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Model Notes (80 NB Shell, 32NB Nozzle)
Input Echo:
Model Type : Cylindrical Shell
Parent Outside Diameter : 88.900 mm.
Thickness : 5.490 mm.
Fillet Along Shell : 5.000 mm.
Parent Properties:
Material DB # 1068318.
(See Output Reports for Allowables.)
Elastic Modulus (Amb) : 195100.0 MPa
Poissons Ratio : 0.300
Expansion Coefficient : 0.1707E-04 mm./mm./deg.
Weight Density : 0.0000E+00 N /cu.mm.(NOT USED)
Nozzle Outside Diameter : 42.100 mm.
Thickness : 3.680 mm.
Length : 150.000 mm.
Nozzle Weld Length : 5.000 mm.
Nozzle Tilt Angle : 0.000 deg.
Distance from Top : 0.000 mm.
Distance from Bottom : 500.000 mm.
Nozzle PropertiesMaterial DB # 1064818.
(See Output Reports for Allowables.)
Elastic Modulus (Amb) : 195100.0 MPa
Poissons Ratio : 0.300
Expansion Coefficient : 0.1707E-04 mm./mm./deg.
Weight Density : 0.0000E+00 N /cu.mm. (NOT USED)
Design Operating Cycles : 7000.
Ambient Temperature (Deg.) : 21.10
The following temperatures have been specified for the analysis:
Nozzle Inside Temperature : 200.00 deg.
Nozzle Outside Temperature : 200.00 deg.
Vessel Inside Temperature : 200.00 deg.
Vessel Outside Temperature : 200.00 deg.
Nozzle Pressure : 2.800 MPa
Vessel Pressure : 2.800 MPa
User Defined Load Input Echo:
Loads are given at the Nozzle/Header Junction
Loads are defined in Local Coordinatesc
Forces( N ) Moments (N-m)
Load Case FX FY FZ MX MY MZ
---------------------------------------------------------------------------
OPER: 1200.0 1200.0 1200.0 350.0 350.0 350.0
FEA Model Loads:
These are the actual loads applied to the FEA model.
These are the User Defined Loads translated to the
end of the nozzle and reported in global coordinates.
Forces( N ) Moments (N-m)
Load Case FX FY FZ MX MY MZ
---------------------------------------------------------------------------
OPER: 1200.0 1200.0 1200.0 350.0 530.0 170.0
The "top" or "positive" end of this model is "free" in
the axial and translational directions.
Stresses ARE nodally AVERAGED.
Vessel Centerline Vector : 0.000 1.000 0.000
Nozzle Orientation Vector : 1.000 0.000 0.000
Table of Contents
Load Case Report
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3 672. 16509. 1200.
4 353202. 0. 0.
5 0. 0. 0.
6 0. 0. 0.
7 0. 0. 0.
8 -528. 15309. 0.
Table of Contents
ASME Code Stress Output Plots
1) Pl < (1.5)(S) (SUS,Membrane) Case 1
2) Qb < SPS (SUS,Bending) Case 1
3) S1+S2+S3 < 4S (SUS,S1+S2+S3) Case 1
4) Pl+Pb+Q < SPS (OPE,Inside) Case 3
5) Pl+Pb+Q < SPS (OPE,Outside) Case 3
6) Pl+Pb+Q+F < Sa (EXP,Inside) Case 3
7) Pl+Pb+Q+F < Sa (EXP,Outside) Case 3
8) Membrane < User (OPE,Membrane) Case 3
9) Bending < User (OPE,Bending) Case 3
10) Pl+Pb+Q+F < Sa (SIF,Outside) Case 4
11) Pl+Pb+Q+F < Sa (SIF,Outside) Case 5
12) Pl+Pb+Q+F < Sa (SIF,Outside) Case 6
13) Pl+Pb+Q+F < Sa (SIF,Outside) Case 7
14) Pl+Pb+Q+F < Sa (SIF,Outside) Case 8
Table of Contents
Region Data
Header Next to Nozzle Weld
Cold Allowable ........... 138. MPa
Hot Allowable @ 200 deg .. 133. MPa
Case 1
Nominal Stress (M/Z) ... 0. MPa
Pressure Stress (Pd/2t) .. 23. MPa
Case 3
Nominal Stress (M/Z) ... 237. MPa
Pressure Stress (Pd/2t) .. 23. MPa
Case 4
Nominal Stress (M/Z) ... 795. MPaPressure Stress (Pd/2t) .. 0. MPa
Case 5
Nominal Stress (M/Z) ... 90. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 6
Nominal Stress (M/Z) ... 90. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 7
Nominal Stress (M/Z) ... 90. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 8
Nominal Stress (M/Z) ... 23. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Smallest Thickness ....... 3.680 mm.
Stress Concentration ..... 1.350
Branch Next to Header Weld
Cold Allowable ........... 115. MPa
Hot Allowable @ 200 deg .. 109. MPa
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Case 1
Nominal Stress (M/Z) ... 0. MPa
Pressure Stress (Pd/2t) .. 23. MPa
Case 3
Nominal Stress (M/Z) ... 237. MPa
Pressure Stress (Pd/2t) .. 23. MPa
Case 4
Nominal Stress (M/Z) ... 795. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 5
Nominal Stress (M/Z) ... 90. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 6
Nominal Stress (M/Z) ... 90. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 7
Nominal Stress (M/Z) ... 90. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 8
Nominal Stress (M/Z) ... 23. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Smallest Thickness ....... 3.680 mm.
Stress Concentration ..... 1.350
Branch Transition
Cold Allowable ........... 115. MPaHot Allowable @ 200 deg .. 109. MPa
Case 1
Nominal Stress (M/Z) ... 0. MPa
Pressure Stress (Pd/2t) .. 23. MPa
Case 3
Nominal Stress (M/Z) ... 237. MPa
Pressure Stress (Pd/2t) .. 23. MPa
Case 4
Nominal Stress (M/Z) ... 795. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 5
Nominal Stress (M/Z) ... 90. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 6
Nominal Stress (M/Z) ... 90. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 7
Nominal Stress (M/Z) ... 90. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 8
Nominal Stress (M/Z) ... 23. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Smallest Thickness ....... 3.680 mm.
Stress Concentration ..... 1.350
Header away from Junction
Cold Allowable ........... 138. MPa
Hot Allowable @ 200 deg .. 133. MPa
Case 1
Nominal Stress (M/Z) ... 0. MPa
Pressure Stress (Pd/2t) .. 23. MPa
Case 3
Nominal Stress (M/Z) ... 237. MPa
Pressure Stress (Pd/2t) .. 23. MPaCase 4
Nominal Stress (M/Z) ... 795. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 5
Nominal Stress (M/Z) ... 90. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 6
Nominal Stress (M/Z) ... 90. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 7
Nominal Stress (M/Z) ... 90. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 8
Nominal Stress (M/Z) ... 23. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Smallest Thickness ....... 3.680 mm.
Stress Concentration ..... 1.000
Branch away from Junction
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Cold Allowable ........... 115. MPa
Hot Allowable @ 200 deg .. 109. MPa
Case 1
Nominal Stress (M/Z) ... 0. MPa
Pressure Stress (Pd/2t) .. 23. MPa
Case 3
Nominal Stress (M/Z) ... 237. MPa
Pressure Stress (Pd/2t) .. 23. MPa
Case 4
Nominal Stress (M/Z) ... 795. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 5
Nominal Stress (M/Z) ... 90. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 6
Nominal Stress (M/Z) ... 90. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 7
Nominal Stress (M/Z) ... 90. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 8
Nominal Stress (M/Z) ... 23. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Smallest Thickness ....... 3.680 mm.
Stress Concentration ..... 1.000
Table of Contents
Stress Results - Notes
- Results in this analysis were generated using the finite
element solution method.
- Using post 07 ASME Section VIII Division 2
- Use Polished Bar fatigue curve.
- Ratio between Operating and Design Pressure = 0.9000000
Assume pressure increases all other stresses.
Use operating pressure for occasional load cases.
- Assume free end displacements of attached pipe are
secondary loads within limits of nozzle reinforcement.
- Use Equivalent Stress (Von Mises).
- S1+S2+S3 evaluation omitted from operating stress.
Include S1+S2+S3 evaluation in primary case evaluation.
Assume bending stress not local primary for S1+S2+S3.
Table of Contents
ASME Overstressed Areas
*** NO OVERSTRESSED NODES IN THIS MODEL ***
Table of Contents
Highest Primary Stress Ratios
Header Next to Nozzle Weld
Pl (1.5)(S) Primary Membrane Load Case 1
24 200 Plot Reference:
MPa MPa 1) Pl < (1.5)(S) (SUS,Membrane) Case 1
12%
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Branch Next to Header Weld
Pl (1.5)(S) Primary Membrane Load Case 1
15 163 Plot Reference:
MPa MPa 1) Pl < (1.5)(S) (SUS,Membrane) Case 1
9%
Branch Transition
Pl (1.5)(S) Primary Membrane Load Case 1
14 163 Plot Reference:
MPa MPa 1) Pl < (1.5)(S) (SUS,Membrane) Case 1
8%
Header away from Junction
Pl (1.5)(S) Primary Membrane Load Case 1
22 200 Plot Reference:
MPa MPa 1) Pl < (1.5)(S) (SUS,Membrane) Case 1
10%
Branch away from Junction
Pl (1.5)(S) Primary Membrane Load Case 1
14 163 Plot Reference:
MPa MPa 1) Pl < (1.5)(S) (SUS,Membrane) Case 1
8%
Table of Contents
Highest Secondary Stress Ratios
Header Next to Nozzle Weld
Pl+Pb+Q SPS Primary+Secondary (Outer) Load Case 3
290 407 Plot Reference:
MPa MPa 5) Pl+Pb+Q < SPS (OPE,Outside) Case 3
71%
Branch Next to Header Weld
Pl+Pb+Q SPS Primary+Secondary (Outer) Load Case 3
312 336 Plot Reference:
MPa MPa 5) Pl+Pb+Q < SPS (OPE,Outside) Case 3
92%
Branch Transition
Pl+Pb+Q SPS Primary+Secondary (Outer) Load Case 3
193 336 Plot Reference:
MPa MPa 5) Pl+Pb+Q < SPS (OPE,Outside) Case 3
57%
Header away from Junction
Pl+Pb+Q SPS Primary+Secondary (Inner) Load Case 3
106 407 Plot Reference:
MPa MPa 4) Pl+Pb+Q < SPS (OPE,Inside) Case 3
26%
Branch away from Junction
Pl+Pb+Q SPS Primary+Secondary (Outer) Load Case 3
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147 336 Plot Reference:
MPa MPa 5) Pl+Pb+Q < SPS (OPE,Outside) Case 3
43%
Table of Contents
Highest Fatigue Stress Ratios
Header Next to Nozzle Weld
Pl+Pb+Q+F Damage Ratio Primary+Secondary+Peak (Outer) Load Case 3
196 0.007 Life Stress Concentration Factor = 1.350
MPa 0.406 Stress Strain Concentration Factor = 1.000
Cycles Allowed for this Stress = 944,526.
Allowable "B31" Fatigue Stress Allowable = 339.2
482.0 Markl Fatigue Stress Allowable = 329.8
MPa WRC 474 Mean Cycles to Failure = 317,661.
WRC 474 99% Probability Cycles = 73,796.
40% WRC 474 95% Probability Cycles = 102,456.
BS5500 Allowed Cycles(Curve F) = 31,790.
Membrane-to-Bending Ratio = 0.602
Bending-to-PL+PB+Q Ratio = 0.624Plot Reference:
7) Pl+Pb+Q+F < Sa (EXP,Outside) Case 3
Branch Next to Header Weld
Pl+Pb+Q+F Damage Ratio Primary+Secondary+Peak (Outer) Load Case 3
211 0.013 Life Stress Concentration Factor = 1.350
MPa 0.437 Stress Strain Concentration Factor = 1.000
Cycles Allowed for this Stress = 552,854.
Allowable "B31" Fatigue Stress Allowable = 279.9
482.0 Markl Fatigue Stress Allowable = 329.8
MPa WRC 474 Mean Cycles to Failure = 319,984.
WRC 474 99% Probability Cycles = 74,335.
43% WRC 474 95% Probability Cycles = 103,205.
BS5500 Allowed Cycles(Curve F) = 18,610.
Membrane-to-Bending Ratio = 0.783
Bending-to-PL+PB+Q Ratio = 0.561
Plot Reference:
7) Pl+Pb+Q+F < Sa (EXP,Outside) Case 3
Branch Transition
Pl+Pb+Q+F Damage Ratio Primary+Secondary+Peak (Outer) Load Case 3
130 0.002 Life Stress Concentration Factor = 1.350
MPa 0.270 Stress Strain Concentration Factor = 1.000
Cycles Allowed for this Stress = 4,505,958.
Allowable "B31" Fatigue Stress Allowable = 279.9
482.0 Markl Fatigue Stress Allowable = 329.8
MPa WRC 474 Mean Cycles to Failure = 1,368,181.
WRC 474 99% Probability Cycles = 317,841.
26% WRC 474 95% Probability Cycles = 441,282.
BS5500 Allowed Cycles(Curve F) = 108,897.
Membrane-to-Bending Ratio = 2.063Bending-to-PL+PB+Q Ratio = 0.327
Plot Reference:
7) Pl+Pb+Q+F < Sa (EXP,Outside) Case 3
Header away from Junction
Pl+Pb+Q+F Damage Ratio Primary+Secondary+Peak (Inner) Load Case 3
53 0.000 Life Stress Concentration Factor = 1.000
MPa 0.110 Stress Strain Concentration Factor = 1.000
Cycles Allowed for this Stress = 1.0000E11
Allowable "B31" Fatigue Stress Allowable = 339.2
482.0 Markl Fatigue Stress Allowable = 329.8
MPa WRC 474 Mean Cycles to Failure = 7,399,607.
WRC 474 99% Probability Cycles = 1,718,996.
11% WRC 474 95% Probability Cycles = 2,386,610.
BS5500 Allowed Cycles(Curve F) = 644,618.
Membrane-to-Bending Ratio = 0.330
Bending-to-PL+PB+Q Ratio = 0.752
Plot Reference:
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6) Pl+Pb+Q+F < Sa (EXP,Inside) Case 3
Branch away from Junction
Pl+Pb+Q+F Damage Ratio Primary+Secondary+Peak (Outer) Load Case 3
73 0.000 Life Stress Concentration Factor = 1.000
MPa 0.152 Stress Strain Concentration Factor = 1.000
Cycles Allowed for this Stress = 1.0000E11
Allowable "B31" Fatigue Stress Allowable = 279.9
482.0 Markl Fatigue Stress Allowable = 329.8
MPa WRC 474 Mean Cycles to Failure = 3,121,431.
WRC 474 99% Probability Cycles = 725,137.
15% WRC 474 95% Probability Cycles = 1,006,761.
BS5500 Allowed Cycles(Curve F) = 245,942.
Membrane-to-Bending Ratio = 22.788
Bending-to-PL+PB+Q Ratio = 0.042
Plot Reference:
7) Pl+Pb+Q+F < Sa (EXP,Outside) Case 3
Table of Contents
Stress Intensification Factors
Branch/Nozzle Sif Summary
Peak Primary Secondary
Axial : 3.289 1.835 4.873
Inplane : 1.144 0.926 1.695
Outplane: 1.934 1.097 2.866
Torsion : 0.816 0.985 1.209
Pressure: 0.879 1.069 1.303
The above stress intensification factors are to be used
in a beam-type analysis of the piping system. Inplane,
Outplane and Torsional sif's should be used with the
matching branch pipe whose diameter and thickness is given
below. The axial sif should be used to intensify the
axial stress in the branch pipe calculated by F/A. The
pressure sif should be used to intensify the nominal
pressure stress in the PARENT or HEADER, calculated
from PD/2T.
Pipe OD : 42.100 mm.
Pipe Thk: 3.680 mm.
Z approx: 4266.306 cu.mm.
Z exact : 3929.104 cu.mm.
B31.3 Branch Pressure i-factor = 2.490
Header Pressure i-factor = 1.759
The B31.3 pressure i-factors should be used with with
F/A, where F is the axial force due to pressure, and
A is the area of the pipe wall. This is equivalent to
finding the pressure stress from (ip)(PD/4T).
B31.3
Peak Stress Sif .... 0.000 Axial1.916 Inplane
2.331 Outplane
1.000 Torsional
B31.1
Peak Stress Sif .... 0.000 Axial
2.407 Inplane
2.407 Outplane
2.407 Torsional
WRC 330
Peak Stress Sif .... 0.000 Axial
1.488 Inplane
1.624 Outplane
1.000 Torsional
Table of Contents
Allowable Loads
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SECONDARY Maximum Conservative Realistic
Load Type (Range): Individual Simultaneous Simultaneous
Occuring Occuring Occuring
Axial Force ( N ) 30620. 9666. 14499.
Inplane Moment (mm. N ) 778910. 173873. 368839.
Outplane Moment (mm. N ) 460549. 102806. 218085.
Torsional Moment (mm. N ) 1091422. 344549. 516824.
Pressure (MPa ) 36.82 2.80 2.80
PRIMARY Maximum Conservative Realistic
Load Type: Individual Simultaneous Simultaneous
Occuring Occuring Occuring
Axial Force ( N ) 39515. 11979. 17969.
Inplane Moment (mm. N ) 692745. 149258. 316625.
Outplane Moment (mm. N ) 584368. 125267. 265732.
Torsional Moment (mm. N ) 651047. 197369. 296054.
Pressure (MPa ) 23.13 2.80 2.80
NOTES:
1) Maximum Individual Occuring Loads are the maximum
allowed values of the respective loads if all other
load components are zero, i.e. the listed axial force
may be applied if the inplane, outplane and torsionalmoments, and the pressure are zero.
2) The Conservative Allowable Simultaneous loads are
the maximum loads that can be applied simultaneously.
A conservative stress combination equation is used
that typically produces stresses within 50-70% of the
allowable stress.
3) The Realistic Allowable Simultaneous loads are the
maximum loads that can be applied simultaneously. A
more realistic stress combination equation is used
based on experience at Paulin Research. Stresses are
typically produced within 80-105% of the allowable.
4) Secondary allowable loads are limits for expansion
and operating piping loads.
5) Primary allowable loads are limits for weight,
primary and sustained type piping loads.
Table of Contents
Flexibilities
The following stiffnesses should be used in a piping,
"beam-type" analysis of the intersection. The stiff-
nesses should be inserted at the surface of the
branch/header or nozzle/vessel junction. The general
characteristics used for the branch pipe should be:
Outside Diameter = 42.100 mm.
Wall Thickness = 3.680 mm.
Axial Translational Stiffness = 328869. N /mm.
Inplane Rotational Stiffness = 5227770. mm. N /deg
Outplane Rotational Stiffness = 2134740. mm. N /deg
Torsional Rotational Stiffness = 17393708. mm. N /deg
Intersection Flexibility Factors for
Branch/Nozzle :
Find axial stiffness: K = 3EI/(kd)^3 N /mm.
Find bending and torsional stiffnesses: K = EI/(kd) mm. N per radian.
The EI product is 0.16128E+11 N mm.^2
The value of (d) to use is: 38.420 mm..
The resulting bending stiffness is in units of force x length per radian.
Axial Flexibility Factor (k) = 1.374
Inplane Flexibility Factor (k) = 1.401
Outplane Flexibility Factor (k) = 3.432
Torsional Flexibility Factor (k) = 0.421
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Model Notes (80NB Shell, 25NB nozzle)
Input Echo:
Model Type : Cylindrical Shell
Parent Outside Diameter : 88.900 mm.
Thickness : 5.490 mm.
Fillet Along Shell : 5.000 mm.
Parent Properties:
Material DB # 1068318.
(See Output Reports for Allowables.)
Elastic Modulus (Amb) : 195100.0 MPa
Poissons Ratio : 0.300
Expansion Coefficient : 0.1707E-04 mm./mm./deg.
Weight Density : 0.0000E+00 N /cu.mm.(NOT USED)
Nozzle Outside Diameter : 33.500 mm.
Thickness : 3.380 mm.
Length : 150.000 mm.
Nozzle Weld Length : 5.000 mm.
Nozzle Tilt Angle : 0.000 deg.
Distance from Top : 0.000 mm.
Distance from Bottom : 500.000 mm.
Nozzle PropertiesMaterial DB # 1064818.
(See Output Reports for Allowables.)
Elastic Modulus (Amb) : 195100.0 MPa
Poissons Ratio : 0.300
Expansion Coefficient : 0.1707E-04 mm./mm./deg.
Weight Density : 0.0000E+00 N /cu.mm. (NOT USED)
Design Operating Cycles : 7000.
Ambient Temperature (Deg.) : 21.10
The following temperatures have been specified for the analysis:
Nozzle Inside Temperature : 200.00 deg.
Nozzle Outside Temperature : 200.00 deg.
Vessel Inside Temperature : 200.00 deg.
Vessel Outside Temperature : 200.00 deg.
Nozzle Pressure : 2.800 MPa
Vessel Pressure : 2.800 MPa
User Defined Load Input Echo:
Loads are given at the Nozzle/Header Junction
Loads are defined in Local Coordinatesc
Forces( N ) Moments (N-m)
Load Case FX FY FZ MX MY MZ
---------------------------------------------------------------------------
OPER: 1100.0 1100.0 1100.0 250.0 250.0 250.0
FEA Model Loads:
These are the actual loads applied to the FEA model.
These are the User Defined Loads translated to the
end of the nozzle and reported in global coordinates.
Forces( N ) Moments (N-m)
Load Case FX FY FZ MX MY MZ
---------------------------------------------------------------------------
OPER: 1100.0 1100.0 1100.0 250.0 415.0 85.0
The "top" or "positive" end of this model is "free" in
the axial and translational directions.
Stresses ARE nodally AVERAGED.
Vessel Centerline Vector : 0.000 1.000 0.000
Nozzle Orientation Vector : 1.000 0.000 0.000
Table of Contents
Load Case Report
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Inner and outer element temperatures are the same
throughout the model. No thermal ratcheting
calculations will be performed.
THE 8 LOAD CASES ANALYZED ARE:
1 SUSTAINED (Pr Only)
Sustained case run to satisfy local primary
membrane and bending stress limits.
/-------- Loads in Case 1
Pressure Case 1
2 Thermal ONLY
Thermal ONLY case run in the event expansion
stresses exceed the secondary stress allowable.
/-------- Loads in Case 2
Temperature Case 1
3 OPERATING (Fatigue Calc Performed)
Case run to compute the operating stresses used in
secondary, peak and range calculations as needed.
/-------- Loads in Case 3
Pressure Case 1
Temperature Case 1
Loads from (Operating)
4 Program Generated -- Force Only
Case run to compute sif's and flexibilities.
/-------- Loads in Case 4
Loads from (Axial)
5 Program Generated -- Force Only
Case run to compute sif's and flexibilities.
/-------- Loads in Case 5
Loads from (Inplane)
6 Program Generated -- Force Only
Case run to compute sif's and flexibilities.
/-------- Loads in Case 6
Loads from (Outplane)
7 Program Generated -- Force Only
Case run to compute sif's and flexibilities.
/-------- Loads in Case 7
Loads from (Torsion)
8 Program Generated -- Force Only
Case run to compute sif's and flexibilities.
/-------- Loads in Case 8
Pressure Case 1
Table of Contents
Solution Data
Maximum Solution Row Size = 870
Number of Nodes = 2256
Number of Elements = 744
Number of Solution Cases = 8
Summation of Loads per Case
Case # FX FY FZ
1 -455. 15299. 0.
2 0. 0. 0.
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3 645. 16399. 1100.
4 205408. 0. 0.
5 0. 0. 0.
6 0. 0. 0.
7 0. 0. 0.
8 -455. 15299. 0.
Table of Contents
ASME Code Stress Output Plots
1) Pl < (1.5)(S) (SUS,Membrane) Case 1
2) Qb < SPS (SUS,Bending) Case 1
3) S1+S2+S3 < 4S (SUS,S1+S2+S3) Case 1
4) Pl+Pb+Q < SPS (OPE,Inside) Case 3
5) Pl+Pb+Q < SPS (OPE,Outside) Case 3
6) Pl+Pb+Q+F < Sa (EXP,Inside) Case 3
7) Pl+Pb+Q+F < Sa (EXP,Outside) Case 3
8) Membrane < User (OPE,Membrane) Case 3
9) Bending < User (OPE,Bending) Case 3
10) Pl+Pb+Q+F < Sa (SIF,Outside) Case 4
11) Pl+Pb+Q+F < Sa (SIF,Outside) Case 5
12) Pl+Pb+Q+F < Sa (SIF,Outside) Case 6
13) Pl+Pb+Q+F < Sa (SIF,Outside) Case 7
14) Pl+Pb+Q+F < Sa (SIF,Outside) Case 8
Table of Contents
Region Data
Header Next to Nozzle Weld
Cold Allowable ........... 138. MPa
Hot Allowable @ 200 deg .. 133. MPa
Case 1
Nominal Stress (M/Z) ... 0. MPa
Pressure Stress (Pd/2t) .. 23. MPa
Case 3
Nominal Stress (M/Z) ... 337. MPa
Pressure Stress (Pd/2t) .. 23. MPa
Case 4
Nominal Stress (M/Z) ... 642. MPaPressure Stress (Pd/2t) .. 0. MPa
Case 5
Nominal Stress (M/Z) ... 94. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 6
Nominal Stress (M/Z) ... 94. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 7
Nominal Stress (M/Z) ... 94. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 8
Nominal Stress (M/Z) ... 23. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Smallest Thickness ....... 3.380 mm.
Stress Concentration ..... 1.350
Branch Next to Header Weld
Cold Allowable ........... 115. MPa
Hot Allowable @ 200 deg .. 109. MPa
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Case 1
Nominal Stress (M/Z) ... 0. MPa
Pressure Stress (Pd/2t) .. 23. MPa
Case 3
Nominal Stress (M/Z) ... 337. MPa
Pressure Stress (Pd/2t) .. 23. MPa
Case 4
Nominal Stress (M/Z) ... 642. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 5
Nominal Stress (M/Z) ... 94. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 6
Nominal Stress (M/Z) ... 94. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 7
Nominal Stress (M/Z) ... 94. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 8
Nominal Stress (M/Z) ... 23. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Smallest Thickness ....... 3.380 mm.
Stress Concentration ..... 1.350
Branch Transition
Cold Allowable ........... 115. MPaHot Allowable @ 200 deg .. 109. MPa
Case 1
Nominal Stress (M/Z) ... 0. MPa
Pressure Stress (Pd/2t) .. 23. MPa
Case 3
Nominal Stress (M/Z) ... 337. MPa
Pressure Stress (Pd/2t) .. 23. MPa
Case 4
Nominal Stress (M/Z) ... 642. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 5
Nominal Stress (M/Z) ... 94. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 6
Nominal Stress (M/Z) ... 94. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 7
Nominal Stress (M/Z) ... 94. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 8
Nominal Stress (M/Z) ... 23. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Smallest Thickness ....... 3.380 mm.
Stress Concentration ..... 1.350
Header away from Junction
Cold Allowable ........... 138. MPa
Hot Allowable @ 200 deg .. 133. MPa
Case 1
Nominal Stress (M/Z) ... 0. MPa
Pressure Stress (Pd/2t) .. 23. MPa
Case 3
Nominal Stress (M/Z) ... 337. MPa
Pressure Stress (Pd/2t) .. 23. MPaCase 4
Nominal Stress (M/Z) ... 642. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 5
Nominal Stress (M/Z) ... 94. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 6
Nominal Stress (M/Z) ... 94. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 7
Nominal Stress (M/Z) ... 94. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 8
Nominal Stress (M/Z) ... 23. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Smallest Thickness ....... 3.380 mm.
Stress Concentration ..... 1.000
Branch away from Junction
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Cold Allowable ........... 115. MPa
Hot Allowable @ 200 deg .. 109. MPa
Case 1
Nominal Stress (M/Z) ... 0. MPa
Pressure Stress (Pd/2t) .. 23. MPa
Case 3
Nominal Stress (M/Z) ... 337. MPa
Pressure Stress (Pd/2t) .. 23. MPa
Case 4
Nominal Stress (M/Z) ... 642. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 5
Nominal Stress (M/Z) ... 94. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 6
Nominal Stress (M/Z) ... 94. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 7
Nominal Stress (M/Z) ... 94. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 8
Nominal Stress (M/Z) ... 23. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Smallest Thickness ....... 3.380 mm.
Stress Concentration ..... 1.000
Table of Contents
Stress Results - Notes
- Results in this analysis were generated using the finite
element solution method.
- Using post 07 ASME Section VIII Division 2
- Use Polished Bar fatigue curve.
- Ratio between Operating and Design Pressure = 0.9000000
Assume pressure increases all other stresses.
Use operating pressure for occasional load cases.
- Assume free end displacements of attached pipe are
secondary loads within limits of nozzle reinforcement.
- Use Equivalent Stress (Von Mises).
- S1+S2+S3 evaluation omitted from operating stress.
Include S1+S2+S3 evaluation in primary case evaluation.
Assume bending stress not local primary for S1+S2+S3.
Table of Contents
ASME Overstressed Areas
*** NO OVERSTRESSED NODES IN THIS MODEL ***
Table of Contents
Highest Primary Stress Ratios
Header Next to Nozzle Weld
Pl (1.5)(S) Primary Membrane Load Case 1
22 200 Plot Reference:
MPa MPa 1) Pl < (1.5)(S) (SUS,Membrane) Case 1
11%
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Branch Next to Header Weld
Pl (1.5)(S) Primary Membrane Load Case 1
11 163 Plot Reference:
MPa MPa 1) Pl < (1.5)(S) (SUS,Membrane) Case 1
6%
Branch Transition
Pl (1.5)(S) Primary Membrane Load Case 1
12 163 Plot Reference:
MPa MPa 1) Pl < (1.5)(S) (SUS,Membrane) Case 1
7%
Header away from Junction
Pl (1.5)(S) Primary Membrane Load Case 1
20 200 Plot Reference:
MPa MPa 1) Pl < (1.5)(S) (SUS,Membrane) Case 1
10%
Branch away from Junction
Pl (1.5)(S) Primary Membrane Load Case 1
12 163 Plot Reference:
MPa MPa 1) Pl < (1.5)(S) (SUS,Membrane) Case 1
7%
Table of Contents
Highest Secondary Stress Ratios
Header Next to Nozzle Weld
Pl+Pb+Q SPS Primary+Secondary (Outer) Load Case 3
286 407 Plot Reference:
MPa MPa 5) Pl+Pb+Q < SPS (OPE,Outside) Case 3
70%
Branch Next to Header Weld
Pl+Pb+Q SPS Primary+Secondary (Outer) Load Case 3
322 336 Plot Reference:
MPa MPa 5) Pl+Pb+Q < SPS (OPE,Outside) Case 3
95%
Branch Transition
Pl+Pb+Q SPS Primary+Secondary (Outer) Load Case 3
254 336 Plot Reference:
MPa MPa 5) Pl+Pb+Q < SPS (OPE,Outside) Case 3
75%
Header away from Junction
Pl+Pb+Q SPS Primary+Secondary (Inner) Load Case 3
100 407 Plot Reference:
MPa MPa 4) Pl+Pb+Q < SPS (OPE,Inside) Case 3
24%
Branch away from Junction
Pl+Pb+Q SPS Primary+Secondary (Outer) Load Case 3
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182 336 Plot Reference:
MPa MPa 5) Pl+Pb+Q < SPS (OPE,Outside) Case 3
54%
Table of Contents
Highest Fatigue Stress Ratios
Header Next to Nozzle Weld
Pl+Pb+Q+F Damage Ratio Primary+Secondary+Peak (Outer) Load Case 3
193 0.007 Life Stress Concentration Factor = 1.350
MPa 0.400 Stress Strain Concentration Factor = 1.000
Cycles Allowed for this Stress = 1,026,306.
Allowable "B31" Fatigue Stress Allowable = 339.2
482.0 Markl Fatigue Stress Allowable = 329.8
MPa WRC 474 Mean Cycles to Failure = 335,511.
WRC 474 99% Probability Cycles = 77,942.
40% WRC 474 95% Probability Cycles = 108,213.
BS5500 Allowed Cycles(Curve F) = 33,329.
Membrane-to-Bending Ratio = 0.561
Bending-to-PL+PB+Q Ratio = 0.640Plot Reference:
7) Pl+Pb+Q+F < Sa (EXP,Outside) Case 3
Branch Next to Header Weld
Pl+Pb+Q+F Damage Ratio Primary+Secondary+Peak (Outer) Load Case 3
218 0.016 Life Stress Concentration Factor = 1.350
MPa 0.452 Stress Strain Concentration Factor = 1.000
Cycles Allowed for this Stress = 446,366.
Allowable "B31" Fatigue Stress Allowable = 279.9
482.0 Markl Fatigue Stress Allowable = 329.8
MPa WRC 474 Mean Cycles to Failure = 302,511.
WRC 474 99% Probability Cycles = 70,276.
45% WRC 474 95% Probability Cycles = 97,570.
BS5500 Allowed Cycles(Curve F) = 15,731.
Membrane-to-Bending Ratio = 0.920
Bending-to-PL+PB+Q Ratio = 0.521
Plot Reference:
7) Pl+Pb+Q+F < Sa (EXP,Outside) Case 3
Branch Transition
Pl+Pb+Q+F Damage Ratio Primary+Secondary+Peak (Outer) Load Case 3
172 0.005 Life Stress Concentration Factor = 1.350
MPa 0.356 Stress Strain Concentration Factor = 1.000
Cycles Allowed for this Stress = 1,503,594.
Allowable "B31" Fatigue Stress Allowable = 279.9
482.0 Markl Fatigue Stress Allowable = 329.8
MPa WRC 474 Mean Cycles to Failure = 609,573.
WRC 474 99% Probability Cycles = 141,609.
35% WRC 474 95% Probability Cycles = 196,607.
BS5500 Allowed Cycles(Curve F) = 47,359.
Membrane-to-Bending Ratio = 2.060Bending-to-PL+PB+Q Ratio = 0.327
Plot Reference:
7) Pl+Pb+Q+F < Sa (EXP,Outside) Case 3
Header away from Junction
Pl+Pb+Q+F Damage Ratio Primary+Secondary+Peak (Inner) Load Case 3
50 0.000 Life Stress Concentration Factor = 1.000
MPa 0.103 Stress Strain Concentration Factor = 1.000
Cycles Allowed for this Stress = 1.0000E11
Allowable "B31" Fatigue Stress Allowable = 339.2
482.0 Markl Fatigue Stress Allowable = 329.8
MPa WRC 474 Mean Cycles to Failure = 9,028,427.
WRC 474 99% Probability Cycles = 2,097,386.
10% WRC 474 95% Probability Cycles = 2,911,956.
BS5500 Allowed Cycles(Curve F) = 783,499.
Membrane-to-Bending Ratio = 0.349
Bending-to-PL+PB+Q Ratio = 0.741
Plot Reference:
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6) Pl+Pb+Q+F < Sa (EXP,Inside) Case 3
Branch away from Junction
Pl+Pb+Q+F Damage Ratio Primary+Secondary+Peak (Outer) Load Case 3
91 0.000 Life Stress Concentration Factor = 1.000
MPa 0.189 Stress Strain Concentration Factor = 1.000
Cycles Allowed for this Stress = 1.0000E11
Allowable "B31" Fatigue Stress Allowable = 279.9
482.0 Markl Fatigue Stress Allowable = 329.8
MPa WRC 474 Mean Cycles to Failure = 1,680,991.
WRC 474 99% Probability Cycles = 390,510.
18% WRC 474 95% Probability Cycles = 542,173.
BS5500 Allowed Cycles(Curve F) = 128,176.
Membrane-to-Bending Ratio = 15.094
Bending-to-PL+PB+Q Ratio = 0.062
Plot Reference:
7) Pl+Pb+Q+F < Sa (EXP,Outside) Case 3
Table of Contents
Stress Intensification Factors
Branch/Nozzle Sif Summary
Peak Primary Secondary
Axial : 2.772 1.656 4.107
Inplane : 1.048 0.911 1.553
Outplane: 1.480 0.921 2.192
Torsion : 0.764 0.919 1.131
Pressure: 0.799 0.980 1.184
The above stress intensification factors are to be used
in a beam-type analysis of the piping system. Inplane,
Outplane and Torsional sif's should be used with the
matching branch pipe whose diameter and thickness is given
below. The axial sif should be used to intensify the
axial stress in the branch pipe calculated by F/A. The
pressure sif should be used to intensify the nominal
pressure stress in the PARENT or HEADER, calculated
from PD/2T.
Pipe OD : 33.500 mm.
Pipe Thk: 3.380 mm.
Z approx: 2408.331 cu.mm.
Z exact : 2192.609 cu.mm.
B31.3 Branch Pressure i-factor = 2.611
Header Pressure i-factor = 1.598
The B31.3 pressure i-factors should be used with with
F/A, where F is the axial force due to pressure, and
A is the area of the pipe wall. This is equivalent to
finding the pressure stress from (ip)(PD/4T).
B31.3
Peak Stress Sif .... 0.000 Axial1.760 Inplane
2.141 Outplane
1.000 Torsional
B31.1
Peak Stress Sif .... 0.000 Axial
1.928 Inplane
1.928 Outplane
1.928 Torsional
WRC 330
Peak Stress Sif .... 0.000 Axial
1.314 Inplane
1.500 Outplane
1.000 Torsional
Table of Contents
Allowable Loads
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SECONDARY Maximum Conservative Realistic
Load Type (Range): Individual Simultaneous Simultaneous
Occuring Occuring Occuring
Axial Force ( N ) 26161. 8332. 12498.
Inplane Moment (mm. N ) 474306. 106818. 226594.
Outplane Moment (mm. N ) 336002. 75670. 160521.
Torsional Moment (mm. N ) 651026. 207347. 311020.
Pressure (MPa ) 42.47 2.80 2.80
PRIMARY Maximum Conservative Realistic
Load Type: Individual Simultaneous Simultaneous
Occuring Occuring Occuring
Axial Force ( N ) 31517. 9772. 14659.
Inplane Moment (mm. N ) 392661. 85818. 182047.
Outplane Moment (mm. N ) 388545. 84939. 180183.
Torsional Moment (mm. N ) 389298. 120709. 181064.
Pressure (MPa ) 25.22 2.80 2.80
NOTES:
1) Maximum Individual Occuring Loads are the maximum
allowed values of the respective loads if all other
load components are zero, i.e. the listed axial force
may be applied if the inplane, outplane and torsionalmoments, and the pressure are zero.
2) The Conservative Allowable Simultaneous loads are
the maximum loads that can be applied simultaneously.
A conservative stress combination equation is used
that typically produces stresses within 50-70% of the
allowable stress.
3) The Realistic Allowable Simultaneous loads are the
maximum loads that can be applied simultaneously. A
more realistic stress combination equation is used
based on experience at Paulin Research. Stresses are
typically produced within 80-105% of the allowable.
4) Secondary allowable loads are limits for expansion
and operating piping loads.
5) Primary allowable loads are limits for weight,
primary and sustained type piping loads.
Table of Contents
Flexibilities
The following stiffnesses should be used in a piping,
"beam-type" analysis of the intersection. The stiff-
nesses should be inserted at the surface of the
branch/header or nozzle/vessel junction. The general
characteristics used for the branch pipe should be:
Outside Diameter = 33.500 mm.
Wall Thickness = 3.380 mm.
Axial Translational Stiffness = 252619. N /mm.
Inplane Rotational Stiffness = 3489170. mm. N /deg
Outplane Rotational Stiffness = 1513391. mm. N /deg
Torsional Rotational Stiffness = 15530895. mm. N /deg
Intersection Flexibility Factors for
Branch/Nozzle :
Find axial stiffness: K = 3EI/(kd)^3 N /mm.
Find bending and torsional stiffnesses: K = EI/(kd) mm. N per radian.
The EI product is 0.71616E+10 N mm.^2
The value of (d) to use is: 30.120 mm..
The resulting bending stiffness is in units of force x length per radian.
Axial Flexibility Factor (k) = 1.460
Inplane Flexibility Factor (k) = 1.189
Outplane Flexibility Factor (k) = 2.742
Torsional Flexibility Factor (k) = 0.267
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Model Notes
Input Echo:
Model Type : Cylindrical Shell
Parent Outside Diameter : 114.300 mm.
Thickness : 6.020 mm.
Fillet Along Shell : 5.000 mm.
Parent Properties:
Material DB # 1085918.
(See Output Reports for Allowables.)
Elastic Modulus (Amb) : 195100.0 MPa
Poissons Ratio : 0.300
Expansion Coefficient : 0.1740E-04 mm./mm./deg.
Weight Density : 0.0000E+00 N /cu.mm.(NOT USED)
Nozzle Outside Diameter : 60.300 mm.
Thickness : 5.540 mm.
Length : 150.000 mm.
Nozzle Weld Length : 5.000 mm.
Nozzle Tilt Angle : 0.000 deg.
Distance from Top : 0.000 mm.
Distance from Bottom : 500.000 mm.
Nozzle PropertiesMaterial DB # 1068318.
(See Output Reports for Allowables.)
Elastic Modulus (Amb) : 195100.0 MPa
Poissons Ratio : 0.300
Expansion Coefficient : 0.1740E-04 mm./mm./deg.
Weight Density : 0.0000E+00 N /cu.mm. (NOT USED)
Design Operating Cycles : 7000.
Ambient Temperature (Deg.) : 21.10
The following temperatures have been specified for the analysis:
Nozzle Inside Temperature : 250.00 deg.
Nozzle Outside Temperature : 250.00 deg.
Vessel Inside Temperature : 250.00 deg.
Vessel Outside Temperature : 250.00 deg.
Nozzle Pressure : 2.800 MPa
Vessel Pressure : 2.800 MPa
User Defined Load Input Echo:
Loads are given at the Nozzle/Header Junction
Loads are defined in Local Coordinatesc
Forces( N ) Moments (N-m)
Load Case FX FY FZ MX MY MZ
---------------------------------------------------------------------------
OPER: 1700.0 1700.0 1700.0 650.0 650.0 650.0
FEA Model Loads:
These are the actual loads applied to the FEA model.
These are the User Defined Loads translated to the
end of the nozzle and reported in global coordinates.
Forces( N ) Moments (N-m)
Load Case FX FY FZ MX MY MZ
---------------------------------------------------------------------------
OPER: 1700.0 1700.0 1700.0 650.0 905.0 395.0
The "top" or "positive" end of this model is "free" in
the axial and translational directions.
Stresses ARE nodally AVERAGED.
Vessel Centerline Vector : 0.000 1.000 0.000
Nozzle Orientation Vector : 1.000 0.000 0.000
Table of Contents
Load Case Report
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Inner and outer element temperatures are the same
throughout the model. No thermal ratcheting
calculations will be performed.
THE 8 LOAD CASES ANALYZED ARE:
1 SUSTAINED (Pr Only)
Sustained case run to satisfy local primary
membrane and bending stress limits.
/-------- Loads in Case 1
Pressure Case 1
2 Thermal ONLY
Thermal ONLY case run in the event expansion
stresses exceed the secondary stress allowable.
/-------- Loads in Case 2
Temperature Case 1
3 OPERATING (Fatigue Calc Performed)
Case run to compute the operating stresses used in
secondary, peak and range calculations as needed.
/-------- Loads in Case 3
Pressure Case 1
Temperature Case 1
Loads from (Operating)
4 Program Generated -- Force Only
Case run to compute sif's and flexibilities.
/-------- Loads in Case 4
Loads from (Axial)
5 Program Generated -- Force Only
Case run to compute sif's and flexibilities.
/-------- Loads in Case 5
Loads from (Inplane)
6 Program Generated -- Force Only
Case run to compute sif's and flexibilities.
/-------- Loads in Case 6
Loads from (Outplane)
7 Program Generated -- Force Only
Case run to compute sif's and flexibilities.
/-------- Loads in Case 7
Loads from (Torsion)
8 Program Generated -- Force Only
Case run to compute sif's and flexibilities.
/-------- Loads in Case 8
Pressure Case 1
Table of Contents
Solution Data
Maximum Solution Row Size = 1296
Number of Nodes = 3076
Number of Elements = 1012
Number of Solution Cases = 8
Summation of Loads per Case
Case # FX FY FZ
1 -1294. 25806. 0.
2 0. 0. 0.
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3 406. 27507. 1700.
4 1090827. 0. 0.
5 0. 0. 0.
6 0. 0. 0.
7 0. 0. 0.
8 -1294. 25806. 0.
Table of Contents
ASME Code Stress Output Plots
1) Pl < (1.5)(S) (SUS,Membrane) Case 1
2) Qb < SPS (SUS,Bending) Case 1
3) S1+S2+S3 < 4S (SUS,S1+S2+S3) Case 1
4) Pl+Pb+Q < SPS (OPE,Inside) Case 3
5) Pl+Pb+Q < SPS (OPE,Outside) Case 3
6) Pl+Pb+Q+F < Sa (EXP,Inside) Case 3
7) Pl+Pb+Q+F < Sa (EXP,Outside) Case 3
8) Membrane < User (OPE,Membrane) Case 3
9) Bending < User (OPE,Bending) Case 3
10) Pl+Pb+Q+F < Sa (SIF,Outside) Case 4
11) Pl+Pb+Q+F < Sa (SIF,Outside) Case 5
12) Pl+Pb+Q+F < Sa (SIF,Outside) Case 6
13) Pl+Pb+Q+F < Sa (SIF,Outside) Case 7
14) Pl+Pb+Q+F < Sa (SIF,Outside) Case 8
Table of Contents
Region Data
Header Next to Nozzle Weld
Cold Allowable ........... 138. MPa
Hot Allowable @ 250 deg .. 122. MPa
Case 1
Nominal Stress (M/Z) ... 0. MPa
Pressure Stress (Pd/2t) .. 27. MPa
Case 3
Nominal Stress (M/Z) ... 134. MPa
Pressure Stress (Pd/2t) .. 27. MPa
Case 4
Nominal Stress (M/Z) ... 1145. MPaPressure Stress (Pd/2t) .. 0. MPa
Case 5
Nominal Stress (M/Z) ... 91. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 6
Nominal Stress (M/Z) ... 91. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 7
Nominal Stress (M/Z) ... 91. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 8
Nominal Stress (M/Z) ... 27. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Smallest Thickness ....... 5.540 mm.
Stress Concentration ..... 1.350
Branch Next to Header Weld
Cold Allowable ........... 138. MPa
Hot Allowable @ 250 deg .. 126. MPa
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Case 1
Nominal Stress (M/Z) ... 0. MPa
Pressure Stress (Pd/2t) .. 27. MPa
Case 3
Nominal Stress (M/Z) ... 134. MPa
Pressure Stress (Pd/2t) .. 27. MPa
Case 4
Nominal Stress (M/Z) ... 1145. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 5
Nominal Stress (M/Z) ... 91. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 6
Nominal Stress (M/Z) ... 91. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 7
Nominal Stress (M/Z) ... 91. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 8
Nominal Stress (M/Z) ... 27. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Smallest Thickness ....... 5.540 mm.
Stress Concentration ..... 1.350
Branch Transition
Cold Allowable ........... 138. MPaHot Allowable @ 250 deg .. 126. MPa
Case 1
Nominal Stress (M/Z) ... 0. MPa
Pressure Stress (Pd/2t) .. 27. MPa
Case 3
Nominal Stress (M/Z) ... 134. MPa
Pressure Stress (Pd/2t) .. 27. MPa
Case 4
Nominal Stress (M/Z) ... 1145. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 5
Nominal Stress (M/Z) ... 91. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 6
Nominal Stress (M/Z) ... 91. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 7
Nominal Stress (M/Z) ... 91. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 8
Nominal Stress (M/Z) ... 27. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Smallest Thickness ....... 5.540 mm.
Stress Concentration ..... 1.350
Header away from Junction
Cold Allowable ........... 138. MPa
Hot Allowable @ 250 deg .. 122. MPa
Case 1
Nominal Stress (M/Z) ... 0. MPa
Pressure Stress (Pd/2t) .. 27. MPa
Case 3
Nominal Stress (M/Z) ... 134. MPa
Pressure Stress (Pd/2t) .. 27. MPaCase 4
Nominal Stress (M/Z) ... 1145. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 5
Nominal Stress (M/Z) ... 91. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 6
Nominal Stress (M/Z) ... 91. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 7
Nominal Stress (M/Z) ... 91. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 8
Nominal Stress (M/Z) ... 27. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Smallest Thickness ....... 5.540 mm.
Stress Concentration ..... 1.000
Branch away from Junction
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Cold Allowable ........... 138. MPa
Hot Allowable @ 250 deg .. 126. MPa
Case 1
Nominal Stress (M/Z) ... 0. MPa
Pressure Stress (Pd/2t) .. 27. MPa
Case 3
Nominal Stress (M/Z) ... 134. MPa
Pressure Stress (Pd/2t) .. 27. MPa
Case 4
Nominal Stress (M/Z) ... 1145. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 5
Nominal Stress (M/Z) ... 91. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 6
Nominal Stress (M/Z) ... 91. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 7
Nominal Stress (M/Z) ... 91. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 8
Nominal Stress (M/Z) ... 27. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Smallest Thickness ....... 5.540 mm.
Stress Concentration ..... 1.000
Table of Contents
Stress Results - Notes
- Results in this analysis were generated using the finite
element solution method.
- Using post 07 ASME Section VIII Division 2
- Use Polished Bar fatigue curve.
- Ratio between Operating and Design Pressure = 0.9000000
Assume pressure increases all other stresses.
Use operating pressure for occasional load cases.
- Assume free end displacements of attached pipe are
secondary loads within limits of nozzle reinforcement.
- Use Equivalent Stress (Von Mises).
- S1+S2+S3 evaluation omitted from operating stress.
Include S1+S2+S3 evaluation in primary case evaluation.
Assume bending stress not local primary for S1+S2+S3.
Table of Contents
ASME Overstressed Areas
*** NO OVERSTRESSED NODES IN THIS MODEL ***
Table of Contents
Highest Primary Stress Ratios
Header Next to Nozzle Weld
Pl (1.5)(S) Primary Membrane Load Case 1
31 182 Plot Reference:
MPa MPa 1) Pl < (1.5)(S) (SUS,Membrane) Case 1
17%
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Branch Next to Header Weld
Pl (1.5)(S) Primary Membrane Load Case 1
20 189 Plot Reference:
MPa MPa 1) Pl < (1.5)(S) (SUS,Membrane) Case 1
10%
Branch Transition
Pl (1.5)(S) Primary Membrane Load Case 1
14 189 Plot Reference:
MPa MPa 1) Pl < (1.5)(S) (SUS,Membrane) Case 1
7%
Header away from Junction
Pl (1.5)(S) Primary Membrane Load Case 1
24 182 Plot Reference:
MPa MPa 1) Pl < (1.5)(S) (SUS,Membrane) Case 1
13%
Branch away from Junction
Pl (1.5)(S) Primary Membrane Load Case 1
14 189 Plot Reference:
MPa MPa 1) Pl < (1.5)(S) (SUS,Membrane) Case 1
7%
Table of Contents
Highest Secondary Stress Ratios
Header Next to Nozzle Weld
Pl+Pb+Q SPS Primary+Secondary (Outer) Load Case 3
313 389 Plot Reference:
MPa MPa 5) Pl+Pb+Q < SPS (OPE,Outside) Case 3
80%
Branch Next to Header Weld
Pl+Pb+Q SPS Primary+Secondary (Outer) Load Case 3
258 395 Plot Reference:
MPa MPa 5) Pl+Pb+Q < SPS (OPE,Outside) Case 3
65%
Branch Transition
Pl+Pb+Q SPS Primary+Secondary (Outer) Load Case 3
115 395 Plot Reference:
MPa MPa 5) Pl+Pb+Q < SPS (OPE,Outside) Case 3
29%
Header away from Junction
Pl+Pb+Q SPS Primary+Secondary (Inner) Load Case 3
107 389 Plot Reference:
MPa MPa 4) Pl+Pb+Q < SPS (OPE,Inside) Case 3
27%
Branch away from Junction
Pl+Pb+Q SPS Primary+Secondary (Inner) Load Case 3
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94 395 Plot Reference:
MPa MPa 4) Pl+Pb+Q < SPS (OPE,Inside) Case 3
23%
Table of Contents
Highest Fatigue Stress Ratios
Header Next to Nozzle Weld
Pl+Pb+Q+F Damage Ratio Primary+Secondary+Peak (Outer) Load Case 3
211 0.013 Life Stress Concentration Factor = 1.350
MPa 0.438 Stress Strain Concentration Factor = 1.000
Cycles Allowed for this Stress = 542,806.
Allowable "B31" Fatigue Stress Allowable = 324.4
482.0 Markl Fatigue Stress Allowable = 329.8
MPa WRC 474 Mean Cycles to Failure = 237,731.
WRC 474 99% Probability Cycles = 55,227.
43% WRC 474 95% Probability Cycles = 76,676.
BS5500 Allowed Cycles(Curve F) = 25,335.
Membrane-to-Bending Ratio = 0.544
Bending-to-PL+PB+Q Ratio = 0.648Plot Reference:
7) Pl+Pb+Q+F < Sa (EXP,Outside) Case 3
Branch Next to Header Weld
Pl+Pb+Q+F Damage Ratio Primary+Secondary+Peak (Outer) Load Case 3
174 0.005 Life Stress Concentration Factor = 1.350
MPa 0.361 Stress Strain Concentration Factor = 1.000
Cycles Allowed for this Stress = 1,433,146.
Allowable "B31" Fatigue Stress Allowable = 329.5
482.0 Markl Fatigue Stress Allowable = 329.8
MPa WRC 474 Mean Cycles to Failure = 446,978.
WRC 474 99% Probability Cycles = 103,837.
36% WRC 474 95% Probability Cycles = 144,165.
BS5500 Allowed Cycles(Curve F) = 45,313.
Membrane-to-Bending Ratio = 0.674
Bending-to-PL+PB+Q Ratio = 0.597
Plot Reference:
7) Pl+Pb+Q+F < Sa (EXP,Outside) Case 3
Branch Transition
Pl+Pb+Q+F Damage Ratio Primary+Secondary+Peak (Outer) Load Case 3
78 0.000 Life Stress Concentration Factor = 1.350
MPa 0.161 Stress Strain Concentration Factor = 1.000
Cycles Allowed for this Stress = 1.0000E11
Allowable "B31" Fatigue Stress Allowable = 329.5
482.0 Markl Fatigue Stress Allowable = 329.8
MPa WRC 474 Mean Cycles to Failure = 5,160,248.
WRC 474 99% Probability Cycles = 1,198,772.
16% WRC 474 95% Probability Cycles = 1,664,344.
BS5500 Allowed Cycles(Curve F) = 510,190.
Membrane-to-Bending Ratio = 1.897Bending-to-PL+PB+Q Ratio = 0.345
Plot Reference:
7) Pl+Pb+Q+F < Sa (EXP,Outside) Case 3
Header away from Junction
Pl+Pb+Q+F Damage Ratio Primary+Secondary+Peak (Inner) Load Case 3
53 0.000 Life Stress Concentration Factor = 1.000
MPa 0.111 Stress Strain Concentration Factor = 1.000
Cycles Allowed for this Stress = 1.0000E11
Allowable "B31" Fatigue Stress Allowable = 324.4
482.0 Markl Fatigue Stress Allowable = 329.8
MPa WRC 474 Mean Cycles to Failure = 6,838,555.
WRC 474 99% Probability Cycles = 1,588,658.
11% WRC 474 95% Probability Cycles = 2,205,652.
BS5500 Allowed Cycles(Curve F) = 640,861.
Membrane-to-Bending Ratio = 0.362
Bending-to-PL+PB+Q Ratio = 0.734
Plot Reference:
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6) Pl+Pb+Q+F < Sa (EXP,Inside) Case 3
Branch away from Junction
Pl+Pb+Q+F Damage Ratio Primary+Secondary+Peak (Inner) Load Case 3
47 0.000 Life Stress Concentration Factor = 1.000
MPa 0.098 Stress Strain Concentration Factor = 1.000
Cycles Allowed for this Stress = 1.0000E11
Allowable "B31" Fatigue Stress Allowable = 329.5
482.0 Markl Fatigue Stress Allowable = 329.8
MPa WRC 474 Mean Cycles to Failure = 9,393,385.
WRC 474 99% Probability Cycles = 2,182,169.
9% WRC 474 95% Probability Cycles = 3,029,666.
BS5500 Allowed Cycles(Curve F) = 929,255.
Membrane-to-Bending Ratio = 14.331
Bending-to-PL+PB+Q Ratio = 0.065
Plot Reference:
6) Pl+Pb+Q+F < Sa (EXP,Inside) Case 3
Table of Contents
Stress Intensification Factors
Branch/Nozzle Sif Summary
Peak Primary Secondary
Axial : 4.530 2.243 6.711
Inplane : 1.383 1.316 2.049
Outplane: 3.047 1.370 4.513
Torsion : 0.901 0.982 1.334
Pressure: 0.951 1.171 1.409
The above stress intensification factors are to be used
in a beam-type analysis of the piping system. Inplane,
Outplane and Torsional sif's should be used with the
matching branch pipe whose diameter and thickness is given
below. The axial sif should be used to intensify the
axial stress in the branch pipe calculated by F/A. The
pressure sif should be used to intensify the nominal
pressure stress in the PARENT or HEADER, calculated
from PD/2T.
Pipe OD : 60.300 mm.
Pipe Thk: 5.540 mm.
Z approx: 13047.465 cu.mm.
Z exact : 11970.017 cu.mm.
B31.3 Branch Pressure i-factor = 3.318
Header Pressure i-factor = 1.902
The B31.3 pressure i-factors should be used with with
F/A, where F is the axial force due to pressure, and
A is the area of the pipe wall. This is equivalent to
finding the pressure stress from (ip)(PD/4T).
B31.3
Peak Stress Sif .... 0.000 Axial2.916 Inplane
3.582 Outplane
1.000 Torsional
B31.1
Peak Stress Sif .... 0.000 Axial
3.582 Inplane
3.582 Outplane
3.582 Torsional
WRC 330
Peak Stress Sif .... 0.000 Axial
2.309 Inplane
2.602 Outplane
1.316 Torsional
Table of Contents
Allowable Loads
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SECONDARY Maximum Conservative Realistic
Load Type (Range): Individual Simultaneous Simultaneous
Occuring Occuring Occuring
Axial Force ( N ) 56160. 17639. 26459.
Inplane Moment (mm. N ) 2310468. 508404. 1078488.
Outplane Moment (mm. N ) 1032534. 224472. 476178.
Torsional Moment (mm. N ) 3547619. 1114283. 1671424.
Pressure (MPa ) 29.11 2.80 2.80
PRIMARY Maximum Conservative Realistic
Load Type: Individual Simultaneous Simultaneous
Occuring Occuring Occuring
Axial Force ( N ) 80128. 23038. 34557.
Inplane Moment (mm. N ) 1659555. 324434. 688228.
Outplane Moment (mm. N ) 1647272. 346564. 735173.
Torsional Moment (mm. N ) 2259663. 624731. 937096.
Pressure (MPa ) 16.41 2.80 2.80
NOTES:
1) Maximum Individual Occuring Loads are the maximum
allowed values of the respective loads if all other
load components are zero, i.e. the listed axial force
may be applied if the inplane, outplane and torsionalmoments, and the pressure are zero.
2) The Conservative Allowable Simultaneous loads are
the maximum loads that can be applied simultaneously.
A conservative stress combination equation is used
that typically produces stresses within 50-70% of the
allowable stress.
3) The Realistic Allowable Simultaneous loads are the
maximum loads that can be applied simultaneously. A
more realistic stress combination equation is used
based on experience at Paulin Research. Stresses are
typically produced within 80-105% of the allowable.
4) Secondary allowable loads are limits for expansion
and operating piping loads.
5) Primary allowable loads are limits for weight,
primary and sustained type piping loads.
Table of Contents
Flexibilities
The following stiffnesses should be used in a piping,
"beam-type" analysis of the intersection. The stiff-
nesses should be inserted at the surface of the
branch/header or nozzle/vessel junction. The general
characteristics used for the branch pipe should be:
Outside Diameter = 60.300 mm.
Wall Thickness = 5.540 mm.
Axial Translational Stiffness = 332999. N /mm.
Inplane Rotational Stiffness = 9792365. mm. N /deg
Outplane Rotational Stiffness = 3616443. mm. N /deg
Torsional Rotational Stiffness = 30174178. mm. N /deg
Intersection Flexibility Factors for
Branch/Nozzle :
Find axial stiffness: K = 3EI/(kd)^3 N /mm.
Find bending and torsional stiffnesses: K = EI/(kd) mm. N per radian.
The EI product is 0.70375E+11 N mm.^2
The value of (d) to use is: 54.760 mm..
The resulting bending stiffness is in units of force x length per radian.
Axial Flexibility Factor (k) = 1.569
Inplane Flexibility Factor (k) = 2.291
Outplane Flexibility Factor (k) = 6.202
Torsional Flexibility Factor (k) = 0.743
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Model Notes
Input Echo:
Model Type : Cylindrical Shell
Parent Outside Diameter : 168.300 mm.
Thickness : 7.110 mm.
Fillet Along Shell : 5.000 mm.
Parent Properties:
Material DB # 1064818.
(See Output Reports for Allowables.)
Elastic Modulus (Amb) : 195100.0 MPa
Poissons Ratio : 0.300
Expansion Coefficient : 0.1730E-04 mm./mm./deg.
Weight Density : 0.0000E+00 N /cu.mm.(NOT USED)
Nozzle Outside Diameter : 88.900 mm.
Thickness : 5.490 mm.
Length : 150.000 mm.
Nozzle Weld Length : 5.000 mm.
Nozzle Tilt Angle : 0.000 deg.
Distance from Top : 0.000 mm.
Distance from Bottom : 500.000 mm.
Nozzle PropertiesMaterial DB # 1064818.
(See Output Reports for Allowables.)
Elastic Modulus (Amb) : 195100.0 MPa
Poissons Ratio : 0.300
Expansion Coefficient : 0.1730E-04 mm./mm./deg.
Weight Density : 0.0000E+00 N /cu.mm. (NOT USED)
Design Operating Cycles : 7000.
Ambient Temperature (Deg.) : 21.10
The following temperatures have been specified for the analysis:
Nozzle Inside Temperature : 235.00 deg.
Nozzle Outside Temperature : 235.00 deg.
Vessel Inside Temperature : 235.00 deg.
Vessel Outside Temperature : 235.00 deg.
Nozzle Pressure : 2.800 MPa
Vessel Pressure : 2.800 MPa
User Defined Load Input Echo:
Loads are given at the Nozzle/Header Junction
Loads are defined in Local Coordinatesc
Forces( N ) Moments (N-m)
Load Case FX FY FZ MX MY MZ
---------------------------------------------------------------------------
OPER: 2700.0 2700.0 2700.0 1000.0 1000.0 1000.0
FEA Model Loads:
These are the actual loads applied to the FEA model.
These are the User Defined Loads translated to the
end of the nozzle and reported in global coordinates.
Forces( N ) Moments (N-m)
Load Case FX FY FZ MX MY MZ
---------------------------------------------------------------------------
OPER: 2700.0 2700.0 2700.0 1000.0 1405.0 595.0
The "top" or "positive" end of this model is "free" in
the axial and translational directions.
Stresses ARE nodally AVERAGED.
Vessel Centerline Vector : 0.000 1.000 0.000
Nozzle Orientation Vector : 1.000 0.000 0.000
Table of Contents
Load Case Report
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Inner and outer element temperatures are the same
throughout the model. No thermal ratcheting
calculations will be performed.
THE 8 LOAD CASES ANALYZED ARE:
1 SUSTAINED (Pr Only)
Sustained case run to satisfy local primary
membrane and bending stress limits.
/-------- Loads in Case 1
Pressure Case 1
2 Thermal ONLY
Thermal ONLY case run in the event expansion
stresses exceed the secondary stress allowable.
/-------- Loads in Case 2
Temperature Case 1
3 OPERATING (Fatigue Calc Performed)
Case run to compute the operating stresses used in
secondary, peak and range calculations as needed.
/-------- Loads in Case 3
Pressure Case 1
Temperature Case 1
Loads from (Operating)
4 Program Generated -- Force Only
Case run to compute sif's and flexibilities.
/-------- Loads in Case 4
Loads from (Axial)
5 Program Generated -- Force Only
Case run to compute sif's and flexibilities.
/-------- Loads in Case 5
Loads from (Inplane)
6 Program Generated -- Force Only
Case run to compute sif's and flexibilities.
/-------- Loads in Case 6
Loads from (Outplane)
7 Program Generated -- Force Only
Case run to compute sif's and flexibilities.
/-------- Loads in Case 7
Loads from (Torsion)
8 Program Generated -- Force Only
Case run to compute sif's and flexibilities.
/-------- Loads in Case 8
Pressure Case 1
Table of Contents
Solution Data
Maximum Solution Row Size = 1164
Number of Nodes = 2764
Number of Elements = 908
Number of Solution Cases = 8
Summation of Loads per Case
Case # FX FY FZ
1 -2027. 57168. 0.
2 0. 0. 0.
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3 673. 59868. 2700.
4 2349565. 0. 0.
5 0. 0. 0.
6 0. 0. 0.
7 0. 0. 0.
8 -2027. 57168. 0.
Table of Contents
ASME Code Stress Output Plots
1) Pl < (1.5)(S) (SUS,Membrane) Case 1
2) Qb < SPS (SUS,Bending) Case 1
3) S1+S2+S3 < 4S (SUS,S1+S2+S3) Case 1
4) Pl+Pb+Q < SPS (OPE,Inside) Case 3
5) Pl+Pb+Q < SPS (OPE,Outside) Case 3
6) Pl+Pb+Q+F < Sa (EXP,Inside) Case 3
7) Pl+Pb+Q+F < Sa (EXP,Outside) Case 3
8) Membrane < User (OPE,Membrane) Case 3
9) Bending < User (OPE,Bending) Case 3
10) Pl+Pb+Q+F < Sa (SIF,Outside) Case 4
11) Pl+Pb+Q+F < Sa (SIF,Outside) Case 5
12) Pl+Pb+Q+F < Sa (SIF,Outside) Case 6
13) Pl+Pb+Q+F < Sa (SIF,Outside) Case 7
14) Pl+Pb+Q+F < Sa (SIF,Outside) Case 8
Table of Contents
Region Data
Header Next to Nozzle Weld
Cold Allowable ........... 115. MPa
Hot Allowable @ 235 deg .. 105. MPa
Case 1
Nominal Stress (M/Z) ... 0. MPa
Pressure Stress (Pd/2t) .. 33. MPa
Case 3
Nominal Stress (M/Z) ... 91. MPa
Pressure Stress (Pd/2t) .. 33. MPa
Case 4
Nominal Stress (M/Z) ... 1633. MPaPressure Stress (Pd/2t) .. 0. MPa
Case 5
Nominal Stress (M/Z) ... 83. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 6
Nominal Stress (M/Z) ... 83. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 7
Nominal Stress (M/Z) ... 83. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 8
Nominal Stress (M/Z) ... 33. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Smallest Thickness ....... 5.490 mm.
Stress Concentration ..... 1.350
Branch Next to Header Weld
Cold Allowable ........... 115. MPa
Hot Allowable @ 235 deg .. 105. MPa
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Case 1
Nominal Stress (M/Z) ... 0. MPa
Pressure Stress (Pd/2t) .. 33. MPa
Case 3
Nominal Stress (M/Z) ... 91. MPa
Pressure Stress (Pd/2t) .. 33. MPa
Case 4
Nominal Stress (M/Z) ... 1633. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 5
Nominal Stress (M/Z) ... 83. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 6
Nominal Stress (M/Z) ... 83. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 7
Nominal Stress (M/Z) ... 83. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 8
Nominal Stress (M/Z) ... 33. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Smallest Thickness ....... 5.490 mm.
Stress Concentration ..... 1.350
Branch Transition
Cold Allowable ........... 115. MPaHot Allowable @ 235 deg .. 105. MPa
Case 1
Nominal Stress (M/Z) ... 0. MPa
Pressure Stress (Pd/2t) .. 33. MPa
Case 3
Nominal Stress (M/Z) ... 91. MPa
Pressure Stress (Pd/2t) .. 33. MPa
Case 4
Nominal Stress (M/Z) ... 1633. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 5
Nominal Stress (M/Z) ... 83. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 6
Nominal Stress (M/Z) ... 83. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 7
Nominal Stress (M/Z) ... 83. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 8
Nominal Stress (M/Z) ... 33. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Smallest Thickness ....... 5.490 mm.
Stress Concentration ..... 1.350
Header away from Junction
Cold Allowable ........... 115. MPa
Hot Allowable @ 235 deg .. 105. MPa
Case 1
Nominal Stress (M/Z) ... 0. MPa
Pressure Stress (Pd/2t) .. 33. MPa
Case 3
Nominal Stress (M/Z) ... 91. MPa
Pressure Stress (Pd/2t) .. 33. MPaCase 4
Nominal Stress (M/Z) ... 1633. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 5
Nominal Stress (M/Z) ... 83. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 6
Nominal Stress (M/Z) ... 83. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 7
Nominal Stress (M/Z) ... 83. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 8
Nominal Stress (M/Z) ... 33. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Smallest Thickness ....... 5.490 mm.
Stress Concentration ..... 1.000
Branch away from Junction
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Cold Allowable ........... 115. MPa
Hot Allowable @ 235 deg .. 105. MPa
Case 1
Nominal Stress (M/Z) ... 0. MPa
Pressure Stress (Pd/2t) .. 33. MPa
Case 3
Nominal Stress (M/Z) ... 91. MPa
Pressure Stress (Pd/2t) .. 33. MPa
Case 4
Nominal Stress (M/Z) ... 1633. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 5
Nominal Stress (M/Z) ... 83. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 6
Nominal Stress (M/Z) ... 83. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 7
Nominal Stress (M/Z) ... 83. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Case 8
Nominal Stress (M/Z) ... 33. MPa
Pressure Stress (Pd/2t) .. 0. MPa
Smallest Thickness ....... 5.490 mm.
Stress Concentration ..... 1.000
Table of Contents
Stress Results - Notes
- Results in this analysis were generated using the finite
element solution method.
- Using post 07 ASME Section VIII Division 2
- Use Polished Bar fatigue curve.
- Ratio between Operating and Design Pressure = 0.9000000
Assume pressure increases all other stresses.
Use operating pressure for occasional load cases.
- Assume free end displacements of attached pipe are
secondary loads within limits of nozzle reinforcement.
- Use Equivalent Stress (Von Mises).
- S1+S2+S3 evaluation omitted from operating stress.
Include S1+S2+S3 evaluation in primary case evaluation.
Assume bending stress not local primary for S1+S2+S3.
Table of Contents
ASME Overstressed Areas
*** NO OVERSTRESSED NODES IN THIS MODEL ***
Table of Contents
Highest Primary Stress Ratios
Header Next to Nozzle Weld
Pl (1.5)(S) Primary Membrane Load Case 1
47 157 Plot Reference:
MPa MPa 1) Pl < (1.5)(S) (SUS,Membrane) Case 1
29%
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Branch Next to Header Weld
Pl (1.5)(S) Primary Membrane Load Case 1
39 157 Plot Reference:
MPa MPa 1) Pl < (1.5)(S) (SUS,Membrane) Case 1
24%
Branch Transition
Pl (1.5)(S) Primary Membrane Load Case 1
22 157 Plot Reference:
MPa MPa 1) Pl < (1.5)(S) (SUS,Membrane) Case 1
13%
Header away from Junction
Pl (1.5)(S) Primary Membrane Load Case 1
33 157 Plot Reference:
MPa MPa 1) Pl < (1.5)(S) (SUS,Membrane) Case 1
20%
Branch away from Junction
Pl (1.5)(S) Primary Membrane Load Case 1
22 157 Plot Reference:
MPa MPa 1) Pl < (1.5)(S) (SUS,Membrane) Case 1
14%
Table of Contents
Highest Secondary Stress Ratios
Header Next to Nozzle Weld
Pl+Pb+Q SPS Primary+Secondary (Outer) Load Case 3
238 330 Plot Reference:
MPa MPa 5) Pl+Pb+Q < SPS (OPE,Outside) Case 3
72%
Branch Next to Header Weld
Pl+Pb+Q SPS Primary+Secondary (Outer) Load Case 3
246 330 Plot Reference:
MPa MPa 5) Pl+Pb+Q < SPS (OPE,Outside) Case 3
74%
Branch Transition
Pl+Pb+Q SPS Primary+Secondary (Outer) Load Case 3
86 330 Plot Reference:
MPa MPa 5) Pl+Pb+Q < SPS (OPE,Outside) Case 3
26%
Header away from Junction
Pl+Pb+Q SPS Primary+Secondary (Outer) Load Case 3
95 330 Plot Reference:
MPa MPa 5) Pl+Pb+Q < SPS (OPE,Outside) Case 3
28%
Branch away from Junction
Pl+Pb+Q SPS Primary+Secondary (Inner) Load Case 3
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79 330 Plot Reference:
MPa MPa 4) Pl+Pb+Q < SPS (OPE,Inside) Case 3
23%
Table of Contents
Highest Fatigue Stress Ratios
Header Next to Nozzle Weld
Pl+Pb+Q+F Damage Ratio Primary+Secondary+Peak (Outer) Load Case 3
160 0.004 Life Stress Concentration Factor = 1.350
MPa 0.333 Stress Strain Concentration Factor = 1.000
Cycles Allowed for this Stress = 1,869,714.
Allowable "B31" Fatigue Stress Allowable = 275.0
482.0 Markl Fatigue Stress Allowable = 329.8
MPa WRC 474 Mean Cycles to Failure = 500,365.
WRC 474 99% Probability Cycles = 116,239.
33% WRC 474 95% Probability Cycles = 161,384.
BS5500 Allowed Cycles(Curve F) = 57,872.
Membrane-to-Bending Ratio = 0.534
Bending-to-PL+PB+Q Ratio = 0.652Plot Reference:
7) Pl+Pb+Q+F < Sa (EXP,Outside) Case 3
Branch Next to Header Weld
Pl+Pb+Q+F Damage Ratio Primary+Secondary+Peak (Outer) Load Case 3
166 0.004 Life Stress Concentration Factor = 1.350
MPa 0.344 Stress Strain Concentration Factor = 1.000
Cycles Allowed for this Stress = 1,683,686.
Allowable "B31" Fatigue Stress Allowable = 275.0
482.0 Markl Fatigue Stress Allowable = 329.8
MPa WRC 474 Mean Cycles to Failure = 538,848.
WRC 474 99% Probability Cycles = 125,179.
34% WRC 474 95% Probability Cycles = 173,796.
BS5500 Allowed Cycles(Curve F) = 52,553.
Membrane-to-Bending Ratio = 0.560
Bending-to-PL+PB+Q Ratio = 0.641
Plot Reference:
7) Pl+Pb+Q+F < Sa (EXP,Outside) Case 3
Branch Transition
Pl+Pb+Q+F Damage Ratio Primary+Secondary+Peak (Outer) Load Case 3
58 0.000 Life Stress Concentration Factor = 1.350
MPa 0.121 Stress Strain Concentration Factor = 1.000
Cycles Allowed for this Stress = 1.0000E11
Allowable "B31" Fatigue Stress Allowable = 275.0
482.0 Markl Fatigue Stress Allowable = 329.8
MPa WRC 474 Mean Cycles to Failure = 13,044,634.
WRC 474 99% Probability Cycles = 3,030,384.
12% WRC 474 95% Probability Cycles = 4,207,306.
BS5500 Allowed Cycles(Curve F) = 1,208,851.
Membrane-to-Bending Ratio = 1.181Bending-to-PL+PB+Q Ratio = 0.459
Plot Reference:
7) Pl+Pb+Q+F < Sa (EXP,Outside) Case 3
Header away from Junction
Pl+Pb+Q+F Damage Ratio Primary+Secondary+Peak (Outer) Load Case 3
48 0.000 Life Stress Concentration Factor = 1.000
MPa 0.099 Stress Strain Concentration Factor = 1.000
Cycles Allowed for this Stress = 1.0000E11
Allowable "B31" Fatigue Stress Allowable = 275.0
482.0 Markl Fatigue Stress Allowable = 329.8
MPa WRC 474 Mean Cycles to Failure = 8,456,431.
WRC 474 99% Probability Cycles = 1,964,506.
9% WRC 474 95% Probability Cycles = 2,727,469.
BS5500 Allowed Cycles(Curve F) = 903,240.
Membrane-to-Bending Ratio = 0.889
Bending-to-PL+PB+Q Ratio = 0.529
Plot Reference:
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7) Pl+Pb+Q+F < Sa (EXP,Outside) Case 3
Branch away from Junction
Pl+Pb+Q+F Damage Ratio Primary+Secondary+Peak (Inner) Load Case 3
39 0.000 Life Stress Concentration Factor = 1.000
MPa 0.082 Stress Strain Concentration Factor = 1.000
Cycles Allowed for this Stress = 1.0000E11
Allowable "B31" Fatigue Stress Allowable = 275.0
482.0 Markl Fatigue Stress Allowable = 329.8
MPa WRC 474 Mean Cycles to Failure = 16,800,968.
WRC 474 99% Probability Cycles = 3,903,014.
8% WRC 474 95% Probability Cycles = 5,418,844.
BS5500 Allowed Cycles(Curve F) = 1,602,801.
Membrane-to-Bending Ratio = 4.413
Bending-to-PL+PB+Q Ratio = 0.185
Plot Reference:
6) Pl+Pb+Q+F < Sa (EXP,Inside) Case 3
Table of Contents
Stress Intensification Factors
Branch/Nozzle Sif Summary
Peak Primary Secondary
Axial : 5.172 2.413 7.663
Inplane : 1.761 1.426 2.608
Outplane: 3.838 1.805 5.686
Torsion : 0.838 1.050 1.242
Pressure: 1.110 1.409 1.644
The above stress intensification factors are to be used
in a beam-type analysis of the piping system. Inplane,
Outplane and Torsional sif's should be used with the
matching branch pipe whose diameter and thickness is given
below. The axial sif should be used to intensify the
axial stres
