压缩空气罐计算书

1.DESIGN DATA:设计参数(1) APPLICABLE CODE相关规程CUSTOMER SPECIFICATION用户条件书ASME CODE SEC.ⅧDIV. 1 2010ASME标准2010版本第八章第一部分DOC. NO. 01-AU-11-01-00 REV.0文件号：(2) DESIGN PRESSURE设计压力INTERNAL 1.0 MPa 内压(3) DESIGN TEMPERA TURE设计温度60℃(4) TYPE OF JOINTS OF CA TEGORIES AAND BA、B类焊接接头类型TYPE NO.1 1号类型(5) RADIOGRAPHY射线透照检查CA TEGORY A、B BUTT JOINT SPOT UW-11(b)A、B类焊缝射线抽样检测按UW-11（b）(6) JOINT EFFICIENCY焊接接头系数SHELL AND HEAD:85% 筒体和封头:85%(7) CORROSION ALLOWANCE腐蚀裕量1.0mm .(8) MATERIAL材料SHELL & HEAD:SA-516M Gr.485 筒体和封头:SA-516M Gr.485 NOZZLE: SA-105M接管：SA-105MFLANGE: SA-105M法兰：SA-105MLEGS:SA-516M Gr.485支腿：SA-516M Gr.485LUG: SA-105M吊耳: SA-105M(9) MAX. ALLOWABLE STRESS A TDESIGN TEMPERA TURE设计温度下的最大许用应力SA-516M Gr.485: 138MPa at 60℃SA-105M: 138MPa at 60℃(10) MATERIAL UNDERTOLERANCESHELL AND HEAD筒体和封头材料的厚度负偏差<0.25mm(11) HEAD TYPE封头类型2:1 S.E.(12) TANK CAPACITY罐容积4.9 m³(13) SERVICE FLUID工作介质COMPRESSED AIR (no lethal) 压缩空气（非致死）(14) MIN. SERVICE TEMPERA TURE最低操作温度0℃at 1.0MPa(15) THE LOADING CONSIDERED INDESIGNING设计中所考虑的载荷SEE TABLE 1-1见表1-1(16) TANK DIMENSIONS容器尺寸SEE FIG. 1-1 见图1-1TABLE 1-1 LOADING CONSIDERED IN DESIGNING 表1-1 设计过程中考虑的负载问题LIST OF NOZZLES 接管明细表2、TANK CAPACITY CHECKED罐容量审查The volume of head is given by封头体积计算公式：V head = 0.1309 × Di3= 0.1309 ×1.43= 0.359m3Where Di = Inside diameter of vessel, m；Di=容器内径V head = V olume of elliptical dished head to tangent Line, m3V head =椭圆中凹封头到切线的体积The volume of shell is given by壳体体积计算公式：V shell = 1/4 ×π× D2 × L= 1/4 ×π× (1.4) 2 ×2.82= 4.339m3Where D = Inside diameter of shell, mD=壳体内径L = Length of shell tangent to tangent, mL=壳体两切线间的长度V shell = V olume of shell, m3V shell =壳体的体积The total volume of vessel is容器的总体积计算方法是:V total =0.359× 2 +4.339= 5.057m3> 4.9 m3(REQUIRED用户要求) OK3、THICKNESS OF CYLINDRICAL SHELL UNDER INTERNALPRESSURE内压作用下的筒体厚度ASME SEC.ⅧDIV.1 UG-27 ASME第八章节第一部分UG-27●Part部件: Shell筒体●Design pressure设计压力P (MPa) : 1.0●Design temperature设计温度(℃) : 60●Material材料: SA-516M Gr.485 ●Maximum allowable stress value at design temperature设计温度下最大许用应力值S d(MPa) : 138●Maximum allowable stress value at test temperature试验温度下最大许用应力值S t(MPa) : 138●Height to point under consideration到上封头接管密封面的距离H (m) : 3.305●Density of test medium at test temperature试验温度下试验介质的密度g t(Kg/m3) : 1000●Type of welded joints in TABLE UW-12焊接接头类型按表UW-12: Type No. (1)●Radiographic examination射线透照检查: SPOT●Joint efficiency (specified in UW-12)焊接接头系数(按UW-12)E : 0.85●Corrosion allowance腐蚀裕量C (mm) : 1●Inside radius corroded考虑腐蚀的内径R (mm) : 701●Final center line radius最终中心线半径R f (mm) : 706●Original center line radius成形前中心线半径R o (mm) : ∞(1) Minimum required thickness (circumferential stress)最小厚度（环向应力）0.385SE = 0.385×(138)×(0.85) =45.16 > P (a) For operating condition操作工况PE S PRd 6.0t 1-=.16.085.01387010.1⨯-⨯⨯=6.007m m =(b) For hydrostatic test condition水压试验工况662108.96.0108.96.0 t tt tt Hg E S R Hg P E S PR -+-= 66101000305.38.96.085.0138701101000305.38.916.085.01387011⨯⨯⨯-⨯⨯⨯⨯+⨯-⨯⨯= m m 201.60.1946.007 =+=(2) Design thickness设计厚度t=Greater of (t1 or t2) +C 取较大值 = t 2+C =7.2mm(3) Provided thickness验证厚度Nominal thickness (mm)12> t OK 名义厚度 12mm> t OK(4) Check minimum required thickness for paragraph UG-16 (b) (4)按UG-16 (b) (4)校核最小厚度Minimum thickness required (including corrosion allowance) is 3.5mm,所需最小厚度（包括腐蚀裕量）是3.5mm nominal thickness is 12mm>3.5mm OK 名义厚度是12mm>3.5mm 合格Due to E=0.85>0.5, longitudinal stress can not affect the thickness of the wall. 因为E=0.85＞0.5 所以纵向应力不是决定壁厚的因素。

(5) Check extreme fiber elongation for paragraph UCS-79按UCS-79校核纤维伸长量Maximum allowable fiber elongation without post weld heat treatment is based on the following formula:在不进行热处理时纤维最大允许伸长量，计算公式如下：%85.070617061250150 elongation %=⎪⎭⎫⎝⎛∞-⨯⨯=⎪⎪⎭⎫ ⎝⎛-=O F f R R R t ＜5% So no heat treatment after cold forming need to apply. 故冷成形后不必进行热处理。

4、THICKNESS OF ELLIPSOIDAL HEAD, PRESSURE ON CONCA VE SIDE凹面受压的椭圆型封头厚度ASME SEC.ⅧDIV.1 UG-32●Part部件: Heads封头●Design pressure设计压力P (MPa) : 1.0●Design temperature设计温度(℃) : 60●Material材料: SA-516M Gr.485●Maximum allowable stress value at design temperature设计温度下的最大许用应力值S d(MPa) : 138●Maximum allowable stress value at test temperature试验温度下的最大许用应力值S t(MPa) : 138●Height to point under consideration（bottom head）到上封头接管密封面的距离（下封头）H (m) : 3.68●Height to point under consideration (top head)到上封头接管密封面的距离（上封头）H (m) : 0.51●Density of test medium at test temperature试验温度下试验介质的密度g t(Kg/m3) : 1000●Weld joining heads to shell封头和筒体的焊缝类型: Type No. (1)●Radiographic examination (A)射线透照检查（A）: Spot●Joint efficiency (specified in UW-12)焊接接头系数(按UW-12)E : 0.85●Corrosion allowance腐蚀裕量C (mm) : 1● Inside length of the major axis of an ellipsoidal head corroded考虑腐蚀的椭圆形封头内直径D (mm) : 1402● Inside spherical radius of hemispherical head corroded 考虑腐蚀的半球形封头内半径L 1 (mm) : 701● Joint efficiency of head-to-shell 封头到壳体的焊接接头系数E : 0.85● Inside spherical radius of ellipsoidal head corroded 椭圆形封头球面部分的内半径L 2 : 1260● Spherical radius center line of hemispherical head corroded 凸面中心线半径R f (mm) : 1266●Minimum specified thickness of head after forming成型后封头规定的最小厚度 t s 9.5● Knuckle center line radius 转角内半径r f (mm) : 244● Original center line radius 成形前中心线半径R 0 (mm) : ∞(1) Minimum required thickness所需最小厚度 UG-32(d) With t s / L 20075.012605.9==> 0.002 (a) For the top head对上封头PE S PDd 2.02t 1-=.12.085.0138214020.1⨯-⨯⨯⨯=m m 981.5=(b) For the bottom head对下封头(b-1) Under operating condition操作工况下PE S PDd 2.02t 2-=.12.085.0138214020.1⨯-⨯⨯⨯==5.981mm(b-2) Under hydrostatic test condition水压试验工况下663108.92.02108.92.02t tt tt Hg E S D Hg P E S PD -+-= 6610100068.38.92.085.01382140210100068.38.90.12.085.0138214020.1⨯⨯⨯-⨯⨯⨯⨯⨯+⨯-⨯⨯⨯= m m 197.6 216.0 5.981 =+=(2) Design thickness设计厚度t=Greater of (t1, t2or t3) +C 取较大值 = t3+C =7.197mm (3) Provided thickness验证厚度Nominal thickness (mm) 12 名义厚度(mm) 12Minimum thickness after forming (mm) 9.5≥ t OK 成形后最小厚度（mm ）9.5≥ t 合格(4) Check minimum head thickness for paragraph UG-32 (b) for hemispherical head按UG-32 (b)用半球形封头校核封头最小厚度 0.665SE = 0.665 × 138×0.85 = 78.0> P.mm 99.20.12.085.013827010.12.021'=⨯-⨯⨯⨯=-=P SdE PL t9.5mm mm 52.385.099.2'<===E t t OK(5) Check minimum required thickness for paragraph UG-16(b)(4)按UG-16(b)(4)校核所需最小厚度Minimum thickness required (including corrosion allowance) is 3.5mm, minimum thickness after forming is 9.5mm.>3.5mm OK所需最小厚度（包含腐蚀裕量）是3.5mm ，成形后最小厚度是9.5 mm.>3.5mm 合格 (6) Check extreme fiber elongation for paragraph UCS-79按UCS-79校核纤维伸长率Maximum allowable fiber elongation without post weld heat treatment is based on the following formula:不经热处理的最大允许纤维伸长率计算公式如下：)1.(75 % elongation radius Crown 0R R R tf f -⨯=曲面半径伸长率 5%0.71%)1266-(112661275<=∞⨯=)1.(75 % elongation radius Knuckle 0R r r tf f -⨯=过渡段半径伸长率 5%3.68%)238-(12441275<=∞⨯=So no heat treatment of heads after cold forming need to apply for SA-516M Gr.485 (P-NO.1 Group NO.2).因此材料SA-516M Gr.485 (P-NO.1 Group NO.2).制成的封头冷成形之后不必进行热处理。

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压缩空气罐计算书

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。

压缩空气储罐计算书

最大允许工作压力
[Pw]= =1.16051
MPa
设计温度下计算应力
t= =138.43
MPa
t
160.65
MPa
校核条件
t≥t
结论
合格
内筒上封头内压计算
计算单位
计算条件
椭圆封头简图
计算压力Pc
1.00
MPa
设计温度t
100.00
C
内径Di
2400.00
mm
曲面高度hi
600.00
mm
材料
Q345R (板材)
64
mm2
A1+A2+A3=1610mm2，小于A，需另加补强。
补强圈面积A4
2716
mm2
A-(A1+A2+A3)
1856
mm2
结论:补强满足要求。
2400.00
mm
材料
Q345R(板材)
试验温度许用应力
189.00
MPa
设计温度许用应力t
189.00
MPa
试验温度下屈服点s
345.00
MPa
钢板负偏差C1
0.30
mm
腐蚀裕量C2
1.00
mm
焊接接头系数
0.85
厚度及重量计算
计算厚度
= = 7.49
mm
有效厚度
e=n-C1- C2--C3=8.70
软件批准号：CSBTS/TC40/SC5-D01-1999
DATA SHEET OF PROCESS EQUIPMENT DESIGN
工程名：
PROJECT
设备位号：
ITEM
设备名称：压缩空气储罐

(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。

压缩空气储气罐体积计算公式

压缩空气储气罐体积计算公式嘿，说起压缩空气储气罐体积的计算公式，这可真是个有点复杂但又特别实用的知识。

咱先来讲讲为啥要了解这个。

比如说，一家工厂里，各种机器设备都得靠压缩空气来干活儿。

要是储气罐的体积没算好，那要么供气不足，机器闹罢工；要么罐子太大，浪费空间和成本。

所以，把这个公式搞清楚，那可太重要啦！那这计算公式到底是啥呢？一般来说，我们可以用下面这个式子：V = Q × t / （P1 - P2）。

这里的 V 就是储气罐的体积，Q 表示平均用气量，t 是储备时间，P1 是最高工作压力，P2 是最低工作压力。

举个例子吧，我之前去一家小机械厂参观。

那厂子里机器轰隆隆响，压缩空气可少不了。

厂长就跟我诉苦，说之前储气罐买小了，生产的时候老是供气跟不上，耽误了不少活儿。

我一看，他们的平均用气量大概每小时 10 立方米，想要保证 20 分钟的储备时间，最高工作压力 8 个大气压，最低工作压力 6 个大气压。

按照公式一算，这储气罐的体积起码得5 立方米。

后来他们换了个合适的储气罐，生产就顺畅多啦。

再深入点说，这里面每个参数都有讲究。

像平均用气量，得根据不同的设备和工作流程仔细测算。

储备时间呢，得考虑到万一设备出点小故障，或者用气高峰的时候，不能让生产掉链子。

而工作压力，那更是得严格按照设备的要求来，高了低了都不行。

而且，实际应用中还得考虑一些其他因素。

比如说，温度的变化会影响气体的体积，还有管道的阻力也会消耗一部分压力。

所以，计算的时候得留点儿余量，别卡得太死。

总之，压缩空气储气罐体积的计算公式虽然看起来有点头疼，但只要咱把每个参数搞清楚，结合实际情况仔细算，就能给生产和工作带来稳稳的保障。

可别小瞧了这公式，算好了能省不少事儿，算不好那麻烦可就大喽！希望大家都能把这个知识掌握好，让压缩空气乖乖为咱服务！。

20m3立式压缩空气储罐-new

t
最大允许工作压力结论
2[ ] e [Pw]= KDi 0.5 e = 0.93941
合格
全国化工设备设计技术中心站
3
过程设备强度计算书
SW6-2011
内筒下封头内压计算计算单位计算所依据的标准计算条件计算压力 Pc 0.90 MPa 设计温度 t 40.00 C 内径 Di 2400.00 mm 曲面深度 hi 600.00 mm 材料 S30408 (板材) t 设计温度许用应力 137.00 MPa 试验温度许用应力 137.00 MPa 钢板负偏差 C1 0.30 mm 腐蚀裕量 C2 0.00 mm 焊接接头系数 0.85 压力试验时应力校核压力试验类型试验压力值压力试验允许通过的应力t 试验压力下封头的应力校核条件校核结果液压试验 PT = 1.25Pc [ ]t = 1.1250
形状系数
6
2h i
计算厚度有效厚度最小厚度名义厚度结论重量
h = 2[ ]t 0.5 P c
KPc Di
= 9.29
mm mm mm mm Kg 算 MPa
eh =nh - C1- C2= 9.70 min = 3.60 nh = 10.00 满足最小厚度要求 502.21 压力计
立式搅拌容器计算筒体设计条件设计压力 p 设计温度 t 内径 Di 名义厚度 n 材料名称许用应力
t
计算单位 MPa C mm mm
宝鸡忠诚制药机械有限责任公司内 40 2400 设计 S30408 137 筒 0.9
MPa
137 205
压力试验温度下的屈服点 s 钢材厚度负偏差 C1 腐蚀裕量 C2 厚度附加量 C＝C1＋C2 焊接接头系数压力试验类型试验压力 pT 筒体长度 Lw 内筒外压计算长度 L 封头设计条件封头形式名义厚度 n 材料名称设计温度下的许用应力钢材厚度负偏差 C1 腐蚀裕量 C2 厚度附加量 C＝C1＋C2 焊接接头系数

压缩空气缓冲罐容积计算

压缩空气缓冲罐容积计算压缩空气缓冲罐是一种常见的气体容器，用于存储和释放压缩空气。

它在工业领域广泛应用，能够平衡压缩空气系统中的压力波动，保护设备和管道免受过高或过低的压力影响。

我们来了解一下压缩空气缓冲罐的基本构造。

它通常由一个密封的容器和一个空气阀组成。

容器的形状可以是圆柱形、球形或其他形状，具体取决于应用需求。

容器内部通常涂有防锈涂层，以保护其免受腐蚀。

空气阀用于调节缓冲罐内的压力，保持系统的稳定运行。

压缩空气缓冲罐的容积是非常重要的参数。

容积的大小决定了缓冲罐能够存储多少压缩空气，从而影响了系统的稳定性和性能。

一般来说，缓冲罐的容积应根据系统的需求进行合理选择。

我们需要根据系统的最大压力和流量来确定所需的缓冲罐容积。

当系统中的压缩空气流量增加时，缓冲罐需要有足够的容积来储存额外的空气，以保持系统的稳定。

另外，当系统中的压力波动较大时，缓冲罐也需要有足够的容积来吸收这些波动，避免对设备和管道造成损坏。

我们需要考虑缓冲罐的排放速度。

当系统需要释放压缩空气时，缓冲罐需要具备足够的排放速度来满足系统的需求。

排放速度取决于缓冲罐的容积和空气阀的设计。

一般来说，较大容积的缓冲罐能够提供更大的排放速度。

缓冲罐的容积还会受到空间和成本的限制。

在选择缓冲罐容积时，需要考虑到可用的空间和预算。

如果空间有限，我们可能需要选择较小容积的缓冲罐，但这可能会影响系统的性能。

因此，在进行容积选择时，需要在空间和成本之间进行权衡。

需要注意的是，缓冲罐的容积应根据系统运行的特点进行调整。

随着系统使用时间的增长，其运行特性可能会发生变化，容积的选择也需要相应调整。

定期检查和维护缓冲罐，根据实际情况进行容积调整，可以确保系统的稳定性和性能。

压缩空气缓冲罐的容积是影响系统稳定性和性能的重要参数。

在选择容积时，需要考虑系统的最大压力和流量、排放速度、空间和成本等因素。

合理选择缓冲罐的容积可以保护设备和管道，确保系统的正常运行。

因此，在设计和维护压缩空气系统时，我们应充分考虑压缩空气缓冲罐的容积问题。

压缩空气储气罐设计计算

压缩空气储气罐设计计算
压缩空气储气罐设计计算
1 理论背景
压缩空气是一种节能技术，利用某一压强下的空气来调制压力、温度、流量等。

压缩空气储气罐是在压缩机出口建立的一个储气容器，其主要功能是保持压力稳定、减少压力的晃动，同时也可以缓冲压缩机的开闭频率，以达到节能的目的。

2 设计计算步骤
2.1、根据节能需求和压缩机性能，确定压缩机出口端的冲击压力和压力晃动范围；
2.2、选择压缩空气储气罐的形状；
2.3、根据确定好的形状进行储气罐参数的计算，包括储气罐容积、表面积、周长等；
2.4、根据储气罐的表面积以及压缩机出口温度，确定储气罐的厚度；
2.5、根据确定好的容积和厚度，计算储气罐的重量及外形尺寸。

3 注意事项
3.1、储气罐的容积要考虑到压力表的容量；
3.2、储气罐的厚度要考虑到温度变化，应使用较厚的材料；
3.3、储气罐的尺寸要根据压缩机的出口端口位置和安装方式进行定型；
3.4、储气罐必须安装压力表，用来监测储气罐内压力的变化；
3.5、在储气罐的上部应安装滤清器，以防止外界的杂质污染压缩空气；
3.6、储气罐的外表必须与环境保持一致，并应具备防爆的功能。

气压罐选型计算书

气压罐选型计算书
选型依据
一、气压罐是水泵可以进入睡眠的前提条件
气压罐——利用波义耳(Robert Boyle)气体定律：
V是指气体的体积，P指压强，C为一常数。

这个公式又可以继续推导，理想气体的体积与压强的乘积成为一定的常数，即：PV=C （constant）。

如果在温度相同的状态下，1、2两种状态下的气体关系式可表示成：P1V1=P2V2
习惯上，这个公式会写成：
稳压罐总容积=工作初始状态气体容积+预充水量容积=工作最终状态气体容积+停泵充水容积
Vz= V1+ V1 S = V2+V2S
稳压罐调节容积=停泵充水容积-预充水量容积=工作初始状态气体容积-工作最终状态气体容积
V t = V2S-V1 S = V1-V2
稳压罐可调节容积计算，实例计算：
么。

20m3压缩空气罐安全阀计算书

安全阀计算书
共1页第1页
泄放装置泄放能力计算 1 已知条件
项容器的工作压力安全阀工作压力(整定压力) 容器设计压力容器的超压限度安全阀出口侧压力（绝压）泄放条件下介质的密度容器进料管内径容器进料管内的流速容器的安全泄放量泄放装置泄放系数气体绝热指数气体特性系数气体的摩尔质量泄放装置泄放温度气体的压缩指数目符号 pw pz p pc p0 ρ d v WS K k C M Tf Z kg/kmol K 单位 MPa MPa MPa MPa MPa kg/m3 mm m/s kg/h 数值 0.80 0.84 0.84 0.040 0.10133 10.57 147 9 5818 0.65 1.40 356.1 28.97 323 1.000 查图B.1，空气Z=1 WS=2.83× -3ρvd2 10 全启式K=0.6-0.7 查表B.6 按k值查GB150-2011表B.4 由热力计算知 pz=（1.05-1.1）pw p≥pz pc≤0.1p 大气压力备注
2 泄放压力计算
泄放压力(绝压)pf
p'f=p+pc+0.1= p'f＞0.018Mpa
0.980
MPa
取较大值 pf=
0.98
MPa
3 安全阀排放面积计算
A WS 7 . 6 10 2 CKp
AfLeabharlann 2 B K 1= 5.11
K K 1
B≥1
Pf P0
B<1
M ZT f
WS
=
1126.91 mm2
55 .84 Kp f
k 1 2 p0 k p0 k k p k 1 p f f

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