK4-5 FOR NOZZLE cASME SEC.Ⅷ DIV .1 UG-45●Design pressure P (MPa) : 1.3 ●Design temperature T (℃) : 50●Material of nozzle neck: SA-106Gr.B ●Allowablestress of nozzle neck material at design temperatureS d (MPa):118 ●Allowablestress of nozzle neck material at test temperatureS t (MPa):118●Material of shell: SA-516M Gr.485 ●Allowable stress of shell (or head) at design temperatureS s (MPa):138 ●Height to point under considerationH (m) : 0.55 ●Density of test medium at test temperature (water) ρ(kg/m 3) : 1000 ●Typeof welded joints of nozzle neck in TABLEUW-12:Seamless●Joint efficiency of nozzle neckE : 1.0 ●Corrosion allowance (designated by customer) C (mm) : 1 ●Outside radius of nozzle neckR o (mm) : 10.65 ●Nominal thickness of the standard wall pipe(B36.10M )Per UG45(b)(4) note26 OD38 next larger pipe size OD42.2t std (mm): 2.77●Inside radius of shell corrodedR s (mm): 501(1) Minimum required thickness of nozzle neck for par. UG-45 (a)0.385SE = 0.385× 118 ×1.00 = 45.43 > P (a) under design condition A ppendix 1-1 Required minimum thickness including allowancemm C P E S PR t d o 12.113.14.0111865.103.14.01min =+⨯+⨯⨯=++=(b)under hydrostatic test conditionRequired minimum thickness including allowancemmC H E S R H P E S PR t t ot o 1205.110005.012.01)10/1000550.081.9(4.0111865.1010/1000550.081.93.14.0111865.103.1)10/81.9(4.0)10/81.9(4.066662min =++=+⨯⨯⨯+⨯⨯⨯⨯+⨯+⨯⨯=++++=ρρ (2) Minimum required thickness of shell for par. UG-45 (b) (1),and UG-16 (b) (4), Es = 1.00mm3.512.575.5175.413.16.011385013.16.0=+>=+=+⨯-⨯⨯=+-=mm C P E S PR t s s s s(3) Minimum thickness of standard wall pipe including allowance for par. UG-45 (b) (4)t p = 0.875t std + C = 0.875 × 2.77 + 1 =3.42mm t = (the smaller value of t s or t p ) per UG-45(b) = 3.42mm. > t min1,t min2(4) Provided thicknessNominal thickness (mm) 4.78Minimum thickness (mm) 4.78×0.875 =4.1825 ≥ t OK 4-6 FOR MANHOLE NOZZLE eASME SEC.Ⅷ DIV .1 UG-45●Design pressure P (MPa) : 1.3 ●Design temperature T (℃) : 50●Material of nozzle neck: SA-516M Gr.485 ●Allowable stress of nozzle neck material at design temperatureS d (MPa) :138 ●Allowable stress of nozzle neck material at test temperature S t (MPa) 138●Height to point under considerationH (m) : 1.57 ●Density of test medium at test temperature (water) ρ(kg/m 3) : 1000 ●Type of welded joints of nozzle neck in TABLE UW-12 Type No. (1) ●Radiographic examination of nozzle neckSPOT Per UW-11(b)●Joint efficiency of nozzle neck (specified in UW-12) E : 0.85 ●Corrosion allowance (designated by customer) C (mm) : 1 ●Outside radius of nozzle neckR o (mm): 228.5●Inside radius of nozzle corroded R (mm) : 219.5 ●Inside radius of shell corroded R s (mm) : 501 ●Final center line radius of nozzle R f (mm) : 223.5 ●Original center line radius of nozzleR 0 (mm): ∞(Infinity)(1) Minimum required thickness of nozzle par. UG-45 (a) and UG-27 (c) (1)0.385SE = 0.385×138×0.85 = 45.16> P(a) under design conditionRequired minimum thickness including allowancemm C P E S PR t d 25.3125.213.16.085.01385.2193.16.01min =+=+⨯-⨯⨯=+-=(b)under hydrostatic test conditionRequired minimum thickness including allowancemmC H E S R H P E S PR t t t 28.3103.025.21)10/1000590.181.9(6.085.01385.21910/1000590.181.93.16.085.01385.2193.1)10/81.9(6.0)10/81.9(6.066662min =++=+⨯⨯⨯-⨯⨯⨯⨯+⨯-⨯⨯=+-+-=ρρ (c) With supplemental loading by flange and cover●Weight of flange and cover W =170kg ●Bending moment due to supplemental loadingUnder operating condition M 1 =170x9.81x0.260= 433.6N ·mUnder cover opened condition M 2 =170x9.81x0.560=933.9N ·mPer UG-27(c) and Appendix L, Use S = 138 × 1.5 = 207MPa (see UG-23(c))mmmm CSER MP SE PR t 84.1843015.11000015.0843.0185.02075.2286.4333.14.085.020725.2283.14.022213≈≈++=+⨯⨯⨯+⨯+⨯⨯⨯=+++=ππ mm C SE R M t 0.11000032.0185.02075.2289.9332224≈+=+⨯⨯⨯=+=ππ(2) Provided thicknessNominal thickness (mm) 10 > t min1,t min2,t 3,t 4 OK (3) Check extreme fiber elongation for paragraph UCS-79Maximum allowable fiber elongation without post weld heat treatment is based on the following formula: for single curvature%5%24.2%5.22315.2231050%1500<=⎪⎭⎫⎝⎛∞-⨯⨯=⎪⎪⎭⎫ ⎝⎛-=R R R t r ff None of the condition list in UCS-79 (d) (1-5) exists, so no heat treatment after cold forming need to apply.5Max. Allowable working pressure (corroded)The maximum allowable working pressure may be assumed to be the same as the design pressure when calculations are not made to determine the maximum allowable working pressure.(ASME SEC.ⅧDIV.1 UG-99 notes: 34)So we take the maximum allowable working pressure is 1.3MPa at 50 ℃6 HYDROSTATIC TEST PRESSURE AND TEMPERA TUREASME SEC. ⅧDIV.1 UG-99 ●Maximum allowable working pressure (Hot & Corroded) * (MPa) : 1.3 at 50 ℃●Hydrostatic test pressure (MPa) : 1.69●Design temperature (℃) : 50●Test temperature (℃) : 5～40●Minimum design metal temperature (℃) : -29●Material of parts of the vessel : See table 5.1●Allowable stress of vessel wall at design temperature S d (MPa) : See table 5.1●Allowable stress of vessel wall at test temperature S t (MPa) : See table 5.1*: The maximum allowable working pressure may be assumed to be the same as the design pressure.(specified in UG-99 note34)(1)Minimum required test pressure per UG-99 (b)Table 5.1 Hydrostatic Test Pressure per UG-99 (b)(2)Provided test pressure per UG-99 (h)Hydrostatic test pressure (MPa) is 1.69 at 5~40℃7REINFORCEMENT FOR OPENINGS7-1 Since the welded nozzles a(DN50)、f(DN50)、c(DN15)、d(DN40) and f(DN40) are neither subject to rapid fluctuations in pressure nor larger than 89mm, reinforcement of openings is not required. [UG-36 (c) (3)]7-2 For manhole nozzle e(DN450)per UG-37●Internal design pressure P (MPa) : 1.3●Design temperature (℃) : 50●Material of the vessel wall : SA-516M Gr.485 ●Allowable stress of the vessel wall at design temperature S V (MPa) : 138●Material of the nozzle wall : SA-516M Gr.485 ●Allowable stress of the nozzle wall at design temperature S n (MPa) : 138●Corrosion allowance (designated by customer) C (mm) : 1●Inside radius of shell corroded R (mm) : 501●Analysis thickness of the vessel wall corroded t (mm) : 9●Outside radius of the nozzle R no(mm) : 228.5●Inside radius of the nozzle corroded R n (mm) : 219.5●Analysis thickness of nozzle wall corroded t n (mm) : 9●Finished diameter of opening corroded d (mm) : 439●Leg length of outward nozzle fillet weld t nc (mm): 10●Angle of plane with longitudinal axis θ (deg): 0.0●Correction factor F : 1.07-2-1 Size of openingSince ID is 1000mm, according to UG-36(b) (1), one half the vessel diameter is 500mm, and doesn’t exceed 500mm, therefore, 500mm is maximum limit without considering supplementalrules of 1-7.Now, the diameter of opening is 439mm, so supplemental rules of 1-7 are not applied. 7-2-2 Wall thicknesses RequiredShell Required thickness of a seamless shell t r (E=1.0)mm P E S PR t V r 75.43.16.011385013.16.0=⨯-⨯⨯=-=Nozzle Minimum nozzle thickness due to pressure t rn (E 1=1.0)mm P E S PR t n no rn 14.23.14.011385.2283.14.01=⨯+⨯⨯=+=7-2-3 Material Strength Reduction FactorStrength reduction factor for nozzle f r1 f r1=S n /S V =138/138=1.0Strength reduction factor for nozzle f r2 f r2=S n /S V =138/138=1.07-2-4 Check for limits of reinforcement: 7-2-4(a)Limit parallel to the vessel wall:larger of d=439mm or Rn+tn+t=219.5+9+9=237.5mm Use 439mm7-2-4(a)Limit normal to the vessel wall:smaller of 2.5t==2.5×9=22.5mm or 2.5tn+te==2.5×9+0=22.5mm Use 22..5mm7-2-5Area of reinforcement required Area available in shell A 1[][]()()21111175.1865075.419143912mm f Ft t E t Ft t E d A r r n r =-⨯-⨯⨯=----=()()()()()()211112153075.4191992122mm f Ft t E t Ft t E t t A r r n r n =-⨯-⨯⨯+⨯=----+= A 1=the larger of (A 11,A 12)=1865.75 mm 2 Area available in nozzle projecting outward A 2()()22217.3089114.2955mm t f t t A r rn n =⨯⨯-⨯=-=()()22227.3089114.2955mm t f t t A n r rn n =⨯⨯-⨯=-=A 2=the smaller of (A 21,A 22)=308.7 mm 2 Area available in welds A 4 Area available in outward weld A 412222341100110)(mm f t A r L =⨯==A 4=A 41+A 42+A 43=100+0+0=100 mm 2 Total Area availableTotalA=A 1+A 2+A 3+A 4=1865.75+308.7+0+100=2274.75 mm 2 Total Area RequiredTotalA mm f F t t F dt A r r n r <=+⨯⨯=-+=2125.20850175.4439)1(2So the opening is adequately reinforced.GENERAL NOTE8 Strength calculations for nozzle attachment welds for pressure loadingFor nozzle a (DN50)、b (DN50)、c(DN15)、d(DN40)、e(DN450) and f(DN40) because their welded types are follow Fig.UW –16.1 sketch (c) so the strength calculations for nozzle attachment welds for pressure loading are not required [UW – 15 (b)].9.Check the adequacy of the attachment welds at openings9-1 For DN50 nozzle (a and b)Size of weld required [UW – 16 (c), Fig. UW – 16.1 sketch (c)]Outer fillet weld:0.7 t min= 0.7×5.54=3.88 mm (min. Throat required)t c= the smaller of (0.7 t min. or 6mm)= 3.88mmActual fillet weld sizet c = 5mm (actual) > 3.88mm OKWeld sizes are satisfactory.9-2 For DN40 nozzle (d and f)Size of weld required [UW – 16 (c), Fig. UW – 16.1 sketch (c)]Outer fillet weld:0.7 t min. = 0.7×5.08=3.56mm (min. Throat required)t c= the smaller of (0.7 t min or 6mm)= 3.56 mmActual fillet weld sizet c= 5mm (actual) >3.56mm OKWeld sizes are satisfactory.9-3 For DN15 nozzles (c)Size of weld required [UW – 16 (c), Fig. UW – 16.1 sketch (e)] Outer fillet weld:0.7 t min = 0.7 × 4.78= 3.35mmt c= the smaller of (0.7t min or 6mm)= 3.35mmActual fillet weld sizet c = 5mm (actual) > 3.35mm OKWeld sizes are satisfactory.9-4 For DN450 Manhole nozzle (e)Size of weld required [UW – 16 (c), Fig. UW – 16.1 sketch (c)] Outer fillet weld:0.7 t min= 0.7×10 =7mmt c= the smaller of (0.7t min or 6mm)=6mmActual fillet weld sizet c = 7mm (actual) > 6mm OKWeld sizes are satisfactory.10.Check flange to nozzle neck weldsSize of weld required [UW – 21 (b), Fig. UW – 21 sketch (1)] x min=the lesser of 1.4t min or the thickness of the hub,t min= the smaller thickness of nozzle or hub.t hub= the thickness of the hub of Flange accoding to ASME B16.5-2003 10-1 For DN50 nozzle (a and b)t n=5.54mm, t hub =8.05mm, t min=5.54mm.1.4t min= 1.4×5.54 =7.76mmx min=7.76mmActual fillet weld sizex = 8mm (actual) > 7.76mm OK10-2 For DN40 nozzle (d and f)t n=5.08mm, t hub =7.75mm, t min=5.08mm.1.4t min= 1.4×5.08 =7.11mmx min=7.11mmActual fillet weld sizex = 8mm (actual) > 7.11mm OK10-3 For DN15 nozzle (c)t n=4.78mm, t hub =3.95mm, t min=3.95mm.1.4t min= 1.4×3.95 =5.53mmx min=3.95mmActual fillet weld sizex = 4mm (actual) > 3.95mm OK10-4 For DN450 nozzle (e)t n=10mm, t hub =21.6mm, t min=10mm.1.4t min= 1.4×10=14mmx min=14mmActual fillet weld sizex = 14mm (actual) = 14mm OK11 Design of the supporting legs according to ( Appendix A of JB/T4712.4-2007) 11-1 Actual Load Q on Supporting LegEarthquake loading and wind loading need not be considered. Installation Size D=630mmEccentric Load G e =200×9.81=1962N Height from horizontal force acting point to base plate H=1490mm Unequal Factor k=1 Total Mass m 0=900kg Number of Supporting Leg n=3 Vessel outside diameter D 0=1020mm Total Vessel Height H 0=2525mm Eccentric Distance S e =760 mm Actual Load borne on supporting leg:kNQ kN nD S G kn G g m Q e e e 150][8.5106303)7601962431196281.9900104330=<=⨯⎥⎦⎤⎢⎣⎡⨯⨯⨯+⨯+⨯=⨯⎥⎦⎤⎢⎣⎡++=-- Load on supporting leg during hydrostatic test:150kN [Q]53.81031196281.9241010330=<=⨯⨯+⨯=⨯+=--KN kn G g m Q e <[Q] Therefore the B2 supporting leg with an allowable 150kN is safely selected in accordance with JB/T4712.4-2007《Supporting Leg 》.11-2 Verification for Allowable Vertical Load Limited by Vessel HeadEffective thickness of head: mm C n e 5.715.8=-=-=δδ。
ASME 取证(专业部分)
ASME 取证试题（专业部分）一、设计方面（压力容器UG、UW 和UCS）1.常规压力容器强度计算书应该包含哪些基本内容？筒体的强度计算应该考虑哪些要求？椭圆封头的强度计算应该考虑哪些要求？2.如何确定压力容器设计过程中引用标准的版本？如何考虑单位制统一的问题，规范怎么要求的？3.如何考虑规范中没有提到的计算，比如支座计算？4.压力容器的腐蚀裕量是由设计工程师指定吗？设计工程师如何审核用户设计规范？5.对于锅炉和压力容器，静压头是否都一定要考虑？6.压缩空气储罐的受压件最小要求壁厚是多少？7.哪些材料可以允许用于制造压力容器的受压件？允许的螺栓，螺母材料是哪些？压力容器非受压件是否需要是ASME 材料？8.压力容器人孔的设计方面的有什么要求？容器排污孔的位置有什么要求？计算书中的所有的尺寸是腐蚀前还是腐蚀后？9.判定压力容器是否需要焊后热处理的因素有哪些？公称厚度的定义？10.什么情况下压力容器必须拍片？如果规范不强制拍片，那么由谁决定拍片的比例？11.如果容器接管开孔在焊缝上，接管满足UG-36(c)(3)的要求不需要计算开孔补强，对这样的开孔处的焊缝有没有RT 的要求？12.判定压力容器是否需要冲击试验的因素有哪些？是否只是受压件需要考虑低温冲击？考虑低温冲击时，控制厚度的定义？设计工程师请熟悉附录JJ!13.对于压力容器，免除开孔补强计算的开孔应满足什么条件？14.是不是所有尺寸的补强圈都可以完整的考虑为补强的范围内，即补强的范围？15.压力容器接管厚度的计算需满足那些要求？16. 针对容器，考虑冲击试验时，SA-105,SA-516 Gr70 正火，SA-106B 分别属于哪一种曲线？17. 一台容器打了RT-3 标记，封头和筒体焊接用Type 1 的接头形式，封头计算时的焊接接头系数为多少？18. 一台容器封头为无缝，筒体纵缝RT抽拍，封头与筒体的环缝抽拍并同时满足UW-11(a)5(b)的要求，计算封头壁厚时的焊接接头系数为多少？筒体接头系数为多少？容器打RT-1,RT-2,RT-3 还是RT-4?19. SA 106B 和A106B 什么区别？能等同的材料吗？20.针对容器，封头成型后如何判定是否需要成型后热处理？如何判定是否需要带成型试板？21.如何判定焊缝强度是否需要计算？22.压力容器的水压试验压力值如何确定？水压试验温度是指介质温度还是金属温度？具体的温度值有何要求？23.压力容器铭牌的要求有哪些？24.如果容器的铭牌直接装在设备上，铭牌可以装在与设备相连的支架上，这种情况下，铭牌与容器的距离有无具体的要求？二、材料方面1. SA-516 Gr70 的质保书有哪些要求？SA-106 GrB 质保书有哪些要求？2. SA-516 Gr 70 ，20mm 厚，允许的尺寸变差是多少？板材原始标记的要求是哪些？3.B16.5 法兰，材料SA-105 要求的标记有哪些？质保书要求哪些内容？是否需要作入厂验收？4.SA-106B 要求的标记有哪些？要求哪些性能试验,允许的尺寸偏差为多少？5. N, QT, Ceq 是什么意思？6.ASME 材料如何进行验收？是否需要复验？是否一定需要质保书？哪些材料需要质保书？ASME 焊材如何进行验收？是否一定需要质保书？第I 卷和VIII-1 卷对材料质保书方面的要求是否一样？7.材料入厂验收的基本流程是怎样的？每一过程需要哪些文件？验收合格的材料由谁指定材料追踪号？如何指定？8.谁负责登记材料追踪号的台帐？9.如果材料验收不合格，如何处理？如果需要对母材进行补焊，应该如何操作？10.如果外购的无缝封头，应该如何进行验收？采取什么样的方式追踪其材料追踪号？三、焊接方面1.手工焊，自动焊，机器焊的定义？2. 哪些焊接方法能用于焊接VIII-1 卷的容器？3. WPS,PQR 都应该分别包含哪些变素？4. WPS 里的非重要变素发生变化时，如何处理？5.P-No.,F-No. A-No.分别含义？6. WPS 中的焊材不属于任何一个A-No.,如何处理？7.焊工考试试样的试验有哪些项目？哪些焊接方法可以用RT替代力学性能试验？RT评定合格的依据是第五卷吗？这种情况下对焊缝长度有要求吗？8.PQR 机械性能包含哪些试验项目？合格依据是什么？可以用RT代替力学性能试验吗？9.管接头与筒体的焊接接头采用骑座式，管接头尺寸为1'', 那么焊这条焊缝的焊工应该如何进行考试？如果接头形式为插入式呢？焊工应该具有什么位置的资格？10.焊接非受压件与受压件的焊工是否需要评定合格的焊工？是否需要评定合格的WPS, 允许进行焊接的最低温度是多少？11.非受压件是否一定需要是ASME 材料？非受压件与受压件的焊缝要求在哪一章节？12. 如果WPS 评定P-NO. 1 材料并合格，那么这个WPS 能覆盖哪些材料？13. 如果焊工考试有F-NO.3 带垫板，那么这个焊工焊接哪些F-No.？14. 如何维持焊工的资格？15. 焊接工艺评定试板材料为SA-516 Gr 70，厚度为9mm,那么弯曲半径为多少？如果试样厚度为40mm,那么做拉伸实验时如何处理？16.低氢焊条的烘培温度，烘培时间依据是什么？能够回收几次？如何标识回收焊条？如何控制回收的焊条？四、检验方面1.检验员如何进行装配检查？点焊检查？焊缝检查？如果是RT抽拍，由谁指定抽拍的位置？2.错边量的要求在哪一章节？焊缝余高要求在哪一章节？3.检验员在焊接前应该检查什么？焊接中检查什么？焊接后检查什么？4.如果在检验过程中出现NCR, 应该采取怎样的步骤？5.检验接管与筒体的角焊缝尺寸时，图纸规定的尺寸是是仅值沿筒体纵向的焊脚尺寸还是针对整个焊缝焊脚？6.热处理工程师在准备焊后热处理工艺卡时，保温温度，升温速度，降温速度，如炉温度，出炉温度，保温时间依据在那一章节？7.热处理分包前和分包后如何控制？8.容器在水压试验之后，打U 钢印之前，在受压件上焊接非受压件，是否需要重新进行水压试验？9. MDR 是什么？如何选用相应格式的MDR? 请质检部经理负责熟悉并填写MDR。
(整理)压缩空气储罐计算书-ASMEU钢印.
CALCULATION SHEET FOR COMPRESSED AIR STORAGE TANK(JOB NO.: SP09-U-001)(DRAWING NO.: SP09-001-1. REV. 1)SUZHOU PFAUDLER GLASS-LINED EQUIPMENT CO., LTD苏州法德尔搪玻璃设备有限公司.TABLE OF CONTENTS1. DESIGN DATA:(1) APPLICABLE CODECUSTOMER SPECIFICA TIONASME SEC.ⅧDIV. 1 2007EDITION AND2009 ADDENDA.DOC. NO. DC-09-1/Rev 0(2) DESIGN PRESSURE INTERNAL 1.3MPa(3) DESIGN TEMPERA TURE 50℃(4) TYPE OF JOINTS OF CA TEGORIES A AND B TYPE NO.1(5) RADIOGRAPHY SPOT per UW-11(b)(6) JOINT EFFICIENCY SHELL: 0.85, HEAD: 0.85, SHEEL to HEAD: 0.85(7) CORROSION ALLOWANCE 1 mm.(8) MA TERIAL SHELL & HEAD :SA-516M Gr.485NOZZLE: SA-106Gr.BFLANGE: SA-105MSUPPORT LEGS:20(GB/T8163-2008)SUPPORT PLA TE: SA-285M Gr.CLUG:SA-516M Gr.485(9) MAX. ALLOWABLE STRESS A T DESIGNTEMPERA TURE SA-285M Gr.C:108MPa at 50℃SA-105M: 138MPa at 50℃SA-106Gr.B: 118MPa at 50℃SA-516M Gr.485: 138MPa at 50℃(10) HEAD TYPE 2:1 Standard Ellipsoidal Head(11) TANK CAPACITY 1.5 m3(12) SERVICE FLUID COMPRESSED AIR (no lethal)(13) MIN. SERVICE TEMPERA TURE -10℃(14) THE LOADING CONSIDERED IN DESIGNING SEE TABLE 1-1(15) TANK DIMENSIONS SEE FIG. 1-1TABLE 1-1 LOADING CONSIDERED IN DESIGNINGItem Description Yes No1 Internal pressure [ √ ] [ ]2 External pressure [ ] [ √ ]3 Weight of vessel [ √ ] [ ]4 Weight of normal contents under operation conditions [ ] [√ ]5 Weight of normal contents under test conditions [ √ ] [ ]6 Superimposed static reactions from weight of attached equipment [ ] [ √ ]7 The attachments of internals[ ] [ √ ]8 The attachments of vessel supports (skirt, legs, saddles etc.) [ √ ] [ ]9 The attachments of lifting lugs [ √ ] [ ]10 Cyclic and dynamic reactions due to pressure [ ] [ √ ]11 Cyclic and dynamic reactions due to thermal variations [ ] [ √ ]12 Cyclic and dynamic reactions due to equipment mounted on the vessel [ ] [ √ ]13 Cyclic and dynamic reactions due to mechanical loadings [ ] [ √ ]14 Wind reactions [ ] [ √ ]15 Snow reactions [ ] [ √ ]16 Seismic reactions [ ] [ √ ]17 Impact reactions, such as those due to fluid shock [ ] [ √ ]18 Temperature gradients [ ] [ √ ]19 Differential thermal expansion [ ] [ √ ]20 Abnormal pressure, such as those caused by deflagration [ ] [ √ ]21 Test pressure and coincident static head acting during the test[√ ] [ ] (See UG-99)LIST OF NOZZLESFIG.1-1 Brief Drawing of Shell2. THICKNESS OF CYLINDRICAL SHELL UNDER INTERNAL PRESSUREASME SEC.Ⅷ DIV.1 UG-27 ● Part: Shell ● Design pressure P (MPa) : 1.3 ● Design temperature (℃):50● Material: SA-516M Gr.485● Maximum allowable stress value at design temperature S d (MPa) : 138 ● Maximum allowable stress value at test temperature S t (MPa) : 138 ● Height to point under considerationH (m) : 1.900 ● Density of test medium (water) at test temperature ρ (kg/m 3) : 1000 ● Type of welded joints in TABLE UW-12 : Type No. (1)● Radiographic examination:SPOT Per UW-11(b)● Joint efficiency (specified in UW-12) E : 0.85 ● Corrosion allowance (designated by customer) C (mm) : 1.0 ● N ominal shell thickness tn (mm) 10 ● Inside radius corroded R (mm) : 501 ● Final center line radiusR f (mm) : 505● Original center line radius (specified in UCS-79) R o (mm):∞（Infinity ）(1) Required minimum shell thickness excluding allowance (circumferential stress)0.385SE = 0.385×138×0.85=45.16> P according to UG-27(b)&(c) (a) For design conditionmm P E S PR t d 59.53.16.085.01385013.16.01min =⨯-⨯⨯=-=(b) For hydrostatic test conditionmmH E S R H P E S PR t t t 67.508.059.5)10/1000900.181.9(6.085.013850110/1000900.181.93.16.085.01385013.1)10/81.9(6.0)10/81.9(6.066662min =+=⨯⨯⨯-⨯⨯⨯⨯+⨯-⨯⨯=-+-=ρρ (2) Design thicknessRequired minimum shell thickness including allowance t=max(t min1,t min2)+C=5.67+1.0=6.67 mm (3) Provided thicknessNominal thickness (mm) 10 > t OK(4) Check minimum required thickness for paragraph UG-16 (b) (4)Minimum thickness required (including corrosion allowance) : 2.5+1=3.5mm, nominal thickness is 10mm>3.5mm, OK(5) Check extreme fiber elongation for paragraph UCS-79Maximum allowable fiber elongation without post weld heat treatment is based on the following formula: For single curvature%5%99.0%50515051050%1500<=⎪⎭⎫⎝⎛∞-⨯⨯=⎪⎪⎭⎫ ⎝⎛-=R R R t r ff None of the conditions in UCS-79 (1~5) apply, so no heat treatment after cold forming need to apply.3.THICKNESS OF ELLIPSOIDAL HEAD, PRESSURE ON CONCA VE SIDEASME SEC.ⅧDIV.1 UG-32●Part : heads●Design pressure P (MPa) : 1.3●Design temperature (℃) : 50●Material : SA-516M Gr.485 ●Maximum allowable stress value at design temperature S d(MPa) : 138●Maximum allowable stress value at test temperature S t(MPa) : 138●Height to point under consideration (bottom head) H (m) : 2.190●Height to point under consideration (top head) H (m) : 0.400●Density of test medium at test temperature ρ(kg/m3) : 1000●Type of welded joints in TABLE UW-12 : Seamless●Radiographic examination (A) : N.A●Weld joining heads to shell : Type No. (1)，SPOT Per UW-11(b)●Joint efficiency (specified in UW-12(d)) E : 0.85●Corrosion allowance (designated by customer) C (mm) : 1●Inside diameter of ellipsoidal head (corroded) D 1002●Inside spherical radius of hemispherical head L (mm) : 501R f (mm) : 905●Crown final centerline radius (specified in UG-32(d)and UCS-79)r f (mm): 174.25●Knuckle final centerline radius (specified in UG-32(d)and UCS-79)●Original center line radius (specified in UCS-79) R0 (mm): ∞（Infinity）(1) Required minimum head thicknessWithout joint, according to UW-12(d), E=0.85,L=0.9D=0.9×1002=901.8mm t s /L = 8.5/901.8=0.0094> 0.002 according to UG-32(d) (a) For the top head according to UG-32(d)(a-1) for design conditionRequired minimum head thickness excluding allowance t minmm P E S PD t d 56.53.12.085.0138210023.12.021min =⨯-⨯⨯⨯=-=(b) For the bottom head(b-1) for design conditionRequired minimum head thickness excluding allowance tminmm P E S PD t d 56.53.12.085.0138210023.12.022min =⨯-⨯⨯⨯=-=(b-2) for hydrostatic test condition(Due to same dimension for ellipsoidal heads, the bottom head will be applied forcalculation)mmH E S D H P E S PD t t t 65.509.056.5)10/1000190.281.9(2.085.01382100210/1000190.281.93.12.085.0138210023.1)10/81.9(2.02)10/81.9(2.0266663min =+=⨯⨯⨯-⨯⨯⨯⨯⨯+⨯-⨯⨯⨯=-+-=ρρ (2) Design thicknessRequired minimum head thickness including allowance t=max(t min1,t min2,t min3)+C=5.65+1.0=6.65 mm(3) Provided thicknessNominal thickness (mm) 10Minimum thickness after forming (mm) 8.5 ≥ t OK(4) Check minimum head thickness for hemispherical head from paragraph UG-32 (b) & (f)0.665SE = 0.665 × 138× 1=91.77 MPa >PRequired minimum hemispherical head thicknessmm P SE PL t h 36.23.12.0113825013.12.02min =⨯-⨯⨯⨯=-=tr=t minh /E=2.36/0.85=2.78 mm < 8.5 mm OK(5) Check minimum required thickness for paragraph UG-16(b)(4)Minimum thickness required (including corrosion allowance) : 2.5+1= 3.5mm,minimum thickness after forming is 8.5mm.>3.5mm OK (6) Check extreme fiber elongation for paragraph UCS-79Maximum allowable fiber elongation without heat treatment is based on the following formula: For double curvature Crown radius elongation%5%83.0%90519051075%1750<=⎪⎭⎫⎝⎛∞-⨯⨯=⎪⎪⎭⎫ ⎝⎛-=R R R t r ff Knuckle radius elongation%5%3.4%25.174125.1741075%1750<=⎪⎭⎫⎝⎛∞-⨯⨯=⎪⎪⎭⎫ ⎝⎛-=R r r t r f f None of the conditions listed in UCS-79(d)(1) through (5) exist, so no heat treatment of heads after cold forming need to apply for SA-516M Gr.485 (P-NO.1 Group NO.2).4. THICKNESS OF NOZZLE NECK INTERNAL PRESSURE 4-1 FOR NOZZLE aASME SEC.Ⅷ DIV .1 UG-45●Design pressure P (MPa) : 1.3 ●Design temperature T (℃) : 50●Material of nozzle neck: SA-106Gr.B ●Allowablestress of nozzle neck material at design temperatureS d (MPa):118 ●Allowablestress of nozzle neck material at test temperatureS t (MPa):118●Material of shell: SA-516M Gr.485 ●Allowable stress of shell (or head) at design temperatureS s (MPa):138 ●Height to point under considerationH (m) : 1.580 ●Density of test medium at test temperature (water) ρ(kg/m 3) : 1000 ●Typeof welded joints of nozzle neck in TABLEUW-12:Seamless●Joint efficiency of nozzle neckE : 1.0 ●Corrosion allowance (designated by customer) C (mm) : 1 ●Outside radius of nozzle neckR o (mm) : 30.15 ●Nominal thickness of the standard wall pipe(B36.10M ) t std (mm) : 3.91 ●Inside radius of shell corrodedR s (mm): 501(1) Minimum required thickness of nozzle neck for par. UG-45 (a)0.385SE = 0.385× 118 ×1.00 = 45.43 > P (a) under design condition A ppendix 1-1 Required minimum thickness including allowancemmC P E S PR t d o 33.113.14.0111815.303.14.01min =+⨯+⨯⨯=++=(b)under hydrostatic test conditionRequired minimum thickness including allowancemmC H E S R H P E S PR t t ot o 334.11004.033.01)10/1000580.181.9(4.0111815.3010/1000580.181.93.14.0111815.303.1)10/81.9(4.0)10/81.9(4.066662min =++=+⨯⨯⨯+⨯⨯⨯⨯+⨯+⨯⨯=++++=ρρ (2)(3) Minimum required thickness of shell for par. UG-45 (b) (1),and UG-16 (b) (4), Es = 1.00mm3.512.575.5175.413.16.011385013.16.0=+>=+=+⨯-⨯⨯=+-=mm C P E S PR t s s s s (4)(5) Minimum thickness of standard wall pipe including allowance for par. UG-45 (b) (4)t p = 0.875t std + C = 0.875 × 3.91 + 1 =4.42mmt = (the smaller value of t s or t p ) per UG-45(b)= 4.42mm. > t min1,t min2(6) Provided thicknessNominal thickness (mm) 5.54Minimum thickness (mm) 5.54×0.875 =4.8475 ≥ t OK4-2 FOR NOZZLE bASME SEC.Ⅷ DIV .1 UG-45●Design pressure P (MPa): 1.3●Design temperature T (℃) : 50●Material of nozzle neck: SA-106Gr.B●Allowablestress of nozzle neck material at design temperatureS d (MPa):118 ●Allowablestress of nozzle neck material at test temperatureS t (MPa):118●Material of shell: SA-516M Gr.485 ●Allowable stress of shell (or head) at design temperatureS s (MPa):138 ●Height to point under considerationH (m) : 0.680 ●Density of test medium at test temperature (water) ρ(kg/m 3) : 1000 ●Typeof welded joints of nozzle neck in TABLEUW-12:Seamless●Joint efficiency of nozzle neckE : 1.0 ●Corrosion allowance (designated by customer) C (mm) : 1 ●Outside radius of nozzle neckR o (mm) : 30.15 ●Nominal thickness of the standard wall pipe(B36.10M ) t std (mm) : 3.91 ●Inside radius of shell corrodedR s (mm): 501(1) Minimum required thickness of nozzle neck for par. UG-45 (a)0.385SE = 0.385× 118 ×1.00 = 45.43 > P (a) under design condition A ppendix 1-1 Required minimum thickness including allowancemm C P E S PR t d o 33.113.14.0111815.303.14.01min =+⨯+⨯⨯=++=(b)under hydrostatic test conditionRequired minimum thickness including allowancemmC H E S R H P E S PR t t o t o 332.11002.033.01)10/1000680.081.9(4.0111815.3010/1000680.081.93.14.0111815.303.1)10/81.9(4.0)10/81.9(4.066662min =++=+⨯⨯⨯+⨯⨯⨯⨯+⨯+⨯⨯=++++=ρρ (2) Minimum required thickness of shell for par. UG-45 (b) (1),and UG-16 (b) (4), Es = 1.00mm3.512.575.5175.413.16.011385013.16.0=+>=+=+⨯-⨯⨯=+-=mm C P E S PR t s s s s(3) Minimum thickness of standard wall pipe including allowance for par. UG-45 (b) (4)t p = 0.875t std + C = 0.875 × 3.91 + 1 =4.42mm t = (the smaller value of t s or t p ) per UG-45(b) = 4.42mm. > t min1,t min2(4) Provided thicknessNominal thickness (mm) 5.54Minimum thickness (mm) 5.54×0.875 =4.8475 ≥ t OK 4-3 FOR NOZZLE dASME SEC.Ⅷ DIV .1 UG-45●Design pressure P (MPa) : 1.3 ●Design temperature T (℃) : 50●Material of nozzle neck: SA-106Gr.B ●Allowablestress of nozzle neck material at design temperatureS d (MPa):118 ●Allowablestress of nozzle neck material at test temperatureS t (MPa):118●Material of shell: SA-516M Gr.485 ●Allowable stress of shell (or head) at design temperatureS s (MPa):138 ●Height to point under considerationH (m) : 0.11 ●Density of test medium at test temperature (water) ρ(k/m 3) : 1000 ●Typeof welded joints of nozzle neck in TABLEUW-12:Seamless●Joint efficiency of nozzle neckE : 1.0 ●Corrosion allowance (designated by customer) C (mm) : 1 ●Outside radius of nozzle neckR o (mm) : 24.15 ●Nominal thickness of the standard wall pipe(B36.10M )t std (mm): 3.68●Inside diameter of ellipsoidal head (corroded)D (mm) : 1002(1) Minimum required thickness of nozzle neck for par. UG-45 (a)0.385SE = 0.385× 118 ×1.00 = 45.43 > P (a) under design condition A ppendix 1-1 Required minimum thickness including allowancemm C P E S PR t d o 265.113.14.0111815.243.14.01min =+⨯+⨯⨯=++=(b)under hydrostatic test conditionRequired minimum thickness including allowancemmC H E S R H P E S PR t t o t o 2752.110002.0275.01)10/1000110.081.9(4.0111815.2410/1000110.081.93.14.0111815.243.1)10/81.9(4.0)10/81.9(4.066662min =++=+⨯⨯⨯+⨯⨯⨯⨯+⨯+⨯⨯=++++=ρρ (2) Minimum required thickness of head for par. UG-45 (b) (1),and UG-16 (b) (4), Es = 1.00m m3.512.572.5172.413.12.01138210023.12.02=+>=+=+⨯-⨯⨯⨯=+-=mm C P E S PD t s s s(3) Minimum thickness of standard wall pipe including allowance for par. UG-45 (b) (4)t p = 0.875t std + C = 0.875 × 3.68 + 1 =4.22mm t = (the smaller value of t s or t p ) per UG-45(b) = 4.22mm. > t min1,t min2(4) Provided thicknessNominal thickness (mm) 5.08Minimum thickness (mm) 5.08×0.875 =4.445≥ t OK 4-4 FOR NOZZLE fASME SEC.Ⅷ DIV .1 UG-45●Design pressure P (MPa) : 1.3 ●Design temperature T (℃) : 50●Material of nozzle neck: SA-106Gr.B ●Allowablestress of nozzle neck material at designtemperatureS d (MPa): 118 ●Allowablestress of nozzle neck material at test temperatureS t (MPa):118●Material of shell: SA-516M Gr.485 ●Allowable stress of shell (or head) at design temperatureS s (MPa):138 ●Height to point under considerationH (m) : 2.300 ●Density of test medium at test temperature (water) ρ(kg/m 3) : 1000 ●Typeof welded joints of nozzle neck in TABLEUW-12:Seamless●Joint efficiency of nozzle neckE : 1.0 ●Corrosion allowance (designated by customer) C (mm) : 1 ●Outside radius of nozzle neckR o (mm) : 24.15 ●Nominal thickness of the standard wall pipe(B36.10M ) t std (mm) : 3.68 ●Inside diameter of ellipsoidal head (corroded)D (mm): 1002(1) Minimum required thickness of nozzle neck for par. UG-45 (a)0.385SE = 0.385× 118 ×1.00 =45.43 > P (a) under design condition A ppendix 1-1 Required minimum thickness including allowancemm C P E S PR t d o 265.113.14.0111815.243.14.01min =+⨯+⨯⨯=++=(b)under hydrostatic test conditionRequired minimum thickness including allowancemmC H E S R H P E S PR t t o t o 27.11005.0265.01)10/1000300.281.9(4.0111815.2410/1000300.281.93.14.0111815.243.1)10/81.9(4.0)10/81.9(4.066662min =++=+⨯⨯⨯+⨯⨯⨯⨯+⨯+⨯⨯=++++=ρρ (2) Minimum required thickness of head for par. UG-45 (b) (1),and UG-16 (b) (4), Es = 1.00m m3.512.572.5172.413.12.01138210023.12.02=+>=+=+⨯-⨯⨯⨯=+-=mm C P E S PD t s s s(3)Minimum thickness of standard wall pipe including allowance for par. UG-45 (b) (4)t p= 0.875t std + C = 0.875 × 3.68 + 1 =4.22mmt= (the smaller value of t s or t p) per UG-45(b)= 4.22mm. > t min1,t min2(4)Provided thicknessNominal thickness (mm) 5.08Minimum thickness (mm) 5.08×0.875 =4.445 ≥t OK4-5 FOR NOZZLE c ASME SEC.ⅧDIV.1 UG-45●Design pressure P (MPa) : 1.3●Design temperature T (℃) : 50●Material of nozzle neck : SA-106Gr.B●Allowable stress of nozzle neck material at designtemperature S d (MPa) : 118●Allowable stress of nozzle neck material at testtemperature S t (MPa) : 118●Material of shell : SA-516M Gr.485●Allowable stress of shell (or head) at designtemperature S s (MPa) : 138●Height to point under consideration H (m) : 0.55●Density of test medium at test temperature (water) ρ(kg/m3) : 1000●Type of welded joints of nozzle neck in TABLEUW-12 : Seamless●Joint efficiency of nozzle neck E : 1.0●Corrosion allowance (designated by customer) C (mm) : 1●Outside radius of nozzle neck R o (mm) : 10.65t std (mm) : 2.77●Nominal thickness of the standard wall pipe(B36.10M)Per UG45(b)(4) note26 OD38 next larger pipe size OD42.2●Inside radius of shell corroded R s(mm) : 501(1) Minimum required thickness of nozzle neck for par. UG-45 (a)0.385SE = 0.385× 118 ×1.00 = 45.43 > P (a) under design condition A ppendix 1-1 Required minimum thickness including allowancemm C P E S PR t d o 12.113.14.0111865.103.14.01min =+⨯+⨯⨯=++=(b)under hydrostatic test conditionRequired minimum thickness including allowancemmC H E S R H P E S PR t t o t o 1205.110005.012.01)10/1000550.081.9(4.0111865.1010/1000550.081.93.14.0111865.103.1)10/81.9(4.0)10/81.9(4.066662min =++=+⨯⨯⨯+⨯⨯⨯⨯+⨯+⨯⨯=++++=ρρ (2) Minimum required thickness of shell for par. UG-45 (b) (1),and UG-16 (b) (4), Es = 1.00mm3.512.575.5175.413.16.011385013.16.0=+>=+=+⨯-⨯⨯=+-=mm C P E S PR t s s s s(3) Minimum thickness of standard wall pipe including allowance for par. UG-45 (b) (4)t p = 0.875t std + C = 0.875 × 2.77 + 1 =3.42mm t = (the smaller value of t s or t p ) per UG-45(b) = 3.42mm. > t min1,t min2(4) Provided thicknessNominal thickness (mm) 4.78Minimum thickness (mm) 4.78×0.875 =4.1825 ≥ t OK 4-6 FOR MANHOLE NOZZLE eASME SEC.Ⅷ DIV .1 UG-45●Design pressure P (MPa) : 1.3 ●Design temperature T (℃) : 50●Material of nozzle neck: SA-516M Gr.485 ●Allowable stress of nozzle neck material at design temperatureS d (MPa):138●Allowable stress of nozzle neck material at test temperature S t (MPa) 138●Height to point under considerationH (m) : 1.57 ●Density of test medium at test temperature (water) ρ(kg/m 3) : 1000 ●Type of welded joints of nozzle neck in TABLE UW-12 Type No. (1) ●Radiographic examination of nozzle neckSPOT Per UW-11(b)●Joint efficiency of nozzle neck (specified in UW-12) E : 0.85 ●Corrosion allowance (designated by customer) C (mm) : 1 ●Outside radius of nozzle neck R o (mm) : 228.5 ●Inside radius of nozzle corroded R (mm) : 219.5 ●Inside radius of shell corroded R s (mm) : 501 ●Final center line radius of nozzle R f (mm) : 223.5 ●Original center line radius of nozzleR 0 (mm): ∞(Infinity)(1) Minimum required thickness of nozzle par. UG-45 (a) and UG-27 (c) (1)0.385SE = 0.385×138×0.85 = 45.16> P(a) under design conditionRequired minimum thickness including allowancemm C P E S PR t d 25.3125.213.16.085.01385.2193.16.01min =+=+⨯-⨯⨯=+-=(b)under hydrostatic test conditionRequired minimum thickness including allowancemmC H E S R H P E S PR t t t 28.3103.025.21)10/1000590.181.9(6.085.01385.21910/1000590.181.93.16.085.01385.2193.1)10/81.9(6.0)10/81.9(6.066662min =++=+⨯⨯⨯-⨯⨯⨯⨯+⨯-⨯⨯=+-+-=ρρ (c) With supplemental loading by flange and cover●Weight of flange and cover W =170kg ●Bending moment due to supplemental loadingUnder operating condition M 1 =170x9.81x0.260= 433.6N ·mUnder cover opened condition M 2 =170x9.81x0.560=933.9N ·mPer UG-27(c) and Appendix L, Use S = 138 × 1.5 = 207MPa (see UG-23(c))mmmm CSER MP SE PR t 84.1843015.11000015.0843.0185.02075.2286.4333.14.085.020725.2283.14.022213≈≈++=+⨯⨯⨯+⨯+⨯⨯⨯=+++=ππ mm C SE R M t 0.11000032.0185.02075.2289.9332224≈+=+⨯⨯⨯=+=ππ(2) Provided thicknessNominal thickness (mm) 10 > t min1,t min2,t 3,t 4 OK (3) Check extreme fiber elongation for paragraph UCS-79Maximum allowable fiber elongation without post weld heat treatment is based on the following formula: for single curvature%5%24.2%5.22315.2231050%1500<=⎪⎭⎫⎝⎛∞-⨯⨯=⎪⎪⎭⎫ ⎝⎛-=R R R t r ff None of the condition list in UCS-79 (d) (1-5) exists, so no heat treatment after cold forming need to apply.5Max. Allowable working pressure (corroded)The maximum allowable working pressure may be assumed to be the same as the design pressure when calculations are not made to determine the maximum allowable working pressure.(ASME SEC.ⅧDIV.1 UG-99 notes: 34)So we take the maximum allowable working pressure is 1.3MPa at 50 ℃6 HYDROSTATIC TEST PRESSURE AND TEMPERA TUREASME SEC. ⅧDIV.1 UG-99 ●Maximum allowable working pressure (Hot & Corroded) * (MPa) : 1.3 at 50 ℃●Hydrostatic test pressure (MPa) : 1.69●Design temperature (℃) : 50●Test temperature (℃) : 5～40●Minimum design metal temperature (℃) : -29●Material of parts of the vessel : See table 5.1●Allowable stress of vessel wall at design temperature S d (MPa) : See table 5.1●Allowable stress of vessel wall at test temperature S t (MPa) : See table 5.1*: The maximum allowable working pressure may be assumed to be the same as the design pressure.(specified in UG-99 note34)(1)Minimum required test pressure per UG-99 (b)Table 5.1 Hydrostatic Test Pressure per UG-99 (b)(2)Provided test pressure per UG-99 (h)Hydrostatic test pressure (MPa) is 1.69 at 5~40℃7REINFORCEMENT FOR OPENINGS7-1 Since the welded nozzles a(DN50)、f(DN50)、c(DN15)、d(DN40) and f(DN40) are neither subject to rapid fluctuations in pressure nor larger than 89mm, reinforcement of openings is not required. [UG-36 (c) (3)]7-2 For manhole nozzle e(DN450)per UG-37●Internal design pressure P (MPa) : 1.3●Design temperature (℃) : 50●Material of the vessel wall : SA-516M Gr.485 ●Allowable stress of the vessel wall at design temperature S V (MPa) : 138●Material of the nozzle wall : SA-516M Gr.485 ●Allowable stress of the nozzle wall at design temperature S n (MPa) : 138●Corrosion allowance (designated by customer) C (mm) : 1●Inside radius of shell corroded R (mm) : 501●Analysis thickness of the vessel wall corroded t (mm) : 9●Outside radius of the nozzle R no(mm) : 228.5●Inside radius of the nozzle corroded R n (mm) : 219.5●Analysis thickness of nozzle wall corrodedt n (mm) : 9 ●Finished diameter of opening corrodedd (mm) : 439 ●Leg length of outward nozzle fillet weldt nc (mm): 10●Angle of plane with longitudinal axis θ (deg) : 0.0 ●Correction factorF: 1.07-2-1 Size of openingSince ID is 1000mm, according to UG-36(b) (1), one half the vessel diameter is 500mm, and doesn ’t exceed 500mm, therefore, 500mm is maximum limit without considering supplemental rules of 1-7.Now, the diameter of opening is 439mm, so supplemental rules of 1-7 are not applied. 7-2-2 Wall thicknesses RequiredShell Required thickness of a seamless shell t r (E=1.0)mm P E S PR t V r 75.43.16.011385013.16.0=⨯-⨯⨯=-=Nozzle Minimum nozzle thickness due to pressure t rn (E 1=1.0)mm P E S PR t n no rn 14.23.14.011385.2283.14.01=⨯+⨯⨯=+=7-2-3 Material Strength Reduction FactorStrength reduction factor for nozzle f r1 f r1=S n /S V =138/138=1.0Strength reduction factor for nozzle f r2 f r2=S n /S V =138/138=1.07-2-4 Check for limits of reinforcement: 7-2-4(a)Limit parallel to the vessel wall:larger of d=439mm or Rn+tn+t=219.5+9+9=237.5mm Use 439mm7-2-4(a)Limit normal to the vessel wall:smaller of 2.5t==2.5×9=22.5mm or 2.5tn+te==2.5×9+0=22.5mm Use 22..5mm7-2-5Area of reinforcement required Area available in shell A 1[][]()()21111175.1865075.419143912mm f Ft t E t Ft t E d A r r n r =-⨯-⨯⨯=----=()()()()()()211112153075.4191992122mm f Ft t E t Ft t E t t A r r n r n =-⨯-⨯⨯+⨯=----+= A 1=the larger of (A 11,A 12)=1865.75 mm 2 Area available in nozzle projecting outward A 2()()22217.3089114.2955mm t f t t A r rn n =⨯⨯-⨯=-=()()22227.3089114.2955mm t f t t A n r rn n =⨯⨯-⨯=-=A 2=the smaller of (A 21,A 22)=308.7 mm 2 Area available in welds A 4 Area available in outward weld A 412222341100110)(mm f t A r L =⨯==A 4=A 41+A 42+A 43=100+0+0=100 mm 2 Total Area availableTotalA=A 1+A 2+A 3+A 4=1865.75+308.7+0+100=2274.75 mm 2 Total Area RequiredTotalA mm f F t t F dt A r r n r <=+⨯⨯=-+=2125.20850175.4439)1(2So the opening is adequately reinforced.GENERAL NOTE8 Strength calculations for nozzle attachment welds for pressure loadingFor nozzle a (DN50)、b (DN50)、c(DN15)、d(DN40)、e(DN450) and f(DN40) because their welded types are follow Fig.UW – 16.1 sketch (c) so the strength calculations for nozzle attachment welds for pressure loading are not required [UW – 15 (b)].9.Check the adequacy of the attachment welds at openings9-1 For DN50 nozzle (a and b)Size of weld required [UW – 16 (c), Fig. UW – 16.1 sketch (c)]Outer fillet weld:0.7 t min= 0.7×5.54=3.88 mm (min. Throat required)t c= the smaller of (0.7 t min. or 6mm)= 3.88mmActual fillet weld sizet c = 5mm (actual) > 3.88mm OKWeld sizes are satisfactory.9-2 For DN40 nozzle (d and f)Size of weld required [UW – 16 (c), Fig. UW – 16.1 sketch (c)] Outer fillet weld:0.7 t min. = 0.7×5.08=3.56mm (min. Throat required)t c= the smaller of (0.7 t min or 6mm)= 3.56 mmActual fillet weld sizet c= 5mm (actual) >3.56mm OKWeld sizes are satisfactory.9-3 For DN15 nozzles (c)Size of weld required [UW – 16 (c), Fig. UW – 16.1 sketch (e)] Outer fillet weld:0.7 t min = 0.7 × 4.78= 3.35mmt c= the smaller of (0.7t min or 6mm)= 3.35mmActual fillet weld sizet c = 5mm (actual) > 3.35mm OKWeld sizes are satisfactory.9-4 For DN450 Manhole nozzle (e)Size of weld required [UW – 16 (c), Fig. UW – 16.1 sketch (c)] Outer fillet weld:0.7 t min= 0.7×10 =7mmt c= the smaller of (0.7t min or 6mm)=6mmActual fillet weld sizet c = 7mm (actual) > 6mm OKWeld sizes are satisfactory.10.Check flange to nozzle neck weldsSize of weld required [UW – 21 (b), Fig. UW – 21 sketch (1)] x min=the lesser of 1.4t min or the thickness of the hub,t min= the smaller thickness of nozzle or hub.t hub= the thickness of the hub of Flange accoding to ASME B16.5-2003 10-1 For DN50 nozzle (a and b)t n=5.54mm, t hub =8.05mm, t min=5.54mm.1.4t min= 1.4×5.54 =7.76mmx min=7.76mmActual fillet weld sizex = 8mm (actual) > 7.76mm OK10-2 For DN40 nozzle (d and f)t n=5.08mm, t hub =7.75mm, t min=5.08mm.1.4t min= 1.4×5.08 =7.11mmx min=7.11mmActual fillet weld sizex = 8mm (actual) > 7.11mm OK10-3 For DN15 nozzle (c)t n=4.78mm, t hub =3.95mm, t min=3.95mm.1.4t min= 1.4×3.95 =5.53mmx min=3.95mmActual fillet weld sizex = 4mm (actual) > 3.95mm OK10-4 For DN450 nozzle (e)t n=10mm, t hub =21.6mm, t min=10mm.1.4t min= 1.4×10=14mmx min=14mmActual fillet weld sizex = 14mm (actual) = 14mm OK11Design of the supporting legs according to ( Appendix A of JB/T4712.4-2007) 11-1 Actual Load Q on Supporting LegEarthquake loading and wind loading need not be considered.Installation Size D=630mmEccentric Load G e=200×9.81=1962N Height from horizontal force acting point to base plate H=1490mmUnequal Factor k=1Total Mass m0=900kgNumber of Supporting Leg n=3Vessel outside diameter D0=1020mmTotal Vessel Height H0=2525mm。
ASME中国制造-国外储罐计算 API 620 Tank Calculations
LENGTH WIDTH
STANDARD SHEET Length of the sheet, feet Width of the sheet, feet Area of Standard Sheet, m2
AREA STD S: DENSITY
Net Tanks Capacity (Barrels): Net Tanks Capacity (Gallons):
Net Tanks Capacity (Liters): Net Tanks Capacity (Mts3):
18.00 0.35 9.02 6.35 1.70 13,424.16
18.00 0.31 7.94 10.00 2.68 21,140.41
TWALL-A6 = TWALL-A6n =
TWALL-A7 = TWALL-A7n =
TWALL-A8 = TWALL-A8n =
TWALL-A9 = TWALL-A9n = TWALL-A10 = TWALL-A10n =
Vct=
Pct=
Minimum Thickness of sheet in Ring 5, mm Thickness of Sheet on Ring 5 Nominal, mm Minimum Thickness of sheet in Ring 6, mm Thickness of Sheet on Ring 6 Nominal, mm Minimum Thickness of sheet in Ring 7, mm Thickness of Sheet on Ring 7 Nominal, mm Minimum Thickness of sheet in Ring 8, mm Thickness of Sheet on Ring 8 Nominal, mm Minimum Thickness of sheet in Ring 9, mm Thickness of Sheet on Ring 9 Nominal, mm Minimum Thickness of sheet in Ring 10, mm Thickness of Sheet on Ring 10 Nominal, mm
玻璃钢罐体力学性能校核计算书(基于ASME标准)概要
缠绕大罐容器罐体力学性能校核计算书年月日合同编号：图纸编号：设备名称：制造单位：1.设计条件1.1工况参数:设计内压：______ Pa 设计外压：______ Pa 工作介质：______ 设计温度：______℃介质比重：______ 设计风压：______ Pa 抗震烈度：______ 积雪载荷：______ Pa 罐顶附加载荷：____ Pa 罐体附加载荷：____ Pa1.2几何参数:设备直径：______ mm 设备总高：______ mm设备容积：______ m32.设计依据标准规范主要参照ASME RTP-1-2007、HG/T 20696、HG/3983、JC/T587、Q/SH1020、SH3046、GB 50011（建筑抗震设计规范）等标准。
（上述未标注具体年份的，均参考依据最新版标准）3.计算过程（计算参数、抵抗外载荷稳定性、罐体刚度、罐体强度四个方面） 3.1 计算参数根据给定工况条件，按照ASME-RTP-1-2007标准计算方法，初步得出分段计算壁厚（见附件1），具体材料力学参数如下（见表1)。
3.2 载荷计算 3.2.1封头部分3.2.1.1设计内压力计算其中：K ——为超载系数,K=1.2 P max ——为罐内为设计压力q 1 ——为罐顶单位面积自重,pa1max q KPP -=内3.2.1.2设计外压力计算其中：q2——为罐内设计负压q3——为总附加载荷,顶部活载+雪载荷,pa3.2.2筒体部分3.2.2.1 设计内压力计算其中: H ——为罐内任意截面处贮液高度。
γ ——为贮液比重。
3.2.2.2 设计外压力计算 其中: K1——为体形系数。
K1=1.0K2——为风压转换系数,K2=2.25Kz ——为风压高度变化系数, Kz=1.0 W 0——为设计风压,paK3——为滞后系数，K3=1.2。
P ——为设计外压，常压容器取500pa 。
3.2.2.3 地震载荷计算（采用动液压力理论）其中: Cz ——为综合影响系数，取Cz=0.4；αmax ——为地震影响系数，取αmax =0.23W ——为产生地震载荷的贮罐总重量，取 321q q qP ++=外H KPγ+=max P 内P K W K K K z 3021P +=外WC Q z m ax 0α='W F W r =Fr ——为动液系数W'——为贮罐内贮液重量,N地震弯矩:其中: Hw ——为贮罐底面至贮液面的高度,m3.2.2.4风载荷计算 （取风载荷作用于贮罐重心位置）其中: A ——为风载荷作用面积，A=H ×DN ；C ——为形状系数,C=0.7风弯距：3.3 筒身应力计算 3.3.1 环向应力3.3.1.1 环向薄膜应力计算3.3.1.2底端部弯矩引起的环向应力其中: M ——为底部最大弯矩3.3.1.3组合环向应力拉应力： 其中:为有正压时，其他为零；2H M w0Q =AW CK Q z 0=[]拉压y y y y σσσσ≤+=21HQ M 21=()tDNP P y 21外内-=σ2111226tD MD y =σ1y σ压应力： 其中: 为有负压时，其他为零。
ASME强度计算（1）
ASME强度计算（1）1最大工作工作压力P 12.992筒体外径D 273.13筒体取用壁厚t 44.45下偏差百分数m 0.1254筒体下偏差c10.125*t5.556255腐蚀余量c216筒体计算壁厚tj t-c1-c237.893757筒体内径Dn D-2t 184.2筒体内半径Rv Dn/292.18筒体许用应力S 1179减弱系数E 详见下表110温度系数y 见P130.411理论壁厚tl PD/2SE+2yP 14.515912最小需要厚度tmin tl+c1+c221.0721513未减弱筒体理论壁厚tv PD/2S*1+2yP 14.5159加强计算时未减弱筒体理论壁厚tr PRv/Sv-(1-y)P 10.9552514系数kk PD/1.82St 0.37480215最大允许开孔尺寸dmax2.75[Dt(1-k)]1/36.254276判断是否需要进行补强(1)管接头外径dw 114.3(2)管接头壁厚tn 22.225(3)实际最大开孔尺寸dsj 插入式结构时：管子外径减2倍壁厚254(4)4倍单孔直径4dsj1016(5)判断实际开孔是否大于最大允许开孔尺寸不满足条件，需要加强。
(6)判断4倍实际开孔是否小于筒体内径不满足条件，需要加强。
(7)判断是否需要进行补强FALSEdsj<=dmax 或 Dn>=4dsjFALSE11(1)管孔1直径d145.3136(2)管孔2直径d245.3136(3)管孔直径d45.3136以下红色字体的数据为输入部分ASME强度计算计算纵向减弱系数(4)管孔节距p254(5)纵向减弱系数p-d/p0.821612(1)管孔1直径d155.8038(2)管孔2直径d255.8038(3)管孔平均直径d (d1+d2)/255.8038(4)筒体中径R[D-(t-c1-c2)]/2117.6031(5)管孔间度数53(6)弧度0.925024(7)管孔横向节距a108.7858(8)横向减弱系数a-d/a0.97406113(1)管孔1直径d129.1846(2)管孔2直径d229.1846(3)管孔平均直径d (d1+d2)/229.1846(4)管孔纵向节距p 114.3(5)筒体中径R[D-(t-c1-c2)]/2117.6031(6)管孔间度数53(7)弧度0.925024(8)管孔横向节距a 108.7858(9)管孔斜向节距p'((p/2)2+b 2)0.597(10)纵向减弱系数p-d/p 0.744667(11)比值p'/p j(p'/p)20.720197(12)斜向减弱系数图PG-52.189.8656214(1)管孔1直径d155.8038(2)管孔2直径d255.8038(3)管孔平均直径d (d1+d2)/255.8038(4)筒体中径R[D-(t-c1-c2)]/2117.6031(5)管孔间度数53(6)弧度0.925024(7)横向展开长度a 108.7858计算斜向减弱系数(规则错列布置)计算斜向减弱系数(不规则布置)计算横向减弱系数(8)管孔纵向节距s 95.25(9)管孔斜向节距p'144.5922(10)管孔连线与纵轴夹角的正切值sec θp'/s 1.518028(11)斜向当量减弱系数图PG-52.673.71537插入式1骑座式(1)管接头形式插入式或骑座式插入式(2)管接头许用应力Sn 107.5862(3)管接头应力折算系数fr1Sn/Sv0.91954(4)管子外径dl 88.9(5)管子壁厚tn 15.24(6)管子内径dnj dl-2*tn 58.42(7)管子外伸长度Hw 外筒壁至外管端91.2876(8)管子内伸长度Hn 内筒壁顶点至内管端172.72(9)左侧相邻管外径dlz 无管时取为00(10)左侧相邻管壁厚tnz 无管时取为00(11)左侧管内径dz dlz-2*tnz 0(12)右侧相邻管外径dly 无管时取为00(13)右侧相邻管壁厚tny 无管时取为00(14)右侧管内径dy dly-2*tny0(15)外侧焊缝高度wl10(16)内侧焊缝高度wl22确定有效补强范围(1)管接头纵向半补强范围(离管子中心线距离) Lg max(d,0.5dnj+tn+t)88.9(2)左侧相邻管纵向半补强范围(离管子中心线距离)Lz max(d,0.5dnj+tn+t)z 0(3)右侧相邻管纵向半补强范围(离管子中心线距离)Ly max(d,0.5dnj+tn+t)y0(4)管接头与左侧相邻管间的节距pz 无相邻管时取1000inch 25400(5)管接头与右侧相邻管间的节距py无相邻管时取1000inch25400(6)判断左侧补强区是否重叠不相互重叠(7)判断右侧补强区是否重叠不相互重叠(8)左侧补强宽度(离管子中心线距离)Bz pzdnj/(dz+dnj)88.9(9)右侧补强宽度(离管子中心线距离)By pyd/(dy+d)88.9开孔补强计算管接头参数(10)外伸补强高度hw Min(2.5t,2.5tn)38.1(11)内伸补强高度hn Min(2.5t,2.5tn,Hn)38.13考虑补强时的最小需要壁厚(1)筒体的最小需要壁厚tr PRv/[Sv-(1-y)P 1.4478(2)管接头的最小需要壁厚trn P(0.5dl-tn)/[Sn-(1-y)P 3.80228 4加强面积计算(1)焊缝金属应力折算系数fr21(2)截面与纵面轴间夹角a0(3)该夹角所产生的修正系数F图PG-33.31(4)筒体富裕壁厚补强面积A1[(Bz-dl/2)+(By-dl/2)]*(t-Ftr)(insert) [(Bz-d/2)+(By-d/2)]*(t-Ftr)(set on)3822.896(5)筒外管接头加强面积A22(tn-trn)hw*fr1801.4292(6)筒内管接头加强面积A32tn(hn+t)*fr12313.677(7)焊缝加强面积A4wl1*wl1+wl2*wl2*fr20(8)总加强面积A A1+A2+A3+A46938.002(9)需要加强面积Ar(d+2tn)*trF128.7094(10)判断加强面积是否满足要求A≥Ar,故满足加强条件英制1公制MPa630psi12.99Mpa mm7inch273.1mm mm0.114inch44.45mmmmmmmmmmmmMPa13600psi117MPa#NAME?mmmm0.57149inchmm0.43131inchinch158.859mm英制公制mm 4.5inch114mm mm0.875inch8.6mm mm10inch12mm mm英制公制mm 1.784inch114mm mm 1.784inch114mm mm英制公制mm 2.197inch114mm mm 2.197inch114mm mmmmmm英制公制mm 1.149inch114mm mm 1.149114mm mmmmmmmm0.8486英制公制mm 2.197inch45.32mm mm 2.197inch141mm mmmmmmmm英制公制Mpa 15600psi 114Mpa mm 3.5inch 114mmmm 0.6inch25mm mm 3.594inch 76mm 6.8inch 56mm mm 0inch 114mm 0inch22mm mm 0inch 114mm 0inch22mm mm 0inch 28mminch 13mm 3.5inch mm 0inch mm0inch 1000inch 1200mm 1000inch228mmmm 3.5inch mm3.5inch公制英制mm0.057inch mm0.150inch度mm2 5.926inch2mm2 1.242inch2 mm2 3.586inch2 mm20.000inch2 mm210.754inch2 mm20.200inch2。
ASME 取证(专业部分)
ＡSMＥ取证试题(专业部分）一、设计方面(压力容器ＵG、UW与UCＳ)1.常规压力容器强度计算书应该包含哪些基本内容?筒体得强度计算应该考虑哪些要求?椭圆封头得强度计算应该考虑哪些要求？2.如何确定压力容器设计过程中引用标准得版本？如何考虑单位制统一得问题,规范怎么要求得？3.如何考虑规范中没有提到得计算,比如支座计算?4.压力容器得腐蚀裕量就是由设计工程师指定吗?设计工程师如何审核用户设计规范?5.对于锅炉与压力容器,静压头就是否都一定要考虑？6.压缩空气储罐得受压件最小要求壁厚就是多少?7.哪些材料可以允许用于制造压力容器得受压件？允许得螺栓，螺母材料就是哪些？压力容器非受压件就是否需要就是AＳMＥ材料？8.压力容器人孔得设计方面得有什么要求?容器排污孔得位置有什么要求?计算书中得所有得尺寸就是腐蚀前还就是腐蚀后?9.判定压力容器就是否需要焊后热处理得因素有哪些?公称厚度得定义?10.什么情况下压力容器必须拍片?如果规范不强制拍片，那么由谁决定拍片得比例？11.如果容器接管开孔在焊缝上，接管满足ＵG－3６（ｃ)(3)得要求不需要计算开孔补强,对这样得开孔处得焊缝有没有ＲＴ得要求?12.判定压力容器就是否需要冲击试验得因素有哪些?就是否只就是受压件需要考虑低温冲击?考虑低温冲击时,控制厚度得定义？设计工程师请熟悉附录ＪJ!13.对于压力容器，免除开孔补强计算得开孔应满足什么条件？14.就是不就是所有尺寸得补强圈都可以完整得考虑为补强得范围内，即补强得范围？15.压力容器接管厚度得计算需满足那些要求？16.针对容器，考虑冲击试验时,ＳA-105,SA-５１6 Gr70 正火， SA-106B 分别属于哪一种曲线？17.一台容器打了ＲT－3标记,封头与筒体焊接用Type 1得接头形式,封头计算时得焊接接头系数为多少？18.一台容器封头为无缝,筒体纵缝ＲT抽拍，封头与筒体得环缝抽拍并同时满足UW-1１(a）5(ｂ)得要求,计算封头壁厚时得焊接接头系数为多少？筒体接头系数为多少?容器打RT-1,RＴ-2,ＲT－３还就是RＴ-4?19.SA 10６B 与 A10６Ｂ什么区别?能等同得材料吗?20.针对容器,封头成型后如何判定就是否需要成型后热处理？如何判定就是否需要带成型试板?21.如何判定焊缝强度就是否需要计算？22.压力容器得水压试验压力值如何确定？水压试验温度就是指介质温度还就是金属温度？具体得温度值有何要求？23.压力容器铭牌得要求有哪些？24.如果容器得铭牌直接装在设备上，铭牌可以装在与设备相连得支架上,这种情况下，铭牌与容器得距离有无具体得要求？二、材料方面1.SＡ－516 Gr70得质保书有哪些要求?SA-106 GｒB质保书有哪些要求？2.SA-516 Gr70 ,20ｍｍ厚,允许得尺寸变差就是多少?板材原始标记得要求就是哪些？3.B16、5法兰,材料SA-10５要求得标记有哪些?质保书要求哪些内容？就是否需要作入厂验收?4.SA-106B要求得标记有哪些?要求哪些性能试验，允许得尺寸偏差为多少?5.N, QT, Ｃｅq就是什么意思?6.ＡＳＭＥ材料如何进行验收？就是否需要复验?就是否一定需要质保书？哪些材料需要质保书?ASME焊材如何进行验收？就是否一定需要质保书?第I 卷与VIＩI-1卷对材料质保书方面得要求就是否一样？7.材料入厂验收得基本流程就是怎样得?每一过程需要哪些文件？验收合格得材料由谁指定材料追踪号？如何指定?8.谁负责登记材料追踪号得台帐？9.如果材料验收不合格,如何处理？如果需要对母材进行补焊,应该如何操作？10.如果外购得无缝封头,应该如何进行验收?采取什么样得方式追踪其材料追踪号？三、焊接方面1.手工焊,自动焊,机器焊得定义？2.哪些焊接方法能用于焊接VIＩＩ-1卷得容器?3.WＰＳ,ＰQＲ都应该分别包含哪些变素?4.ＷＰS里得非重要变素发生变化时,如何处理?5.Ｐ-No、,F-Ｎo、Ａ－No、分别含义?6.WＰＳ中得焊材不属于任何一个Ａ－No、，如何处理?7.焊工考试试样得试验有哪些项目？哪些焊接方法可以用RT替代力学性能试验？ＲT评定合格得依据就是第五卷吗？这种情况下对焊缝长度有要求吗？8.ＰQＲ机械性能包含哪些试验项目？合格依据就是什么？可以用RT代替力学性能试验吗?9.管接头与筒体得焊接接头采用骑座式，管接头尺寸为1’’, 那么焊这条焊缝得焊工应该如何进行考试?如果接头形式为插入式呢？焊工应该具有什么位置得资格?10.焊接非受压件与受压件得焊工就是否需要评定合格得焊工？就是否需要评定合格得WPS，允许进行焊接得最低温度就是多少?11.非受压件就是否一定需要就是ASMＥ材料？非受压件与受压件得焊缝要求在哪一章节?12.如果WPS评定P－NO、1材料并合格,那么这个ＷPS能覆盖哪些材料?13.如果焊工考试有F-NO、3 带垫板，那么这个焊工焊接哪些Ｆ－Ｎｏ、?14.如何维持焊工得资格？15.焊接工艺评定试板材料为ＳA-51６ Gr 70,厚度为9mm，那么弯曲半径为多少？如果试样厚度为40mｍ，那么做拉伸实验时如何处理？16.低氢焊条得烘培温度，烘培时间依据就是什么？能够回收几次?如何标识回收焊条？如何控制回收得焊条？四、检验方面1.检验员如何进行装配检查？点焊检查?焊缝检查?如果就是ＲT抽拍,由谁指定抽拍得位置？2.错边量得要求在哪一章节？焊缝余高要求在哪一章节？3.检验员在焊接前应该检查什么?焊接中检查什么?焊接后检查什么？4.如果在检验过程中出现ＮCR, 应该采取怎样得步骤？5.检验接管与筒体得角焊缝尺寸时,图纸规定得尺寸就是就是仅值沿筒体纵向得焊脚尺寸还就是针对整个焊缝焊脚？6.热处理工程师在准备焊后热处理工艺卡时,保温温度,升温速度,降温速度，如炉温度,出炉温度，保温时间依据在那一章节？7.热处理分包前与分包后如何控制?8.容器在水压试验之后，打U钢印之前,在受压件上焊接非受压件，就是否需要重新进行水压试验?9.MDＲ就是什么？如何选用相应格式得ＭDＲ? 请质检部经理负责熟悉并填写MDR。
ASME 取证(专业部分)
ASME取证试题（专业部分）一、设计方面(压力容器UG、UW和UCS)1.常规压力容器强度计算书应该包含哪些基本内容？筒体的强度计算应该考虑哪些要求？椭圆封头的强度计算应该考虑哪些要求？2.如何确定压力容器设计过程中引用标准的版本？如何考虑单位制统一的问题，规范怎么要求的？3.如何考虑规范中没有提到的计算，比如支座计算？4.压力容器的腐蚀裕量是由设计工程师指定吗？设计工程师如何审核用户设计规范？5.对于锅炉和压力容器，静压头是否都一定要考虑？6.压缩空气储罐的受压件最小要求壁厚是多少？7.哪些材料可以允许用于制造压力容器的受压件？允许的螺栓，螺母材料是哪些？压力容器非受压件是否需要是ASME 材料？8.压力容器人孔的设计方面的有什么要求？容器排污孔的位置有什么要求？计算书中的所有的尺寸是腐蚀前还是腐蚀后？9.判定压力容器是否需要焊后热处理的因素有哪些？公称厚度的定义？10.什么情况下压力容器必须拍片？如果规范不强制拍片，那么由谁决定拍片的比例？11.如果容器接管开孔在焊缝上，接管满足UG-36(c)(3)的要求不需要计算开孔补强，对这样的开孔处的焊缝有没有RT的要求？12.判定压力容器是否需要冲击试验的因素有哪些？是否只是受压件需要考虑低温冲击？考虑低温冲击时，控制厚度的定义？设计工程师请熟悉附录JJ!13.对于压力容器，免除开孔补强计算的开孔应满足什么条件？14.是不是所有尺寸的补强圈都可以完整的考虑为补强的范围内，即补强的范围？15.压力容器接管厚度的计算需满足那些要求？16.针对容器，考虑冲击试验时，SA-105,SA-516 Gr70 正火， SA-106B 分别属于哪一种曲线？17.一台容器打了RT-3标记，封头和筒体焊接用Type 1的接头形式，封头计算时的焊接接头系数为多少？18.一台容器封头为无缝，筒体纵缝RT抽拍，封头与筒体的环缝抽拍并同时满足UW-11(a)5(b)的要求，计算封头壁厚时的焊接接头系数为多少？筒体接头系数为多少？容器打RT-1,RT-2,RT-3还是RT-4?19.SA 106B 和 A106B 什么区别？能等同的材料吗？20.针对容器，封头成型后如何判定是否需要成型后热处理？如何判定是否需要带成型试板？21.如何判定焊缝强度是否需要计算？22.压力容器的水压试验压力值如何确定？水压试验温度是指介质温度还是金属温度？具体的温度值有何要求？23.压力容器铭牌的要求有哪些？24.如果容器的铭牌直接装在设备上，铭牌可以装在与设备相连的支架上，这种情况下，铭牌与容器的距离有无具体的要求？二、材料方面1.SA-516 Gr70的质保书有哪些要求？SA-106 GrB质保书有哪些要求？2.SA-516 Gr 70 ，20mm厚，允许的尺寸变差是多少？板材原始标记的要求是哪些？3.B16.5 法兰，材料SA-105 要求的标记有哪些？质保书要求哪些内容？是否需要作入厂验收？4.SA-106B要求的标记有哪些？要求哪些性能试验,允许的尺寸偏差为多少？5.N, QT, Ceq是什么意思？6.ASME 材料如何进行验收？是否需要复验？是否一定需要质保书？哪些材料需要质保书？ASME焊材如何进行验收？是否一定需要质保书？第I 卷和VIII-1卷对材料质保书方面的要求是否一样？7.材料入厂验收的基本流程是怎样的？每一过程需要哪些文件？验收合格的材料由谁指定材料追踪号？如何指定？8.谁负责登记材料追踪号的台帐？9.如果材料验收不合格，如何处理？如果需要对母材进行补焊，应该如何操作？10.如果外购的无缝封头，应该如何进行验收？采取什么样的方式追踪其材料追踪号？三、焊接方面1.手工焊，自动焊，机器焊的定义？2.哪些焊接方法能用于焊接VIII-1卷的容器？3.WPS,PQR都应该分别包含哪些变素？4.WPS里的非重要变素发生变化时，如何处理？5.P-No.,F-No. A-No.分别含义？6.WPS中的焊材不属于任何一个A-No.,如何处理？7.焊工考试试样的试验有哪些项目？哪些焊接方法可以用RT替代力学性能试验？RT评定合格的依据是第五卷吗？这种情况下对焊缝长度有要求吗？8. PQR 机械性能包含哪些试验项目？合格依据是什么？可以用RT代替力学性能试验吗？9.管接头与筒体的焊接接头采用骑座式，管接头尺寸为1’’, 那么焊这条焊缝的焊工应该如何进行考试？如果接头形式为插入式呢？焊工应该具有什么位置的资格？10.焊接非受压件与受压件的焊工是否需要评定合格的焊工？是否需要评定合格的WPS, 允许进行焊接的最低温度是多少？11.非受压件是否一定需要是ASME材料？非受压件与受压件的焊缝要求在哪一章节？12.如果WPS 评定P-NO. 1材料并合格，那么这个WPS能覆盖哪些材料？13.如果焊工考试有F-NO.3 带垫板，那么这个焊工焊接哪些F-No.？14.如何维持焊工的资格？15.焊接工艺评定试板材料为SA-516 Gr 70，厚度为9mm,那么弯曲半径为多少？如果试样厚度为40mm,那么做拉伸实验时如何处理？16.低氢焊条的烘培温度，烘培时间依据是什么？能够回收几次？如何标识回收焊条？如何控制回收的焊条？四、检验方面1.检验员如何进行装配检查？点焊检查？焊缝检查？如果是RT抽拍，由谁指定抽拍的位置？2.错边量的要求在哪一章节？焊缝余高要求在哪一章节？3.检验员在焊接前应该检查什么？焊接中检查什么？焊接后检查什么？4.如果在检验过程中出现NCR, 应该采取怎样的步骤？5.检验接管与筒体的角焊缝尺寸时，图纸规定的尺寸是是仅值沿筒体纵向的焊脚尺寸还是针对整个焊缝焊脚？6.热处理工程师在准备焊后热处理工艺卡时，保温温度，升温速度，降温速度，如炉温度，出炉温度，保温时间依据在那一章节？7.热处理分包前和分包后如何控制？8.容器在水压试验之后，打U钢印之前，在受压件上焊接非受压件，是否需要重新进行水压试验？9.MDR 是什么？如何选用相应格式的MDR? 请质检部经理负责熟悉并填写MDR。
100立方0.2Mpa不锈钢储罐压力容器强度计算书
内筒体下段内压计算 计算单位 工程公司计算所依据的标准GB/T 150.3-2011计算条件筒体简图计算压力 p c 0.52 MPa设计温度 t -196.00 ︒ C 内径 D i 3000.00 mm材料S30408(Rp1.0)# ( 板材 ) 试验温度许用应力 [σ]166.60 MPa 设计温度许用应力 [σ]t166.60 MPa 试验温度下屈服点 R eL 250.00 MPa 负偏差 C 1 0.30 mm 腐蚀裕量 C 2 0.00 mm 焊接接头系数 φ1.00厚度及重量计算计算厚度 δ = ct ic ][2P D p -φσ = 4.69mm 有效厚度 δe =δn - C 1- C 2= 7.70 mm 名义厚度 δn = 8.00 mm 重量899.22Kg压力试验时应力校核压力试验类型 气压试验试验压力值 p T = 1.10p [][]σσt = 0.3900MPa 压力试验允许通过 的应力水平 [σ]T [σ]T ≤ 0.80 R eL = 200.00MPa试验压力下 圆筒的应力 σT = p D T i e e .().+δδφ2 = 76.17 MPa校核条件 σT ≤ [σ]T 校核结果合格压力及应力计算最大允许工作压力 [p w ]= 2δσφδe t i e []()D += 0.85302MPa 设计温度下计算应力 σt= ee i c 2)(δδ+D p = 101.56 MPa [σ]tφ 166.60 MPa校核条件 [σ]tφ ≥σt结论 合格内容器上封头内压计算计算单位 工程公司 计算所依据的标准GB/T 150.3-2011 计算条件椭圆封头简图计算压力 p c 0.35 MPa设计温度 t -196.00 ︒ C 内径 D i 3000.00 mm 曲面深度 h i 750.00 mm 材料S30408 (板材) 设计温度许用应力 [σ]t166.60 MPa 试验温度许用应力 [σ] 166.60 MPa 负偏差 C 1 0.30mm 腐蚀裕量 C 2 0.50（封头加工减薄量） mm焊接接头系数 φ 1.00压力试验时应力校核压力试验类型 气压试验 试验压力值p T = 1.10pt][][σσ= 0.3900MPa 压力试验允许通过的应力[σ]t [σ]T ≤ 0.80 R eL = 200.00MPa 试验压力下封头的应力σT = φδδ.2)5.0.(eh eh i T KD p += 112.60MPa校核条件 σT ≤ [σ]T 校核结果合格厚度及重量计算形状系数K = ⎥⎥⎦⎤⎢⎢⎣⎡⎪⎪⎭⎫ ⎝⎛+2i i 2261h D = 1.0000计算厚度 δh = ct ic 5.0][2p D Kp -φσ = 3.15mm 有效厚度 δeh =δnh - C 1- C 2= 5.20 mm 最小厚度 δmin = 4.50 mm 名义厚度 δnh = 6.00 mm 结论 满足最小厚度要求 重量468.64Kg压 力 计 算最大允许工作压力 [p w ]= eh i eht 5.0][2δφδσ+KD = 0.57705MPa结论 合格内筒下封头压力计算计算单位 工程公司 计算所依据的标准GB/T 150.3-2011 计算条件椭圆封头简图计算压力 p c 0.55 MPa设计温度 t -196.00 ︒ C 内径 D i 3000.00 mm 曲面深度 h i 750.00 mm 材料S30408 (板材) 设计温度许用应力 [σ]t166.60 MPa 试验温度许用应力 [σ] 166.60 MPa 负偏差 C 1 0.30mm 腐蚀裕量 C 2 0.90（封头加工减薄量） mm焊接接头系数 φ 1.00压力试验时应力校核压力试验类型 气压试验 试验压力值p T = 1.10pt][][σσ= 0.3900MPa 压力试验允许通过的应力[σ]t [σ]T ≤ 0.80 R eL = 200.00MPa 试验压力下封头的应力σT = φδδ.2)5.0.(eh eh i T KD p += 86.13MPa校核条件 σT ≤ [σ]T 校核结果合格厚度及重量计算形状系数K = ⎥⎥⎦⎤⎢⎢⎣⎡⎪⎪⎭⎫ ⎝⎛+2i i 2261h D = 1.0000计算厚度 δh = ct ic 5.0][2p D Kp -φσ = 4.96mm 有效厚度 δeh =δnh - C 1- C 2= 6.80 mm 最小厚度 δmin = 4.50 mm 名义厚度 δnh = 8.00 mm 结论 满足最小厚度要求 重量625.86Kg压 力 计 算最大允许工作压力 [p w ]= eh i eht 5.0][2δφδσ+KD = 0.75440MPa结论 合格注：带#号的材料数据是设计者给定的。
150m3储罐强度计算书.
MPa
设计温度
65
℃
壳体型式
圆形筒体
壳体材料
名称及类型
Q345Rቤተ መጻሕፍቲ ባይዱ
板材
壳体开孔处焊接接头系数φ
0.85
壳体内直径Di
5000
mm
壳体开孔处名义厚度δn
16
mm
壳体厚度负偏差C1
0.3
mm
壳体腐蚀裕量C2
1
mm
壳体材料许用应力[σ]t
189
MPa
接管实际外伸长度
150
mm
接管实际内伸长度
0
mm
接管材料
接管计算厚度δt
0.11
mm
补强圈强度削弱系数frr
0
接管材料强度削弱系数fr
0.958
开孔直径d
69.25
mm
补强区有效宽度B
138.5
mm
接管有效外伸长度h1
18.61
mm
接管有效内伸长度h2
0
mm
开孔削弱所需的补强面积A
650.5
mm2
壳体多余金属面积A1
368.6
mm2
接管多余金属面积A2
116.4
1.69001e+08
N·mm
系数计算
K1=1
K2=1
K3=0.485135
K4=0.295241
K5=0.673288
K6=0.00791865
K6’=
K7=
K8=
K9=0.259372
C4=
C5=
筒体轴向应力计算
轴向应力计算
操作状态
54.5452
50.6886
MPa
ASME强度计算精选全文
9216 mm2
0
度
1.0
7881.7 mm2
23.4 mm
195 mm
25
mm
26
mm
103 MPa 103 MPa 390 317 390 90 533914 N
序 号
项
目
符 号
14
角焊缝强度
B
15
最小需要强度
W
16 17
据PG-37.2，因A+B＞W，故补强 件根强据度结符构合可要判求断。：其它开孔也符 合要求。
数值 单位 0.731
610 mm 101.5 mm 666.3 mm 23.72 度 6.565 0.88
430 mm 109 mm 506.7 mm 31.9 度 4.65 0.845
350 mm
94
mm
440.9 mm
37.5 度
4.7
0.87
350 mm 101.5 mm 440.9 mm 37.5 度 4.34 0.835
8
in
720 mm
195 mm
525 mm
18900 mm2
0
度
1.0
16214 mm2
402.12 mm
195 mm
207.12 mm
7456.3 mm2
90
度
0.5
4527.7 mm2
335.1 mm 109 mm 226.1 mm 8139.6 mm2
序 号
项
目
符 号
数据来源或计算公式
24
截面与纵面间夹角
序 号
项
目
符 号
数据来源或计算公式
数值 单位
150tds/d碱回收锅炉受压元件强度计算
ASME压力容器强度计算PVELITETableofContents
ASME压力容器强度计算PVELITETableofContentsTable of ContentsCover Sheet (2)Title Page (3)Warnings and Errors : (4)Input Echo : (5)XY Coordinate Calculations : (11)Internal Pressure Calculations : (12)External Pressure Calculations : (18)Element and Detail Weights : (23)Nozzle Flange MAWP : (26)Conical Section : (27)Center of Gravity Calculation : (29)Nozzle Calcs. : Noz N1 Fr20 (30)Nozzle Calcs. : Noz N1 Fr40 (32)Nozzle Calcs. : Noz N1 Fr50 (34)Nozzle Schedule : (41)Nozzle Summary : (42)MDMT Summary : (43)Vessel Design Summary : (44)Problems/Failures Summary : (47)Cover Page 2DESIGN CALCULATIONIn Accordance with ASME Section VIII Division 1ASME Code Version : 2010 Edition, 2011a AddendaAnalysis Performed by : ZISHAN ENGINEERS (PVT.) LTD.Job File : C:\DOCUMENTS AND SETTINGS\ADMINISTRATOR\桌面\UNTDate of Analysis : Oct 8,2014PV Elite 2012, January 2012Title Page 3Warnings and Errors : Step: 0 2:56p Oct 8,2014Class From To : Basic Element Checks.====================================== ==================================== Warn. 30 40 Inconsistent external pressure definition. The givenexternal pressure was not the same as the internal pressure on thefollowing element.Class From To: Check of Additional Element Data====================================== ==================================== Warn 30 40 Check UG-32(j) and UG-81 for Crown Radius > ODPV Elite is a trademark of Intergraph CADWorx & Analysis Solutions, Inc. 2012Input Echo : Step: 1 2:56p Oct 8,2014 PV Elite Vessel Analysis Program: Input DataDesign Internal Pressure (for Hydrotest) 100.00 psigDesign Internal Temperature 200 FType of Hydrotest not SpecifiedHydrotest Position HorizontalProjection of Nozzle from Vessel Top 0.0000 in.Projection of Nozzle from Vessel Bottom 0.0000 in.Minimum Design Metal Temperature -20 FType of Construction WeldedSpecial Service NoneDegree of Radiography RT 1Miscellaneous Weight Percent 0.0Use Higher Longitudinal Stresses (Flag) YSelect t for Internal Pressure (Flag) NSelect t for External Pressure (Flag) NSelect t for Axial Stress (Flag) NSelect Location for Stiff. Rings (Flag) NConsider Vortex Shedding YPerform a Corroded Hydrotest NIs this a Heat Exchanger NoUser Defined Hydro. Press. (Used if > 0) 0.0000 psig User defined MAWP 0.0000 psigUser defined MAPnc 0.0000 psigLoad Case 1 NP+EW+WI+FW+BWLoad Case 2 NP+EW+EE+FS+BSLoad Case 3 NP+OW+WI+FW+BWLoad Case 4 NP+OW+EQ+FS+BSLoad Case 5 NP+HW+HILoad Case 6 NP+HW+HELoad Case 7 IP+OW+WI+FW+BWLoad Case 8 IP+OW+EQ+FS+BSLoad Case 9 EP+OW+WI+FW+BWLoad Case 10 EP+OW+EQ+FS+BSLoad Case 11 HP+HW+HILoad Case 12 HP+HW+HELoad Case 13 IP+WE+EWLoad Case 14 IP+WF+CWLoad Case 15 IP+VO+OWLoad Case 16 IP+VE+EWLoad Case 17 NP+VO+OWLoad Case 18 FS+BS+IP+OWLoad Case 19 FS+BS+EP+OW。
ASME取证用储罐强度计算书汇总
ASME取证⽤储罐强度计算书汇总设计计算书Design Calculation Sheet1. 设计参数和条件Design Data and Condition:1) 设计所遵循的规范Applicable Design Code:ASME SectionⅧ，Div.1, 20132) 设计压⼒(p) : 内部1.3MpaDesign Pressure (p): Internal 1.3 MPa3) 设计温度: 60℃Design Temperature: 60℃4) 焊接接头系数(E): 壳体为0.85，封头为0.85(⽆缝)Joint Efficiency (E): 0.85 for Shell and 0.85 for Heads（seamless）5) 材料最⼤许⽤应⼒Material Max. Allowable Stress:Based on ASME Code Sec.Ⅱ, Part D Table 1A壳体和封头: SA516 Gr. 485，60℃时为138MPaShell & Heads: SA516 Gr. 485 Material Max. Allowable Stress is 138MPa at 60℃；接管: SA105M钢，60℃时为138MPaNozzles：SA105M Steel Material Max. Allowable Stress 138 MPa at 60℃；6) 媒介: 空⽓Medium: Air (Non lethal)7) 封头类型: 2:1椭圆封头Head type: 2:1Ellipsoidal Head；8) 其他载荷: 依据“客户设计说明书”（Doc. No. TS-15-01 Rev.0）Others Loadings: As Shown in“Customer’s Design Specification”(Doc. No. TS-15-01 Rev. 0)9) 腐蚀余度:2.0 mmCorrosion Allowance: 2.0 mm10) 容器外形和尺⼨：依据“客户设计说明书”（Doc. No. TS-15-01 Rev.0）Layout of Vessel and Dimension:As Shown in“Customer’s Design Specification”(Doc. No. TS-15-01 Rev. 0) 11) 钢印要求: 要求ASME标识Stamp required: ASME Certification Mark required12) NB要求: 不要求NB钢印NB stamp required: NO “NB” stamp required.Verify for UG-22 LoadingPressure符号 Symbols:t= 壳体要求最⼩厚度，mmt = minimum required thickness of shell, mm P = 内部设计压⼒, 1.3MPaP = internal design pressure, 1.3 MPa [see UG-21] R = 预计容器筒内半径， 250mmR = inside radius of the shell course under consideration, 250mm S = 最⼤许⽤应⼒值，138MPa S = maximum allowable stress value, 138MPa [ see ASME Code Part II DTable 1A for material SA-516 Gr.485] E = 焊接接头系数，0.85E = joint efficiency, 0.85 [see Table UW-12(1)]Since P=1.3MPa is less than 0.385SE=45.16MPa, Formula UG-27(c)(1) is used:)(2.811.36.085.0381)2025(3.16.0mm P SE PR t =?-?+?=-=考虑腐蚀裕量：Consider of corrosion allowable: tr= t + Ca = 2.81 + 2.0 = 4.81mmThese formulas will govern only when the circumferential joint efficiency is less than one-half the longitudinal joint efficiency, according to UG-27(c) (2) note 20, the formula UG-27(c) (2) for longitudinal stress needn’t considered. 公称钢板规则厚度=10mmNominal Plate Thickness Ordered = 10 mm钢板厚度可允许下偏差=0.25mm[see UG-16(c)] Plate Under tolerance=0.25 mm [ see UG-16(c)]UG-16 (b)(4) the minimum thickness of pressure retaining components >2.5mm for air service(exclusive any corrosion allowance). 实际使⽤厚度=10-0.25=9.75> 4.81mm ，并且也>2.5+2mm,可以。
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设计计算书Design Calculation Sheet1. 设计参数和条件Design Data and Condition:1) 设计所遵循的规范Applicable Design Code:ASME SectionⅧ，Div.1, 20132) 设计压力(p) : 内部1.3MpaDesign Pressure (p): Internal 1.3 MPa3) 设计温度: 60℃Design Temperature: 60℃4) 焊接接头系数(E): 壳体为0.85，封头为0.85(无缝)Joint Efficiency (E): 0.85 for Shell and 0.85 for Heads（seamless）5) 材料最大许用应力Material Max. Allowable Stress:Based on ASME Code Sec.Ⅱ, Part D Table 1A壳体和封头: SA516 Gr. 485，60℃时为138MPaShell & Heads: SA516 Gr. 485 Material Max. Allowable Stress is 138MPa at 60℃；接管: SA105M钢，60℃时为138MPaNozzles：SA105M Steel Material Max. Allowable Stress 138 MPa at 60℃；6) 媒介: 空气Medium: Air (Non lethal)7) 封头类型: 2:1椭圆封头Head type: 2:1Ellipsoidal Head；8) 其他载荷: 依据“客户设计说明书”（Doc. No. TS-15-01 Rev.0）Others Loadings: As Shown in“Customer’s Design Specification”(Doc. No. TS-15-01 Rev. 0)9) 腐蚀余度:2.0 mmCorrosion Allowance: 2.0 mm10) 容器外形和尺寸：依据“客户设计说明书”（Doc. No. TS-15-01 Rev.0）Layout of Vessel and Dimension:As Shown in“Customer’s Design Specification”(Doc. No. TS-15-01 Rev. 0) 11) 钢印要求: 要求ASME标识Stamp required: ASME Certification Mark required12) NB要求: 不要求NB钢印NB stamp required: NO ―NB‖ stamp required.Verify for UG-22 LoadingPressure符号 Symbols:t= 壳体要求最小厚度，mmt = minimum required thickness of shell, mm P = 内部设计压力, 1.3MPaP = internal design pressure, 1.3 MPa [see UG-21] R = 预计容器筒内半径， 250mmR = inside radius of the shell course under consideration, 250mm S = 最大许用应力值，138MPaS = maximum allowable stress value, 138MPa [ see ASME Code Part II DTable 1A for material SA-516 Gr.485] E = 焊接接头系数，0.85E = joint efficiency, 0.85 [see Table UW-12(1)]Since P=1.3MPa is less than 0.385SE=45.16MPa, Formula UG-27(c)(1) is used:)(2.811.36.085.0381)2025(3.16.0mm P SE PR t =⨯-⨯+⨯=-=考虑腐蚀裕量：Consider of corrosion allowable: tr= t + Ca = 2.81 + 2.0 = 4.81mmThese formulas will govern only when the circumferential joint efficiency is less than one-half the longitudinal joint efficiency, according to UG-27(c) (2) note 20, the formula UG-27(c) (2) for longitudinal stress needn’t considered. 公称钢板规则厚度=10mmNominal Plate Thickness Ordered = 10 mm钢板厚度可允许下偏差=0.25mm[see UG-16(c)] Plate Under tolerance=0.25 mm [ see UG-16(c)]UG-16 (b)(4) the minimum thickness of pressure retaining components >2.5mm for air service(exclusive any corrosion allowance). 实际使用厚度=10-0.25=9.75> 4.81mm ，并且也>2.5+2mm,可以。
Actual Used Thickness = 10 -0.25=9.75>4.81 mm, and >2.5+2 mm(Ca) So it is satisfactory.2.2 椭圆封头最小厚度 Min. Required Thickness of Ellipsoidal Headst = 封头成形后要求最小厚度，mmt = minimum required thickness of head after forming, mm.t s = 封头成形后规定的最小厚度，ts=8.8mmt s = minimum specified thickness of head after forming , ts=8.8mmP = 内部设计压力, 1.3 MPaP = internal design pressure, 1.3 MPa [see UG-21]D =椭圆封头长轴内部长度，500+4mm(考虑腐蚀裕量)D = inside length of major axis of the ellipsoidal head, 500+4mm(undercorrosion condition)h =椭圆封头短轴长度的一半，125+2mm(考虑腐蚀裕量)h = one-half of the length of the minor axis of the ellipsoidal head,125+2mm(under corrosion condition)S =最大安全允许应力值，138 MPaS = maximum allowable stress value, 138MPa [ see ASME Code Part II D, Table 1A for material SA516 Gr.485],E =焊接接头系数，0.85E = joint efficiency, 0.85 [ for Seamless Head and see UW-12(d) ].E1 =筒体与封头的焊接接头系数，0.85E1 = joint efficiency of shell and head,0.85Ca=腐蚀裕量，2mmCa=corrosion allowance, 2mmK1 = 球半径系数，0.9K1 = 0.9 [see Table UG-37, D/2h=2]L =当量球半径K1D = 0.9×504 = 453.6mmL = K1D = 0.9×504=453.6mm [see 1-4(b)]Since t s /L=7.1÷450=0.015 More Than 0.002, Formula UG-32(d)(1) to Be Used:考虑允许的腐蚀裕量：t= t+Ca=2.78+Ca=2.78+2.00=4.78mmConsider of corrosion allowable: t = t+Ca=2.78+Ca=2.78+2.00=4.78mmUG-16 (b)(4) the minimum thickness of pressure retaining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，mmt = minimum required thickness of nozzles, mmP =内部设计压力，1.3 MPaP = internal design pressure, 1.3 MPa [see UG-21]R1 =管口内半径，24.61mmR1= inside radius of the nozzle, 24.61 mmS =最大许用应力值，138 MPaS = 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]t b3=3.42+Ca=3.42+2.0=5.42mmt b=min[t b3, t b31]=4.39mmt=max(t a,t b)=4.39mm管壁的实际使用最小厚度：= 5.54mm >4.39mmActual min. used thickness of tube wall:= 5.54mm > 4.39mm, so it is satisfactory.符号Symbols:θ1=0°θ2=53°d1=60.3mm d2=60.3mm d3=60.3mm2.4.1 Nozzles N1,N2,N3. The finished diameter of circular opening is 49.22 mm, and minimum required thickness of shell is4.81mm. 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，N3t min = 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;t min = the smaller of 19mm or the thickness of the thinner of the parts jointed by a fillet, single-bevel, or single-J weld = 5.54mmt c =不小于6mm，或0.7 t min = 3.87mmt c= not less than the smaller of 6mm or 0.7t min = 3.87mm角焊的实际焊喉尺寸= 6.0×sin45°=4.24mm > 3.87mmActual throat size of fillet weld = 4.24mm >3.87mm, so it is satisfactory.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。