Horizontal Vessel Calculation

8/10/2019 Horizontal Vessel Calculation

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Sample Vessel #3

96" Horizontal VesselPressure Vessel Calculations

May 21, 2002

Aquacare Inc.10 East Airport Road

Huntsville, Ontario

Laurence Brundrett P. Eng.

Charles Liu M. Eng.

Pressure Vessel Engineering Ltd.

PVE-Sample 3

1 of 24



Table of Contents 21-May-02 of 24

Contents Page

Cover 1

Table of Contents 2

Summary 3

Material Properties 4

Pipe and Shell 5

Elliptical Head 6

0.75" Coupling In Top Shell 76" Nozzle B 8 - 9

6" Nozzle C 10 - 11

6" Slip On Flange B & C 12

Manway D & E 13

Manway F 14

1.5" Coupling In Bottom Shell 15

Weight and Volume 16

Lifting Lug 17

Zick 18 - 19

Hor. Vessel Forces 20

Flexible Saddle Stress 21

Flexible Saddle 22 - 24



Pressure Vessel Design Summary 21-May-02 of 24

Customer

Vessel

Part Number

Drawing

Job

96 Outside Diameter [inch]

120 straight Shell (not including straight flange on heads)640 Volume [cuft]

Water Fluid

6393 Weight Empty [lbs.]

46324 Weight Full

46324 Weight Under Test

Maximum Internal pressure, psi Maximum External Pressure, psi At Temperature, ºF

75 0 150Maximum Temperature, ºF Minimum Temperature, ºF At Pressure, psi

150 -20 75Test Pressure, psi At a Minimum Temperature of: ºF For a Minimum Duration of:

98 60 30 min.

3 Seismic Zone

1.5 Foundation Factor

SA-516 70 Primary Material of Construction

20,000 Allowable Stress

0.063 Minimum allowed thickness per UG-16(b)

no Material Normalized

no Material Impact Tested (not required per UG-20(f))

none Radiography required

0 Corrosion Allowance

ASME VIII-1 Code2001 Edition

none Addenda

IID Materials

none Code Cases Required

UG-22 Loadings Considered

Yes (a) Internal pressure

- (a) External pressure

Yes (b) Vessel weight full, empty and at hydro test

- (c) Weight of attached equipment and piping

Yes (d)(1) Attachment of internals

Yes (d)(2) Attachment of vessel supports - (d) Cyclic or dynamic reactions

- (f) Wind

- (f) Snow

Yes (f) Seismic

- (g) Fluid impact shock reactions

- (h) Temperature gradients

- (h) Differential thermal expansion

- (i) Abnormal pressures like deflagration

Hydrostatic Test

Maximum Allowed Working Pressure

Aquacare Inc.

PVE-Sample 3

PVE-Sample 3

96" Horizontal Vessel

Sample Vessel #3

Maximum Design Metal Temperature



1 Material Properties ver 1.28 www.pveng.com 21-May-02 of 24

2 ASME VIII, IID 2001 edition no addenda

3 Sample Vessel #3 <- vessel4

5 Design Pressure UG-22(a)

6 75.0 <- P, internal operating pressure at top of vessel (psig)

7 0.0 <- mPa, external operation pressure

8 Water <- Operating Fluid

9 8 <- h, fluid height (ft)

10 1.00 <- rho, fluid density (1.0 for water)

11 Design Pressure = P + 0.4331*rho*h = 75 + 0.4331 * 1 * 8 mDp = 78.5

13 Hydro Test (UG-99(b)) pressure measured at top of vessel

14 Test Press = P * 1.3 * MR = 75 * 1.3 * 1 mTp = 97.5

16 Material Properties (ASME IID)

17 150 <- mTemp, design temp ºF Test at ambient temp

18

Where Used Ambient

Strength

Design

Strength

Strength

Ratio

Max ºF Ext

Graph

19 Head and Shell 20000 20000 1.000 1000 CS-2

20 Flanges/couplings 20000 20000 1.000 1000 CS-2

21 Nozzles 17100 17100 1.000 1000 CS-2

22 Saddle 17100 17100 1.000 650 CS-2

23

24

25

26

27

28

29

30

31

32

33

34

35

36

37

38

39

40

41

42

43

44 Min Ratio (MR) = 1.000

45

46 Use a Test Pressure of 98 PSI

47

48

SA-106 B Seamless Pipe

SA/CSA-G40.21 44W

SA-105 Forging

Material

SA-516 70 Plate



12 Pipe and Shell ver 2.33 21-May-02 of 24

13 ASME Code VIII Div I 2001 edition no addenda

14 <- Vessel

15 <- Description

17 Dimensions:

18 96.000 <- Do - Outside Diameter

19 0.313 <- t - Nominal Wall Thickness

20 120.000 <- Le - Effective Length

21 120.000 <- Length for volume and weight22 0.000 <- Corr, Corrosion Allowance

24 Material and Conditions:

25 SA-516 70 <- Material

26 20,000 <- S, Allowable Stress Level (psi)

27 0.7 <- El - Longitudinal Efficiency (circ. stress)

28 0.7 <- Ec - Circ. Connecting Efficiency (longitudinal stress)

29 0.0% <- UTP, Undertolerance allowance (%) 496.12 <- Volume (cubic ft)

30 0.000 <- UTI, Undertolerance allowance (inch) 3,202.2 <- Material Weight (lbs cs)

32 78.5 <- P, Interior Pressure

33 0.0 <- Pa, Exterior Pressure

37 Variables:

38 UT = t*UTP+UTI = 0.313*0+0 undertollerance UT = 0.000

39 nt = t-Corr-UT = 0.313-0-0 nominal thick nt = 0.313

40 Ri = Do/2-nt = 96/2-0.313 effective inside radius Ri = 47.687

41 LDo = Le/Do = 120/96 LDo = 1.250

43 Interior Pressure UG-27 (c) (1,2)

44 ta = P*Ri/(S*El-0.6*P) = 78.465*47.687/(20000*0.7-0.6*78.465) ta = 0.268

45 tb = P*Ri/(2*S*Ec+0.4*P) = 78.465*47.687/(2*20000*0.7+0.4*78.465 tb = 0.133

46 tmin = Max(ta,tb) <= nt Acceptable tmin = 0.268

47 PMaxA = PMaxA = 91.5

48 PMaxB = PMaxB = 184.3

49

PMax = Min(PMaxA,PMaxB) Acceptable PMax = 91.5 50 tr1 = P*Ri/(S*1-0.6*P) = 78.465*47.687/(20000*1-0.6*78.465) tr1 = 0.188

62 Shell stress relief -UCS-79(d), UNF-79(d), UHA-44(d)

63 Rf = (do-t)/2 = (96-0.313)/2 47.8435

64 % elong = (50*t/Rf)*(1-0) = (50*0.313/47.844)*(1-0) % elongation = 0.3

65 5.0% <- Max Elongation

66 Yes <- Cold formed 0.3% <- Elongation Required no

67 no <- Vessel carries lethal substances (Yes/no) no no

68 no <- Impact testing is required (Yes/no) no no

69 no <- Greater than 10% reduction in thickness no no

70 no <- Formed between 250 and 900 Degrees F no no

71 no <- Shell is greater than 5/8" thick before forming no no

72 Stress Relieve ? no

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(2*S*Ec*nt)/(Ri-0.4*nt)

(S*El*nt)/(Ri+0.6*nt) = (20000*0.7*0.313)/(47.687+0.6*0.313)

= (2*20000*0.7*0.313)/(47.687-0.4*0.313)

Sample Vessel #3

3/8" Rolled Plate Shell

t

Do

L e n g

t h

L o n g S e

a m



1 Elliptical Head ver 2.16 of 24

2 ASME Code VIII Div I 2001 edition no Addenda

3 <- Vessel4 <- Component

6 Dimensions:

7 96.000 <- Do, outside diameter

8 23.859 <- h 24.14 <- ho

9 0.313 <- tb, thickness before forming

10 0.282 <- tf, thickness after forming11 0.000 <- Corr, corrosion allowance

12 1.500 <- Skirt, straight skirt length

14 Material and Conditions: Calculated Properties:

15 SA-516 70 <- material 116.440 <- Approximate blank diameter

16 20,000 <- S, allowable stress level (psi) 945.3 <- Approximate weight for steel, (lbs)

17 0.85 <- E, efficiency 72.06 <- Volume (cuft, includes skirt)

19 78.5 <- P, interior pressure 76.35 <- Spherical Limit (0.8 * D)

20 0.0 <- Pa, exterior pressure

24 Variables:

25 D = Do-2*t = 96-2*0.282 D = 95.44

26 ho = h+t = 23.859+0.282 ho = 24.14

27 D/2h = D/(2*h) UG-37 & Ap 1-4(c) = 95.437/(2*23.859) D/2h = 2.000

28 Do/2ho = Do/(2*ho) UG-37 & Ap 1-4(c) = 96/(2*24.141) Do/2ho = 1.988

29 K = Interpolated value from table 1-4.1 D/2h interior K = 1.000

30 Kone = Interpolated value from table UG-37 D/2h spherica Kone = 0.900

31 Kzero = Interpolated value from table UG-33.1 Do/2ho exterior Kzero = 0.895

32 t = tf-corr = 0.282-0 t = 0.282

33 Ro = Ko*Do UG-33(d) = 0.895*96 Ro = 85.896

35 Interior Pressure App 1-4(c)(d), UG-37 1(a)

36 TMinI = (P*D*K)/(2*S*E-0.2*P) <= t TMinI (min thickness) = 0.220

37 = (78.465*95.437*1)/(2*20000*0.85-0.2*78.465) <= 0.282 Okay

38 PMax = (2*S*E*t)/(K*D+0.2*t) >= P PMax = 100.339 = (2*20000*0.85*0.282)/(1*95.437+0.2*0.282) >= 78 Okay

40 TSpI = (P*D*Kone)/(2*S*E-0.2*P) TSpI (required sphere zone thick) = 0.169

41 = (78.465*95.437*0.9)/(2*20000*1-0.2*78.465)

51 Head stress relief UCS-79(d), UNF-79(d), UHA-44(d)

52 % elong = ((75*t)/h)*(1-0) = ((75*0.282)/23.859)*(1-0) % elong = 1.0

53 5.0% <- Max Elongation

54 Yes <- Cold Formed 1.0% <- Elongation Required no

55 no <- Vessel carries lethal substances(Yes/no) no no

56 no <- Impact testing is required (Yes/no) no no

57 no <- Formed between 250 and 900 Degrees F no no

58 no <- Greater than 10% reduction in thickness no no

59 no <- Head is greater than 5/8" thick before forming no no60 Stress Relieve ? no

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Sample Vessel #3

3/8" Thick Semi Elliptical Head

21-May-02

ThickSkirt

Do

h

D

ho

Sperical Limit



15 Coupling ver 2.02 UW16.1Z1M 21-May-02 of 24

16 ASME Code VIII Div I 2001 edition, no addenda

22 <- Vessel

18 <- Description

20 Shell:

23 0.313 <- t, Shell Wall Thick (inch)

27 1.500 <- D, Shell Opening Diameter (inch)

29 78.5 <- P,design Pressure (psi)

31 Coupling:32 3/4 inch 3000# <- Coupling

33 SA-105 <- Coupling Material

34 20,000 <- Sn, Allowable Stress Level (Sn)

36 0.250 <- F1, Weld Size

38 0.000 <- Corrc, Coupling Corrosion Allowance (inch)

39 1.380 <- COD - Coupling OD

40 1.050 <- POD - Pipe OD

42 14.000 <- n, Treads Per Inch

44 0.219 <- pt, Corresponding sch160 Wall Thickness (inch)

46 12.5% <- UT, Under Tolerence (%)

47

49 Geometry Restrictions Fig. UW-16.1

50 tcp = (COD-POD)/2-CORRC = (1.38-1.05)/2-0 Tcp = 0.165

51 Tmin = Min(0.75,tcp,t) = Min(0.75,0.165,0.313) Tmin = 0.165

53 tcmin = Min(0.25,0.7*Tmin) = Min(0.25,0.7*0.165) tcmin = 0.116

56 t1 = 0.7*F1 = 0.7*0.25 t1 = 0.175

61 t1 > = tcMin = 0.175 >= 0.116 Okay

78

79 Required Coupling Wall Thickness B16.11 - 2.1.1 and UG-31 (C) (2)

80 Ro = POD/2-0.8/n = 1.05/2-0.8/14 Ro = 0.468

81 tp = (1-UT)*pt-Corrc-0.8/n = (1-0.125)*0.219-0-0.8/14 tp = 0.134

82 Min Thick = P*Ro/(Sn*1+0.4*P) = 78*0.468/(20000*1+0.4*78.465 Okay trn = 0.002 83

84 Pressure Weld Stress UW-18(d) - Pressure Load only UW-16(f)(3)(a)(3)(b)

85 Load = COD^2*(PI()/4)*P = 1.38^2*(PI()/4)*78.465 Load = 117

86 Weld Area = pi()*((COD+F1)^2-COD^2)/4 Weld Area = 0.591

87 = pi()*((1.38+0.25)^2-1.38^2)/4

92 Max Stress = Min(Sn,Sv) * 0.55 = Min(20000,20000) * 0.55 Max Stress = 11000

93 Weld Stress = Load / Area = 117 / 0.591 Weld Stress = 199

94 Okay

99

100

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Sample Vessel #3

3/4" Class 3000 Half Coupling A

F1

Inside Vessel

Outside

t

D

COD

POD

UW-16.1 Z-1 (Modified) Coupling

t1



298 Sample Vessel #3 6" SCH 80 Nozzle B 21-May-02 of 24

300 Nozzle

301 Tstd = Standard pipe wall thickness from chart Tstd = 0.280

302 Swre = tr * Pa / P = 0.22 * 0 / 78.465 Req. Exterior pressure Swre = 0.000

303 Nact = Nt * (1-UTp) = 0.432 * (1-0.125) Actual Wall Thick. Nact = 0.378

304 Tt = 0.8/Nth = 0.8/0 Ug-31(c)(2) threads Tt = 0.000

308 UG-45

313 UG45 = Max(UG45a, UG45b) <= Nact UG45 = 0.220

314 = Max(0.014, 0.22) <= 0.378 Acceptable

316 UG-45(a)

321 UG45a = Max(trn,trnE) + Nca + Tt UG45a = 0.014

322 Max(0.014,0) + 0 + 0

324 UG-45(b)

330 UB45b = Min(UG45b1, UG45b2, UG45b3, UG45b4) UB45b = 0.220

331 = Min(0.22, , 0.22, 0.245)

333 UG-45(b)(1)

337 UG45b1 = Max(tr + Sca, Tmin16b + Sca) UG45b1 = 0.220

338 Max(0.22 + 0, 0.063 + 0)

340 UG-45(b)(2)

345 UG45b2 = Max(Swre + Sca,Tmin + Sca) UG45b2 =

346 Max(0 + 0,0.063 + 0)

348 UG-45(b)(3)

351 UG45b3 = Max(UG45b1,UG45b2) = Max(0.22,) UG45b3 = 0.220

353 UG-45(b)(4)

357 UG45b4 = Tstd*0.875 + Nca = 0.28*0.875 + 0 UG45b4 = 0.245



156 Sample Vessel #3 6" SCH 80 Nozzle C 0.0135 0.22035 21-May-02 of 24

158 Area Replacement: Fig UG-37.1 Pressure From: Internal External

159 A = 1.0*d*tr*F + 2*tn*tr*F*(1-frone) A Required (internal) = 1.354

160 = 1.0*6.02*0.22*1 + 2*0.432*0.22*1*(1-0.855)

163 Ae = 0.5*(d*trE*1 + 2*tn*trE*1*(1-frone)) A Required (external) = 0.000

164 =

167 A1 = max(d, 2*(t+tn)) * (E1*t-F*tr)-2*tn*(E1*t-F*tr)*(1-fr1) A1 = 0.000

168 =

172 A1e = max(d, 2*(t+tn)) * (Eone*t-F*trE)-2*tn*(Eone*t-F*trE)*(1-frone) A1e = 1.162

173 =

177 A2 = min((tn-trn)*fr2*min(5*t,2*L) , (tn-trn)*(Min(2.5*tn+te,L)*fr1*2) A2 = 0.504178 =

182 A2e = min((tn-trnE)*frtwo*Min(5*t,2*L) , 2*(tn-trnE)*Min(2.5*tn+te,L)*frone) A2e = 0.520

183 =

190 A5 = (Dp - d - 2tn)te*fr4 =(12 - 6.02 - 2*0.432)*0.313*1 A5 = 1.601 1.601

195 A41 = Leg41 2̂*frThree A41 = 0.313^2*0.855 A41 = 0.084 0.084

198 A42 = Leg42^2*frfour A42 = 0.25^2*1 A42 = 0.063 0.063

203 Actual Area = 2.252 3.430

204 Acceptable Actual-Required = 0.897 3.430

210 Internal Weld Load: (UG-41)

211 WmaxI = (A - A1 + 2*Tn*Fr1*(E1*t-F*tr))*Sv, min0 Max value for weld loads WmaxI = 26,740

212 = (1.354 - 0 + 2*0.432*0.855*(0.7*0.282-1*0.22))*20000

217 W1-1 = MIN((A2 + A5 + A41 + A42)*Sv,WmaxI) Weld load W1-1 = 26,740

218 = MIN((0.504 + 1.601 + 0.084 + 0.063)*20000,26740)

219 W2-2 = Min((A2 + A3 + A41 + A43 + 2*Tn*t*frone)*Sv,WmaxI) Weld load W2-2 = 15,917

220 = Min((0.504 + 0 + 0.084 + 0 + 2*0.432*0.282*0.855)*20000,26740)

224 W3-3 = Min((A2 + A3 + A5 + A41 + A42 + A43 + 2*Tn*t*fr1)*Sv,WmaxI) Weld load W3-3 = 26,740

225 = Min((0.504 + 0 + 1.601 + 0.084 + 0.063 + 0 + 2*0.432*0.282*0.855)*20000,26740)

230 External Weld Load: (UG-41)

231 WmaxE = (Ae - A1e + 2*Tn*Fr1*(E1*t-F*tr))*Sv, min0 Max value for weld loads WmaxE = 0

232 = (0 - 1.162 + 2*0.432*0.855*(0.7*0.282-1*0.22))*20000

237 W1-1 = MIN((A2e + A5 + A41 + A42)*Sv,WmaxE) Weld load W1-1e = 0

238 = MIN((0.52 + 1.601 + 0.084 + 0.063)*20000,0)

239 W2-2 = Min((A2e + A3 + A41 + A43 + 2*Tn*t*frone)*Sv,WmaxE) Weld load W2-2e = 0

240 = Min((0.52 + 0 + 0.084 + 0 + 2*0.432*0.282*0.855)*20000,0)

244 W3-3 = Min((A2e + A3 + A5 + A41 + A42 + A43 + 2*Tn*t*fr1)*Sv,WmaxE) Weld load W3-3e = 0

245 = Min((0.52 + 0 + 1.601 + 0.084 + 0.063 + 0 + 2*0.432*0.282*0.855)*20000,0)

255 Component Strength (UG-45(c), UW-15(c))

256 A2 shear = PI()/2*(Do-tn)*tn*Sn*0.7 A2s = 50,304

257 g tension = PI()/2*Do*LegG*Min(Sv,Sn)*0.74 gt = 43,433

258 A41 shear = PI()/2*Do*Leg41*Min(Sn,Sp)*0.49 A41s = 27,292

262 A42 shear = PI()/2*DP*Leg42*Min(Sv,Sp)*0.49 A42s = 46,181

270 Failure mode along strength path (Greater than Weld Load, see App L-7)

273 S1-1 = A42s + A2s >= W1-1 Acceptable S1-1 = 96,485

274 = 46181 + 50304 >= 26740

283 S2-2 = A41s + gt >= W2-2 Acceptable S2-2 = 70,725

284 = 27292 + 43433 >= 15917

287 S3-3 = gt + A42s >= W3-3 Acceptable S3-3 = 89,614

288 = 43433 + 46181 >= 26740

292

293

294

0.5*(6.02*0*1 + 2*0.432*0*1*(1-0.855))

max(6.02, 2*(0.282+0.432)) * (0.7*0.282-1*0.22)-2*0.432*(0.7*0.282-1*0.22)*(1-0.855)

= PI()/2*6.625*0.313*Min(17100,20000)*0.49

= PI()/2*12*0.25*Min(20000,20000)*0.49

max(6.02, 2*(0.282+0.432)) * (0.7*0.282-1*0)-2*0.432*(0.7*0.282-1*0)*(1-0.855)

min((0.432-0.014)*0.855*min(5*0.282,2*2) , (0.432-0.014)*(Min(2.5*0.432+0.313,2*2)*0.855*2)

min((0.432-0)*0.855*Min(5*0.282,2*2) , 2*(0.432-0)*Min(2.5*0.432+0.313,2)*0.855)

= PI()/2*(6.625-0.432)*0.432*17100*0.7

= PI()/2*6.625*0.282*Min(20000,17100)*0.74



12 B16.5 Slip On Flange Ver 1.35 www.pveng.com 21-May-02 of 24

13 ASME B16.5-1996 ASME VIII A2001 edition no addenda

15 <- Comments

16 <- Description

18 Select Flange

19 SA <- Category

20 Forged <- Material Type

21 SA 105 <- Material

22 150 <- Pressure Class23 6.00 <- Nominal Size

25 Nozzle

26 0.432 <- tn, Nozzle Wall Thickness (inch)

27 0.014 <- tnr, Required Nozzle Wall Thickness (inch)28

29 Operating Conditions

30 150 <- T, temperature ºF Max press @100ºF [p1] 285

31 78.5 <- P, pressure, psig Max press @150ºF [p2] 273

0.000 <- Corr, corrosion allowance Acceptable

34 Flange Welds: VIII UW-15 (c)

35 0.250 <- F1, pipe fillet size Nominal - C-Si

36 0.250 <- Setback

37 0.250 <- F2, flange fillet size F2 Table - 2-1.1

38 17100 <- Sp, allowable stress, pipe Max Temp ºF - 1000

39 20000 <- Sf, allowable stress, flange Pod, pipe OD - 6.625

41 Geometry constraint: VIII UW-21 (b)

42 c = Min(tn,tx) = Min(0.432,0.027) c = 0.027

43 tx = 2*tnr = 2*0.014 tx = 0.027

44 wtmin = 0.7*c = 0.7*0.027 wtmin = 0.019

45 wt = 0.7*MIN(F1,F2) weld throat wt = 0.175

46 = 0.7*MIN(0.25,0.25) Acceptable4

48 Maxsetback = c+0.25 = 0.027+0.25 Maxsetback = 0.277

49 Setback = 0.250 Acceptable

51 Weld Strength:

52 Min Sa = MIN(Sp,Sf) = MIN(17100,20000) Min Sa = 17,100

53 Max Weld Stress = Sa * 0.49 = 17100 * 0.49 Max S = 8,379

54 Weld Load = Pod^2*pi*P/4 = 6.625^2*pi*78.465/4 Load = 2,705

55 Weld Area = Pod*pi*(F1-corr + F2) Area = 10.407

56 = 6.625*pi*(0.25-0 + 0.25)

57 Weld Stress = Load/Area = 2704.808/10.407 Stress = 260

58 Acceptable

60

61

62

Sample Vessel #3

6" Class 150 RFSO Flange B & C

F1

F1F2

F2

F1

F2



26 Nozzle Reinforcement ver 3.53 UW16(c)mod 21-May-02 of 24

27 ASME Code VIII Div I 2001 edition no addenda Automatic dh - not hillside

22 <- Vessel Manually enter Limit Diameter

29 <- Desc Curved Shell or Head Section

30 Shell:

31 SA-516 70 <- Shell material

32 20,000 <- Sv, shell allowable stress level, PSI

33 1.00 <- Eone, efficiency of shell at nozzle

35 0.282 <- Vt, shell wall thick, uncorroded, UT removed

36 0.169 <- tr, required shell wall thickness int. press.

37 0.000 <- trE, required shell wall thickness ext. press.

38 0.000 <- sca, shell corrosion allowance

39 0.063 <- tmin16b, Min allowed wall per UG-16(b)

40 Nozzle:

41 SA-106B <- Nozzle material

42 17,100 <- Sn, allowable stress level (Sn)

44 1.00 <- E nozzle

46 78.5 <- P, internal design pressure

47 0.0 <- Pa, external design pressure


51 8.110 <- dLr, Limit radius <= d

52 0.750 <- Nt, wall thick, uncorroded

53 12.5% <- UTp, undertolerance (%)

55 0.000 <- nca, nozzle corrosion allowance

57 1.000 <- L, exterior Projection

58 1.000 <- Ip, interior projection61 Reinforcing:

71 0.313 <- Leg41, size of weld fillet


74 1.000 <- F

77 Variables:

78 UT = Nt*UTp = 0.75 * 0.125 Undertolerance UT = 0.094

79 Rn = Do/2 - (Nt-nca) + UT = 17.5/2 - (0.75-0) + 0.094 Effective Radius Rn = 8.094

84 t = Vt-sca = 0.282 - 0 Effective Shell Thickness t = 0.282

85 ti = Nt-2*nca = 0.75 - 2 * 0 Nom Thick of Int. Proj. ti = 0.750

90 tn = Nt-nca = 0.75-0 Avail. Nozzle Thick. No UT tn = 0.750

93 d = Do-2*tn = 17.5 - 2*0.75 Opening Dia. d = 16.000

99 fr1 = MIN(Sn/Sv,1) = MIN(17100/20000, 1) fr1 = 0.855

102 fr2 = MIN(Sn/Sv,1) = MIN(17100/20000, 1) fr2 = 0.855

112 h = MIN(Ip-sca,2.5*t,2.5*ti) = MIN(1-0,2.5*0.282,2.5*0.75) h = 0.705

113 tcLeg41 = Min(0.25,0.7*Min(0.75,tn,t)) = Min(0.25,0.7*Min(0.75,0.75,0.282)) tc41 = 0.197

115 tcLeg43 = Min(0.25,0.7*Min(0.75,t,tn)) = Min(0.25,0.7*Min(0.75,0.282,0.75)) tc43 = 0.197

117 F = Min(Fenterered, 1) F = 1.000

126 Pipe Required Wall Thickness - trn from internal, trnE from external pressure

127 LDo = L/Do LDo = 0.057 Dot = Do/trnE Dot = 0.000

128 trn = (P*Rn)/(Sn*E - 0.6*P) <= tn-UT trn = 0.037 Acceptable

129 trnE = (3*Do*Pa)/(4*B) <= tn-ut trnE = 0.000 Acceptable

131 Geometry Constraints:

133 0.7*Leg41 >= tc41 0.7*0.313 >= 0.197 0.219 >= 0.197 Acceptable


151 UG45 = Long form calculations are not shown in this view UG45 = 0.169 Acceptable



160 = 1.0*16*0.169*1 + 2*0.75*0.169*1*(1-0.855)


164 =167 A1 = max(dLr, 2*(t+tn)) * (E1*t-F*tr)-2*tn*(E1*t-F*tr)*(1-fr1) A1 = 0.895

168 =

172 A1e = max(dLr, 2*(t+tn)) * (Eone*t-F*trE)-2*tn*(Eone*t-F*trE)*(1-frone) A1e = 2.226

173 =

179 A2 = min((tn-trn)*fr2*Min(5*t,2*L) , (tn-trn)*fr2*Min(5*tn,2*L)) A2 = 0.859

180 =

184 A2e = min((tn-trnE)*frtwo*Min(5*t,2*L) , (tn-trnE)*frtwo*Min(5*tn,2*L)) A2e = 0.904

185 =

187 A3 = Min(5*t*ti*frtwo, 5*ti*ti*frtwo, 2*h*ti*frtwo) A3 = 0.904 0.904

188 = Min(5*0.282*0.75*0.855, 5*0.75*0.75*0.855, 2*0.705*0.75*0.855)

194 A41 = Leg41^2*frTwo A41 = 0.313^2*0.855 A41 = 0.084 0.084

201 A43 = (Leg43-nca)̂ 2*frtwo A43 = (0.313-0)^2*0.855 A43 = 0.084 0.084

203 Actual Area = 2.826 4.202


Sample Vessel #3

12" Manway D & E With 3/4"x4" Ring

0.5*(16*0*1 + 2*0.75*0*1*(1-0.855))

min((0.75-0)*0.855*Min(5*0.282,2*1) , (0.75-0)*0.855*Min(5*0.75,2*1))

max(8.11, 2*(0.282+0.75)) * (1*0.282-1*0.169)-2*0.75*(1*0.282-1*0.169)*(1-0.855)

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= (78.5*8.094)/(17100*1 - 0.6*78.5)

= (3*17.5*0)/(4*1)

max(8.11, 2*(0.282+0.75)) * (1*0.282-1*0)-2*0.75*(1*0.282-1*0)*(1-0.855)

min((0.75-0.037)*0.855*Min(5*0.282,2*1) , (0.75-0.037)*0.855*Min(5*0.75,2*1))

UW-16.1 (c) modified

Leg41

OD Nozzle

Nt

Leg41

Leg43

Leg43

Proj

Vt N o z z l e

Shell

FullPenn.t



26 Nozzle Reinforcement ver 3.53 UW16(c)mod 21-May-02 of 24

27 ASME Code VIII Div I 2001 edition no addenda Automatic dh - not hillside

22 <- Vessel Automatic Limit Diameter

29 <- Desc Curved Shell or Head Section

30 Shell:

31 SA-516 70 <- Shell material

32 20,000 <- Sv, shell allowable stress level, PSI

33 1.00 <- Eone, efficiency of shell at nozzle

35 0.313 <- Vt, shell wall thick, uncorroded, UT removed

36 0.188 <- tr, required shell wall thickness int. press.

37 0.000 <- trE, required shell wall thickness ext. press.

38 0.000 <- sca, shell corrosion allowance

39 0.063 <- tmin16b, Min allowed wall per UG-16(b)

40 Nozzle:

41 SA-106B <- Nozzle material

42 17,100 <- Sn, allowable stress level (Sn)

44 1.00 <- E nozzle

46 78.5 <- P, internal design pressure

47 0.0 <- Pa, external design pressure


52 0.750 <- Nt, wall thick, uncorroded

53 12.5% <- UTp, undertolerance (%)

55 0.000 <- nca, nozzle corrosion allowance

57 1.000 <- L, exterior Projection

58 1.000 <- Ip, interior projection

61 Reinforcing:71 0.375 <- Leg41, size of weld fillet


74 1.000 <- F

77 Variables:

78 UT = Nt*UTp = 0.75 * 0.125 Undertolerance UT = 0.094

79 Rn = Do/2 - (Nt-nca) + UT = 17.5/2 - (0.75-0) + 0.094 Effective Radius Rn = 8.094

84 t = Vt-sca = 0.313 - 0 Effective Shell Thickness t = 0.313

85 ti = Nt-2*nca = 0.75 - 2 * 0 Nom Thick of Int. Proj. ti = 0.750

90 tn = Nt-nca = 0.75-0 Avail. Nozzle Thick. No UT tn = 0.750

93 d = Do-2*tn = 17.5 - 2*0.75 Opening Dia. d = 16.000

99 fr1 = MIN(Sn/Sv,1) = MIN(17100/20000, 1) fr1 = 0.855

102 fr2 = MIN(Sn/Sv,1) = MIN(17100/20000, 1) fr2 = 0.855

112 h = MIN(Ip-sca,2.5*t,2.5*ti) = MIN(1-0,2.5*0.313,2.5*0.75) h = 0.783

113 tcLeg41 = Min(0.25,0.7*Min(0.75,tn,t)) = Min(0.25,0.7*Min(0.75,0.75,0.313)) tc41 = 0.219

115 tcLeg43 = Min(0.25,0.7*Min(0.75,t,tn)) = Min(0.25,0.7*Min(0.75,0.313,0.75)) tc43 = 0.219

117 F = Min(Fenterered, 1) F = 1.000

126 Pipe Required Wall Thickness - trn from internal, trnE from external pressure

127 LDo = L/Do LDo = 0.057 Dot = Do/trnE Dot = 0.000

128 trn = (P*Rn)/(Sn*E - 0.6*P) <= tn-UT trn = 0.037 Acceptable

129 trnE = (3*Do*Pa)/(4*B) <= tn-ut trnE = 0.000 Acceptable

131 Geometry Constraints:



151 UG45 = Long form calculations are not shown in this view UG45 = 0.188 Acceptable



160 = 1.0*16*0.188*1 + 2*0.75*0.188*1*(1-0.855)


164 =

167 A1 = max(d, 2*(t+tn)) * (E1*t-F*tr)-2*tn*(E1*t-F*tr)*(1-fr1) A1 = 1.980 168 =

172 A1e = max(d, 2*(t+tn)) * (Eone*t-F*trE)-2*tn*(Eone*t-F*trE)*(1-frone) A1e = 4.940

173 =

179 A2 = min((tn-trn)*fr2*Min(5*t,2*L) , (tn-trn)*fr2*Min(5*tn,2*L)) A2 = 0.954

180 =

184 A2e = min((tn-trnE)*frtwo*Min(5*t,2*L) , (tn-trnE)*frtwo*Min(5*tn,2*L)) A2e = 1.004

185 =

187 A3 = Min(5*t*ti*frtwo, 5*ti*ti*frtwo, 2*h*ti*frtwo) A3 = 1.004 1.004

188 = Min(5*0.313*0.75*0.855, 5*0.75*0.75*0.855, 2*0.783*0.75*0.855)

194 A41 = Leg41^2*frTwo A41 = 0.375^2*0.855 A41 = 0.120 0.120

201 A43 = (Leg43-nca)̂ 2*frtwo A43 = (0.375-0)^2*0.855 A43 = 0.120 0.120

203 Actual Area = 4.178 7.188


max(16, 2*(0.313+0.75)) * (1*0.313-1*0)-2*0.75*(1*0.313-1*0)*(1-0.855)

min((0.75-0.037)*0.855*Min(5*0.313,2*1) , (0.75-0.037)*0.855*Min(5*0.75,2*1))

min((0.75-0)*0.855*Min(5*0.313,2*1) , (0.75-0)*0.855*Min(5*0.75,2*1))

max(16, 2*(0.313+0.75)) * (1*0.313-1*0.188)-2*0.75*(1*0.313-1*0.188)*(1-0.855)

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= (78.5*8.094)/(17100*1 - 0.6*78.5)

= (3*17.5*0)/(4*1)

Sample Vessel #3

12" Manway F With 3/4"x4" Ring

0.5*(16*0*1 + 2*0.75*0*1*(1-0.855))

UW-16.1 (c) modified

Leg41

OD Nozzle

Nt

Leg41

Leg43

Leg43

Proj

Vt N o z z l e

Shell

FullPenn.t



Vessel Weight and Volume 21-May-02 of 24

<- Vessel

Volume:

1.00 <- Fluid Specific Gravity

72.06 <- Head each (cuft) 144.11 2 heads496.12 <- Shell (cuft) 496.12

======

640.24 <- cuft

3988.03 <- Imp Gallons

4789.29 <- US Gallons

39,931 <- fluid wt 39,931

Construction:

945.29 <- Head (ea, lbs) 1890.58 2 heads

3202.22 <- Shell 3202.22

1300 <- Misc 1300

=======6,393 <- lbs 6,393

======

Total 46,324 lbs

Sample Vessel #3



1 Zick Analysis - Unstiffened Vessel ver 1.02 21-May-02 of 24

2 L.P. Zick - 1951

4 <- vessel

5 <- Item

7 123.000 <- L - Length (inch)

8 48.000 <- R - Radius of Shell (inch)

9 24.000 <- H - depth of Head

10 120.000 <- Theta - Saddle Contact Angleº11 12.000 <- b - Saddle Width (inch)

12 12.000 <- A - Overhang (inch)

13 0.313 <- ts - Nominal Shell Thickness (inch)

14 0.313 <- th - Nominal Head Thickness (inch)

16 23,162 <- Q, Load on one saddle (lbs)

17 78.5 <- P, Design Pressure, (psi)

18 SA-516 70 <- Shell Material

19 20,000 <- Sa, Allowable Shell Stress (psi)

20 38,000 <- Sy, Yield Point (psi)

21 11,500 <- Comp Limit for Shell, psi

22 0.70 <- E, Circ Joint Efficiency

24 K Factors - From Charts25 K1 = 0.335 K4 = 0.880 K5 = 0.401 K7 = 0.760

26 K2 = 1.171 K3 = 0.319 K6 = 0.013 K8 = 0.603

28 Stress - Longitudinal Bending - Tension29 S1a top saddle = ((Q*A)(K1*Rvar^2*ts))*(*(1-(1-A/L+(Rvar^2-H^2)/(2*A*L))/(1+(4*H)/(3*L)))) S1a = -208

30 = (23162.1340737743*12/(0.335*48^2*0.313))*(1-(1-12/123+(48^2-24^2)/(2*12*123)/(1+(4*24)/(3*123)

31 1b bot. saddle = ((Q*A)(K8*Rvar^2*ts))*(*(1-(1-A/L+(Rvar^2-H^2)/(2*A*L))/(1+(4*H)/(3*L)))) S1b = -115

32 = (23162.1340737743*12/(0.603*48^2*0.313))*(1-(1-12/123+(48^2-24^2)/(2*12*123)/(1+(4*24)/(3*123)

33 S1c midspan = ((Q*L/4)/(Pi()*Rvar^2*ts))*(1+(2*(Rvar̂ 2-H^2)/L^2/(1+(4*H)/(3*L))-(4*A/L)) S1c = 249

34 = ((23162.1340737743*123/4)/(3.14*48^2*0.313))*(1+(2*(48^2-24^2)/123^2/(1+(4*24)/(3*123))-(4*12/123))

35 S1max = Max(S1a, S1b, S1c) = Max(-208, -115, 249) S1max = 249

36 S1from Press. = P*R/(2*ts) = 78.4648*48/(2*0.313) S1p = 6,016 37 S1total = S1max + S1p = 249 + 6016 S1total = 6,265

38 S1Limit = Sa * E = 20000 * 0.7 S1Limit = 14,000

39 Acceptable

40 Stress - Longitudinal Bending - Compression41 A = 0.125/(R/t) = 0.125/(48/0.313) A = 0.00082

42 Max Comp = max(S1b, S1c) = Max(-115, 249) Max Comp = 249

43 Comp Limit = 11,500

44 Acceptable

45 Stress - Tangential Shear - Shell 46 S2a in Shell = ((K2*Q)/(R*ts))*((L-2*A)/(L+4/3*H) S2a = 1,153

47 = ((1.171*23162.1340737743)/(48*0.313))*((123-2*12/(123+4/3*24)

48 S2b in Shell = ((K3*Q)/(R*ts))*((L-2*A)/(L+4/3*H) S2b = 314

49 = ((0.319*23162.1340737743)/(48*0.313))*((123-2*12/(123+4/3*24)

50 S2c in Shell = (K4*Q)/(R*ts) = (0.88*23162.1340737743)/(48*0.3 S2c = 1,357

51 S2d in Head = (K4*Q)/(R*th) = (0.88*23162.1340737743)/(48*0.3 S2d = 1,357

52 S2e (A>R/2) = max(S2a, S2b) = max(1153, 314) S2e = 1,153

53 S2f (A<=R/2) = max(S2c, S2d) = max(1357, 1357) S2f = 1,357

54 S2 = Use S2f S2 = 1,357

55 S2 limit = 0.8*Sa = 0.8*20000 S2 limit = 16,000

56 Acceptable

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Sample Vessel #3

Saddle Support Calculations

Q Q

L

R



60 Sample Vessel #3 Saddle Support Calculations 21-May-02 of 24

61

67 Stress - Circumferential Bending - Saddle Horn68 S4a (L >= 8R) = (Q/(4*ts*(b+1.56*sqrt(R*ts))))-((3*K6*Q)/(2*ts^2)) S4a = 3,611

69 = (23162.1340737743/(4*0.313*(12+1.56*sqrt(48*0.313))))-((3*0.013*23162.1340737743)/(2*

70 S4b (L < 8R) = (Q/(4*ts*(b+1.56*sqrt(R*ts))))-((12*K6*Q*Rvar)/(2*L*ts^2)) S4b = 6,212

71 = (23162.1340737743/(4*0.313*(12+1.56*sqrt(48*0.313))))-((12*0.013*23162.1340737743*4

72 S4 = Use S4b S4 = 6,212

73 S4 limit = 1.5*Sa = 1.5*20000 S4 limit = 30,000

74 Acceptable

75 Stress - Circumferential Bending - Bottom of Shell 76 S5 = Q*K7/(ts*(b+1.56*sqrt(R*ts))) S5 = 3116

77 = (23162.1340737743*0.76)/(0.313*(12+1.56*SQRT(48*0.313)))

78 S5 limit = 0.5*Sy = 0.5*Sy S5 limit = 19,000

79 Acceptable

80

81



1 Horizontal Vessel Loads ver1.0 21-May-02 of 24

2 Moss - Pressure Vessel Design Manual

4 <- Vessel

5 <- Item

7 Vessel:8 48.0 <- R, Radius (inch) 96.0 <- D

9 123.0 <- L, Length (inch)

10 46,324 <- W, Largest Weight (lbs)

12 Environment:13 0 <- Exposure Factor (E)

14 0 <- Wind velocity (mph)

15 1.0 <- Wind Importance factor (I)

16 10 <- Highest height above ground, ft (Hmax)

17 3 <- Seismic Zone 0.116 <- Coefficient

18 1.00 <- Slide Pad Coeficient of Friction (Cf)

20 Gravity

21 Q = W/2 = 46324.2681475486 / 2 Q = 23,162

23 Wind

24 Kz = 0.00 ANSI A58.1 1982

25 Gh = 0.00 ANSI A58.1 1982

26 Area L = pi*R^2/144 = 3.14 * 48 ^ 2 / 144 Area L = 50

27 Area T = AreaL + D*L/144 = 50 + 96 * 123 / 144 Area T = 132

28 Qz = 0.00256*Kz*(I*V)^2 = 0.00256 * 0 * (1 * 0)^2 Qz = 0.0

29 WL = AreaL*0.6*Gh*Qz = 50 * 0.6 * 0 * 0 WL = 0

30 WT = AreaT*0.6*Gh*Qz = 132 * 0.6 * pi*R^2/144 * 0 WT = 0

32 Seismic

33 SL = C*W = 0.116 * 46324.2681475486 SL = 5,374

34 ST = C*Q = 0.116 * 23162.1340737743 ST = 2,687

36 Thermal Expansion

37 ET = 038 EL = Cf*Q = 0.116 * 23162.1340737743 EL = 23,162

40 Combined Forces

41 Q = Fg Q = 23,162

42 Ft = Max(WT,ST) = Max(0 , 2687) Ft = 2,687

43 Fl = Max(WL+EL,SL) = Max(0 + 23162 , 5374) Fl = 23,162

44

45 No slide pads used - both ends bolted

46

www.xlpv.com On line help

Sample Vessel #3

Support Loads

Q

Fl

Q

FixedHmax

Moving

Weight

L

Ft

R



59 Sample Vessel #3 Saddle Design- 44w cs 21-May-02 of 24

61 Foundation Load 62 Ba = A * Bp = 67 * 12 Base Area - Ba = 804

63 Bs = Fg / Ba = 23162 / 804 Foundation Stress - Bs = 29

64 Okay Max 500 psi for concret

65 Moment of Inertia - Saddle Splitting

67 Width = Bp + 1.56*SQRT(VarR*Ts) Shell Effective Width = 18.6

68 = 12 + 1.56*SQRT(48*0.375)70 Width Height Area Y A*Y A*Y2 Io

71 Shell 18.62 0.31 5.83 18.16 106 1921 0.0

72 Wear Plate 12.00 0.38 4.50 17.81 80 1428 0.1

73 Saddle 0.38 16.88 6.33 9.19 58 534 150.2

74 Base 12.00 0.75 9.00 0.38 3 1 0.4

75 Sum 18.3 25.66 247 3884 150.7

77 C1 = Sum(Ay)/Sum(A) = 247.5 / 25.7 Centroid C1 = 9.6

78 I = SumAY2 + SumIo - Ci*SumAy

79 = 3884.3 + 150.7 - 9.6 * 247.5 I = 1647.8

80 A5 = SumA-AShell = 25.7 - 5.8 A5 = 19.8

81

82 Tension Stress - Saddle Splitting 83 Fh = K1*Fg = 0.206 * 23162.1 Saddle Splitting force Fh = 4771.4

84 Tension = 2*Fh/A5 = 2 * 4771 / 20 Tension = 481

85

86 en ng ress - a e p ng 87 d = Hc - 0.827*R = 66 - 0.827 * 48 d = 26.3

88 M = 2*fh*d = 2 * 4771 * 26.3 M = 251014

89 fb = MC1/I = 251014 * 10 / 1648 fb = 1469

90

91 Base plate thickness92 M2 = Q*Bp/8 = 23162*12/8 M2 = 34743.2

93 Z = A*tb^2/6 = 67*0.75^2/6 Z = 6.28194 fb2 = M/Z = 34743 / 6.2813 fb2 = 5531

95

96 Moment of Inertia - Longitudinal Direction97 Width Thick Area Y A*Y A*Y2 Io

98 Saddle 66.3 0.4 24.8 5.3 130.4 684.8 0.3

99 Half Ribs 0.4 5.1 9.5 2.5 24.0 60.8 4.1

100 Half Ribs 0.4 5.1 9.5 8.0 75.6 602.8 4.1

101 Sum 10.5 43.8 230.1 1348.3 8.4

103 C3 = Sum(Ay)/Sum(A) = 230.1 / 43.8 Centroid C3 = 5.3

104 I = SumAY2 + SumIo - C2*SumAy

105 = 1348.3 + 8.4 - 5.3 * 230.1 I3 = 148.7

106

107 Support Shear - Longitudinal Load 108 Shear L = FL / area = 23162 / 44 Shear L = 528

109

110 Bending Stress - Longitudinal Load 111 Lr = h+0.29*R-tb-ts = 18.313 + 0.29 * 48 - 0.375 - 0.75Longest Rib - Lr = 31.1

112 Ls = Hc-R-tb-ts-tp = 66 - 48 - 0.75 - 0.375 - 0.375 Shortest Rib - Ls = 16.5

113 Lave = (Lr + Ls)/2 = (31.1 + 16.5)/2 Lave = 23.8

114 M3 = fl*Lave = 23162 * 23.8 M3 = 551351

115 fb3 = MC2/I2 = 551351 * 5 / 149 fb3 = 19463

116

Horizontal Vessel Calculation

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