asme viii calcs
DESCRIPTION
Asme Viii CalcsTRANSCRIPT
ASME SECTION VIII Div.1
SHELL CALCULATIONS NOZZLE CALCULATIONS
CIRCUMFERENTIAL STRESSES CIRCUMFERENTIAL STRESSESVALUES VALUES
Maximum Allowable Working Pressure (P): 300 Maximum Allowable Working Pressure (P): 300
Maximum Allowable Stress Value (S): 17500 Maximum Allowable Stress Value (S): 17500Height: 75
Joint Efficiency: 1 Joint Efficiency: 1 Static Head 32.5 psi
Inside Diameter of Shell: 69.875 34.9375 inside R Outside Diameter of Nozzle: 6.625 2.7125 Rn
Corrosion Allowance: Corrosion Allowance:
Given total wall thickness: 0.653 0.6530 Nom-CA Given total wall thickness: 0.6 0.6000 Nom-CA
FOR CIRCUMFERENTIAL STRESS (Longitudinal Joints): FOR CIRCUMFERENTIAL STRESS (Longitudinal Joints):
t = PR/SE - 0.6P P = SEt/R + 0.6t t = PR/SE - 0.6P P = SEt/R + 0.6t
t =: 0.6052 inches P =: 323 psig t =: 0.0470 inches P =: 3417 psig
FOR LONGITUDINAL STRESS (Circumferential Joints): FOR LONGITUDINAL STRESS (Circumferential Joints):
t = PR/2SE + 0.4P P = 2SEt/R - 0.4t t = PR/2SE + 0.4P P = 2SEt/R - 0.4t
t =: 0.2984 inches P =: 659 psig t =: 0.0232 inches t =: 8493 psig 0.605150.0470
The minimum required shell thickness for a MAWP of 300 psig The minimum required nozzle thickness for a MAWP of 300 psig 0.6052
is 0.6052 inches, including CA. is 0.0470 inches, including CA. 0.0470
The MAWP with a shell 0.6530 inches, including CA The MAWP with a shell 0.6000 inches, including CA
thick is: 323 psig. thick is: 3417 psig.
NOZZLES
Required thickness of shell (tr): 0.6052 L1 = 5.4250 3.9655L2 = 1.6325 2.2500
Required thickness of nozzle (trn): 0.0470
Diameter of circular opening (d): 5.4250 Nozzle: Inserted (Inserted or Abutting)
Correction Factor (F): 1
Nominal thickness of nozzle wall (tn): 0.6000 Actual tn: 0.60000
Stress value of nozzle (Sn): 17500
Stress value of shell (Sv): 17500 1.25
Stress value of reinforcment (Sp): 12500
Inside shell diameter (D): 69.8750
Outside diameter of reinforcement (Dp): 10 Actual Dp: 10.0000 5.42505.4250
Thickness of reinforcement (te): 0.75 Actual te: 0.7500 0.751.6325
Efficiency (E1): 1.0000
Nominal thickness of shell (t): 0.6530 Actual t: 0.65300
Nozzle projection (h): 0
Corrosion allowance: 0.0000
Top nozzle weld size: 0.75 Actual Weld: 0.7500 1.5 0.75001.6325
Outer reinforcement weld size: 0.5 0.4250 0.4250
Inward nozzle weld: 0.0000
Area required: dtrF+2tntrF(1-fr1) A=: 3.2832 SQUARE INCHES
Area: sheld(Et-Ftr)-2tn(Et-Ftr)(1-fr1) A1=: 0.2593 0.2593or 2(t+tn)(Et-Ftr)-2tn(Et-Ftr)(1-fr1) 0.1198
Area: nozzle 5(tn-trn)fr2t A2=: 1.6590 1.8055or 5(tn-trn)fr2tn 1.659
Area: inward nozzle 2(tn-c)fr2h A3=: 0.0000
Area:nozzle weld ouleg*leg*fr2 A41=: 0.5625
Area: nozzle weld inleg*leg*fr2 A43=: 0.0000Nozzle is acceptable.
FIRST CALCULATIONS Reinforcement is required.More reinforcement is required
A1 + A2 + A3 + A41 + A43=: 2.4808
Reinforcement is required.
REINFORCEMENT CALCULATIONS
Area required: dtrF+2tntrF(1-fr1) A=: 3.2832 SQUARE INCHES
Area: shell: d(Et-Ftr)-2tn(Et-Ftr)(1-fr1 A1=: 0.2593 0.2593or 2(t+tn)(Et-Ftr)-2tn(Et-Ftr)(1-fr1) 0.1198
Area: nozzle: 5(tn-trn)fr2t A2=: 1.8055 1.8055or 2(tn-trn)(2.5tn+te)fr2 2.4885
Area: inward nozzle 2(tn-c)fr2h A3=: 0.0000
Area nozzle out wel leg*leg*fr3 A41=: 0.4018 fr1 = 1.0000 1 1fr2 = 1.0000 1
Area out rein. weld: leg*leg*fr4 A42=: 0.1290 fr3 = 0.7143 0.7143fr4= 0.7143 0.7143
Area in nozzle weld leg*leg*fr2 A43=: 0.0000
Area in repad (Dp-d-2tn)tefr4 A5=: 1.8081
A1 + A2 + A3 + A41 + A42 + A43 + A5 =: 4.4037
Nozzle is acceptable.
High Temp 650 High Stress 18.8Low Temp 600 Low Stress 19.4Difference 50 Difference 0.6
MAWT 620 2040
Actual Stress 19,160 0.24
Inspection Intervals:
Time: 7 years Corrosion Rate: 0.0171 in/yr
Previous thickness: 0.5 in. Corrosion Allowance: 0.2029 in.
Present thickness: 0.38 in Remaining Life: 11.836 years
Required thickness: 0.1771 in.
Metal Loss: 0.12 in.
Semi-Elliptical Heads
HEAD CALCULATIONS
VALUES
Maximum Allowable Working Pressure (P): 150
Maximum Allowable Stress Value (S): 17500
Joint Efficiency: 1
Inside Diameter of Head: 69.875 34.9375 (inside radius minus corrosion allowance)
Corrosion Allowance:
Mill tolerance:
Given total wall thickness: 1.125 1.1250 (Nominal Thickness minus corrosion allowance)
FOR SEMI-ELLIPTICAL HEADS:
t = PD/2SE - 0.2P P = 2SEt/D + 0.2t
t =: 0.2997 inches P =: 562 psig
Critical Thickness: 0.315 in. 0.7124
Flat Circular Heads
HEAD CALCULATIONS
VALUES
Maximum Allowable Working Pressure (P): 250
Maximum Allowable Stress Value (S): 20000
Joint Efficiency: 1
Inside Diameter of Head: 32 16.0000 (inside radius minus corrosion allowance)
Corrosion Allowance: 0.0000C Factor 0.17Given total wall thickness: 2.6883 2.2313 (Nominal Thickness minus corrosion allowance)
FOR SEMI-ELLIPTICAL HEADS:
t =: 1.4751 inches
Critical Thickness: 1.549 in. 1.8532
t = D√(CP/SE)
Flat Circular Heads (raised face)
HEAD CALCULATIONS
Maximum Allowable Working Pressure (P):
Maximum Allowable Stress Value (S):
Joint Efficiency:
(inside radius minus corrosion allowance) Inside Diameter of Head:
Corrosion Allowance:
C Factor
(Nominal Thickness minus corrosion allowance) Given total wall thickness:WhG
FOR SEMI-ELLIPTICAL HEADS:
t =: 1.9596 inches
Critical Thickness: 2.058
t = D√(CP/SE)
VALUES
250
20000
1
32 16.0000 (inside radius minus corrosion allowance)
0.00000.3
2.6883 1.8818 (Nominal Thickness minus corrosion allowance)
in. 1.9207
HEAD CALCULATIONS
VALUES
Maximum Allowable Working Pressure (P): 750
Maximum Allowable Stress Value (S): 19100
Joint Efficiency: 0.85
Inside Diameter of Head: 72 36.1250 (inside radius minus corrosion allowance)
Corrosion Allowance: 0.1250
Mill tolerance:
Given total wall thickness: 0.2722 0.1472 (Nominal Thickness minus corrosion allowance)
FOR HEMISPERICAL HEADS:
t = PL t = 0.8383 inches P = 2SEt P =
2SE - 0.2P L + 0.2t
Critical thickness: 0.8802 inches or 0.4927 inches
(inside radius minus corrosion allowance)
(Nominal Thickness minus corrosion allowance)
245 psig
VALUES
Maximum Allowable Working Pressure (P):
Maximum Allowable Stress Value (S): 20000
Joint Efficiency: 1
Outside Diameter of Pipe: 4.5 1.99
Corrosion Allowance: 0.0500Mill tolerance: 0Given total wall thickness: 0.26 0
For Straight Run Pipe:
t = PD/2(SE + Py) P =: 2tSE/D-2tyt =: 0.0000 inches P =: 2423 psig
t required = 0.0500
d = 168.25C = 0.3P = 147S = 20,000E = 1W = 3,000,000hg = 4.625
t = 8.3817
API 650 Tanks
D = 50 ft. t nom = 0.5 in.
H = 48 ft.
G = 1.3
Sd = 20000
CA = 0.0625 in.
t = 2.6D(H-1)G + CASd
min t = 0.3972 in. critical t = 0.421 in.
t = 0.4597 in. Flag t = 0.4375 in.
ASME SECTION I
DRUM CALCULATIONS
VALUES
Maximum Allowable Working Pressure (P): 2500
Maximum Allowable Stress Value (S): 18800
Joint Efficiency (E): 1
Ouside Diameter of Drum (D): 84 Inside Radius of Drum (R):
Temperature Coefficient (y): 0.4000
Threading Allowance (C: 0.0000
Given total wall thickness: 5.303
For Outside Diameter:
t = (PD/2SE + 2yP) + C P = 2SE(t - C)/D - 2y(t - C)
t =: 5.3030 inches P =: 2500 psig
For Inside Radius
t = (PR/SE (1 - y)P) + C P = SE(t-C)/R + (1 - y)(t - C)
t =: 5.3210 inches P =: 2492 psig
Inside Radius of Drum (R): 36.8212
Boiler Tubes
P = 1949
D = 2.5
S = 15000
E = 1
e = 0
t = PD + 0.005D + e2S + P
t = 0.1650
0.2050
P = (2St)/D * 1000 * F CSA Z662
P = Design PressureS = Specified Minimum Yield Strength (SMYS)t = Nominal Wall ThicknessD = Outside DiameterF = Combined Factor (F, L, J & T)CA = Corrosion Allowance
S = 359 Mpat = 5.56 mmD = 114.3 mmF = 0.6CA = 1.61 mm
P = 20956 kPa
Pit Depth Evaluation Pit Length Evaluation
CA % = 29% L = 1.12Bsqrt(Dt)
Pit Depth = 1 mm L = Maximum Length of Corroded Area18% B = 4.0 for depths >10% & <=17.5%, calculated value for >17.5% & <= 80%
Acceptable Yes D = Outside Diametert = Nominal Wall Thickness
L = 102.32 mm
P = 2F(s/D)t ASME B31G
P = Design PressureF = Design Factor, usually 0.72S = Specified Minimum Yield Strength (SMYS)t = Nominal Wall ThicknessD = Outside Diameter
S = 48000 psit = 0.159 in
D = 4.5 inF = 0.72
P = 2,442 psig16,827 kPa
4.0 for depths >10% & <=17.5%, calculated value for >17.5% & <= 80%
B = 3.624
t = Pd/2F-P
P = 586 kPag
D = 1372 mm
F = 165000 kPa
t = 2.440673 mm
0.09609 in