Hangzhou Boiler Group Co.Ltd. Project no.
1 of 23
TAG no.
-
Job No :
06B103
Technical specification specification
06745 Hariza Hari za 9E HRSG HRSG
Plant
Page of
Customer / final customer
Purpose
FOR APPROVAL
Pressu Pressure re Parts Parts Strength Calcu Calculation lation s-Modu s-Module le 4 (IBR) (IBR)
DWG. No.:06745JS2(7 No.:06745JS2(7) Calculation Criterion:Indian Boiler Act 1923,and Regulations 1950 up to Amendment 22nd.Feb.2005
Revision
A
No.
1 st issue
2006-12-17
Date
Prepared
Approved
Text
Hangzhou Hangzhou Bo iler Group Co.,Ltd
PRESSURE PARTS STRENGTH CALCULATIONS-MOD CAL CULATIONS-MODULE ULE 4# CONTENTS DESIGNATION
No.
06745JS2(7)
PAGE
HP ECON1 AND IP ECON 1
COIL OF HP ECON1 AND IP ECON
3
2
OUTLET AND INLET HEADER OF HP ECON1
3
3
5
4
INTERMEDIATE HEADER 1 3 OF HP ECON1 OUTLET AND INLET HEADER OF HP ECON1/IP ECON
5
INTERMEDIATE HEADER 1 3 OF HP ECON1/IP ECON (LEFT)
8
6
INTERMEDIATE HEADER 1 3 OF HP ECON1/IP ECON (RIGHT)
9
～
6
～
～
LP EVAP 1
COIL OF LP EVAP
13
2
OUTLET AND INLET HEADER OF LP EVAP
14
3
LP EVAP MANIFOLD
19
NOTE: 1.THIS CALCULATION BASED ON THE PRESSURE PRESSURE PARTS CAL.06745JS2(4)(ASME) CAL.06745JS2(4)(ASME) REV:A,CHECK THE MAIN PRESSUERING PARTS AS PER IBR(ACT 1923 ,AND REGULATIONS 1950 UP TO AMENDMENT 22ND FEB,2005). 2.MARGIN FOR CORROSION CORROSION IN THIS CALCULATION TAKE 0mm FOR COIL AND HEADER.
Drawn Date
Checked Date
Reviewed Date
page 2 of 23
Approved Date
Hangzhou Boiler Group Co.,Ltd No.
NAME
PRESSURE PARTS STRENGTH CALCULATIONS-HP ECON/ IP ECON SIGNUNITS
FORMULA AND CALCULATION
06745JS2(7)
VALUE custormary
metric
Caculati on of Headers and coils 1. COIL OF HP ECON1 AND IP ECON DWG.NO.:745147-1-0 Coil Calculation 1.1
Design Pressure of HP ECON1 Design Pressure of IP ECON
1.2
Design Temperature
1.3
Material Of tube
1.4
Outer Diameter of Tube
1.5 1.6
1.9
1.10
DP
t
psi
℉
1290
8.89
700
4.83
700
371.11
1.5
38.1
SA210 A-1 Do
in
Actual Thickness of Row tn in 0.105 2.667 1-19 Allowable Stress of Row 1f t psi ASME Ⅱ,PART D TABLE 1A,P12 15600 107.56 19 The principle of selecting allowable stress is same as HP SHTR2, allowance stress value in ASME code Sec Ⅱ Part D is more conservation.
1.7 1.8
IBR-338(a)(Eqn87)
C Corrosion
C'
in
Selected According to IBR338(a), Dp ≤ 1000psi,C=0.75;Dp＞1000psi,C=0
in
0
0
0.03
0.75
0
Caculation Thickness of Tcal in (Dp*Do)/(2*f t +Dp)+C 0.060 1.51 HP ECON1 Caculation Thickness of IP 0.062 1.59 ECON Min Required Thickness of Tmin in Tcal+C' 0.060 HP ECON1 Min Required Thickness of 0.062 IP ECON CONCLUSION:The thic kness p rovi ded are greater than the value required by IBR,so th e design is s afe.
page 3 of 23
2.OUTLET AND INLET HEADER OF HP ECON1 DWG.NO.:745148-8-0 & 745148-9-0 2.1
Header Shell Calculation
IBR-342(Eqn72)
2.1.1
Design Pressure
2.1.2
Design Temperature
2.1.3
Material Of Header
2.1.4
Outer Diameter of Header
Do
in
2.1.5
Inside Diameter of Header
D
in
2.1.6
Nominal Thickness of Header
Tn
in
DP t
psi 1290psi+25ft water column ℉
max{inle=395;outlet=475}
1301 475
SA106 B 8"
Sch 120
8.625
219.1
7.19
182.58
0.719
18.26
2.1.7
Allowable Stress fs psi ASME Ⅱ,PART D TABLE 1A,P12 17100 The principle of selecting allowable stress is the same as HP SHTR2, allowance stress value in ASME code Sec Ⅱ Part D is more conservative.
2.1.8
Efficiency
E P
3.72
94.52
d
1.5
38.1
E
2.1.9
Allowable Deviation of Thickness
IBR-215：(P-d)/P
0.597
a
%
12.5
2.1.10 Corrision
C
in
0
2.1.11 Effective Thichness
Te
in
Te=Tn*(1-a%)
0.629
2.1.12 Calculation Thickness
Tcal
in
(Dp*D)/(2*fs*E-Dp)+0.03
0.519
2.1.13 Min Required Thickness
Tmin
in
Tcal+C
0.519
2.1.14 Working Pressure
W.P.
psi 2*fs*E(Te-0.03-C)/(D+Te-0.03-C)
1571
CONCLUSION:The thickness & working pressure provided are greater than the value required by IBR,so the design is safe. 2.2
Header End Plate Calculation
IBR-340(89A)
2.2.1
Material Of End Plate
SA516 Gr.70
2.2.2
Inside Diameter of Header
2.2.3 2.2.4
Nominal Thickness of End Plate Allowable Stress Under Design Temperature
D
in
7.19
Tn
in
fp
psi ASME Ⅱ,PART D TABLE 1A,P16
1 20000
182.55 25.4 137.90
2.2.5
Ratio
C
Selected
0.04
1
2.2.6
Ratio
K
Selected According to IBR-342
0.19
0.19
2.2.7
Corrosion
C'
in
0
0
2.2.8
Actual Thickness
T
in
1
25.4
2.2.9
Working Pressure W.P. psi fp*(T-C)2/(D2*K) 1878 13.0 CONCLUSION:The worki ng press ure provi ded are greater than the value required by IBR,so th e design is safe.
Tn-C'
page 4 of 23
2.3
Opening Reinforcement Calculation
According to IBR-279
ASME opening reinforcement cal.meet the requirements. 2.3.1
Material of nozzle
SA106 B
2.3.2
Nozzle Specification
6"Sch 80
2.3.3
do
in
6.625
168.3 10.97
2.3.4
Nominal Thickness
tn
in
0.432
2.3.5
Inside Diameter of Nozzle
dn
in
5.761
2.3.6
Actual Thickness of Header Shell
ts
in
0.719
fs
psi ASME Ⅱ,PART D TABLE 1A,P12
17100
fn
psi ASME Ⅱ,PART D TABLE 1A,P12
17100
2.3.7 2.3.8
Allowable Stress of Nozzle
2.3.9
fn/fs
2.3.10 Efficiency of Header
The openings is larger than the Max. Uncompensated Holes should be treated as no opening after selfreinforcement. Therefore the Weld efficiency is taken as 1 .
2.3.11
E
Equivalent Thickness of Header Shell
2.3.12 Efficiency of Nozzle
es
in
1.000
IBR-270(Eqn72) (Dp*D)/(2*fs*E-Dp)+0.03+C
E'
Equivalent Thickness of Nozzle 2.5 Nominal Thickness of 2.3.14 Shell 2.3.13
1
0.314 1
IBR-270(Eqn72) (Dp*dn)/(2*fn*E'-Dp)+0.03+C
en
in
2.5ts
in
1.798
2.5tn
in
1.080
b
in
b'
in
0
2.3.17 Height of Fillet Weld
Cw1
in
0.394
2.3.18 Height of Fillet Weld
Cw2
in
0.000
Cw
in
2.3.15 2.5 Thickness of Nozzle 2.3.16
2.3.19
Efficient Compensation Height
Total Transverse Section Area of Fillet Weld
2
min{2.5ts,2.5tn}
2
0.258
1.080
2
(Cw1) fn/fs+(Cw2) fn/f s
0.155
2.3.20
ts+3in
3.719
2.3.21
dn/2
2.881
MAX{ts+3in,dn/2}
3.719
dn*es
1.810
2(tn-en)b*fn/fs+2tn*b'*fn/fs+2(tses)Ci+Cw
3.542
2.3.22
Efficient Compensation Width Ci
Ci
in
2.3.23 Area Required
X
in
2.3.24 Area Compensation
Y
in
CONCLUSION: Y
2 2
X, so the opening o f reinforc ement meets the requirements of IBR.
page 5 of 23
10
page 6 of 23
3.INTERMEDIATE HEADER 1
3 OF HP ECON1
DWG.NO.:745148-12-0 3.1
Header Shell Calculation
IBR-342(Eqn72)
3.1.1
Design Pressure
3.1.2
Design Temperature
3.1.3
Material Of Header
3.1.4
Outer Diameter of Header
Do
in
3.1.5
Inside Diameter of Header
D
in
3.1.6
Nominal Thickness of Header
Tn
in
3.1.7
Allowable Stress
fs
psi ASME Ⅱ,PART D TABLE 1A,P12
3.1.8
Efficiency
E
DP t
psi 1290psi+95ft water column
475
℉
SA106 B 4"
XXS
4.5
114.3
3.15
80.06
0.674
17.12
17100
a
1.87
47.575
b
1.374
34.91
d
1.5
38.1
b/a
0.734
(2a-d)/2a
0.600
E
3.1.9
1331
Allowable Deviation of Thickness
IBR-215：FIG-14
0.385
a
%
12.5
3.1.10 Corrision
C
in
0
3.1.11 Effective Thichness
Te
in
Te=Tn*(1-a%)
0.590
3.1.12 Calculation Thickness
Tcal
in
(Dp*D)/(2*fs*E-Dp)+0.03
0.384
3.1.13 Min Required Thickness
Tmin
in
Tcal+C
3.1.14 Working Pressure
W.P.
psi 2*fs*E(Te-0.03-C)/(D+Te-0.03-C)
0.38 1986
CONCLUSION:The thic kness & w orki ng press ure prov ided are greater than th e value requir ed by IBR,so the design is safe. 3.2
Header End Plate Calculation
IBR-340(89A)
3.2.1
Material Of End Plate
SA516 Gr.70
3.2.2
Inside Diameter of Header
3.2.3 3.2.4
Nominal Thickness of End Plate Allowable Stress Under Design Temperature
D
in
3.15
Tn
in
fp
psi ASME Ⅱ,PART D TABLE 1A,P16
0.5 20000
80.06 12.7 137.90
3.2.5
Ratio
C
Selected
0.04
1
3.2.6
Ratio
K
Selected According to IBR-342
0.19
0.19
3.2.7
Corrosion
C'
0
0
in
page 7 of 23
3.2.8
Actual Thickness
T
in
Tn-C'
3.2.9
Working Pressure W.P. psi fp*(T-C)2/(D2*K) 2242 15.5 CONCLUSION:The worki ng press ure provi ded are greater than the value required by IBR,so th e design is safe.
page 8 of 23
0.5
12.7
4.OUTLET AND INLET HEADER OF HP ECON1/IP ECON DWG.NO.:745148-10-0 & 745148-11-0 4.1
Header Shell Calculation
IBR-342(Eqn72)
4.1.1
Design Pressure
4.1.2
Design Temperature
4.1.3
Material Of Header
4.1.4
Outer Diameter of Header
Do
in
4.1.5
Inside Diameter of Header
D
in
4.1.6
Nominal Thickness of Header
Tn
in
4.1.7
Allowable Stress
fs
psi ASME Ⅱ,PART D TABLE 1A,P12
4.1.8
Efficiency
E
DP t
psi 1290psi+25ft water column
Allowable Deviation of Thickness
500
℉
SA106 B 8"
Sch 120
8.625
219.1
7.19
182.58
0.719
18.26
17100
P
3.60
91.4
d
1.5
38.1
E
4.1.9
1301
IBR-215：(P-d)/P
0.583
a
%
12.5
4.1.10 Corrision
C
in
0
4.1.11 Effective Thichness
Te
in
Te=Tn*(1-a%)
4.1.12 Calculation Thickness
Tcal
in
(Dp*D)/(2*fs*E-Dp)+0.03
4.1.13 Min Required Thickness
Tmin
in
Tcal+C
4.1.14 Working Pressure
W.P.
psi 2*fs*E(Te-0.03-C)/(D+Te-0.03-C)
0.629 -7.157 -7.16 1535
CONCLUSION:The thickness & working pressure provided are greater than the value required by IBR,so the design is safe. 4.2
Header End Plate Calculation IBR-340(89A) The material and size of end plate is same as outlet and inlet header of HP ECON1, and the allowance stress is same ,so the calculation is same as the end plate of outlet and inlet header of HP ECON1.
4.3
Opening Reinforcement Calculation
According to IBR-279 Opening Reinforcement Calculation of Nozzle 6" Sch80 is same as outlet and inlet header of OF HP ECON1,here is calculation about 3" Sch40.
ASME opening reinforcement cal.meet the requirements. 4.3.1
Material of nozzle
SA106 B
4.3.2
Nozzle Specification
3"Sch 40
4.3.3
do
in
3.5
88.9 5.49
4.3.4
Nominal Thickness
tn
in
0.216
4.3.5
Inside Diameter of Nozzle
dn
in
3.068
page 9 of 23
4.3.6
Actual Thickness of Header Shell
4.3.7 4.3.8
Allowable Stress of Nozzle
ts
in
0.719
fs
psi ASME Ⅱ,PART D TABLE 1A,P12
17100
fn
psi ASME Ⅱ,PART D TABLE 1A,P12
17100
4.3.9
fn/fs
4.3.10 Efficiency of Header
The openings is larger than the Max. Uncompensated Holes should be treated as no opening after selfreinforcement. Therefore the Weld efficiency is taken as 1 .
4.3.11
E
Equivalent Thickness of Header Shell
4.3.12 Efficiency of Nozzle
es
in
1.000
IBR-270(Eqn72) (Dp*D)/(2*fs*E-Dp)+0.03+C
E'
Equivalent Thickness of Nozzle 2.5 Nominal Thickness of 4.3.14 Shell 4.3.13
1
0.314 1
IBR-270(Eqn72) (Dp*dn)/(2*fn*E'-Dp)+0.03+C
en
in
2.5ts
in
1.798
2.5tn
in
0.540
b
in
b'
in
0
4.3.17 Height of Fillet Weld
Cw1
in
0.394
4.3.18 Height of Fillet Weld
Cw2
in
0.000
Cw
in
4.3.15 2.5 Thickness of Nozzle 4.3.16
4.3.19
Efficient Compensation Height
Total Transverse Section Area of Fillet Weld
2
min{2.5ts,2.5tn}
2
0.151
0.540
2
(Cw1) fn/fs+(Cw2) fn/f s
0.155
4.3.20
ts+3in
3.719
4.3.21
dn/2
1.534
MAX{ts+3in,dn/2}
3.719
2
dn*es
0.964
2
2(tn-en)b*fn/fs+2tn*b'*fn/fs+2(tses)Ci+Cw
3.236
4.3.22
Efficient Compensation Width Ci
Ci
in
4.3.23 Area Required
X
in
4.3.24 Area Compensation
Y
in
CONCLUSION: Y
X, so the opening o f reinforc ement meets the requirements of IBR.
4.4
Blocker Plate Calculation
4.4.1
Material Of Blocker Plate
4.4.2
Inside Diameter of Header
4.4.3 4.4.4
10
Nominal Thickness of End Plate Allowable Stress Under Design Temperature
SA516 Gr.70 D
in
7.19
Tn
in
1.260
fp
psi ASME Ⅱ,PART D TABLE 1A,P16
20000
182.55 32 137.90
4.4.5
Ratio
C
Selected
0.04
1
4.4.6
Ratio
K
Selected According to IBR-342
0.28
0.28
4.4.7
Corrosion
C'
in
0
0
4.4.8
Actual Thickness
T
in
1.260
32
4.4.9
Working Pressure W.P. psi fp*(T-C)2/(D2*K) 2058 14.2 CONCLUSION:The worki ng press ure provi ded are greater than the value required by IBR,so th e design is safe.
Tn-C'
page 10 of 23
5.INTERMEDIATE HEADER 1
3 OF HP ECON1/IP ECON (LEFT)
DWG.NO.:745148-13-0 5.1
Header Shell Calculation
IBR-342(Eqn72)
5.1.1
Design Pressure
5.1.2
Design Temperature
5.1.3
Material Of Header
5.1.4
Outer Diameter of Header
Do
in
5.1.5
Inside Diameter of Header
D
in
5.1.6
Nominal Thickness of Header
Tn
in
5.1.7
Allowable Stress
fs
psi ASME Ⅱ,PART D TABLE 1A,P12
5.1.8
Efficiency
E
DP t
psi 1290psi+95ft water column
475
℉
SA106 B 4"
XXS
4.5
114.3
3.152
80.06
0.674
17.12
17100
a
1.86
47.285
b
1.374
34.9
d
1.5
38.1
b/a
0.738
(2a-d)/2a
0.597
E
5.1.9
1331
Allowable Deviation of Thickness
IBR-215：FIG-14
0.405
a
%
12.5
5.1.10 Corrision
C
in
0
5.1.11 Effective Thichness
Te
in
Te=Tn*(1-a%)
0.590
(Dp*D)/(2*fs*E-Dp)+0.03
0.365
Tcal+C
0.365
5.1.12 Calculation Thickness
Tcal
5.1.13 Min Required Thickness
Tmin
in
5.1.14 Working Pressure
W.P.
psi 2*fs*E(Te-0.03-C)/(D+Te-0.03-C)
2089
CONCLUSION:The thic kness & w orki ng press ure prov ided are greater than th e value requir ed by IBR,so the design is safe. 5.2
Header End Plate Calculation
IBR-340(89A)
The material and size of end plate is same as intermediate header 1 ～3 of HP ECON1, and the allowance stress is same ,so the calculation is same as the end plate of outlet and inlet header of HP ECON1.
page 11 of 23
6.INTERMEDIATE HEADER 1
3 OF HP ECON1/IP ECON (RIGHT)
DWG.NO.:745148-14-0 6.1
Header Shell Calculation
IBR-342(Eqn72)
6.1.1
Design Pressure
6.1.2
Design Temperature
6.1.3
Material Of Header
6.1.4
Outer Diameter of Header
Do
in
6.1.5
Inside Diameter of Header
D
in
6.1.6
Nominal Thickness of Header
Tn
in
6.1.7
Allowable Stress
fs
psi ASME Ⅱ,PART D TABLE 1A,P12
6.1.8
Efficiency
E
DP t
psi 700psi+95ft water column
741
℉
500 SA106 B
Sch 80
4.5
114.3
3.83
97.18
0.337
8.56
17100
a
1.85
46.89
b
1.374
34.9
d
1.5
38.1
b/a
0.744
(2a-d)/2a
0.594
E
6.1.9
4"
Allowable Deviation of Thickness
IBR-215：FIG-14
0.408
a
%
12.5
6.1.10 Corrision
C
in
0
6.1.11 Effective Thichness
Te
in
Te=Tn*(1-a%)
0.295
6.1.12 Calculation Thickness
Tcal
in
(Dp*D)/(2*fs*E-Dp)+0.03
0.245
6.1.13 Min Required Thickness
Tmin
in
Tcal+C
0.245
6.1.14 Working Pressure
W.P.
psi 2*fs*E(Te-0.03-C)/(D+Te-0.03-C)
903
CONCLUSION:The thic kness & w orki ng press ure prov ided are greater than th e value requir ed by IBR,so the design is safe. 6.2
Header End Plate Calculation
IBR-340(89A)
6.2.1
Material Of End Plate
SA516 Gr.70
6.2.2
Inside Diameter of Header
6.2.3 6.2.4
Nominal Thickness of End Plate Allowable Stress Under Design Temperature
D
in
3.83
Tn
in
fp
psi ASME Ⅱ,PART D TABLE 1A,P16
0.5 20000
97.18 12.7 137.90
6.2.5
Ratio
C
Selected
0.04
1
6.2.6
Ratio
K
Selected According to IBR-342
0.19
0.19
page 12 of 23
6.2.7
Corrosion
C'
in
6.2.8
Actual Thickness
T
in
6.2.9
Tn-C' 2
2
0
0
0.5
12.7
Working Pressure W.P. psi fp*(T-C) /(D *K) 1522 10.5 CONCLUSION:The worki ng press ure provi ded are greater than the value required by IBR,so th e design is safe.
page 13 of 23
Hangzhou Boiler Group Co.,Ltd No.
NAME
PRESSURE PARTS STRENGTH CALCULATIONS-LP EVAP SIGNUNITS
FORMULA AND CALCULATION
06745JS2(7)
VALUE custormary
metric
Caculati on of Headers and coils 1. COIL OF LP EVAP DWG.NO.:745127-1-0 Coil Calculation 1.1
Design Pressure
1.2
Design Temperature
1.3
Material Of tube
1.4
Outer Diameter of Tube
1.5 1.6
IBR-338(a)(Eqn87) DP
psi
155
1.07
t
℉
700
371.11
SA210 A-1 Do
in
2
50.8
Actual Thickness
tn
in
0.105
2.667
Allowable Stress
ft
psi ASME Ⅱ,PART D TABLE 1A,P12 15600 107.56 The principle of selecting allowable stress is same as HP SHTR2, allowance stress value in ASME code Sec Ⅱ Part D is more conservation.
1.7
C
in
C'
in
Selected According to IBR338(a)
0.030
1.8
Corrosion
1.9
Caculation Thickness
Tcal
in
(Dp*Do)/(2*f t +Dp)+C
0.039
1.10
Min Required Thickness
Tmin
in
Tcal+C'
0.039
0.75
0 1.00
CONCLUSION:The thic kness p rovi ded are greater than the value required by IBR,so th e design is s afe.
page 13 of 23
2.OUTLET AND INLET HEADER OF LP EVAP DWG.NO.:745148-1-0,745148-2-0,745148-3-0,745148-5-0,745148-6-0,745148-7-0 Header size: Outlet 2-3:10" Sch120,others:10" Sch80, design temperature is same , so the calculation is based on the header of 10" Sch80 . 2.1
Header Shell Calculation
IBR-342(Eqn72)
2.1.1
Design Pressure
2.1.2
Design Temperature
2.1.3
Material Of Header
2.1.4
Outer Diameter of Header
Do
in
2.1.5
Inside Diameter of Header
D
in
2.1.6
Nominal Thickness of Header
Tn
in
DP
psi
t
℉
based on inlet header(lower): 155psi+95ft water column
196 420
SA106 B 10"
Sch 80
10.75
273
9.56
242.82
0.594
15.09
2.1.7
Allowable Stress fs psi ASME Ⅱ,PART D TABLE 1A,P12 17100 The principle of selecting allowable stress is the same as HP SHTR2, allowance stress value in ASME code Sec Ⅱ Part D is more conservation.
2.1.8
Efficiency
E a
2.31
58.77
b
2.626
66.7
d
2.0
50.8
b/a
1.135
(2a-d)/2a
0.568
E
2.1.9
Allowable Deviation of Thickness
IBR-215：FIG-14
0.480
a
%
12.5
2.1.10 Corrision
C
in
0
2.1.11 Effective Thichness
Te
in
Te=Tn*(1-a%)
0.520
2.1.12 Calculation Thickness
Tcal
in
(Dp*D)/(2*fs*E-Dp)+0.03
0.146
2.1.13 Min Required Thickness
Tmin
in
Tcal+C
0.146
2.1.14 Working Pressure
W.P.
psi 2*fs*E(Te-0.03-C)/(D+Te-0.03-C)
800
CONCLUSION:The thic kness & w orki ng press ure prov ided are greater than th e value requir ed by IBR,so the design is safe. 2.2
Header End Plate Calculation
IBR-340(89A)
2.2.1
Material Of End Plate
SA516 Gr.70
2.2.2
Inside Diameter of Header
D
in
2.2.3
Nominal Thickness of End Plate
Tn
in
9.56 0.5
page 14 of 23
242.87 12.7
2.2.4
Allowable Stress Under Design Temperature
fp
2.2.5
Ratio
C
Selected
0.04
1
2.2.6
Ratio
K
Selected According to IBR-342
0.19
0.19
2.2.7
Corrosion
C'
in
0
0
2.2.8
Actual Thickness
T
in
0.5
12.7
psi ASME Ⅱ,PART D TABLE 1A,P16
Tn-C' 2
20000
137.90
2
2.2.9
Working Pressure W.P. psi fp*(T-C) /(D *K) 244 1.7 CONCLUSION:The worki ng press ure provi ded are greater than the value required by IBR,so th e design is safe.
2.3
Opening Reinforcement Calculation
According to IBR-279
Nozzle of outlet 1
ASME opening reinforcement cal.meet the requirements. 2.3.1
Material of nozzle
SA106 B
2.3.2
Nozzle Specification
6"Sch 40
2.3.3
do
in
6.625
273 7.11
2.3.4
Nominal Thickness
tn
in
0.28
2.3.5
Inside Diameter of Nozzle
dn
in
6.065
2.3.6
Actual Thickness of Header Shell
ts
in
0.594
fs
psi ASME Ⅱ,PART D TABLE 1A,P12
17100
fn
psi ASME Ⅱ,PART D TABLE 1A,P12
17100
2.3.7 2.3.8
Allowable Stress of Nozzle
2.3.9
fn/fs
2.3.10 Efficiency of Header
The openings is larger than the Max. Uncompensated Holes should be treated as no opening after selfreinforcement. Therefore the Weld efficiency is taken as 1 .
2.3.11
Equivalent Thickness of Header Shell
2.3.12 Efficiency of Nozzle Equivalent Thickness of Nozzle 2.5 Nominal Thickness of 2.3.14 Shell 2.3.13
E
es
in
1.000
IBR-270(Eqn72) (Dp*D)/(2*fs*E-Dp)+0.03+C
E'
1
0.085 1
IBR-270(Eqn72) (Dp*dn)/(2*fn*E'-Dp)+0.03+C
en
in
2.5ts
in
1.485
2.5tn
in
0.700
b
in
b'
in
0
2.3.17 Height of Fillet Weld
Cw1
in
0.394
2.3.18 Height of Fillet Weld
Cw2
in
0.000
Cw
in
2.3.15 2.5 Thickness of Nozzle 2.3.16
2.3.19
Efficient Compensation Height
Total Transverse Section Area of Fillet Weld
2
min{2.5ts,2.5tn}
2
0.700
2
(Cw1) fn/fs+(Cw2) fn/f s
page 15 of 23
0.065
0.155
10
2.3.20
ts+3in
3.594
2.3.21
dn/2
3.033
MAX{ts+3in,dn/2}
3.594
2
dn*es
0.516
2
2(tn-en)b*fn/fs+2tn*b'*fn/fs+2(tses)Ci+Cw
4.114
2.3.22
Efficient Compensation Width Ci
Ci
in
2.3.23 Area Required
X
in
2.3.24 Area Compensation
Y
in
CONCLUSION: Y
2.4
X, so the opening o f reinforc ement meets the requirements of IBR.
Opening Reinforcement Calculation
According to IBR-279
Nozzle of inlet 1 and 2
ASME opening reinforcement cal.meet the requirements. 2.4.1
Material of nozzle
SA106 B
2.4.2
Nozzle Specification
5"Sch 40
2.4.3
do
in
5.563
141.3 6.55
2.4.4
Nominal Thickness
tn
in
0.258
2.4.5
Inside Diameter of Nozzle
dn
in
5.047
2.4.6
Actual Thickness of Header Shell
ts
in
0.594
fs
psi ASME Ⅱ,PART D TABLE 1A,P12
17100
fn
psi ASME Ⅱ,PART D TABLE 1A,P12
17100
2.4.7 2.4.8
Allowable Stress of Nozzle
2.4.9
fn/fs
2.4.10 Efficiency of Header
The openings is larger than the Max. Uncompensated Holes should be treated as no opening after selfreinforcement. Therefore the Weld efficiency is taken as 1 .
2.4.11
Equivalent Thickness of Header Shell
2.4.12 Efficiency of Nozzle Equivalent Thickness of Nozzle 2.5 Nominal Thickness of 2.4.14 Shell 2.4.13
E
es
in
1.000
IBR-270(Eqn72) (Dp*D)/(2*fs*E-Dp)+0.03+C
E'
1
0.085 1
IBR-270(Eqn72) (Dp*dn)/(2*fn*E'-Dp)+0.03+C
en
in
2.5ts
in
1.485
2.5tn
in
0.645
b
in
b'
in
0
2.4.17 Height of Fillet Weld
Cw1
in
0.394
2.4.18 Height of Fillet Weld
Cw2
in
0.000
Cw
in
2.4.15 2.5 Thickness of Nozzle 2.4.16
2.4.19
Efficient Compensation Height
Total Transverse Section Area of Fillet Weld
2
min{2.5ts,2.5tn}
2
0.645
2
(Cw1) fn/fs+(Cw2) fn/fs
page 16 of 23
0.059
0.155
10
2.4.20
ts+3in
3.594
2.4.21
dn/2
2.524
MAX{ts+3in,dn/2}
3.594
2
dn*es
0.430
2
2(tn-en)b*fn/fs+2tn*b'*fn/fs+2(tses)Ci+Cw
4.069
2.4.22
Efficient Compensation Width Ci
Ci
in
2.4.23 Area Required
X
in
2.4.24 Area Compensation
Y
in
CONCLUSION: Y
2.5
X, so the opening o f reinforc ement meets the requirements of IBR.
Opening Reinforcement Calculation
According to IBR-279
Nozzle of inlet 3
ASME opening reinforcement cal.meet the requirements. 2.5.1
Material of nozzle
SA106 B
2.5.2
Nozzle Specification
4"Sch 40
2.5.3
do
in
4.5
114.3 6.02
2.5.4
Nominal Thickness
tn
in
0.237
2.5.5
Inside Diameter of Nozzle
dn
in
4.026
2.5.6
Actual Thickness of Header Shell
ts
in
0.594
fs
psi ASME Ⅱ,PART D TABLE 1A,P12
17100
fn
psi ASME Ⅱ,PART D TABLE 1A,P12
17100
2.5.7 2.5.8
Allowable Stress of Nozzle
2.5.9
fn/fs
2.5.10 Efficiency of Header
The openings is larger than the Max. Uncompensated Holes should be treated as no opening after selfreinforcement. Therefore the Weld efficiency is taken as 1 .
2.5.11
Equivalent Thickness of Header Shell
2.5.12 Efficiency of Nozzle Equivalent Thickness of Nozzle 2.5 Nominal Thickness of 2.5.14 Shell 2.5.13
E
es
in
1.000
IBR-270(Eqn72) (Dp*D)/(2*fs*E-Dp)+0.03+C
E'
1
0.085 1
IBR-270(Eqn72) (Dp*dn)/(2*fn*E'-Dp)+0.03+C
en
in
2.5ts
in
1.485
2.5tn
in
0.593
b
in
b'
in
0
2.5.17 Height of Fillet Weld
Cw1
in
0.394
2.5.18 Height of Fillet Weld
Cw2
in
0.000
Cw
in
2.5.15 2.5 Thickness of Nozzle 2.5.16
2.5.19
Efficient Compensation Height
Total Transverse Section Area of Fillet Weld
2
min{2.5ts,2.5tn}
2
0.593
2
(Cw1) fn/fs+(Cw2) fn/fs
page 17 of 23
0.053
0.155
10
2.5.20
ts+3in
3.594
2.5.21
dn/2
2.013
MAX{ts+3in,dn/2}
3.594
2
dn*es
0.343
2
2(tn-en)b*fn/fs+2tn*b'*fn/fs+2(tses)Ci+Cw
4.031
2.5.22
Efficient Compensation Width Ci
Ci
in
2.5.23 Area Required
X
in
2.5.24 Area Compensation
Y
in
CONCLUSION: Y
X, so the opening o f reinforc ement meets the requirements of IBR.
page 18 of 23
3.LP EVAP MANIFOLD DWG.NO.:745148-4-0 3.1
Header Shell Calculation
IBR-342(Eqn72)
3.1.1
Design Pressure
3.1.2
Design Temperature
3.1.3
Material Of Header
3.1.4
Outer Diameter of Header
Do
in
3.1.5
Inside Diameter of Header
D
in
3.1.6
Nominal Thickness of Header
Tn
in
3.1.7
Allowable Stress
fs
psi ASME Ⅱ,PART D TABLE 1A,P12
3.1.8
Efficiency
E
DP t
psi 155psi+95ft water column
196
℉
420 SA106 B 10"
Sch 80
10.75
273
9.56
242.82
0.594
15.09
17100 1
All the openings which are larger than the Max. permissible opening should be treated as no opening after self-reinforcement. Therefore the Weld efficiency is taken as 1 . 3.1.9
Allowable Deviation of Thickness
a
%
12.5
3.1.10 Corrision
C
in
0
3.1.11 Effective Thichness
Te
in
Te=Tn*(1-a%)
0.520
3.1.12 Calculation Thickness
Tcal
in
(Dp*D)/(2*fs*E-Dp)+0.03
0.085
3.1.13 Min Required Thickness
Tmin
in
Tcal+C
0.085
3.1.14 Working Pressure
W.P.
psi 2*fs*E(Te-0.03-C)/(D+Te-0.03-C)
1666
CONCLUSION:The thickness & working pressure provided are greater than the value required by IBR,so the design is safe. 3.2
Header End Plate Calculation
IBR-340(89A)
The calculation of end plate is same as outlet and inlet header. 3.3
Opening Reinforcement Calculation
According to IBR-279
Nozzle N1 and N2
ASME opening reinforcement cal.meet the requirements. 3.3.1
Material of nozzle
SA106 B
3.3.2
Nozzle Specification
5"Sch 40
3.3.3
do
in
5.563
141.3 6.55
3.3.4
Nominal Thickness
tn
in
0.258
3.3.5
Inside Diameter of Nozzle
dn
in
5.047
3.3.6
Actual Thickness of Header Shell
ts
in
0.594
fs
psi ASME Ⅱ,PART D TABLE 1A,P12
17100
fn
psi ASME Ⅱ,PART D TABLE 1A,P12
17100
3.3.7 3.3.8 3.3.9
Allowable Stress of Nozzle
fn/fs
page 19 of 23
1.000
3.3.10 Efficiency of Header
3.3.11
The openings is larger than the Max. Uncompensated Holes should be treated as no opening after selfreinforcement. Therefore the Weld efficiency is taken as 1 .
E
Equivalent Thickness of Header Shell
3.3.12 Efficiency of Nozzle
es
in
IBR-270(Eqn72) (Dp*D)/(2*fs*E-Dp)+0.03+C
E'
Equivalent Thickness of Nozzle 2.5 Nominal Thickness of 3.3.14 Shell 3.3.13
1
0.085 1
IBR-270(Eqn72) (Dp*dn)/(2*fn*E'-Dp)+0.03+C
en
in
2.5ts
in
1.485
2.5tn
in
0.645
b
in
b'
in
0
3.3.17 Height of Fillet Weld
Cw1
in
0.394
3.3.18 Height of Fillet Weld
Cw2
in
0.000
Cw
in
3.3.15 2.5 Thickness of Nozzle 3.3.16
3.3.19
Efficient Compensation Height
Total Transverse Section Area of Fillet Weld
2
min{2.5ts,2.5tn}
0.059
0.645
2
2
(Cw1) fn/fs+(Cw2) fn/fs
0.155
3.3.20
ts+3in
3.594
3.3.21
dn/2
2.524
MAX{ts+3in,dn/2}
3.594
2
dn*es
0.430
2
2(tn-en)b*fn/fs+2tn*b'*fn/fs+2(tses)Ci+Cw
4.069
3.3.22
Efficient Compensation Width Ci
Ci
in
3.3.23 Area Required
X
in
3.3.24 Area Compensation
Y
in
CONCLUSION: Y
3.4
10
X, so the opening o f reinforc ement meets the requirements of IBR.
Opening Reinforcement Calculation
According to IBR-279
Nozzle N3
ASME opening reinforcement cal.meet the requirements. 3.4.1
Material of nozzle
SA106 B
3.4.2
Nozzle Specification
4"Sch 40
3.4.3
do
in
4.5
114.3 6.02
3.4.4
Nominal Thickness
tn
in
0.237
3.4.5
Inside Diameter of Nozzle
dn
in
4.026
3.4.6
Actual Thickness of Header Shell
ts
in
0.594
fs
psi ASME Ⅱ,PART D TABLE 1A,P12
17100
fn
psi ASME Ⅱ,PART D TABLE 1A,P12
17100
3.4.7 3.4.8 3.4.9
Allowable Stress of Nozzle
fn/fs
page 20 of 23
1.000
3.4.10 Efficiency of Header
3.4.11
The openings is larger than the Max. Uncompensated Holes should be treated as no opening after selfreinforcement. Therefore the Weld efficiency is taken as 1 .
E
Equivalent Thickness of Header Shell
3.4.12 Efficiency of Nozzle
es
in
IBR-270(Eqn72) (Dp*D)/(2*fs*E-Dp)+0.03+C
E'
Equivalent Thickness of Nozzle 2.5 Nominal Thickness of 3.4.14 Shell 3.4.13
1
0.085 1
IBR-270(Eqn72) (Dp*dn)/(2*fn*E'-Dp)+0.03+C
en
in
2.5ts
in
1.485
2.5tn
in
0.593
b
in
b'
in
0
3.4.17 Height of Fillet Weld
Cw1
in
0.394
3.4.18 Height of Fillet Weld
Cw2
in
0.000
Cw
in
3.4.15 2.5 Thickness of Nozzle 3.4.16
3.4.19
Efficient Compensation Height
Total Transverse Section Area of Fillet Weld
2
min{2.5ts,2.5tn}
0.053
0.593
2
2
(Cw1) fn/fs+(Cw2) fn/fs
0.155
3.4.20
ts+3in
3.594
3.4.21
dn/2
2.013
MAX{ts+3in,dn/2}
3.594
2
dn*es
0.343
2
2(tn-en)b*fn/fs+2tn*b'*fn/fs+2(tses)Ci+Cw
4.031
3.4.22
Efficient Compensation Width Ci
Ci
in
3.4.23 Area Required
X
in
3.4.24 Area Compensation
Y
in
CONCLUSION: Y
3.5
10
X, so the opening o f reinforc ement meets the requirements of IBR.
Opening Reinforcement Calculation
According to IBR-279
Nozzle DC
ASME opening reinforcement cal.meet the requirements. 3.5.1
Material of nozzle
SA106 B
3.5.2
Nozzle Specification
8"Sch 80
3.5.3
do
in
8.625
219.1 12.7
3.5.4
Nominal Thickness
tn
in
0.5
3.5.5
Inside Diameter of Nozzle
dn
in
7.625
3.5.6
Actual Thickness of Header Shell
ts
in
0.594
fs
psi ASME Ⅱ,PART D TABLE 1A,P12
17100
fn
psi ASME Ⅱ,PART D TABLE 1A,P12
17100
3.5.7 3.5.8 3.5.9
Allowable Stress of Nozzle
fn/fs
page 21 of 23
1.000
3.5.10 Efficiency of Header
3.5.11
The openings is larger than the Max. Uncompensated Holes should be treated as no opening after selfreinforcement. Therefore the Weld efficiency is taken as 1 .
E
Equivalent Thickness of Header Shell
3.5.12 Efficiency of Nozzle
es
in
IBR-270(Eqn72) (Dp*D)/(2*fs*E-Dp)+0.03+C
E'
Equivalent Thickness of Nozzle 2.5 Nominal Thickness of 3.5.14 Shell 3.5.13
1
0.085 1
IBR-270(Eqn72) (Dp*dn)/(2*fn*E'-Dp)+0.03+C
en
in
2.5ts
in
1.485
2.5tn
in
1.250
b
in
b'
in
0
3.5.17 Height of Fillet Weld
Cw1
in
0.394
3.5.18 Height of Fillet Weld
Cw2
in
0.000
Cw
in
3.5.15 2.5 Thickness of Nozzle 3.5.16
3.5.19
Efficient Compensation Height
Total Transverse Section Area of Fillet Weld
2
min{2.5ts,2.5tn}
2
0.074
1.250
2
(Cw1) fn/fs+(Cw2) fn/fs
0.155
3.5.20
ts+3in
3.594
3.5.21
dn/2
3.813
MAX{ts+3in,dn/2}
3.813
2
dn*es
0.649
2
2(tn-en)b*fn/fs+2tn*b'*fn/fs+2(tses)Ci+Cw
5.100
3.5.22
Efficient Compensation Width Ci
Ci
in
3.5.23 Area Required
X
in
3.5.24 Area Compensation
Y
in
CONCLUSION: Y
X, so the opening o f reinforc ement meets the requirements of IBR.
page 22 of 23
10
