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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
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Table of Contents 21-May-02 Page 2 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
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Pressure Vessel Design Summary 21-May-02 Page 3 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
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1 Material Properties ver 1.28 www.pveng.com 21-May-02 Page 4 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
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12 Pipe and Shell ver 2.33 21-May-02 Page 5 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
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1 Elliptical Head ver 2.16 Page 6 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
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15 Coupling ver 2.02 UW16.1Z1M 21-May-02 Page 7 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
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298 Sample Vessel #3 6" SCH 80 Nozzle B 21-May-02 Page 9 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
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156 Sample Vessel #3 6" SCH 80 Nozzle C 0.0135 0.22035 21-May-02 Page 11 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
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12 B16.5 Slip On Flange Ver 1.35 www.pveng.com 21-May-02 Page 12 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
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26 Nozzle Reinforcement ver 3.53 UW16(c)mod 21-May-02 Page 13 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
49 17.500 <- Do, outside diameter
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
73 0.313 <- Leg43, 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
142 0.7*Leg43 >= tc43 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
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) = 2.734
160 = 1.0*16*0.169*1 + 2*0.75*0.169*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(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
204 Acceptable Actual-Required = 0.093 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
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26 Nozzle Reinforcement ver 3.53 UW16(c)mod 21-May-02 Page 14 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
49 17.500 <- Do, outside diameter
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
73 0.375 <- Leg43, 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:
133 0.7*Leg41 >= tc41 0.7*0.375 >= 0.219 0.263 >= 0.219 Acceptable
142 0.7*Leg43 >= tc43 0.7*0.375 >= 0.219 0.263 >= 0.219 Acceptable
151 UG45 = Long form calculations are not shown in this view UG45 = 0.188 Acceptable
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) = 3.041
160 = 1.0*16*0.188*1 + 2*0.75*0.188*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 = 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
204 Acceptable Actual-Required = 1.137 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
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Vessel Weight and Volume 21-May-02 Page 16 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
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1 Zick Analysis - Unstiffened Vessel ver 1.02 21-May-02 Page 18 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
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60 Sample Vessel #3 Saddle Support Calculations 21-May-02 Page 19 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
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1 Horizontal Vessel Loads ver1.0 21-May-02 Page 20 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
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59 Sample Vessel #3 Saddle Design- 44w cs 21-May-02 Page 23 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
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