md pv asme v0.1
DESCRIPTION
wqewTRANSCRIPT
Doc. No.
Date
Revision 0 1
1. Introduction Sheet No. 1 of 1
This guide is intended to outline a program for mechnical design of pressure vessels in accordance with
ASME.
2. References
The program is based on the following, which shall be referred to for further understanding.
Design ASME Sec. VIII, Div. 1
Materials ASME Sec. II - D
Technicals Process Vessel Design Manual, Dennis R. Moss
Design of Process Equipment, 3rd Ed., K. K. Mahajan
Catalogues for Flanges
3. Future Development
Nozzle
Conical Section
Shell Flange
Header, Box Type
Support Saddle
Leg
Lug
Skirt
Lifting Lug
Nozzle External Load
External Pressure
Tall Tower
Davit
4. Program Architecture
Inside the Program
" IS " Input and Summary Sheet
" shell " Calculation Sheet for Shell
" head " Calculation Sheet for Head
" consec " Calculation Sheet for conical Section
" s.flg " Calculation Sheet for Shell Flange
" tube " Calculation Sheet for Tube
" HD " Calculation Sheet for Header
" cv " Calculation Sheet for Cover for Header
" Nx " Calculation Sheet for Nozzle
Data Files
" materials ASTM " Stress Values of ASTM / ASME materials
" materials common " Material Index, Flange Data, Modulus of Elasticity, …...
" materials JIS " Stress Values of JIS materials
" materials KS " Stress Values of KS materials
5. General Information
Data are inputed via cells with blue words / numbers and comboboxes.
Attention shall be paid to cells with red words / numbers.
각 Sheet 의 하단에 나타나는 회사명을 바꾸려면 아래에 있는 푸른색 회사명을 바꾸기만 하면 된다.
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Program User Guide :
Description
05. 8. 15. 0.1
05. 8. 15. 0.1
PUG - MDPV - 000
2005. 8. 15.
Mechanical Design of P / V in acc. with ASME
Date Version Remarks
05. 8. 15. 0.1
Doc. No.
Date
Revision 0
1. Introduction Sheet No. 1 of 1
These notes are intended to help designers follow normal design practices, and further reach an optimum
design.
2. Notes
Flange
The procedures are from Taylor Forge Bulletin No. 502, 7th Ed., " Modern Flange Design ".
In general, bolts should be used in multiples of four(4).
For large diameter flanges, many smaller bolts on a tight bolt circle are recommended to reduce the flange
thickness.
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Design Notes :
DN - MDPV - 000
2005. 7. 28.
Mechanical Design of P / V in acc. with ASME
Date
1 of 1
D E S I G N D A T A UG - 16 ( b )
Code ASME Sec. VIII Div. 1 Minimum Thickness of Press. Retaining Parts
Service acc. to UG-16 (b) General
General P. R. Parts
Design Pressure kPa.g kg/cm2.g Unfired Steam Boiler Shell & Head
Design Temperature ℃ ℃ Compressed Air Shell & Head
Test Press. / Test Method kPa.g / Hydrostatic Steam Shell & Head
Water Shell & Head
* Excluding corrosion allowance,
Corrosion Allowance mm after forming,
C O N S T R U C T I O N D A T A regardless of material.
t
Shell plate ###
Head plate 2:1 Ellipsoidal Thick Reduction after Forming 15 %
Shell #2 plate
Conical Sec. plate Conical Length > Concentric BSA BSP GW Wt
Flat Head forging Flanged Bolt > ASTM A 193-B7,<=2.5" Thk Redu ### ### ### 1" 48
Shell Flange forging AWWA Ring NZ.t > 14 Gasket> Confined Spiral W.,SUS 15 % ### ### ### 1" 48
tube U-tube ###
Triangular Pitch, Trans. Long.
Header, Inlet pipe Circular C.A. 0 ###
Blind Flg, Inletplate Welded Bolt > BSA GW
Flange > Gasket>
Header, Outletpipe Circular C.A. 0 ###
Blind Flg, Outletplate Flanged Bolt > ASTM A 193-B8, <=3/4" BSA GW
Flange > ANSI Slip-on Gasket> ConfinedSpiral W.,SUS ### ###
N O Z Z L E S
A1, Manhole plate Inserted Location > Shell ###
Pad > plate Ar ### Sr ### Access or Inspection Opening > Yes
K1 & K2 pipe Inserted Location > Shell ###
Pad > Ar ### Sr ### Access or Inspection Opening > No
Notes : 1. - N/R - : Not Required. Ar Area Requirement BSA Requirement for Bolt Sectional Area
2. - N/A - : Not Applicable Sr Strength Requirement BSP Requirement for Bolt Spacing
3. GW Requirement for Gasket Width
4. Bolt Bolt Detail, Size / Q'ty
4.6
I N T E R N A L E X T E R N A L
0.85 2500
Code
A 516-70
3
Tube
OD
###### 14 #######ASTM
ASTM
#######
ASTM
A 516-70
ID
3
300
340 30
Pipe SizeI.D., mm
3 0
Judge
Incinerator Chamber
F - 37040 - 3100 - 25
Sohar Refinery Project Project Service
H E A D N O Z Z L E T U B E
Item No.
S H E L L
MD - IS - 000
Sheet No.
Revision 0
2005. 8. 15.
Doc. No.I N P U T & S U M M A R Y S H E E T f o r P / V M E C H . D E S I G N
t, min. t, req. t, usedDescription Type Joint Eff.
Materials
Spec. No.
Job No.
Nozzle ID>
std size>
5.4 ###### 141
#######
######A 105 1450
####### * t std >
M. Input >
19.4 ###### 3
- N/A -std size>
KS
###### 12.0
Pad Th'k > 14
ASTM A 516-70 1 585.6
ASTM 1160
STS 304 TB E 1
A 516-70
ASTM
Pad OD >
ASTM A 516-70
Pad OD >
150 lb
A 106-B 1
14 #######0.85 1450 4.6 ######
15 #######
- N/A -
#############
######KS STS 304 1
Pad Th'k >
Sch.10S
50.8
Sch.16024"
###### ######125 A Sch.80
80 A Sch.80
24" Sch.40
15 A
######
######
######
######
######
######
JIS SUS 304 1
KS STS 304 TP E 1 ######
#######
Thickness, mm
2.4
######KS STS 304 TP E 1 ###### ######
A 105
6
2.4
2.4
Partt,min-CA
1.6
150 lb
############
############ ######XX-STR
ASTM
Service
###### ###### ####### 1 1/2"
###### ######
* t std > ######
######
######
#######
#######
M. Input > ###### 95 #######
#######
ASTM A 516-70 0.85 5.4 ###### Bolt920
70.5
#######
14 #######
50
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Doc. No.
Job No. : 0 - 3100 - 25
Project : Sohar Refinery Project
Client : JGC
Contractor : HCEI
Item No. : F - 3704
Service Incinerator Chamber
5
4
3
2
1
0 Issued for approval.
Tel.
Homepage Fax.
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ApprovedReviewed
Narai Thermal Engineering Services
LTG Lee
Rev. PreparedDescriptionDate
S. J. Lee05. 8. 15.
M E C H A N I C A L D E S I G N
P R E S S U R E V E S S E L
MD - PV - 000
P R E S S U R E V E S S E L : Doc. No.
Date
Rev. 0
Sheet No. 1 of 1
1. Design Data and Summary
2. Shell
3.
4.
5.
6.
7.
8.
9.
10.
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MD - PV - 000
05. 8. 15.
T a b l e of C o n t e n t s
M E C H A N I C A L D E S I G N
P R E S S U R E V E S S E L : Doc. No.
Date
1 Revision 0
2 Sheet No. 1 x
3
4 Project Sohar Refinery Project
5 Item No. F - 3704
6 Service Incinerator Chamber
7
8
9
10 Code ASME Sec. VIII Div. 1
11
12 Pressure kPa.g
13 Temperature ℃
14 Method
15 Pressure kPa.g
16 Ambient Temperature ℃
17
18 Shell mm
19 Head mm
20 Nozzle mm
21 Tube mm
22
23
24
25 Min. Req. Used
26
27 Shell A 516-70 4.6 #### 14
28 Head 2:1 Ellipsoidal A 516-70 5.4 #### 14
29 Shell #2 A 516-70 4.6 #### 14
30 Conical Sec. Conical Concentric A 516-70 2500 1450 5.4 #### 14 L = 920 mm
31 Flat Head Flanged A 105 Nz ID. 1450 #### 50 Bolt = A 193-B7,<=2.5"
32 Shell Flange AWWA / Ring A 105 Nz Thk 14 #### 95 Gasket = Spiral W.,SUS
33
34
35
36 Req. Used.
37
38 Tube U-tube STS 304 TB E 19.4 25.4 #### 3
39 Header, Inlet Circular STS 304 TP E ##### ##### #### #### 125 A / Sch.80
40 Blind Flg, Inlet Welded STS 304 #### 15
41 Header, Outlet Circular STS 304 TP E ##### ##### #### #### 80 A / Sch.80
42 Blind Flg, Outlet Flanged SUS 304 #### #### ANSI / Slip-on / 150 lb
43
44
45
46 Req. Used. OD t
47
48 A1, Manhole A 516-70 585.6 609.6 #### 12.0 1160 14
49 K1 & K2 A 106-B ##### ##### #### ####
50
51
52
53
54 Remarks :
55
56
57
58
59
60
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Design
MD - PV - 000
M E C H A N I C A L D E S I G N
D E S I G N D A T A
***
3
3
05. 8. 15.
of
E X T E R N A L
340
0
Hydrostatic
30
I N T E R N A L
300
Joint Efficiency RadiographyCorrosion Allowance
Spot0.85
Pressure Test
3
D E S I G N S U M M A R Y
No or Full1
***
******0
N O Z Z L E S
Description
Description TypeID
mm
Thickness
1450
RemarksMaterial
2500
Remarks
T U B E & H E A D E R
Description Material LocationID
mm
Material
mm
Remark
Shell
Shell A 516-70
ODThickness Pad
Type Material
mm
ThicknessID OD
P R E S S U R E V E S S E L : Doc. No.
Date
Revision 0
Sheet No. 0 x
ASME Sec. VIII, Div. 1
UG - 27 Thickness of Shells under Internal Pressure * Circumferential stress governs.
( c ) ( 1 ) Circumferential Stress in the Longitudinal Joint So, calculation for long. stress is omitted.
Material Code ASTM
Material A 516-70
Internal design pressure P kPa.g
Design temperature ℃
Inside diameter of the shell course under consideration Uncorroded mm
Inside diameter of the shell course under consideration Corroded D mm
Inside radius Corroded R mm
Maximum allowable stress value S kPa
Joint efficiency for, or the efficiency of, appropriate joint E
Corrosion allowance α mm
Minimum Required Thickness of Shell
Checks : t = ## R = -> ##
P = ## 0.385 S E = -> ##
0.6 P - 0.6
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MD - PV - 000
05. 8. 15.
ofM E C H A N I C A L D E S I G N
t =P R
+S E -
Part Shell
Code
D E S I G N D A T A
= ######
3.0
mm
α =300.0 1,253
## 14 mm used.
+300.00.85
#VALUE!->
#VALUE!
2,500
2,506
300
1,253
#VALUE!
0.85
340
300
###### 0.5 626.5
#VALUE!
3
C A L C U L A T I O N
P R E S S U R E V E S S E L : Doc. No.
Date
Revision 0
Sheet No. 0 x
ASME Sec. VIII, Div. 1
UG - 32 Formed Heads, and Sections, Pressure on Concave Side
( d ), ( e ) or ( f )
Material Code ASTM
Material A 516-70
Internal design pressure P kPa.g
Design temperature ℃Inside diameter of the head Uncorroded mm
Inside diameter of the head Corroded D mm
Inside radius Corroded R mm
Maximum allowable stress value S kPa
Joint efficiency E
Corrosion allowance α mm
Thickness reduction rate after forming rt %
Inside spherical or crown radius = D L mm
Minimum Required Thickness of Head before Forming
2:1 Ellipsoidal * UG - 32 ( d )
Check : t / L = ## -> ##
100
2 - 0.2 100 - 15
10% Dished * UG - 32 ( e )
Check : t / L = ## -> ##
100
- 0.1 100 - 15
Hemi-spherical * UG - 32 ( f )
Checks : t = ## L = -> ##
P = ## 0.665 S E = -> ##
100
2 - 0.2 100 - 15
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-> #VALUE!= ###### mm ## 14 mm used.
+ 3.0 )2 S E - 0.2 P 100 - rt 1 300.0
= (2,267
+ α )100
t = (P L
-> #VALUE!
300.0=
#VALUE!
0.885100 2,267
300.0
= ###### mm ##
###### 0.356
300
( )
3.0 )S E - 0.1 P 100 - rt 1 300.0
( +t = (0.885 P L
+ α
###### 0.002
3.0 )300.0
15
2,267
+300.01
## 14 mm used.
###### 0.002
100 - rt
1,253
#VALUE!
1
340
14 mm used.
100
#VALUE!
0.9045
)
#VALUE!->
(
C A L C U L A T I O N
= ###### mm
α =2,506
D E S I G N D A T A
t =P D
+2 S E - 0.2 P
3
2,500
2,506
300
#VALUE!
806.9
#VALUE!
MD - PV - 000
05. 8. 15.
ofM E C H A N I C A L D E S I G N
Part Head
Code
P R E S S U R E V E S S E L : Doc. No.
Date
Revision 0
Sheet No. 0 x
ASME Sec. VIII, Div. 1
UG - 27 Thickness of Shells under Internal Pressure * Circumferential stress governs.
( c ) ( 1 ) Circumferential Stress in the Longitudinal Joint So, calculation for long. stress is omitted.
Material Code ASTM
Material A 516-70
Internal design pressure P kPa.g
Design temperature ℃
Inside diameter of the shell course under consideration Uncorroded mm
Inside diameter of the shell course under consideration Corroded D mm
Inside radius Corroded R mm
Maximum allowable stress value S kPa
Joint efficiency for, or the efficiency of, appropriate joint E
Corrosion allowance α mm
Minimum Required Thickness of Shell
Checks : t = ## R = -> ##
P = ## 0.385 S E = -> ##
0.6 P - 0.6
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300
###### 0.5 364
#VALUE!
1,456
300
728
#VALUE!
0.85
340
mm used.
+300.00.85
#VALUE!->
#VALUE!
= ######
3.0
mm
α =300.0 728
## 14
Code
D E S I G N D A T A
=P R
+S E -
C A L C U L A T I O N
t
3
1,450
MD - PV - 000
05. 8. 15.
ofM E C H A N I C A L D E S I G N
Part Shell #2
P R E S S U R E V E S S E L : Doc. No.
Date
Revision 0
Sheet No. 0 x
ASME Sec. VIII, Div. 1
UG - 32 Formed Heads, and Sections, Pressure on Concave Side
( g ) Conical Sections ( Without Transition Knuckle )
Material Code ASTM
Material A 516-70
Configuration Concentric
Internal design pressure P kPa.g
Design temperature ℃Inside diameter of the shell, larger Uncorroded mm
Inside diameter of the shell, larger Corroded D mm
Inside radius Corroded R mmInside diameter of the shell, smaller Uncorroded mm
Inside diameter of the shell, smaller Corroded mm
Inside radius Corroded mm
Axial length of conical section L mm
One half apex angle Θ deg
Maximum allowable stress value S kPa
Joint efficiency for, or the efficiency of, appropriate joint E
Corrosion allowance α mm
Minimum Required Thickness of Conical Shell
Checks : Θ = < Θmax = deg -> OK !
x
2 cos Θ ( S E - 0.6 P ) 2 cos ( ) ( - 0.6 )
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MD - PV - 000
05. 8. 15.
ofM E C H A N I C A L D E S I G N
t = +
Part Conical Sec.
Code
D E S I G N D A T A
= ######
3.0+300.00.85
#VALUE!
#VALUE!
mm
α
300
1,253
340
1,450
1,456
## 14 mm used. ->
C A L C U L A T I O N
29.7
P D
29.7
2,506300.0
2,500
2,506
=
728
920
29.7
30
3
#VALUE!
0.85
P R E S S U R E V E S S E L : Doc. No.
Date
Revision 0
Sheet No. 0 x
ASME Sec. VIII, Div. 1
UG - 34 Unstayed Flat Heads and Covers
( c ) ( 2 ) Sketch ( j )
Material Code ASTM
Material A 105
Internal design pressure P kPa.g
Design temperature ℃Diameter measured as indicated in Fig. UG-34 d mm
Maximum allowable stress value S kPa
Joint efficiency for, or the efficiency of, appropriate joint E
Factor depending upon the method of attachment of head, shell dimensions C
Total Bolt load W kPa.mm2
Gasket moment arm, radial distance from bolt center to line of gasket reaction hG mm
Corrosion allowance α mm
Minimum Required Thickness of Flat Head
t = d C P / S E + 1.9 W hG / S E d3
+ α
* Operating Condition
to = / + 1.9 / ^3
+
= mm
* Gasket Seating
tg = / + 1.9 / ^3
+
= mm
t = Larger of to or tg
= mm ## mm used. -> ##
Flange Data
Diameter at location of gasket load reaction d mm t = *Std
Basic gasket seating width b0 mm **Effective gasket seating width b mm
Gasket Spiral W.,SUSGasket factor, Table 2-5.1 m
Gasket unit seating load y kPa
Nominal bolt size *Actual bolt diameter mm
Root diameter d2 mm
No. of bolts n Shell ID
Bolt spacing mm -> ###
" ", "TEMA min. / max. / mm
Total Bolt Load
* Operating Condition
W = Wm1 = H + Hp = 0.785 d2 P + ( 2 b 3.14 d m P )
= ^2
+ ( 2 ) =
* Gasket Seating
Wm2 = 3.14 b d y = =
Sb = kPa * Allowable bolt stress at design temp.
Sa = kPa * Allowable bolt stress at atmospheric temp.
Am1 = Wm1 / Sb = / =
Am2 = Wm2 / Sa = / =
Am = Larger of Am1 or Am2 = * total required cross-sectional area of bolts
Ab = π / 4 d22 n = * cross-sectional area of the bolts using the root diameter
* Ab ## Am -> ###
* Required gasket width = Ab Sa / 2 y π d = ## Gasket width, used = -> ###
W = ( Am + Ab ) Sa / 2 =
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######
136.5
#VALUE!
1
340
300
1,505
3.0
3
Code
D E S I G N D A T A
Bolted with a confined gasket Flange to Shell
MD - PV - 000
05. 8. 15.
ofM E C H A N I C A L D E S I G N
Part Flat Head
300.0 1,505
###### 50
1,505
######
1,505 0.30 0.0
Width
######
1,505
####### 1
C A L C U L A T I O N
###### #######601,244,3370.30
d
##
##
##
##
##
##
0.3
1,5
21
20.0
30
hG
50
Gasket68947.6
1
1
1,4
50
1,505
10.0
8.0
######
36
##
#
300.0
3.0
######
#VALUE!####### 1 ###### #######
1,505
3
601,244,337
##########
#######
#######
***
#VALUE!
300 8.0 3.14 1,505
#VALUE!
######
######
######
17,063
68947.6
###### 20.0
#######
1"
25.4
21.3
48
3.14 8.0 1,505
57
0.785
#######
601,244,337
2,596,510,385
1,505 3
P R E S S U R E V E S S E L : Doc. No.
Date
Revision 0
Sheet No. 0 x
ASME Sec. VIII, Div. 1
UG - 34 Unstayed Flat Heads and Covers
( c ) ( 2 ) Sketch ( p )
Material Code ASTM
Material A 105
Internal design pressure P kPa.g
Design temperature ℃
Diameter measured as indicated in Fig. UG-34 d mm
Maximum allowable stress value S kPa
Joint efficiency for, or the efficiency of, appropriate joint E
Factor depending upon the method of attachment of head, shell dimensions C
Corrosion allowance α mm
Minimum Required Thickness of Flat Head
t
t = d + α *
= / + 3.0
= mm ## mm used. -> ##
Shell ID
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3
0.25
C A L C U L A T I O N
##
#
C P / S E
1,4
50
##
##
##
d =
###### 50
###### 0.25 300.0 #VALUE! 1
300
#VALUE!
Bolted with a full-face gasket to Shell
MD - PV - 000
05. 8. 15.
ofM E C H A N I C A L D E S I G N
#VALUE!
1
340
Part Flat Head
Code
D E S I G N D A T A
P R E S S U R E V E S S E L : Doc. No.
Date
Revision 0
Sheet No. 0 x
ASME Sec. VIII, Div. 1
UG - 34 Unstayed Flat Heads and Covers
( c ) ( 2 ) Sketch ( e ) or ( f )
Material Code ASTM
Material A 105
Internal design pressure P kPa.g
Design temperature ℃
Diameter measured as indicated in Fig. UG-34 Uncorroded mm
Diameter measured as indicated in Fig. UG-34 Corroded d mm
Maximum allowable stress value S kPa
Joint efficiency for, or the efficiency of, appropriate joint E
Factor depending upon the method of attachment of head, shell dimensions C
Corrosion allowance α mm
Minimum Required Thickness of Flat Head
m = the ratio, tr / ts = / =
Where, tr Required thickness of seamless shell
ts Nominal thickness of shell
C = m = x =
t = d + α = / +
= mm ## mm used. -> ##
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3.0
#VALUE!
1
0.2
1
###### 14 ######
###### 300.0 #VALUE!
M E C H A N I C A L D E S I G N
###### 50
C P / S E 1,456
0.33 0.33 ###### ###### * min.
Code
C A L C U L A T I O N
D E S I G N D A T A
300
1450
1456
340
Welded to Shell
3
***
Part Flat Head
MD - PV - 000
05. 8. 15.
of
ts
d t
ts
d t
Sketch (e) Sketch (f)
P R E S S U R E V E S S E L : Doc. No.
Date
Revision 0
Sheet No. 0 x
ASME Sec. VIII, Div. 1
UG - 34 Unstayed Flat Heads and Covers
( c ) ( 2 ) Sketch ( a )
Material Code ASTM
Material A 105
Internal design pressure P kPa.g
Design temperature ℃
Diameter measured as indicated in Fig. UG-34 Uncorroded mm
Diameter measured as indicated in Fig. UG-34 Corroded d mm
Maximum allowable stress value S kPa
Joint efficiency for, or the efficiency of, appropriate joint E
Factor depending upon the method of attachment of head, shell dimensions C
Corrosion allowance α mm
Thickness reduction rate after forming rt %
Minimum Required Thickness of Flat Head
100
100 - r 100 - 15
= mm ## mm used. -> ##
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3.0t C P / S E +100
= ( d α ) /= ( 1,456 0.17
1456
#VALUE!
1
0.17
###### 50
3
C A L C U L A T I O N
#VALUE!
15
)1 +300.0
300
340
1450
Part Flat Head
Code
Formed & Welded to Shell
D E S I G N D A T A
MD - PV - 000
M E C H A N I C A L D E S I G N05. 8. 15.
of
ts
d t
Sketch (a)
r = 3 t min.
W.L T.L.
1 Project Sohar Refinery Project Doc. No.
2 Item No. F - 3704 Serivice Incinerator Chamber Sheet No. 1 of 1
3 Description * Design result ### Revision 0
4 Design Pressure kPa.g
5 Design Temperature ℃
6 Atm. Temp. ℃ Material ASTM Material ASTM
7 Corrosion Allowance mm at Design Temp.Sfo kPa at Design Temp.Sb kPa
8 at Atm. Temp. Sfa kPa at Atm. Temp. Sa kPa
9 Gasket Material Wm2 = b π G y kPa.mm2 Am = greater of Wm2/Sa
10 Gasket Width, N mm HP = 2 b π G m P kPa.mm2 or Wm1/Sb
11 m H = G2 π P / 4 kPa.mm2 Ab = π / 4 d2
2 n mm2
12 y kPa Wm1 = HP + H kPa.mm2 Check Ab > Am
13 b0 / b mm W = 0.5 ( Am + Ab ) SakPa.mm2
14 G mm
15 Bolt Size / Q'ty, n Required Gasket Width
16 Bolt Dia. / Root Dia., d2 mm Nr = Ab Sa / 2 y π G < N
17 Bolt Spacing mm <- * Min. / Max., TEMA /
18 HD = π B2 P / 4 hD = R + 0.5 g1 MD = HD hD
19 HG = Wm1 - H hG = 0.5 ( C - G ) MG = HG hG
20 HT = H - HD hT = 0.5 ( R + g1 + hG ) MT = HT hT
21 Mo = MD + MG + MT
22 HG = W hG = 0.5 ( C - G ) Mo' = HG hG
23
24 K = A / B h / h0
25 T F
26 Z V
27 Y f t = h =
28 U e = F / h0 * STD
29 g1 / g0 U
30 h0 = Bg0 V
31 E =
32 t hG R =
33 α = t e + 1 hT hD
34 β = 4/3 t e + 1
35 γ = α / T
36 δ = t3 / d
37 λ = γ + δ
38 mo = Mo / B g0=
39 mG = Mo' / B tn =
40 If bolt spacing exceeds 2 dB + t, mo and mG in above equations are B =
41 multiplied by ID, uncorroded
42 dB : Nominal Bolt Dia. Unit : mm
Longitudinal Hub, Longitudinal Hub,
SH = f mo / λ g12
SH = f mG / λ g12
Radial Flange Radial Flange
SR = β mo / λ t2
SR = β mG / λ t2
Tangential Flange Tangential Flange
ST = mo Y / t2 - Z SR ST = mG Y / t
2 - Z SR
Greater of 0.5( SH + SR ) Greater of 0.5( SH + SR )
or 0.5( SH + ST ) or 0.5( SH + ST )
NTES Narai Thermal Engineering Services
*HD
#VALUE!
HT
HG
g1=
####
##
##
##
######
Shell Flange
C =
G =
##
##
##
S H A P E F A C T O R S
S T R E S S F O R M U L A F A C T O R S
######
Load, kPa.mm2
#VALUE!
#VALUE!
#VALUE!
#VALUE!
W
#VALUE!
#VALUE!
#VALUE!
95
####
mm2#VALUE!
#VALUE!
#######
h0 g02
#VALUE!
4
#VALUE!
#VALUE!
#VALUE!
#VALUE!
d =
#VALUE!
#VALUE!
###### ######
#VALUE!
#VALUE!
95.000
######
#VALUE!
2 3
6
5
#VALUE!
#VALUE!#VALUE!
DF - WNFLG - 100
Allowable Stresses
D E S I G N C O N D I T I O N
G A S K E T & B O L T D E T A I L S
Flange
L O A D & B O L T C A L C U L A T I O N S
M O M E N T C A L C U L A T I O N S
#VALUE!
1
300
Bolting
S K E T C H
x
#VALUE!
#VALUE!
#VALUE!
#VALUE!
499,498,152
###mm
Operating Condition
Moment, kPa.mm2-mm
#VALUE!
#VALUE!
#VALUE!
#VALUE!
2 dB + t
Bolt Spacing
S T R E S S C A L C U L A T I O N S, unit - kPa
Allowable Stress Gasket SeatingAllowable Stress
7
1,450A =
1,456
Sfo Sfa
#VALUE!
#VALUE!
#VALUE!######
#VALUE!
#VALUE!#VALUE!
#VALUE!
1.5 Sfo
Sfo
Sfo
1.5 Sfa
Sfa
Sfa
#VALUE! #VALUE!
#VALUE!
######
######
#VALUE!
######
#VALUE!
######
#VALUE!
#VALUE!
#VALUE!
######
#VALUE!
#VALUE!
#VALUE!
#VALUE!
#VALUE!
#VALUE!
#VALUE!######
#VALUE!
######
#VALUE!
#VALUE!
3
68,948
Spiral W.,SUS
#VALUE!
#VALUE!
#VALUE!
340
30
3 #VALUE!
A 105 A 193-B7,<=2.5"
#VALUE! #VALUE!
=Lever Arm, mm
######
Operating Condition
#VALUE!
#VALUE!
######
######
Gasket Seating
#VALUE!
#VALUE!
#VALUE!
#VALUE!
##
##
##
######
######
W E L D I N G N E C K F L A N G E D E S I G N
46
43
44
45
###### ######
###### ######
14
######
#####
##
##
##
#VALUE!
####
1 Project Sohar Refinery Project Doc. No.
2 Item No. F - 3704 Serivice Incinerator Chamber* Type Loose Sheet No. 1 of 1
3 Description * Design result ### Revision 0
4 Design Pressure kPa.g
5 Design Temperature ℃
6 Atm. Temp. ℃ Material ASTM Material ASTM
7 Corrosion Allowance mm at Design Temp.Sfo kPa at Design Temp.Sb kPa
8 at Atm. Temp. Sfa kPa at Atm. Temp. Sa kPa
9 Gasket Material Wm2 = b π G y kPa.mm2 Am = greater of Wm2/Sa
10 Gasket Width, N mm HP = 2 b π G m P kPa.mm2 or Wm1/Sb
11 m H = G2 π P / 4 kPa.mm2 Ab = π / 4 d2
2 n mm2
12 y kPa Wm1 = HP + H kPa.mm2 Check Ab > Am
13 b0 / b mm W = 0.5 ( Am + Ab ) SakPa.mm2
14 G mm
15 Bolt Size / Q'ty, n Required Gasket Width
16 Bolt Dia. / Root Dia., d2 mm Nr = Ab Sa / 2 y π G < N
17 Bolt Spacing mm <- * Min. / Max., TEMA /
18 HD = π B2 P / 4 hD = 0.5 ( C - B ) MD = HD hD
19 HG = Wm1 - H hG = 0.5 ( C - G ) MG = HG hG
20 HT = H - HD hT = 0.5 ( hD + hG ) MT = HT hT
21 Mo = MD + MG + MT
22 HG = W hG = 0.5 ( C - G ) Mo' = HG hG
23
24 K = A / B h / h0
25 T FL
26 Z VL
27 Y f t = h =
28 U e = FL / h0 * STD
29 g1 / g0 U
30 h0 = Bg0 VL
31 E =
32 t hG R =
33 α = t e + 1 hT
34 β = 4/3 t e + 1 hD
35 γ = α / T
36 δ = t3 / d HD
37 λ = γ + δ g0 =
38 mo = Mo / B tn =
39 mG = Mo' / B
40 If bolt spacing exceeds 2 dB + t, mo and mG in above equations are B =
41 multiplied by ID, uncorroded
42 dB : Nominal Bolt Dia. Unit : mm
Longitudinal Hub, Longitudinal Hub,
SH = mo / λ g12
SH = mG / λ g12
Radial Flange Radial Flange
SR = β mo / λ t2
SR = β mG / λ t2
Tangential Flange Tangential Flange
ST = mo Y / t2 - Z SR ST = mG Y / t
2 - Z SR
Greater of 0.5( SH + SR ) Greater of 0.5( SH + SR )
or 0.5( SH + ST ) or 0.5( SH + ST )
NTES Narai Thermal Engineering Services
*
A 193-B7,<=2.5"
#VALUE!
#VALUE!
######
#VALUE!
#VALUE!
2 dB + t
#VALUE!
Bolt Spacing
S T R E S S C A L C U L A T I O N S, unit - kPa
Allowable Stress Gasket SeatingAllowable Stress
7
#VALUE!
#VALUE!
#VALUE!
#VALUE! ######
######
95
4
#VALUE!
5
#VALUE!
S H A P E F A C T O R S
Gasket Seating
######
###### #######
#VALUE!
#VALUE!
Operating Condition
Lever Arm, mm
######
Load, kPa.mm2
#VALUE!
Spiral W.,SUS
L O A D & B O L T C A L C U L A T I O N S
#VALUE!
#VALUE!
###### ######
68,948
#VALUE!
###### ######
#VALUE!
#VALUE!h0 g0
2 d =
2 3
3
#VALUE!
G A S K E T & B O L T D E T A I L S
6
95.000
S T R E S S F O R M U L A F A C T O R S
#VALUE!
#VALUE!
#VALUE!
DF - SOFLG - 100
Allowable Stresses
D E S I G N C O N D I T I O N
S K E T C H
x
#VALUE!
#VALUE!
#VALUE!
#VALUE!
514,706,916
1
300
Shell Flange
#VALUE!
Bolting
#VALUE!
mm2#VALUE!
#VALUE!
#VALUE!
1,450A =
1,478
Operating Condition
C =
G =
Sfo Sfa
#VALUE!
#VALUE!
#VALUE!######
#VALUE!
#VALUE!#VALUE!
#VALUE!
#VALUE!
######
1.5 Sfo
Sfo
Sfo
#VALUE!
#VALUE!
######
#VALUE!
######
#VALUE!
#VALUE!
#VALUE!
######
#VALUE!
#VALUE!
1.5 Sfa
Sfa
Sfa
#VALUE!
#VALUE!
#VALUE!
#VALUE!######
#VALUE!
#VALUE!
#VALUE!
#VALUE!
#VALUE!
#VALUE!
#VALUE!
#VALUE!
######
######
30
3 #VALUE!
Flange
A 105
#VALUE!
#VALUE!
#VALUE!
#VALUE!
#VALUE!
######
######
####
#VALUE!
Moment, kPa.mm2-mm
###
=
W
##
##
##
##
##
##
##
##
##
14
46
43
44
45
######
##########
##
##
##
g1=HT
HG
####
######
######mm
#VALUE!
340
#VALUE!
S L I P - O N F L A N G E D E S I G N
#VALUE!
M O M E N T C A L C U L A T I O N S
1 Project Sohar Refinery Project Doc. No.
2 Item No. F - 3704 Serivice Incinerator Chamber* Type Loose Sheet No. 1 of 1
3 Description * Design result ### Revision 0
4 Design Pressure kPa.g
5 Design Temperature ℃
6 Atm. Temp. ℃ Material ASTM Material ASTM
7 Corrosion Allowance mm at Design Temp.Sfo kPa at Design Temp.Sb kPa
8 at Atm. Temp. Sfa kPa at Atm. Temp. Sa kPa
9 Gasket Material Wm2 = b π G y + H'GY kPa.mm2 Am = greater of Wm2/Sa
10 HP = 2 b π G m P kPa.mm2 or Wm1/Sb
11 m H'P = ( hG / h
'G ) HP Ab = π / 4 d2
2 n mm2
12 y kPa H = G2 π P / 4 kPa.mm2 Check Ab > Am
13 b = ( C - B ) / 4 mm Wm1 = HP + H'P + H kPa.mm2 W = 0.5 ( Am + Ab ) SakPa.mm2
14 G = C - 2 hG mm H'GY = ( hG / h
'G ) b π G y
15 Bolt Size / Q'ty, n
16 Bolt Dia. / Root Dia., d2 mm Bolt Hole Dia., dh mm
17 Bolt Spacing mm <- * Min. / Max., TEMA /
18 HD = π B2 P / 4 hD = 0.5 ( C - B ) MD = HD hD
19 HT = H - HD hT = 0.5 ( hD + hG ) MT = HT hT
20 Mo = MD + MT
23 K = A / B h / h0
24 T FL t = h =
25 Z VL * STD
26 Y f
27 U e = FL / h0
28 g1 / g0 U H'G E =
29 h0 = Bg0 VL h'G
30
hG R =
hT
31 t mo = Mo / B hD
32 α = t e + 1
33 β = 4/3 t e + 1 HD
34 γ = α / T g0 =
35 δ = t3 / d tn =
36 λ = γ + δ
37 If bolt spacing exceeds 2 dB + t, mo and mG in above equations are B =
38 multiplied by ID, uncorroded
39 dB : Nominal Bolt Dia. Unit : mm
Longitudinal Hub,
SH = mo / λ g12
Radial Flange
SR = β mo / λ t2
Tangential Flange
ST = mo Y / t2 - Z SR
Greater of 0.5( SH + SR )
or 0.5( SH + ST )
Radial Stress at Bolt Circle
NTES Narai Thermal Engineering Services
*
S K E T C H
######
W######
#VALUE!
#VALUE!
#VALUE!
#VALUE!
#VALUE!=
#VALUE!
#VALUE!
#VALUE!
#VALUE!
#VALUE!
43
40
41
42
#VALUE!
95
#VALUE!
Reverse Moment, kPa.mm2-mm
h'G = #VALUE!
( A - C ) ( 2 A + C )
6 ( C + A )
Lever Arm, mm
#VALUE!
M O M E N T C A L C U L A T I O N S
Load, kPa.mm2
#VALUE!
4
Operating Condition
#VALUE!
###### ######
#VALUE!
######
######
######
#VALUE! MG HG h"G
340
30
3
#VALUE!
#VALUE!
3
68,948
Spiral W.,SUS
#VALUE!
#VALUE!
= Moment, kPa.mm2-mm
1.5 Sfo
Sfo
Sfo
#VALUE!
#VALUE!
######
######
#VALUE!
######
Sfo
#VALUE!
#VALUE!
#VALUE!######
#VALUE!
#VALUE!#VALUE!
#VALUE!
1,450A =
C =
2 dB + t
Bolt Spacing
1,478
G =
Allowable Stress
7
Operating Condition
S T R E S S C A L C U L A T I O N S, unit - kPa
######
##
##
##
##
##
##
##
##
##
14
g1= ######HT
####
x
###### #######
######
Lever Arm, mm
######
Bolting
G A S K E T & B O L T D E T A I L S
#VALUE!
6 ( B + C )=
514,706,916
###### ######
hG
( C - B ) ( 2 B + C )21
22
DF - SOFFG - 100
Allowable Stresses
D E S I G N C O N D I T I O N1
300
S H A P E F A C T O R S
hG + h'G
h"G
Flange
#VALUE!
#VALUE!
#VALUE!
#VALUE!
HG
#VALUE!
W - H=hG h
'G
#VALUE!
#VALUE!
#VALUE!
=
h0 g02
95.000
##
##
##
2 3
6
5
#VALUE!
#VALUE!
#VALUE!
#VALUE!
#VALUE!
mm2
#VALUE!
HG
####
S T R E S S F O R M U L A F A C T O R S
d =
44 Sfo #VALUE!
A 193-B7,<=2.5"
#VALUE!
######
#VALUE!
#VALUE!
#VALUE!
#VALUE!
#VALUE!
#VALUE!
#VALUE!
###### SRAD =
6 MG
t2 ( π C - n dh )
A 105
#VALUE!
#VALUE!
#VALUE!
#VALUE!
L O A D & B O L T C A L C U L A T I O N S
#VALUE!
Shell Flange
S L I P - O N, F U L L F A C E G A S K E T F L A N G E D E S I G N
1 Project Sohar Refinery Project Doc. No.
2 Item No. F - 3704 Serivice Incinerator Chamber* Type Loose Sheet No. 1 of 1
3 Description * Design result ### Revision 0
4 Design Pressure kPa.g
5 Design Temperature ℃
6 Atm. Temp. ℃ Material ASTM Material ASTM
7 Corrosion Allowance mm at Design Temp.Sfo kPa at Design Temp.Sb kPa
8 at Atm. Temp. Sfa kPa at Atm. Temp. Sa kPa
9 Gasket Material Wm2 = b π G y kPa.mm2 Am = greater of Wm2/Sa
10 Gasket Width, N mm HP = 2 b π G m P kPa.mm2 or Wm1/Sb
11 m H = G2 π P / 4 kPa.mm2 Ab = π / 4 d2
2 n mm2
12 y kPa Wm1 = HP + H kPa.mm2 Check Ab > Am
13 b0 / b mm W = 0.5 ( Am + Ab ) SakPa.mm2
14 G mm
15 Bolt Size / Q'ty, n Required Gasket Width
16 Bolt Dia. / Root Dia., d2 mm Nr = Ab Sa / 2 y π G < N
17 Bolt Spacing mm <- * Min. / Max., TEMA /
18 HD = π B2 P / 4 hD = 0.5 ( C - B ) MD = HD hD
19 HG = Wm1 - H hG = 0.5 ( C - G ) MG = HG hG
20 HT = H - HD hT = 0.5 ( hD + hG ) MT = HT hT
21 Mo = MD + MG + MT
22 HG = W hG = 0.5 ( C - G ) Mo' = HG hG
23
24 K = A / B
25
26
27 Y t =
28 * STD
29
30
31 E =
32 t hG R =
33 hT
34 hD h =
35
36 HD
37
38 mo = Mo / B
39 mG = Mo' / B g0 =
40 If bolt spacing exceeds 2 dB + t, mo and mG in above equations are B = tn =
41 multiplied by ID, uncorroded
42 dB : Nominal Bolt Dia. Unit : mm
NTES Narai Thermal Engineering Services
R I N G F L A N G E D E S I G N
Lever Arm, mm
48
S H A P E F A C T O R S
*
#VALUE!
S K E T C H
30.0
26.0g1=
######
HT
HG
95
######
###### #######
#VALUE!
#VALUE!
Moment, kPa.mm2-mm
######
#VALUE!
#VALUE!
#VALUE!
#VALUE!
95.000
43
Operating Condition
2 dB + t
mO Y
Sfo
t = ######
44
Bolt Spacing
68,948
10.00 7.97
1"
S T R E S S F O R M U L A F A C T O R S
=
1
300
Bolting
######### 17063.2
#VALUE!
#VALUE!
3
#VALUE!
Spiral W.,SUS
20.00#VALUE!
340
30
3 #VALUE!
A 105 A 193-B7,<=2.5"
###
#VALUE!
mm2
#########
x
57.0
######
DF - RFLG - 100
Allowable Stresses
D E S I G N C O N D I T I O N
Shell Flange
#########
#########
G A S K E T & B O L T D E T A I L S
Flange
L O A D & B O L T C A L C U L A T I O N S
M O M E N T C A L C U L A T I O N S
1505.1
3
#VALUE!
213.7
mm
5
#VALUE!
Gasket Seating
#VALUE!
#VALUE!
#VALUE!
#VALUE!
514,706,916
#VALUE!
6
2
19,021,440
4
25.40 21.27
Load, kPa.mm2
Operating Condition
67,820,941
#VALUE!
21.5
##
##
## 2
8.6
W
####
t =mG Y
Sfa
######
R E Q U I R E D T H I C K N E S S, unit - mm
Allowable Stress Gasket SeatingFormula
7
A =
C =
G =
######
141,478
1,450
##
##
##
##
##
##
1,5
05
1 Project Sohar Refinery Project Doc. No.
2 Item No. F - 3704 Serivice Incinerator Chamber* Type Loose Sheet No. 1 of 1
3 Description * Design result ### Revision 0
4 Design Pressure kPa.g
5 Design Temperature ℃
6 Atm. Temp. ℃ Material ASTM Material ASTM
7 Corrosion Allowance mm at Design Temp.Sfo kPa at Design Temp.Sb kPa
8 at Atm. Temp. Sfa kPa at Atm. Temp. Sa kPa
9 Gasket Material Wm2 = b π G y + H'GY kPa.mm2 Am = greater of Wm2/Sa
10 HP = 2 b π G m P kPa.mm2 or Wm1/Sb
11 m H'P = ( hG / h
'G ) HP Ab = π / 4 d2
2 n mm2
12 y kPa H = G2 π P / 4 kPa.mm2 Check Ab > Am
13 b = ( C - B ) / 4 mm Wm1 = HP + H'P + H kPa.mm2 W = 0.5 ( Am + Ab ) SakPa.mm2
14 G = C - 2 hG mm H'GY = ( hG / h
'G ) b π G y
15 Bolt Size / Q'ty, n
16 Bolt Dia. / Root Dia., d2 mm Bolt Hole Dia., dh mm
17 Bolt Spacing mm <- * Min. / Max., TEMA /
18 HD = π B2 P / 4 hD = 0.5 ( C - B ) MD = HD hD
19 HT = H - HD hT = 0.5 ( hD + hG ) MT = HT hT
20 Mo = MD + MT
23 K = A / B
24 t =
25 * STD
26 Y
27
28 H'G E =
29 h'G
30
hG R =
hT
31 t mo = Mo / B hD h =
32
33 HD
34
35
36 g0 =
37 If bolt spacing exceeds 2 dB + t, mo and mG in above equations are B = tn =
38 multiplied by ID, uncorroded
39 dB : Nominal Bolt Dia. Unit : mm
Tangential Flange
ST = mo Y / t2
Radial Stress at Bolt Circle
NTES Narai Thermal Engineering Services
Spiral W.,SUS
3
#VALUE!
#VALUE!
#VALUE!
R I N G, F U L L F A C E G A S K E T F L A N G E D E S I G N
#VALUE!#VALUE!
#VALUE!
###### SRAD =
6 MG
t2 ( π C - n dh )
#VALUE!44 Sfo #VALUE!
#VALUE!
Moment, kPa.mm2-mm=
*
1,478
g1=
6
5
#VALUE!
S H A P E F A C T O R S
S T R E S S F O R M U L A F A C T O R S
2 3
HG = #VALUE!
###### #######
Operating Condition
#VALUE!
#VALUE!
Bolting
G A S K E T & B O L T D E T A I L S
Flange
95.000
=W - H
Lever Arm, mm
######
A 105 A 193-B7,<=2.5"
DF - RFFG - 100
Allowable Stresses
D E S I G N C O N D I T I O N1
300
Shell Flange
#VALUE!
Lever Arm, mm
( A - C ) ( 2 A + C )
6 ( C + A )6 ( B + C )
Reverse Moment, kPa.mm2-mm
21
22 h"G
( C - B ) ( 2 B + C ) hG =
95
S K E T C H
######
MG
#VALUE!
h'G =
######
######
#VALUE!
#VALUE!
#VALUE!
#VALUE!
L O A D & B O L T C A L C U L A T I O N S
#VALUE!
Bolt Spacing
S T R E S S C A L C U L A T I O N S, unit - kPa
Allowable Stress
7
1,450A =
C =
Operating Condition
#VALUE!#VALUE!
2 dB + t
#######VALUE!Sfo
#VALUE!
mm2
HG
####
43
40
41
42
##
##
## ####
#VALUE!
W
######
#VALUE! #VALUE!
#VALUE!
#VALUE!
14
#VALUE!
######
######
#VALUE!HG h"G=
######
#VALUE!
4
514,706,916
###### ######
x
###### ######
M O M E N T C A L C U L A T I O N S
Load, kPa.mm2
######
hG + h'G
hG h'G
#VALUE!
G =
#VALUE!
##
##
##
##
##
##
##
##
##
######
HT
340
30
#VALUE!
#VALUE!
3
68,948
P R E S S U R E V E S S E L : Doc. No.
Date
Revision 0
Sheet No. 0 x
ASME Sec. VIII, Div. 1
UG - 27 Thickness of Shells under Internal Pressure * Circumferential stress governs.
( c ) ( 1 ) Circumferential Stress in the Longitudinal Joint So, calculation for long. stress is omitted.
Material Code KS
Material STS 304 TB E
Internal design pressure P kPa.g
Design temperature ℃Outside diameter of the tube course under consideration mm
Nominal thickness of the tube mm
Inside diameter of the tube Uncorroded mm
Inside diameter of the tube Corroded D mm
Inside radius Corroded R mm
Maximum allowable stress value S kPa
Joint efficiency for, or the efficiency of, appropriate joint E
Corrosion allowance α mm
Minimum Required Thickness of Shell
Checks : t = ## R = -> ##
P = ## 0.385 S E = -> ##
0.6 P - 0.6
Minimum Tube Wall Thickness in the Bent Portion before Bending * TEMA RCB - 2. 31 U-bend Requirements
Minimum required thickness, calculated above t mm
Outside tube diameter do mm
Mean radius of bend R mm
4 x
NTES Narai Thermal Engineering Services
19.4
300
9.7
#VALUE!
1
340
25.4
3
## 3 mm used.
+300.01
#VALUE!->
α =
Code
D E S I G N D A T A
#######t =
P R+
S E -
0
19.4
t0 = t [
MD - PV - 000
05. 8. 15.
ofM E C H A N I C A L D E S I G N
Part Tube
] = ###### [1 +4 R
do
C A L C U L A T I O N
= ######
0.0
mm
###### 0.5
300
300.0 9.7
]
= ###### mm ## 3 mm used. -> #VALUE!
1
4.85
#VALUE!
#VALUE!
25.4
37.5
25.4+
37.5
P R E S S U R E V E S S E L : Doc. No.
Date
Revision 0
Sheet No. 0 x
ASME Sec. VIII, Div. 1
UG - 27 Thickness of Shells under Internal Pressure * Circumferential stress governs.
( c ) ( 1 ) Circumferential Stress in the Longitudinal Joint So, calculation for long. stress is omitted.
Material Code KS
Material STS 304 TP E 125 A / Sch.80
Internal design pressure P kPa.g
Design temperature ℃
Inside diameter of the shell course under consideration Uncorroded mm
Inside diameter of the shell course under consideration Corroded D mm
Inside radius Corroded R mm
Maximum allowable stress value S kPa
Joint efficiency for, or the efficiency of, appropriate joint E
Corrosion allowance α mm
Minimum Required Thickness of Shell
Checks : t = ## R = -> ##
P = ## 0.385 S E = -> ##
0.6 P - 0.6
NTES Narai Thermal Engineering Services
300.0
C A L C U L A T I O N
=
300
#VALUE!
#VALUE!
1
340
######
0.0
mm
α =300.0 #VALUE!
###### 1
->
Code
D E S I G N D A T A
t =P R
+S E -
0
#VALUE!
#VALUE!
MD - PV - 000
05. 8. 15.
ofM E C H A N I C A L D E S I G N
Part Header, Inlet
###### 0.5
300
#VALUE!
#VALUE!
#VALUE!## ###### mm used.
+
P R E S S U R E V E S S E L : Doc. No.
Date
Revision 0
Sheet No. 0 x
ASME Sec. VIII, Div. 1
UG - 34 Unstayed Flat Heads and Covers
( c ) ( 2 ) Sketch ( e ) or ( f )
Material Code KS
Material STS 304
Internal design pressure P kPa.g
Design temperature ℃
Diameter measured as indicated in Fig. UG-34 Uncorroded mm
Diameter measured as indicated in Fig. UG-34 Corroded d mm
Maximum allowable stress value S kPa
Joint efficiency for, or the efficiency of, appropriate joint E
Factor depending upon the method of attachment of head, shell dimensions C
Corrosion allowance α mm
Minimum Required Thickness of Flat Head
m = the ratio, tr / ts = / =
Where, tr Required thickness of seamless shell
ts Nominal thickness of shell
C = m = x =
t = d + α = / +
= mm ## mm used. -> ##
NTES Narai Thermal Engineering Services
Code
C A L C U L A T I O N
D E S I G N D A T A
300
#VALUE!
#VALUE!
340
Welded to Shell
MD - PV - 000
05. 8. 15.
ofM E C H A N I C A L D E S I G N
Part Blind Flg, Inlet
###### 15
C P / S E ###### ###### 300.0
###### ###### ######
0.33 0.33 ###### ######
0
***
0.0
#VALUE!
1
* min. 0.2
###### 1
ts
d t
ts
d t
Sketch (e) Sketch (f)
P R E S S U R E V E S S E L : Doc. No.
Date
Revision 0
Sheet No. 0 x
ASME Sec. VIII, Div. 1
UG - 34 Unstayed Flat Heads and Covers
( c ) ( 2 ) Sketch ( p )
Material Code KS
Material STS 304
Internal design pressure P kPa.g
Design temperature ℃
Diameter measured as indicated in Fig. UG-34 d mm
Maximum allowable stress value S kPa
Joint efficiency for, or the efficiency of, appropriate joint E
Factor depending upon the method of attachment of head, shell dimensions C
Corrosion allowance α mm
Minimum Required Thickness of Flat Head
t
t = d + α
= / +
= mm ## mm used. -> ##
Shell ID
NTES Narai Thermal Engineering Services
D E S I G N D A T A
300
#VALUE!
Bolted with a full-face gasket to Shell
MD - PV - 000
05. 8. 15.
ofM E C H A N I C A L D E S I G N
#VALUE!
1
340
Part Blind Flg, Inlet
Code
###### 15
C P / S E
###### 0.25 300.0
0
0.25
0.0###### 1
C A L C U L A T I O N
##
##
##
##
###
##
##
d =
P R E S S U R E V E S S E L : Doc. No.
Date
Revision 0
Sheet No. 0 x
ASME Sec. VIII, Div. 1
UG - 34 Unstayed Flat Heads and Covers
( c ) ( 2 ) Sketch ( j )
Material Code KS
Material STS 304
Internal design pressure P kPa.g
Design temperature ℃Diameter measured as indicated in Fig. UG-34 d mm
Maximum allowable stress value S kPa
Joint efficiency for, or the efficiency of, appropriate joint E
Factor depending upon the method of attachment of head, shell dimensions C
Total Bolt load W kPa.mm2
Gasket moment arm, radial distance from bolt center to line of gasket reaction hG mm
Corrosion allowance α mm
Minimum Required Thickness of Flat Head
t = d C P / S E + 1.9 W hG / S E d3
+ α
* Operating Condition
to = / + 1.9 / ^3
+
= mm
* Gasket Seating
tg = / + 1.9 / ^3
+
= mm
t = Larger of to or tg
= mm ## mm used. -> ##
Flange Data
Diameter at location of gasket load reaction d mm t = *Std
Basic gasket seating width b0 mm
Effective gasket seating width b mm
GasketGasket factor, Table 2-5.1 m
Gasket unit seating load y kPa
Nominal Bolt Size
Actual Bolt Dia. mm
Root Dia. d2 mm
No. of Bolts n Shell ID
Total Bolt Load
* Operating Condition
W = Wm1 = H + Hp = 0.785 d2 P + ( 2 b 3.14 d m P )
= ^2
+ ( 2 ) =
* Gasket Seating
Wm2 = 3.14 b d y = =
Sb = kPa * Allowable bolt stress at design temp.
Sa = kPa * Allowable bolt stress at atmospheric temp.
Am1 = Wm1 / Sb = / =
Am2 = Wm2 / Sa = / =
Am = Larger of Am1 or Am2 = * total required cross-sectional area of bolts
Ab = π / 4 d22 n = * cross-sectional area of the bolts using the root diameter
* Ab ## Am -> ##
* Required gasket width = Ab Sa / 2 y π G = ## Gasket width, used = -> ###
W = ( Am + Ab ) Sa / 2 =
NTES Narai Thermal Engineering Services
#######
#######
######
######
######
######
3.14 ###### ######
#VALUE!
######
######
######
######
0.0
###### ######
#VALUE!
#VALUE!
#######
#######
#VALUE!
#VALUE!
***
#VALUE!
0.785 ###### 300 ###### 3.14 ###### 0 300.0
0.0
######
#VALUE!###### 1 ###### ######
######
0
0.0
1
1 ######
##
##
##
######
######
######
######
##
##
##
##
#
d
##
##
##
##
##
##
0
0.3
##
##
##
######
##
#hG
15
Gasket
Width
######
0.0###### 1
C A L C U L A T I O N
###### #######VALUE!0.30 300.0 ######
###### 15
######
######
###### 0.30 0.0
D E S I G N D A T A
300
#VALUE!
Bolted with a confined gasket Flanget to Shell
MD - PV - 000
05. 8. 15.
ofM E C H A N I C A L D E S I G N
#VALUE!
1
340
Part Blind Flg, Inlet
Code
P R E S S U R E V E S S E L : Doc. No.
Date
Revision 0
Sheet No. 0 x
ASME Sec. VIII, Div. 1
UG - 27 Thickness of Shells under Internal Pressure * Circumferential stress governs.
( c ) ( 1 ) Circumferential Stress in the Longitudinal Joint So, calculation for long. stress is omitted.
Material Code KS
Material STS 304 TP E 80 A / Sch.80
Internal design pressure P kPa.g
Design temperature ℃
Inside diameter of the shell course under consideration Uncorroded mm
Inside diameter of the shell course under consideration Corroded D mm
Inside radius Corroded R mm
Maximum allowable stress value S kPa
Joint efficiency for, or the efficiency of, appropriate joint E
Corrosion allowance α mm
Minimum Required Thickness of Shell
Checks : t = ## R = -> ##
P = ## 0.385 S E = -> ##
0.6 P - 0.6
NTES Narai Thermal Engineering Services
MD - PV - 000
05. 8. 15.
ofM E C H A N I C A L D E S I G N
t =P R
+S E -
Part Header, Outlet
Code
D E S I G N D A T A
= ######
0.0
mm
α =300.0 #VALUE!
######
## ###### mm used.
+300.01
-> #VALUE!
#VALUE!
#VALUE!
300
#VALUE!
#VALUE!
1
340
###### 0.5
300
#VALUE!
#VALUE!
0
C A L C U L A T I O N
P R E S S U R E V E S S E L : Doc. No.
Date
Revision 0
Sheet No. 0 x
ASME Sec. VIII, Div. 1
UG - 34 Unstayed Flat Heads and Covers
( c ) ( 2 ) Sketch ( e ) or ( f )
Material Code JIS
Material SUS 304
Internal design pressure P kPa.g
Design temperature ℃
Diameter measured as indicated in Fig. UG-34 Uncorroded mm
Diameter measured as indicated in Fig. UG-34 Corroded d mm
Maximum allowable stress value S kPa
Joint efficiency for, or the efficiency of, appropriate joint E
Factor depending upon the method of attachment of head, shell dimensions C
Corrosion allowance α mm
Minimum Required Thickness of Flat Head
m = the ratio, tr / ts = / =
Where, tr Required thickness of seamless shell
ts Nominal thickness of shell
C = m = x =
t = d + α = / +
= mm ## mm used. -> ##
NTES Narai Thermal Engineering Services
0.0
* min. 0.2
###### 1300.0
###### ###### ######
0.33 0.33 ###### ######
Code
###### ######
C P / S E ###### ######
Welded to Shell
MD - PV - 000
05. 8. 15.
ofM E C H A N I C A L D E S I G N
Part Blind Flg, Outlet
C A L C U L A T I O N
D E S I G N D A T A
300
#VALUE!
#VALUE!
#VALUE!
1
0
***
340
ts
d t
ts
d t
Sketch (e) Sketch (f)
P R E S S U R E V E S S E L : Doc. No.
Date
Revision 0
Sheet No. 0 x
ASME Sec. VIII, Div. 1
UG - 34 Unstayed Flat Heads and Covers
( c ) ( 2 ) Sketch ( p )
Material Code JIS
Material SUS 304
Internal design pressure P kPa.g
Design temperature ℃
Diameter measured as indicated in Fig. UG-34 d mm
Maximum allowable stress value S kPa
Joint efficiency for, or the efficiency of, appropriate joint E
Factor depending upon the method of attachment of head, shell dimensions C
Corrosion allowance α mm
Minimum Required Thickness of Flat Head
t
t = d + α
= / +
= mm ## mm used. -> ##
Shell ID
NTES Narai Thermal Engineering Services
##
##
##
d =
###### ######
C A L C U L A T I O N
C P / S E
##
##
##
##
#
###### 0.25 300.0 ###### 1 0.0
340
#VALUE!
#VALUE!
1
0.25
0
Part Blind Flg, Outlet
Code
Bolted with a full-face gasket to Shell
D E S I G N D A T A
300
MD - PV - 000
M E C H A N I C A L D E S I G N05. 8. 15.
of
P R E S S U R E V E S S E L : Doc. No.
Date
Revision 0
Sheet No. 0 x
ASME Sec. VIII, Div. 1
UG - 34 Unstayed Flat Heads and Covers
( c ) ( 2 ) Sketch ( j )
Material Code JIS
Material SUS 304
Internal design pressure P kPa.g
Design temperature ℃Diameter measured as indicated in Fig. UG-34 d mm
Maximum allowable stress value S kPa
Joint efficiency for, or the efficiency of, appropriate joint E
Factor depending upon the method of attachment of head, shell dimensions C
Total Bolt load W kPa.mm2
Gasket moment arm, radial distance from bolt center to line of gasket reaction hG mm
Corrosion allowance α mm
Minimum Required Thickness of Flat Head
t = d C P / S E + 1.9 W hG / S E d3
+ α
* Operating Condition
to = / + 1.9 / ^3
+
= mm
* Gasket Seating
tg = / + 1.9 / ^3
+
= mm
t = Larger of to or tg
= mm ## mm used. -> ##
Flange Data
Diameter at location of gasket load reaction d mm t = *Std
Basic gasket seating width b0 mm
Effective gasket seating width b mm
Gasket Spiral W.,SUSGasket factor, Table 2-5.1 m
Gasket unit seating load y kPa
Nominal Bolt Size
Actual Bolt Dia. mm
Root Dia. d2 mm
No. of Bolts n Shell Id
Total Bolt Load
* Operating Condition
W = Wm1 = H + Hp = 0.785 d2 P + ( 2 b 3.14 d m P )
= ^2
+ ( 2 ) =
* Gasket Seating
Wm2 = 3.14 b d y = =
Sb = kPa * Allowable bolt stress at design temp.
Sa = kPa * Allowable bolt stress at atmospheric temp.
Am1 = Wm1 / Sb = / =
Am2 = Wm2 / Sa = / =
Am = Larger of Am1 or Am2 = * total required cross-sectional area of bolts
Ab = π / 4 d22 n = * cross-sectional area of the bolts using the root diameter
* Ab ## Am -> ##
* Required gasket width = Ab Sa / 2 y π G = ## Gasket width, used = -> ###
W = ( Am + Ab ) Sa / 2 =
NTES Narai Thermal Engineering Services
######
######
#VALUE!
######
###### ######
#VALUE! ####### ######
#######
#######
#VALUE! #######
#VALUE!
3.14 ###### ###### 68947.6 #VALUE!
3.14 ###### 3 300.00.785 ###### 300 ######
###### Width ######
######
######
######
Gasket d
##
##
##
##
##
##
##
##
##
##
##
##
##
#
######
###### hG
######
##
##
##
3 ######
##
#
68947.6
######
###### ######
###### ###### ######
#VALUE! ###### ###### 1 ###### 0.0
###### 1 ###### 0.0
######
###### 0.30 0.0 ###### 1
#VALUE!
0
C A L C U L A T I O N
###### 0.30 300.0 ###### 1 #VALUE! ######
340
#VALUE!
#VALUE!
1
0.3
***
Part Blind Flg, Outlet
Code
Bolted with a confined gasket Flanget to Shell
D E S I G N D A T A
300
MD - PV - 000
M E C H A N I C A L D E S I G N05. 8. 15.
of
P R E S S U R E V E S S E L : Doc. No.
Date
Revision 0
Sheet No. 0 x
ASME Sec. VIII, Div. 1
UG - 45 Nozzle Neck Thickness
UW - 16 Minimum Requirements for Attachment Welds at Openings
Material Code ASTM ASTM
Material specification A 516-70 A 516-70
Internal design pressure P kPa.g kPa.g
Design temperature ℃ ℃Inside diameter Uncorroded mm mm
Inside diameter Corroded D mm Dn mm
Inside radius Corroded R mm Rn mm
Maximum allowable stress value S kPa Sn kPa
Joint efficiency E En
Corrosion allowance α mm αn mm
Nominal wall thickness Uncorroded mm mm
Wall thickness Corroded t mm tn mm
Minimum Nozzle Wall Thickness * UG - 45
UG - 45 ( a ) & UG - 27 ( c ) ( 1 )
Checks : tr1 = ## R = -> ##
P = ## 0.385 S E = -> ##
0.6 P - 0.6
UG - 45 ( b )
( 1 ) Shell or head thickness ( E = 1 ) tr2 = mm
UG - 16 ( b ) Minimum thickness tr3 = mm
( 4 ) Minimum thickness of standard wall pipe tr4 = mmLarger of tr2 or tr3 tr5 = mm
tr6 = Smaller of tr4 or tr5 = mm
-> Larger of tr1 or tr6 = mm ## mm used. -> ##
Size of Weld Required * UW - 16 ( c )
Inner Fillet Weld tmin = Smaller of 19 mm or tn or te =
tc min = Smaller of 6 mm or 0.7 tmin =
tc act = 0.7 Leg41 = -> OK !
Outer Fillet Weld tmin = Smaller of 19 mm or te or t =
tw min = 0.5 tmin =
tw act = 0.7 Leg42 = -> OK !
-> The weld is satisfactory.
## ## ##
## ##
NTES Narai Thermal Engineering Services
1,253
5.50
6.30
9.00
6.00
7.00
11.00
14
#VALUE!
0.85
3
αn =
11
+ 3.0300.0
C A L C U L A T I O N
###### 0.5 147.9
9.00
MD - PV - 000
05. 8. 15.
ofM E C H A N I C A L D E S I G N
tr1 =P Rn
+Sn En -
12.00
- N/A -
Part
Code
300
Nozzle > A1, Manhole
300
N O Z Z L EShell
D E S I G N D A T A
4.60
4.60
585.6
591.6
295.8
#VALUE!
1
3
mm
12.00
1
4.60
- N/A -
300 #VALUE!
= ######300.0 295.8
#######
340340
2,500
2,506
######
P R E S S U R E V E S S E L : Doc. No.
Date
Revision 0
Sheet No. 1 x
Code UG - 37 Reinforcements required for Openings in Shells and Formed Heads
Nozzle Placemenent Inserted
Finished diameter of circular opening = Dn d mm
Corrction factor F
Required thickness of a seamless shell or head tr mm
Required thickness of a seamless nozzle wall trn mm
Allowable stress value in tension, Nozzle Sn kPa
Allowable stress value in tension, Vessel Sv kPaStrength reduction factor, ≤ 1.0 = Sn/Sv fr1Strength reduction factor, ≤ 1.0 = Sn/Sv fr2
E1
Pad material code ASTM
Pad material specification A 516-70
Pad O.D. mm
Pad thickness te mm
Allowable stress value in reinforcing element Sp kPaStrength reduction factor, ≤ 1.0 =( lesser of Sn or Sp )/ Sv fr3 kPaStrength reduction factor, ≤ 1.0 = Sp/Sv fr4
Size of Weld Required * UW - 16 ( c )
Leg41 mm * Min.
Leg42 mm * Min.
Leg43 mm * Min.
Limit of reinforcement * UG - 40 mm * Larger of d or Rn + tn + t
Outside diameter of reinforcing element Dp mm
= A, Area required = d tr F + 2 tn tr F ( 1 - fr1 )
= mm2
= A1, Area available in shell
= Larger of d ( E1 t - F tr ) - 2 tn ( E1 t - F tr ) ( 1 - fr1 ) or 2 ( t + tn ) ( E1 t - F tr ) - 2 tn ( E1 t - F tr ) ( 1 - fr1 )
= mm2
= A2, Area available in nozzle projecting outward = Smaller of 5 ( tn - trn ) fr2 t or 2 ( tn - trn ) ( 2.5 tn + te ) fr2
= mm2
= A3, Aea available in inward nozzle = Smallest of 5 t ti fr2, 5 ti ti fr2 or 2 h ti fr2
= mm2
= A41, Area available in outward weld = outward nozzle weld = (leg)^2 fr3
= mm2
= A42, Area available in outer weld = outer element weld = (leg)^2 fr4
= mm2
= A43, Area available in inward weld = inward nozzle weld = (leg)^2 fr2
= mm2
= A5, Area available in element = ( Dp - d - 2 tn ) te fr4
= mm2
A1 + A2 + A41 + A42 + A5 = A = ## ##
NTES Narai Thermal Engineering Services
- N/A -
#VALUE!
######
######
#######
10.0
#VALUE!
#VALUE! #VALUE!######
#######
######
591.6
######
1
######
#VALUE!
- N/A -
1160.0
- N/A -
#VALUE!
591.6
#VALUE!
#VALUE!
of
8.5
7.8
######
9.0
1
1160
14
#######
D E S I G N D A T A
C A L C U L A T I O N
Nozzle > A1, ManholePart
MD - PV - 000
M E C H A N I C A L D E S I G N05. 8. 15.
t R
Dp
trn
tr
c
h ti
d
t
t
* 1 : Smaller of 2.5 t or 2.5 tn + te
* 2 : Smallest of h, 2.5 t, or 2.5 ti
Larger of
d or Rn + tn +
For nozzle wall inserted
Larger of
d or Rn + tn + t
For nozzle wall abutting
the vessel wall through the vessel wall
* 1
* 2
P R E S S U R E V E S S E L : Doc. No.
Date
Revision 0
Sheet No. 2 x
Code UG - 41 Strength of Reinforcement
Allowable Unit Stresses * UG - 45 ( c ) & UW - 15 ( c )
Fillet Weld Shear Sfs = x = kPa
Nozzle Wall Shear Sns = x = kPa
Groove Weld Tension Sgt = x = kPa
Groove Weld Shear Sgs = x = kPa
Strength of Connection Elements * Dimensions are in m.
Inner Fillet Weld Shear
(a) = π / 2 x Nozzle OD x Weld Leg x Sfs= π / 2 x x x = KN = N
Nozzle Wall Shear
(b) = π / 2 x Mean Nozzle Dia. x tn x Sns
= π / 2 x x x = KN = N
Groove Weld Tension
(c) = π / 2 x Nozzle OD x t x Sgt
= π / 2 x x x = KN = N
Outer Fillet Weld Shear
(d) = π / 2 x Pad OD x Weld Leg x Sfs
= π / 2 x x x = KN = N
Upper Groove Weld Tension
(e) = π / 2 x Nozzle OD x te x Sgt
= π / 2 x x x = KN = N
Lower Fillet Weld Shear
(f) = π / 2 x Nozzle OD x Weld Leg x Sfs
= π / 2 x x x = KN = N
Load to be carried by Welds * UG - 41 ( b ) ( 1 ) & ( 2 )
Weld Load for Strength Path 1 - 1
W1-1 = ( A2 + A5 + A41 + A42 ) Sv = KN = N
Weld Load for Strength Path 2 - 2
W2-2 = ( A2 + A3 + A41 + A43 + 2 tn t fr1 ) Sv = KN = N
Weld Load for Strength Path 3 - 3
W3-3 = ( A2 + A3 + A5 + A41 + A42 + A43 + 2 tn t fr1 ) Sv = KN = N
Total Weld Load
W = [ A - A1 + 2 tn fr1 ( E1 t - F tr ) ] Sv = KN = N
Check Strength Paths * UG - 41 ( b ) ( 1 ) & ( 2 )
Path 1-1 (d) + (b) = + = N -> ##
Load for Path 1-1 = Smaller of W1-1 or W = N
Path 2-2 (a) + (c) + (e) = + + = N -> ##
Load for Path 2-2 = Smaller of W2-2 or W = N
Path 3-3 (d) + (c) = + = N -> ##
Load for Path 3-3 = Smaller of W3-3 or W = N
-> ## ##
NTES Narai Thermal Engineering Services
#VALUE!
#VALUE! #VALUE! #VALUE!
#VALUE! #VALUE! #VALUE!
#VALUE!
#VALUE!
#VALUE! #VALUE! #VALUE! #VALUE!
#VALUE! #VALUE!
#VALUE! #VALUE!
#VALUE! #VALUE!
#VALUE! #VALUE!
#VALUE! #VALUE!
0.49 #VALUE! #VALUE!
0.7 #VALUE! #VALUE!
0.74 #VALUE! #VALUE!
0.6 #VALUE! #VALUE!
A1, ManholePart
MD - PV - 000
M E C H A N I C A L D E S I G N05. 8. 15.
of
Nozzle >
C A L C U L A T I O N
#VALUE!
0.6006 0.009 #VALUE! #VALUE! #VALUE!
0.6096 0.01 #VALUE! #VALUE!
#VALUE! #VALUE!
#VALUE!
0.6096 0.011 #VALUE! #VALUE! #VALUE!
1.16 0.009
#VALUE!
0.6096 - N/A - #VALUE! - N/A - - N/A -
0.6096 0.014
P R E S S U R E V E S S E L : Doc. No.
Date
Revision 0
Sheet No. 0 x
ASME Sec. VIII, Div. 1
UG - 45 Nozzle Neck Thickness
UW - 16 Minimum Requirements for Attachment Welds at Openings
Material Code ASTM ASTM
Material specification A 516-70 A 106-B / 1 1/2" / XX-STR
Internal design pressure P kPa.g kPa.g
Design temperature ℃ ℃Inside diameter Uncorroded mm mm
Inside diameter Corroded D mm Dn mm
Inside radius Corroded R mm Rn mm
Maximum allowable stress value S kPa Sn kPa
Joint efficiency E En
Corrosion allowance α mm αn mm
Nominal wall thickness Uncorroded mm mm
Wall thickness Corroded t mm tn mm
Minimum Nozzle Wall Thickness * UG - 45
UG - 45 ( a ) & UG - 27 ( c ) ( 1 )
Checks : tr1 = ## R = -> ##
P = ## 0.385 S E = -> ##
0.6 P - 0.6
UG - 45 ( b )
( 1 ) Shell or head thickness ( E = 1 ) tr2 = mm
UG - 16 ( b ) Minimum thickness tr3 = mm
( 4 ) Minimum thickness of standard wall pipe tr4 = mmLarger of tr2 or tr3 tr5 = mm
tr6 = Smaller of tr4 or tr5 = mm
-> Larger of tr1 or tr6 = mm ## mm used. -> ##
##
Size of Weld Required * UW - 16 ( c )
Inner Fillet Weld tmin = Smaller of 19 mm or tn or t =
tc min = Smaller of 6 mm or 0.7 tmin =
tc act = 0.7 Leg41 = -> ##
Outer Fillet Weld tmin = Smaller of 19 mm or te or t =
tw min = 0.5 tmin =
tw act = 0.7 Leg42 = -> - N/A -
-> ##
Strength cal. for welds are NOT required for this detail which conforms to Fig. UW - 16. 1, sketch ( c ) ~ ( e ).
## ## ##
## ##
NTES Narai Thermal Engineering Services
340340
2,500
2,506
######
4.60
######
300 #VALUE!
= ######300.0 #VALUE!
####### 1
######
######
######
#VALUE!
#VALUE!
#VALUE!
#VALUE!
1
3
mm
######
Code
300
Nozzle > K1 & K2
300
N O Z Z L EShell
D E S I G N D A T A
tr1 =P Rn
+Sn En -
MD - PV - 000
05. 8. 15.
ofM E C H A N I C A L D E S I G N
Part
#VALUE!
11
+ 3.0300.0
C A L C U L A T I O N
###### 0.5 #VALUE!
#VALUE!
#VALUE!
0.85
3
αn =
1,253
- N/A -
- N/A -
######
######
######
- N/A -
14
P R E S S U R E V E S S E L : Doc. No.
Date
Revision 0
Sheet No. 1 x
Code UG - 37 Reinforcements required for Openings in Shells and Formed Heads
Nozzle Placemenent Inserted
Finished diameter of circular opening = Dn d mm
Corrction factor F
Required thickness of a seamless shell or head tr mm
Required thickness of a seamless nozzle wall trn mm
Allowable stress value in tension, Nozzle Sn kPa
Allowable stress value in tension, Vessel Sv kPaStrength reduction factor, ≤ 1.0 = Sn/Sv fr1Strength reduction factor, ≤ 1.0 = Sn/Sv fr2
E1
Pad material code - N/A -
Pad material specification - N/A -
Pad O.D. mm
Pad thickness te mm
Allowable stress value in reinforcing element Sp kPaStrength reduction factor, ≤ 1.0 =( lesser of Sn or Sp )/ Sv fr3 kPaStrength reduction factor, ≤ 1.0 = Sp/Sv fr4
Size of Weld Required * UW - 16 ( c )
Leg41 mm * Min.
Leg42 mm * Min.
Leg43 mm * Min.
Limit of reinforcement * UG - 40 mm * Larger of d or Rn + tn + t
Outside diameter of reinforcing element Dp mm
= A, Area required = d tr F + 2 tn tr F ( 1 - fr1 )
= mm2
= A1, Area available in shell
= Larger of d ( E1 t - F tr ) - 2 tn ( E1 t - F tr ) ( 1 - fr1 ) or 2 ( t + tn ) ( E1 t - F tr ) - 2 tn ( E1 t - F tr ) ( 1 - fr1 )
= mm2
= A2, Area available in nozzle projecting outward = Smaller of 5 ( tn - trn ) fr2 t or 5 ( tn - trn ) fr2 tn
= mm2
= A3, Aea available in inward nozzle = Smallest of 5 t ti fr2, 5 ti ti fr2 or 2 h ti fr2
= mm2
= A41, Area available in outward weld = outward nozzle weld = (leg)^2 fr2
= mm2
= A42, Area available in outer weld = outer element weld = (leg)^2 fr4
= mm2
= A43, Area available in inward weld = inward nozzle weld = (leg)^2 fr2
= mm2
= A5, Area available in element = ( Dp - d - 2 tn ) te fr4
= mm2
A1 + A2 + A41 = A = ## ##
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M E C H A N I C A L D E S I G N05. 8. 15.
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t R
Dp
trn
tr
c
h ti
d
t
t
* 1 : Smaller of 2.5 t or 2.5 tn + te
* 2 : Smallest of h, 2.5 t, or 2.5 ti
Larger of
d or Rn + tn +
For nozzle wall inserted
Larger of
d or Rn + tn + t
For nozzle wall abutting
the vessel wall through the vessel wall
* 1
* 2
P R E S S U R E V E S S E L : Doc. No.
Date
Revision 0
Sheet No. 2 x
Code UG - 41 Strength of Reinforcement
Allowable Unit Stresses * UG - 45 ( c ) & UW - 15 ( c )
Fillet Weld Shear Sfs = x = kPa
Nozzle Wall Shear Sns = x = kPa
Groove Weld Tension Sgt = x = kPa
Groove Weld Shear Sgs = x = kPa
Strength of Connection Elements * Dimensions are in m.
Inner Fillet Weld Shear
(a) = π / 2 x Nozzle OD x Weld Leg x Sfs= π / 2 x x x = KN = N
Nozzle Wall Shear
(b) = π / 2 x Mean Nozzle Dia. x tn x Sns
= π / 2 x x x = KN = N
Groove Weld Tension
(c) = π / 2 x Nozzle OD x t x Sgt
= π / 2 x x x = KN = N
Outer Fillet Weld Shear
(d) = π / 2 x Pad OD x Weld Leg x Sfs
= π / 2 x x x = KN = N
Upper Groove Weld Tension
(e) = π / 2 x Nozzle OD x te x Sgt
= π / 2 x x x = KN = N
Lower Fillet Weld Shear
(f) = π / 2 x Nozzle OD x Weld Leg x Sfs
= π / 2 x x x = KN = N
Load to be carried by Welds * UG - 41 ( b ) ( 1 ) & ( 2 )
Weld Load for Strength Path 1 - 1
W1-1 = ( A2 + A5 + A41 + A42 ) Sv = KN = N
Weld Load for Strength Path 2 - 2
W2-2 = ( A2 + A3 + A41 + A43 + 2 tn t fr1 ) Sv = KN = N
Weld Load for Strength Path 3 - 3
W3-3 = ( A2 + A3 + A5 + A41 + A42 + A43 + 2 tn t fr1 ) Sv = KN = N
Total Weld Load
W = [ A - A1 + 2 tn fr1 ( E1 t - F tr ) ] Sv = KN = N
Check Strength Paths * UG - 41 ( b ) ( 1 ) & ( 2 )
Path 1-1 (d) + (b) = + = N -> ##
Load for Path 1-1 = Smaller of W1-1 or W = N
Path 2-2 (a) + (c) + (e) = + + = N -> ##
Load for Path 2-2 = Smaller of W2-2 or W = N
Path 3-3 (d) + (c) = + = N -> ##
Load for Path 3-3 = Smaller of W3-3 or W = N
-> ## ##
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MD - PV - 000
M E C H A N I C A L D E S I G N05. 8. 15.
of
Nozzle > K1 & K2
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