DESIGN CALCULATIONS OF HEAT EXCHANGER
Page : 36 of 136
According to ASME Code, Sec. VIII, Div. 1, Edition 2001, Addenda 2002 / TEMA "R" 7th Edition 88. Designed by : Eng. Abdel Halim Galala, Galala, Design General Manager (Assistant)
Sheet : 1 of 10 Rev. : 0
Project : Design & Fabrication of Heat Exchanger for APRC Refinery Job No. : 7443-33 Dwg. No. : 7443-33-1A, Rev. 0 Exchanger : Residue Cooler, Type : AES
Date : 4.7.2003 Location : Alex. Client : APRC
N. Integral Type (WN) Main Shell Flange Thickness (item no. 4) Flange Material, [Attached by Bolts] Design Temperature (shell side) Min. Design Metal Temperature, MDMT Bolt-up and Gasket Seating Temperature [UG-25] Assume no corrosion, C Operating Pressure (shell side) Internal Design Pressure, P (MAWP) Allowable Stress of Bolt Material (ASME (ASME SA193 Gr. B7), B7 ), SB :
Sheet : 5
Item : E-323A/B & E-514C/D [Appendix 2] [FIG. 2-4, Sketch (6a)]
ASME SA266 Clas o 302 F o F 53.6 o F 86 0.19685 INCH 241.477 PSIG 284.776 PSIG
Subjected to internal press.
25000 25000
PSIG PSIG
1760 1760
Kg/CM2G
20000
PSIG
1408
Kg/CM2G
* or at atmospheric temp./bolt-up temp. (gasket seating), SfC 20000 Allowable Stress of Nozzle neck, Vessel or Pipe wall Material ((ASME ASME SA106 Gr. B) B) : * at design temp.(operating condition), SnH 17100
PSIG
1408
Kg/CM2G
PSIG
2 1203.84 Kg/CM G
PSIG
2 1203.84 Kg/CM G
INCH
25.4
MM
28 685 482.6 6 23 12.7
MM MM MM MM MM
25.4 38 40 44
MM MM MM MM
6.35 6 5 31
MM MM MM MM
* at design temp.(operating condition), Sb * or at atmospheric temp./bolt-up temp. (gasket seating), Sa Allowable Stress of Flange Material (ASME (ASME SA266 Class 2) 2) : * at design temp.(operating condition), SfH
* or at atmospheric temp./bolt-up temp.(gasket seating), SnC
17100
o
150 C o C 12 o C 30 5 MM 2 Kg/CM G 17 2 20.0483 Kg/CM G
Kg/CM2G
[Table 1A , SubPart 1 , ASME Sec. II , Part D]
FIG. 2-4, Sketch (6a) Figure (1)
Nominal bolt dia., dB
No. of bolts
28 1
Bolt Hole, d Flange outside diameter, A Flange inside diameter, B Bolt circut diameter (B.C.D.), C = B + 2(g1 + h1+ R) [Appendix 2-3] Hup thickness at small end, go = Shell Thickness t
1.10236 26.9685 19 24.5276 0.5
INCH INCH INCH INCH
Hup thickness at back of flange, g1 (assume g1 = 2 go) go) R must not less than 1.5 the bolt hole (see TEMA Table D-5) Hup length, h (must greater than 1.5 go) [FIG. 2-4, Sketch 6] Use max. slope 1:3, h = 3.5 g0 Slope angle, Y = arc Tan [(g1-go)/h] Fillet radius, r = 0.25 g1 [but not less than 3/16"(4.7625 MM)] [FIG. MM)] [FIG. 2-4, Sketch 6, Note a] Use r h1 = r * Tan (45-Y/2) E = (A-C)/2
1 1.5 1.5748 1.73228 16.1001 0.25 0.23622 0.17768 1.22047
INCH
(Check D292 )
INCH INCH INCH INCH
Degree INCH INCH INCH INCH
DESIGN CALCULATIONS OF HEAT EXCHANGER
Page : 37 of 136
According to ASME Code, Sec. VIII, Div. 1, Edition 2001, Addenda 2002 / TEMA "R" 7th Edition 88. Designed by : Eng. Abdel Halim Galala, Galala, Design General Manager (Assistant)
Sheet : 2 of 10 Rev. : 0
Project : Design & Fabrication of Heat Exchanger for APRC Refinery Job No. : 7443-33 Dwg. No. : 7443-33-1A, Rev. 0 Exchanger : Residue Cooler, Type : AES
Date : 4.7.2003 Location : Alex. Client : APRC
Sheet : 5
Item : E-323A/B & E-514C/D
N. Integral Type (W.N.) Main Shell Flange Flange Thickness, item no. 4 (cont.) [Attached by Bolts] Nominal shell (pipe) size Pipe Schedule No. of bolts Nominal bolt dia., dB Bolt diameter at root of thread
Subjected to internal pressure 20" 30 28 INCH 1 25.4 MM 0.88189 INCH 22.4 MM
Actual cross-sectional area of each bolt, Total actual cross-sectional area of bolts, Ab
0.551 15.428
[Appendix 2] [FIG. 2-4, Sketch (6a)]
[TEMA Table D-5]
Flange outside diameter, A Flange inside diameter, B Bolt circut diameter (B.C.D.), C Gasket Details: - Flat metal, jacketed asbestos filled, iron or soft steel - Outside diameter = (B.C.D - d) - 2*13 - Inside diameter = O.D - 2N - Width, N Gasket Dimensions: Basic gasket seating width, bO = N/2 [Table 2-5.2] Since bo > 1/4 inch (6.35 MM), [Table 2-5.2] [Table 2-5.2] Effective gasket seating width, b = 0.5*SQRT(bO) Gasket Factor, m [Table 2-5.1] [Table 2-5.1] Min. Seating Stress, y Facing Sketch [Table 2-5.1] Diameter at location of gasket load reaction, G When bo is larger than 1/4", G = O.D.of gasket contact face - 2 b
INCH2 INCH2
26.9685 INCH INCH 19 24.5276 INCH
6 85 482.6 6 23
MM MM MM
22.0472 INCH 20.8661 INCH 0.59055 INCH
560 5 30 15
MM MM MM
0.29528 INCH
7.5
MM
INCH 0.2717 3.75 7600 PSIG (1a); Column II
6.90109 MM
21.5039 INCH [Appendix 2-3]
N.B. When b < 1/4", the effective gasket seating width, b = bo [Table 2-5.2] N.B. When b > 1/4", the effective gasket seating width, b = 0.5*SQRT(b 0.5*SQRT(bO)
2
355.483 MM 2 9953.53 MM
[Table 2-5.2]
535.04
Kg/CM2G
546.198 MM
DESIGN CALCULATIONS OF HEAT EXCHANGER
Page : 38 of 136
According to ASME Code, Sec. VIII, Div. 1, Edition 2001, Addenda 2002 / TEMA "R" 7th Edition 88. Designed by : Eng. Abdel Halim Galala, Galala, Design General Manager (Assistant)
Sheet : 3 of 10 Rev. : 0
Project : Design & Fabrication of Heat Exchanger for APRC Refinery Job No. : 7443-33 Dwg. No. : 7443-33-1A, Rev. 0 Exchanger : Residue Cooler, Type : AES
Date : 4.7.2003 Location : Alex.
Item : E-323A/B & E-514C/D
N. Integral Type (W.N.) (W.N.) Main Shell Flange Thickness, Thickness, item no. 4 (cont.) [Attached by Bolts] [Appendix 2-5(c)] 1. Bolt loading and size of bolts: 2 [Appendix 2-3] (a) Total hydrostatic end force, H = 0.785 G P (b) Total joint-contact surface compression load, Hp =2b*3.14GmP
Client : APRC
Sheet : 5
[Appendix 2] [FIG. 2-4, Sketch (6a)]
Subjected to internal pressure
103373 39182.8
lb lb
46889.2 Kg 17773 Kg
142556 139426
lb lb
64662.2 Kg 63242.6 Kg
25000 25000
PSIG PSIG
1760 1760
[Appendix 2-3]
(c) Min. required bolt load for operating conditions, Wm1 = H + Hp Min. required bolt load for gasket seating, Wm2 = 3.14 b G y Allowable Bolt Stress at atmospheric temp., Sa Allowable Bolt Stress at design temp., Sb
Kg/CM2G 2
Kg/CM G
[Table 1A, SubPart 1, ASME Sec. II, Part D]
(d) Total cross-sectional area of bolts at root of thread required for: - operating conditions, Am1 = Wm1 / Sb - Gasket seating, Am2 = Wm2 / Sa
5.70222 INCH 2 5.57703 INCH
2
3678.84 MM 2 3598.08 MM
2
5.70222 INCH 2 INCH 15.428 OK
2
3678.84 MM 2 9953.53 MM
142556 264128
lb lb
64662.2 Kg 119806 Kg
80701.4
lb
36605.6 Kg
39182.8
lb
17773
22671.4
lb
10283.6 Kg
[Table 2-6]
2.17768
INCH
55.3131 MM
hG = (C - G) / 2
[Table 2-6]
1.51185
INCH
38.4011 MM
hT = (R' + g1 + hG) / 2
[Table 2-6]
2.09477
INCH
53.2071 MM
1.67768
INCH
42.6131 MM
[Appendix 2-3] Total required cross-sectional of bolts, Am = the greater of Am1 & Am2
Actual bolt area Ab Since area Ab > area Am Am,, the bolts are adequately enough. (e) Flange design bolt load, W : [Appendix 2-5(d)] - For operating conditions, Wo = Wm1 [Appendix 2-5(d)] - For gasket seating, Wa = 0.5(Am + Ab) * Sa [Appendix 2-5(c)] 2. Total flange moment for design condition: Flange Loads: Hydrostatic end force on area inside flange, HD = 0.785 B2 P
2
Gasket load (flange design bolt load - total hydrostatic end force), HG
Gasket seating force
HG = Wm1 - H
Kg
Difference bet. total hydrostatic end force and the hydrostatic end force on area inside of flange,HT flange,HT
HT = H - HD Lever arms: hD = R' + 0.5 g1
Where R' = R + h1
DESIGN CALCULATIONS OF HEAT EXCHANGER
Page : 39 of 136
According to ASME Code, Sec. VIII, Div. 1, Edition 2001, Addenda 2002 / TEMA "R" 7th Edition 88. Designed by : Eng. Abdel Halim Galala, Galala, Design General Manager (Assistant)
Sheet : 4 of 10 Rev. : 0
Project : Design & Fabrication of Heat Exchanger for APRC Refinery Job No. : 7443-33 Dwg. No. : 7443-33-1A, Rev. 0 Exchanger : Residue Cooler, Type : AES
Date : 4.7.2003 Location : Alex. Client : APRC
Sheet : 5
Item : E-323A/B & E-514C/D
N. Integral Type (W.N.) (W.N.) Main Shell Flange Thickness, Thickness, item no. 4 (cont.) [Attached by Bolts] Flange Moments: [Appendix 2-3] Component of moment due to HD, MD = HD hD
175742
lb-in
2024.77 Kg-M
Component of moment due to HG, MG = HG hG
[Appendix 2-3]
59238.6
lb-in
682.503 Kg-M
Component of moment due to HT, MT = HT hT
[Appendix 2-3]
47491.3
lb-in
547.16
282472 23539.3
lb-in lb-ft
3254.43 Kg-M
264128
lb
119806
Total moment acting upon the flange, Mo Mo:: - For operating condition
[Appendix 2] [FIG. 2-4, Sketch (6a)]
Subjected to internal presure
Kg-M
[Appendix 2-6]
MO1 = MD + MG + MT
3. Total flange moment for bolt-up condition(Gasket condition (Gasket condition): condition): [Appendix 2-6]
Flange Load:
HG = WA = 0.5 (Am + Ab) * Sa
Lever Arm., hG = (C - G) / 2 Flange Moment for gasket condition, MO2 = HG hG = W A (C - G) / 2
(5)
Mo2 * (SfH / SfC ) 4. MO = The greater of MO1 or MO2 (SfH/SfC)
Kg
1.51185 INCH
38.4011 MM
399323
lb-in
4600.7
Kg-M
399323
lb-in
4600.7
Kg-M
399323
lb-in lb-ft
4600.7
Kg-M
33276.9 5. Shape constants for flange: K
From Appendix 2, FIG. 2-7.1:
A =
T = Z=
(1.0 4 7 2 0 + 1.9 4 4 8 k 2 )( k − 1)
⎡ K 2 L og og10 K ⎤ 0 . 6 6 84 8 4 5 5 . 7 1 69 6 9 0 + ⎢ ⎥ 2 K − 1 ⎣ K − 1 ⎦ 2 52 4 6 L o g K (1 + 8.5 52 K) − 1 1
10
1.3 6 1 3 6( K
1.74578 2.97106
K2 −1
U =
2
K 2 (1 + 8.5 5 2 4 6 L o g10 k ) − 1
K2 + 1
Y =
From Appendix 2, FIG. 2-7.2: From Appendix 2, FIG. 2-7.3: From Appendix 2, FIG. 2-7.6:
1.41939
B
2
− 1) ( K − 1)
g1/go ho = SQRT(B go) h/ho F V f
d = (U/V) ho go (for integral type flanges) [APPENDIX 2-3] e = F / ho (for integral type flanges) [APPENDIX 2-3]
5.71057 6.27534 2 3.08221 0.56203 0.81225 0.21166 1.02557 22.8457 INCH3 0.26353 INCH-1
3
374374 MM -1 0.01038 MM
DESIGN CALCULATIONS OF HEAT EXCHANGER
Page : 40 of 136
According to ASME Code, Sec. VIII, Div. 1, Edition 2001, Addenda 2002 / TEMA "R" 7th Edition 88. Designed by : Eng. Abdel Halim Galala, Galala, Design General Manager (Assistant)
Sheet : 5 of 10 Rev. : 0
Project : Design & Fabrication of Heat Exchanger for APRC Refinery Job No. : 7443-33 Dwg. No. : 7443-33-1A, Rev. 0 Exchanger : Residue Cooler, Type : AES
Date : 4.7.2003 Location : Alex. Client : APRC
Sheet : 5
Item : E-323A/B & E-514C/D
N. Integral Type (W.N.) (W.N.) Main Shell Flange Thickness, Thickness, item no. 4 (cont.)
[Appendix 2] [FIG. 2-4, Sketch (6a)]
Subjected to internal pressure
[Attached by Bolts]
6. Calculation of flange actual stresses Assume t Fact Factor or L =
te + 1 t ^ 3 + T d
[Appendix 2-3]
Where t = flange thickness factor e = F/ ho (for integral type flanges) e = FL/ ho (for loose type flanges) F = factor for integral type flanges T = factor involving K d = (U/V) ho go2
[Appendix 2-3] [Appendix 2-3] [Fig. 2-7.2] [Fig. 2-7.1] [Appendix 2-3]
For integral type flange, actual stresses (calculated) : [Fig. 2-4, Sketch (6a)] 2 1. a. Longitudinal hub stress, operating SH = f Mo / L g1 B (6) [Appendix 2-7(a)] 2 b. Longitudinal hub stress, seating SH = f Mo2 / L g1 B (6) [Appendix 2-7(a)]
1.45669 0.928
INCH
37
MM
-1
0.26353 INCH-1 NA 0.81225 1.74578 22.8457 INCH3
0.01038 MM
374374
MM3
23226.7
PSIG
2 1635.16 Kg/CM G
23226.7
PSIG
2 1635.16 Kg/CM G
2. a. Radial flange stress, operating SR = (1.33 t e +1) Mo / L t B (7) [Appendix 2-7(a 16135.7
2
PSIG
2 1135.96 Kg/CM G
2
PSIG
2 1135.96 Kg/CM G
PSIG
2 606.872 Kg/CM G
PSIG
2 606.872 Kg/CM G
b. Radial flange stress, seating
SR = (1.33 t e +1) Mo2 / L t B (7) [Appendix 2-7( 16135.7 2
3. a. Tangential flange stress, operating ST = (Y Mo / t B) - Z SR (8) [Appendix 2-7(a) 8620.34 b. Tangential flange stress, seating
2
ST = (Y Mo2 / t B) - Z SR (8) [Appendix 2-7(a 8620.34
4. a. Flange stress, operating
0.5 (SH + SR)
[Appendix 2-8(a)(4)]
19681.2
PSIG
2 1385.56 Kg/CM G
b. Flange stress, seating
0.5 (SH + SR)
[Appendix 2-8(a)(4)]
19681.2
PSIG
2 1385.56 Kg/CM G
5. a. Flange stress, operating
0.5 (SH + ST)
[Appendix 2-8(a)(4)]
15923.5
PSIG
2 1121.02 Kg/CM G
b. Flange stress, seating
0.5 (SH + ST)
[Appendix 2-8(a)(4)]
15923.5 PSIG 9240.05 PSIG 9037.19 PSIG 0 PSIG
6. a. Bolt stress, operating = Wm1 / Ab b. Bolt stress, seating = Wm2 / Ab 7. a. Shear stress carried by the fillet weld
1121.02 650.5 636.219 0
7. Actual Stresses (Calculated (Calculated)) Compared with Allowable Stresses [APPENDIX 2-8] 7.a. For Operating Condition : Allowable design stress of flange at operating condiotion, condiotion, Sf 20000 PSIG Allowable design stress of nozzle/vessel at operating condition, condition, Sn 17100 PSIG Assume flange thickness (without C.A), toperating 1.45669 INCH
Longitudinal Hub Stress SH1 = 1.5 Sf
[Appendix 2-8(a)(1)(b)]
30000
Longitudinal Hub Stress SH2 = 2 Sn
[Appendix 2-8(a)(1)(b)]
34200
The calculated (actual) hub stress SH < SH (min.) allowable Radial Flange Stress SR = Sf
[Appendix 2-8(a)(2)]
The calculated (actual) radial stress SR < SR allowable
Kg/CM2G 2
Kg/CM G Kg/CM2G
Kg/CM2G 1408 1203.84 Kg/CM2G 37 MM
Allowable stresses PSIG
Kg/CM2G
2
Kg/CM
Actual stresses (Calculated ) 2 Kg/CM PSIG
30000
>
23226.7
20000
>
16135.7
DESIGN CALCULATIONS OF HEAT EXCHANGER
Page : 41 of 136
According to ASME Code, Sec. VIII, Div. 1, Edition 2001, Addenda 2002 / TEMA "R" 7th Edition 88. Designed by : Eng. Abdel Halim Galala, Galala, Design General Manager (Assistant)
Sheet : 6 of 10 Rev. : 0
Project : Design & Fabrication of Heat Exchanger for APRC Refinery Job No. : 7443-33 Dwg. No. : 7443-33-1A, Rev. 0 Exchanger : Residue Cooler, Type : AES
Date : 4.7.2003 Location : Alex. Client : APRC
Sheet : 5
Item : E-323A/B & E-514C/D
N. Integral Type (W.N.) (W.N.) Main Shell Flange Thickness, Thickness, item no. 4 (cont.)
[Appendix 2] [FIG. 2-4, Sketch (6a)]
Tangential Flange Stress ST = Sf
20000
Subjected to internal pressure > 8620.34
0.5(SH + SR) = Sf < Allowable stress
20000
>
19681.2
0.5(SH + ST) = Sf < Allowable stress
20000
>
15923.5
25000
>
9240.05
[Appendix 2-8(a)(3)]
The calculated (actual) tangential stress S T < ST allowable
The calculated (actual) stress
The calculated (actual) stress Bolt stress = Wm1 / Ab The calculated (actual) stress
< Allowable stress
7.b. For Gasket Seating : 2 Kg/CM G 1408 1203.84 Kg/CM2G 37 MM
20000 PSIG 17100 PSIG 1.45669 INCH
Allowable design stress of flange at gasket seating, Sf Allowable design stress of nozzle/vessel at gasket seating, seating, Sn
Assume flange thickness (without C.A), tgasket
Allowable stresses PSIG
Longitudinal Hub Stress SH1 = 1.5 Sf
[Appendix 2-8(a)(1)(b)]
Longitudinal Hub Stress SH2 = 2 Sn
[Appendix 2-8(a)(1)(b)]
The calculated (actual) hub stress SH < SH (min.) allowable
2
Kg/CM
Actual stresses (Calculated ) 2 Kg/CM PSIG
30000 34200 30000
>
23226.7
20000
>
16135.7
20000
>
8620.34
20000
>
19681.2
The calculated (actual) stress
0.5(SH + SR) = Sf < Allowable stress
20000
>
15923.5
The calculated (actual) stress
0.5(SH + ST) = Sf < Allowable stress
25000
>
9037.19
Radial Flange Stress SR = Sf
[Appendix 2-8(a)(2)]
The calculated (actual) radial stress SR < SR allowable Tangential Flange Stress ST = Sf
[Appendix 2-8(a)(3)]
The calculated (actual) tangential stress S T < ST allowable
Bolt stress = Wm2 / Ab The calculated (actual) stress
< Allowable stress
The min. flange thickness, t = Max. (t (toperating, tgasket)
1.45669 INCH
37
MM
DESIGN CALCULATIONS OF HEAT EXCHANGER
Page : 42 of 136
According to ASME Code, Sec. VIII, Div. 1, Edition 2001, Addenda 2002 / TEMA "R" 7th Edition 88. Designed by : Eng. Abdel Halim Galala, Galala, Design General Manager (Assistant)
Sheet : 7 of 10 Rev. : 0
Project : Design & Fabrication of Heat Exchanger for APRC Refinery Job No. : 7443-33 Dwg. No. : 7443-33-1A, Rev. 0 Exchanger : Residue Cooler, Type : AES
Date : 4.7.2003 Location : Alex. Client : APRC
Sheet : 5
Item : E-323A/B & E-514C/D
N. Integral Type (W.N.) (W.N.) Main Shell Flange Thickness, Thickness, item no. 4 (cont.)
[Appendix 2] [FIG. 2-4, Sketch (6a)]
Subjected to internal pressure Since all actual stresses are less than the allowable stresses, stresses, the selection of t = 4.5 inch, is adequate. If an optimum min. thickness of flange is desired, calculations must be operated with a smaller value of t until one of the actual stresses or stress combination is approximately equal to the allowable stress even though other actual stresses are less than the allowable stress for that actual stress. Flange thickness with C.A & RF = t + 2*corrosion all. + raised face
2.04724
INCH
52
MM
Use flange thickness for construction
2.16535
INCH
55
MM
BOLT SUMMARY Factor K = A/B Gasket width, N Total required cross-sectional area of bolts Actual bolt cross-sectional area, Ab Nominal bolt dia., dB
1.41939 0.59055 5 .7 0 2 2 2 15.428 1
INCH INCH2
15 3678.84 9953.53 25.4
MM 2 MM 2 MM MM
31 20.6375 23.8125 26.9875 28.575 31.75 69.7539 44.45 52.3875 5 7 .1 5 6 3 .5 71.4375 103.035 39.8 28.575 31.75 34.925 3 8 .1 44.45
MM MM MM MM MM MM MM MM MM MM MM MM MM MM MM MM MM MM MM
1. Actual Edge distance, E from drawing = 1/2 (A - C) 1.22047 Min. Edge distance, E (for bolt size 0.75") 0.8125 Min.. Edg Min Edge e dis distan tance, ce, E (fo (forr bol boltt siz size e 7/8 7/8") ") 0.9375 0.9 375 Min. Edge distance, E (for bolt size 1") 1.0625 [TEMA Table D-5] Min. Edge distance, E (for bolt size 1-1/8") 1.125 Min. Edge distance, E (for bolt size 1-1/4") 1.25 2. Actual Bolt spacing, B from drawing 2.74622 Min. Bolt spacing, B (for bolt size 0.75") 1.75 Min.. Bol Min Boltt spa spacin cing, g, B (fo (forr bol boltt siz size e 7/8 7/8") ") 2.0625 2.0 625 Min. Bolt spacing, B (for bolt size 1") 2 .2 5 Min. Bolt spacing, B (for bolt size 1-1/8") [TEMA Table D-5] 2 .5 Min. Bolt spacing, B (for bolt size 1-1/4") 2.8125 Max. Recommended bolt spacing, Bmax = 2 dB + 6 t / (m + 0.5) [TEMA 0.5) [TEMA RCB-11.2 4 RCB-11.2 4.05651 3. Actual Radial distance, Rh from drawing = (C-B)/2-(g1+h1 (C-B)/2-(g1+h1)) 1.56693 Min. Radial distance, Rh (for bolt size 0.75") 1.125 Min. Radial distance, Rh (for bolt size 7/8") 1.25 Min. Radial distance, Rh (for bolt size 1") 1.375 Min. Radial distance, Rh (for bolt size 1-1/8") [TEMA Table D-5] 1 .5 Min. Radial distance, Rh (for bolt size 1-1/4") 1.75
INCH2 INCH INCH
INCH INCH IN CH INCH INCH INCH INCH INCH INCH IN CH INCH INCH INCH INCH INCH INCH INCH INCH INCH INCH
DESIGN CALCULATIONS OF HEAT EXCHANGER
Page : 43 of 136
According to ASME Code, Sec. VIII, Div. 1, Edition 2001, Addenda 2002 / TEMA "R" 7th Edition 88. Designed by : Eng. Abdel Halim Galala, Galala, Design General Manager (Assistant)
Sheet : 8 of 10 Rev. : 0
Project : Design & Fabrication of Heat Exchanger for APRC Refinery Job No. : 7443-33 Dwg. No. : 7443-33-1A, Rev. 0 Exchanger : Residue Cooler, Type : AES
Date : 4.7.2003 Location : Alex. Client : APRC
N. Integral Type (W.N.) (W.N.) Main Shell Flange Thickness, Thickness, item no. 4 (cont.) FLANGE FACTORS (a) For Integral Flanges E F = Factor F per Fig. 2-7.2 is then solved by C (1 + A ) 6
3
[
2.7 3
]
1 / 4
Sheet : 5
Item : E-323A/B & E-514C/D [Appendix 2] [FIG. 2-4, Sketch (6a)]
Subjected to internal pressure 0.81225
C
E4 2.73 1 / 4 [ ] (1 + A ) 3 C
Factor V per Fig. 2-7.3 is then solved by
V =
Factor f per Fig. 2-7.6 is then solved by
f = C36 / (1 + A)
0.21166
1.02557
h/SQRT(BG 0.562026971
The values used in the above equations are solved using Eqs. (1) through (45) below based on the valuesg values g1, g0, h and ho as defined by 2-3. When g1 = go, F = 0.908920, V = 0.550103, and f = 1; 1; thus Eqs. (1) through (45) need not be solved. (b) For Loose Hub Flanges Factor FL per Fig. 2-7.4 is solved by ⎛ 1 + ⎝ 2
C 1 8 ⎜ F L =
A ⎞ A ⎞ A ⎞ 11A ⎞ ⎛ 1 ⎛ 1 ⎛ 1 + + − ⎟ + C 2 1 ⎜ ⎟ + C 2 4 ⎜ ⎟ − ⎜ ⎟ ⎝ 4 ⎝ 7 0 ⎝ 4 0 6 ⎠ 8 4 ⎠ 1 0 5 ⎠ 7 2 ⎠
⎛ C ⎞ ⎜ ⎟ ⎝ 2 .7 3 ⎠
1 / 4
(1 + A )
3
1.435
C
1
V L = 4
Factor VL per Fig. 2-7.5 is solved by
−
C2 4 5
⎛ 2.73 ⎞ ⎜ ⎟ ⎝ C ⎠
−
3C 21 2
− C 18
0.66229
1 / 4
(1 + A )
3
Factor f per Fig. 2-7.6 is set equal to 1. f=1 1 The values used in the above equations are solved using Eqs. (1) through (5), (7), (9), (10), (12), (14), (16), (18), (20), (23), and (26) below based on the values of g1, g0, h, and ho as defined by 2-3. go
0 .5
g1 h ho = SQRT(B go), Effective hub length B
1 INCH 1.73228 INCH 3.08221 INCH 19 INCH
(1) (2) (3)
A = (g1/go) - 1 4 C = 43.68(h/ho) C1 = 1/3 + A/12
1 4.35824 0.41667
(4)
C2 = 5/42 + 17 A / 336
0.16964
(5)
C3 = 1/210 + A/360
0.00754
(6)
C4 = 11/360 + 59 A/5040 + (1+3 A)/C
(7)
3
C5 = 1/90 + 5 A/1008 - (1+ A) /C
0.96006 -1.81953
INCH
1 2 .7
MM
25.4 44 78.2881 482.6
MM MM MM MM
DESIGN CALCULATIONS OF HEAT EXCHANGER
Page : 44 of 136
According to ASME Code, Sec. VIII, Div. 1, Edition 2001, Addenda 2002 / TEMA "R" 7th Edition 88. Designed by : Eng. Abdel Halim Galala, Galala, Design General Manager (Assistant)
Sheet : 9 of 10 Rev. : 0
Project : Design & Fabrication of Heat Exchanger for APRC Refinery Job No. : 7443-33 Dwg. No. : 7443-33-1A, Rev. 0 Exchanger : Residue Cooler, Type : AES
Date : 4.7.2003 Location : Alex. Client : APRC
Sheet : 5
Item : E-323A/B & E-514C/D
N. Integral Type (W.N.) (W.N.) Main Shell Flange Thickness, Thickness, item no. 4 (cont.) FLANGE FACTORS (CONT.) (8) C6 = 1/120 + 17 A /5040 +1 /C (9) (10) (11) (12) (13)
2
[Appendix 2] [FIG. 2-4, Sketch (6a)]
Subjected to internal pressure 0.24116
3
C7 = 215/2772 + 51 A/1232 + (60/7 + 225 A/14 + 75A /7 + 5 A /2)/C 2
8.80529
3
C8 = 31/6930 + 128 A/45045 + (6/7 + 15 A/7 + 12A /7 + 5 A /11)/C 2
1.19331
3
C9 = 533/30240 + 653 A/73920 + (1/2 + 33 A/14 + 39 A /28 + 25 A /84)/C 2
3
C10 = 29/3780 + 3 A/704 - (1/2 + 33 A/14 + 81 A /28 + 13 A /12)/C 2
-1.55598
3
C11 = 31/6048 + 1763 A/665280 A/665280 + (1/2 + 6 A/7 + 15 A /28 + 5 A /42)/C 2
1.06991 0.46941
3
(14)
C12 = 1/2925 + 71 A/300300 A/300300 + (8/35 + 18 A /35 + 156 A /385 + 6 A /55)/C 0.28903
(15)
C13 = 761/831600 + 937 A/1663200 A/1663200 + (1/35 + 6 A /35 + 11 A /70 + 3 A /70) 0.09326
(16)
C14 = 197/415800 + 103 A/332640 A/332640 - (1/35 + 6 A /35 + 17 A /70 + A /10)/C -0.12378
(17)
C15 = 233/831600 + 97 A/554400 + (1/35 + 3 A /35 + A /14 + 2 A /105)/C 0.04744
(18)
C16 = C1C7C12 + C2C8C3 + C3C8C2 - (C3 C7 + C8 C1 + C2 C12)
2
3
2
2
2
2
3
3
2
2 [C4C7C12 + C2C8C13 + C3C8C9 - (C13C7C3 + C8 C4 + C12C2C9)] / C16 2 [C5C7C12 + C2C8C14 + C3C8C10 - (C14C7C3 + C8 C5 + C12C2C10)] / C16 2 [C6C7C12 + C2C8C15 + C3C8C11 - (C15C7C3 + C8 C6 + C12C2C11)] / C16 2 [C1C9C12 + C4C8C3 + C3C13C2 - (C3 C9 + C13C8 C1 + C12C4C2)] / C16 2 [C1C10C12 + C5C8C3 + C3C14C2 - (C3 C10 + C14C8 C1 + C12C5C2)] / C16 2 [C1C11C12 + C6C8C3 + C3C15C2 - (C3 C11 + C15C8 C1 + C12C6C2)] / C16 2 [C1C7C13 + C2C9C3 + C4C8C2 - (C3C7C4 + C8C9 C1 + C2 C13)] / C16 2 [C1C7C14 + C2C10C3 + C5C8C2 - (C3C7C5 + C8C10 C1 + C2 C14)] / C16 2 [C1C7C15 + C2C11C3 + C6C8C2 - (C3C7C6 + C8C11 C1 + C2 C15)] / C16 1/4
0.46133
(19)
C17 =
(20)
C18 =
(21)
C19 =
(22)
C20 =
(23)
C21 =
(24)
C22 =
(25)
C23 =
(26)
C24 =
(27)
C25 =
(28)
C26 = - (C/4)
-1.02168
(29)
C27 = C20 - C17 - 5/12 + C17C26
-4.90543
(30)
C28 = C22 - C19 - 1/12 + C19C26
-1.16343
(31)
2.2676 -4.32293 0.55926 0.0956 -0.11503 0.05056 -0.13119 0.15946 -0.05919
1/2
-1.04382
3/4
C29 = - (C/4)
(32)
C30 = - (C/4)
-1.06644
(33)
C31 = 3 A/2 - C17 C30
3.91827
(34)
C32 = 1/2 - C19 C30
1.09642
(35)
C33 = 0.5 C26C32 + C28C31C29 - (0.5 C30C28 + C32C27C29)
-2.03619
(36)
C34 = 1/12 + C18 - C21 - C18C26
-8.54118
3/4
(37)
C35 = - C18 (C/4)
4.61016
(38)
C36 = (C28C35C29 - C32C34C29)/C33
2.05114
(39)
C37 = [0.5 C26C35 + C34C31C29 - (0.5 C30C34 + C35C27C29)] / C33
-2.16975
(40)
E1 = C17C36 + C18 + C19C37
-0.88522
(41)
E2 = C20C36 + C21 + C22C37
-0.02864
(42)
E3 = C23C36 + C24 + C25C37
0.01881
(43)
E4 = 1/4 + C37 /12 + C36 /4 - E3 /5 - 3E2 /2 - E1
1.50639
(44)
E5 = E1 (1/2 + A/6) + E2(1/4 + 11A/84) + E3(1/70 + A/105)
-0.60061
(45)
E6 = E5 - C36(7/120 +A/36 + 3A/C) - 1/40 - A/72 - C37(1/60 +A/120 + 1/C)
-1.67593
DESIGN CALCULATIONS OF HEAT EXCHANGER
Page : 45 of 136
According to ASME Code, Sec. VIII, Div. 1, Edition 2001, Addenda 2002 / TEMA "R" 7th Edition 88. Designed by : Eng. Abdel Halim Galala, Galala, Design General Manager (Assistant)
Sheet : 10 of 10 Rev. : 0
Project : Design & Fabrication of Heat Exchanger for APRC Refinery Job No. : 7443-33 Dwg. No. : 7443-33-1A, Rev. 0 Exchanger : Residue Cooler, Type : AES
Date : 4.7.2003 Location : Alex. Client : APRC
Sheet : 5
Item : E-323A/B & E-514C/D
N. Integral Type (W.N.) (W.N.) Main Shell Flange Thickness, Thickness, item no. 4 (cont.)
[Appendix 2] [FIG. 2-4, Sketch (6a)]
Subjected to internal pressure APPENDIX 2-3 When B < 20 g1, g1, it will be optional for the designer to substitute B1 in the formula stress SH = f * Mo /( L * g12 * B). B). 20 * g 1 B
20 19
INCH INCH
5 08 482.6
MM MM
B1 = B + g1 for loose & integral type flanges have f <1 ( the min. f permitted is 1) B1 = B + go for integral type flanges when f = > 1
20 19.5
INCH INCH
5 08 495.3
MM MM
