Blind Flange Design Calculations

DESIGN CALCULATIONS OF HEAT EXCHANGER

Page : 76 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, Design General Manager (Assistant)

Sheet : 1 of 6 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, TEMA class : R

Date : 4.7.2003 Location : Alex. Client : APRC

Sheet : 14

Item : E-323A/B & E-514C/D

P. Flat Unstayed Circular Blind Flange(Channel Cover) Thickness (item no. 22) [UG-34 & Fig. UG-34 Sketch (j)] [Attached by Bolts] Subjected to internal pressure Blind Cover Material, Clad Metal : SB171 UNS No. C63000 ASME SA266 Class 2 Stud bolt material SA 193 Grade B7 o o F C Design Temperature 140 60 o o Min. Design Metal Temperature, MDMT F C 53.6 12 o o F C Bolt-up and Gasket Seating Temperature 86 30 Assume corrosion allowance, C [UG-25] 0.19685 INCH 5 MM Kg/CM2G Operating Pressure (tube side) 56.8182 PSIG 4 Internal Design Pressure, P (MAWP) 71.7082 PSIG 5.04826 Kg/CM2G Allowable Stress of Bolt Material, SB : 25000 25000

PSIG PSIG

1760 1760

Kg/CM2G

20000

PSIG

1408

Kg/CM2G

* or at atmospheric temp./bolt-up temp. (gasket seating), SfC [Table 1A , SubPart 1 , ASME Sec. II , Part D] Joint efficiency, E

20000

PSIG

1408

Kg/CM2G

Bolt Hole, Flange outside diameter, A Bolt circut diameter (B.C.D.),

1.10236 26.9685 24.5276

INCH INCH INCH

28 685 623

MM MM MM

INCH

25.4

MM

INCH2

355.4832 9953.528 563 482.6

MM2

* at design temp.(operating condition), Sb * or at atmospheric temp./bolt-up temp. (gasket seating), Sa Allowable Stress of Flange Material : * at design temp.(operating condition), SfH

Kg/CM2G

1

Fig. UG-34, Sketch (j) Figure (5)

No. of bolts Nominal bolt dia., dB Actual cross-sectional area of each bolt, Total actual cross-sectional area of bolts, Ab Flange face outer diameter Flange face inner diameter

28 1 [TEMA Table D-5]

0.551 15.428 22.1654 19

2

INCH INCH INCH

MM2

MM MM

DESIGN CALCULATIONS OF HEAT EXCHANGER

Page : 77 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, Design General Manager (Assistant)

Sheet : 2 of 6 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, TEMA class : R

Date : 4.7.2003 Location : Alex. Client : APRC

Sheet : 14

Item : E-323A/B & E-514C/D

P. Flat Unstayed Circular Blind Flange (Channel Cover) Thickness (item no. 22) (cont.) [Attached by Bolts] [UG-34 & Fig. UG-34 Sketch (j)] Gasket Details: - Flat metal, jacketed asbestos filled, soft copp[er or brass - Outside diameter - Inside diameter = O.D - 2N - Width, N Gasket Dimensions: Basic gasket seating width, bO = N/2 [Table 2-5.2] Since bo > 1/4 ", Effective gasket seating width, b = 0.5 SQRT(bO) [Table [Table 2-5.1] Gasket Factor, m Min. Seating Stress, y [Table 2-5.1] Facing Sketch [Table 2-5.1]

0.125 22.0472 20.8661 0.59055

INCH INCH INCH INCH

3.175 560 530 15

MM MM MM MM

0.29528

INCH

7.5

MM

0.2717 INCH 3.5 6500 PSIG (1a); Column II

6.901087 MM

21.5039

INCH

546.1978 MM

Factor depending upon method of attachment of head, C [Fig. UG-34, Sketch (j)] 0.3 Gasket moment arm, hG = (B.C.D - d)/2 = (C-G)/2 [Table 2-5.2] 1.51185

INCH

38.40109 MM

Diameter at location of gasket load reaction, d ( d represnts G ) When bo is larger than 1/4", d = O.D.of gasket contact face - 2 b [Appendix 2-3]

457.6

Kg/CM2G

Calculating the Min. required Thickness of Blind Flange, t: [UG-34(c)(2)] t = d CP/SE +1.9W hG /SEd3 When using this formula, the thickness t shall be calculated for both operating conditions, and gasket seating, and the greater of the two values shall be used.

SA 193 Grade B7 o F 100 140 PSI 25000 ? ASME SA266 Class 2 o F 100 140 PSI 20000 ?

150 25000 200 20000

DESIGN CALCULATIONS OF HEAT EXCHANGER

Page : 78 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, Design General Manager (Assistant)

Sheet : 3 of 6 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, TEMA class : R

Date : 4.7.2003 Location : Alex. Client : APRC

Sheet : 14

Item : E-323A/B & E-514C/D

P. Flat Unstayed Circular Blind Flange (Channel Cover) Thickness (item no. 22) (cont.) [Attached by Bolts]

[UG-34 & Fig. UG-34 Sketch (j)]

Calculating the total bolt load, W (for circular heads): 1. For operating conditions, the value of P shall be the design pressure, and the value of S at the design temperature and W from Formula (3) of 2-5(e) shall be used. Flange Design Bolt Load for circular heads, W [Appendix 2-5(e)] For operating conditions, W = Wm1 (3) Wm1 = H + Hp = 0.785 G2P + (2b x 3.14 GmP) (1) [Appendix 2-5(e35243.2

lb

15986.05 Kg

Flange thickness

0.85602

INCH

21.74301 MM

0 20000

PSIG PSIG

0 1408

lb

54089.04 Kg

t = d CP / SE + 1.9Wh G / SEd^ 3

2. For gasket seating, P equals zero, and the values of S at atmospheric and W from Formula (4) of 2-5(e) shall be used. [UG-34(c)(2)]

P S [Appendix 2-5(e)] Flange Design Bolt Load for circular heads, W For gasket seating, W = 0.5(Am + Ab) Sa (4)

Kg/CM2G Kg/CM2G

Total required cross-sectional area of bolts, Am = Max (Am1,Am2) Required bolt load under atmospheric temp.conditions, Wm2 = 3.14bGy

(2) 119246

* Total cross-sectional area of bolts at root of thread requiired Am1 = Wm1/ Sb at operating conditions ,

1.40973

INCH2

909.4991 MM2

* Total cross-sectional area of bolts at root of thread required gasket seating, Am2 = Wm2/ Sa

4.76983

INCH2

3077.304 MM2

4.76983

INCH2

3077.304 MM2

252473

lb

114519.9 Kg

1.29857

INCH

32.98372 MM

1.29857 1.29921 2.00787

INCH INCH INCH

32.98372 MM 33 MM 51 MM

2.48031

INCH

63

Total required cross-sectional area of bolts, Am = Max (Am1,Am2) For gasket seating,

W = 0.5(Am + Ab) Sa

(4)

t = d CP / SE + 1.9Wh G / SEd^ 3

t = max. of t of operating and gasket seating Use t without corrosion allowance Use t for construction including R.F. N.B. Check which the deflection is considered a governing thickness or not. The deflection is ehe governing thickness

MM

DESIGN CALCULATIONS OF HEAT EXCHANGER

Page : 79 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, Design General Manager (Assistant)

Sheet : 4 of 6 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, TEMA class : R

Date : 4.7.2003 Location : Alex. Client : APRC

Sheet : 14

Item : E-323A/B & E-514C/D

P. Flat Unstayed Circular Blind Flange (Channel Cover) Thickness (item no. 22) (cont.) [Attached by Bolts] [UG-34 & Fig. UG-34 Sketch (j)]

CONCLUSION: FLANGE SUMMARY Flange thickness (without C.A.) Use t for construction including R.F. For a proper design of flange : 1. You have to make a check for flange deflection.

1.29857 2.04724

INCH INCH

32.98372 MM 52 MM

GASKET SUMMARY Gasket width, N Required cross-sectional of bolts, Am Actual cross-sectional area of bolts, Ab

0.59055 4.76983 15.428

INCH INCH2

15 MM 3077.304 MM2 9953.528 MM2

BOLT SUMMARY No. of bolts Size of bolt (the bolt size is represented by its actual cross-sectional area) Bolt hole dia. Total required cross-sectional area of bolts, Am Total actual cross-sectional area of bolts, Ab Actual cross-sectional area of bolt, [TEMA TABLE D-5]

28 1 1.125 4.76983 15.428 0.551

INCH2

Bolt INCH INCH INCH2 INCH2 INCH2

25.4 28.575 3077.304 9953.528 355.4832

MM MM MM2 MM2 MM2

Since the actual bolt area Ab > The required bolt area Am, the bolts are adequately enough. N.B. When using bolt with size Total required cross-sectional area of bolts, Am Total ctual cross-sectional area of bolts, Ab Actual cross-sectional area of bolt, [TEMA TABLE D-5] Since the actual bolt area Ab < The required bolt area Am, the bolts are inadequately enough. Edge distance, E from drawing = 1/2 (A - C) Min. Edge distance, E (for bolt size 0.75") Min. Edge distance, E (for bolt size 1") Min. edge distance, E (for bolt size 1-1/8") [TEMA Table D-5] Min. Edge distance, E (for bolt size 1.25")

0.75 4.76983 8.456 0.302

INCH INCH2 INCH2 INCH2

NA

1.22047 0.8125 1.0625 1.125 1.25

INCH INCH INCH INCH INCH

31 20.6375 26.9875 28.575 31.75

MM MM MM MM MM

DESIGN CALCULATIONS OF HEAT EXCHANGER

Page : 80 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, Design General Manager (Assistant)

Sheet : 5 of 6 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, TEMA class : R

Date : 4.7.2003 Location : Alex. Client : APRC

Sheet : 14

Item : E-323A/B & E-514C/D

P. Flat Unstayed Circular Blind Flange (Channel Cover) Thickness (item no. 22) (cont.) [Attached by Bolts] [UG-34 & Fig. UG-34 Sketch (j)] Actual Bolt spacing, B (c/c) from drawing 2.74622 INCH Min. Bolt spacing, B (for bolt size 0.75") 1.75 INCH Min. Bolt spacing, B (for bolt size 7/8") [TEMA Table D-5] 2.0625 INCH Min. Bolt spacing, B (for bolt size 1") 2.25 INCH Min. Bolt spacing, B (for bolt size 1-1/8") 2.5 INCH Min. Bolt spacing, B (for bolt size 1-1/4") 2.8125 INCH Max. Recommended bolt spacing, Bmax = 2 dB + 6 t / (m + 0.5) [TEMA RCB 3.94882 INCH Check for Flat Channel Cover Deflection [TEMA RCB-9.21] The effective thickness of a flat channel cover shall be the thickness at the bottom of the pass partition groove (or the face if there is no groove) minus corrosion allowance in excess of groove depth. The thickness is to be at least that required by the appropriate Code formula and thicker if required to meet proper deflection criteria. The recommended limit for channel cover deflection is: 0.03" for nominal diameters thru 24" 0.03 INCH 0.125% of nominal diameters (nominal diameter/800) for larger sizes 0.025 INCH 20 INCH Nominal diameter = Shell ID + 2 ts A method for calculating of channel cover deflection at the center, Y is: G Y = 0.0435G 3 P+0.5S B A B h G ET 3

(

Where

69.75387 44.45 52.3875 57.15 63.5 71.4375 100.3

MM MM MM MM MM MM MM

0.762 0.635 508

MM MM MM

)

G = Gasket load reaction diameter as defined by the Code 21.5039 E = Modulus of elasticity at design temperature [ASME Sec.II,Part D, TM-31460000 T = Thickness under consideration (minus groove and C.A.) 1.29921 P = Design pressure 71.7082 SB = Allowable bolting stress at design temperature (Wm1) 25000 AB =Actual total cross-sectional root area of bolts 15.428 hG = Radial distance from diameter G to bolt circle 1.51185

If the calculated deflection is greater than the recommended limit, the deflection may be reduced by acceptance methods such as: (a) Increase channel cover thickness by the cube root of the ratio of calculated deflection to the recommended limit. (b) Use of strong backs. (c) Change type of construction. Note: For single pass channels, or others in which there is no pass partition gasket seal against the channel cover, no deflection criteria need be considered.

INCH PSI INCH PSIG PSIG INCH2 INCH

546.1978 MM 2

2214784.07 Kg/CM G

33 5.04826 25000 9953.528 38.40109

MM Kg/CM2G Kg/CM2G

MM2 MM

DESIGN CALCULATIONS OF HEAT EXCHANGER

Page : 81 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, Design General Manager (Assistant)

Sheet : 6 of 6 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, TEMA class : R

Date : 4.7.2003 Location : Alex.

Client : APRC

Sheet : 14

Item : E-323A/B & E-514C/D

P. Flat Unstayed Circular Blind Flange (Channel Cover) Thickness (item no. 22) (cont.) [Attached by Bolts] [UG-34 & Fig. UG-34 Sketch (j)] The calculated deflection is

G E T3

(0.0435 G

)

0.10054

INCH

2.553795 MM

0.03

INCH

0.762

2.88948

INCH

73.39285 MM

0.00914

INCH

0.232149 MM

1.88283

INCH

47.824

0.03303

INCH

0.839054 MM

3. Recommended deflection limit

0.03

INCH

0.762

MM

4. Compare the calculated deflection with the recommended deflection

OK

The minimum thickness of channel cover at bottom of pass partition is The thickness neglecting corrosion allowance is

1.88283 1.88976

INCH INCH

47.824 48

MM MM

Conclusion : Checking of Deflection The min. thickness of channel cover to resist the internal pressure is Where the min. thickness of channel cover to avoid deflection is The min. thickness of channel cover as derived from drawings is The flange thickness increased by

1.33858 1.88976 1.9685 0.07874

INCH INCH INCH INCH

34 48 50 2

MM MM MM MM

Tthickness including groove depth ( 5 MM) Overall thickness including raised faces & groove depth

2.08661 2.48031

INCH INCH

53 63

MM MM

Max. Working Pressure, MWP at New (cold) & Operating (corroded) at New (cold) P = SE t2 /d2 c - 1.9 W hG / d3 c

104.094

PSIG

2 7.328196 Kg/CM G

104.094

PSIG

2 7.328196 Kg/CM G

Y =

3

P + 0.5 S B AB hG

The recommended deflection limit

MM

Since the calculated deflection exceeds the recommended deflection, we have to increase the flange tickness by the cubic root of the ratio of deflections, Tassumed = T +

Y =

3

Ycalculated [TEMA RCB-9.21] Yrecommended

G 0.0435 G 3 P + 0.5 S B AB hG E T3

(

)

Easier approach : 1. Assume T, 2. Find Calculated deflection

Y =

at Operating (corroded)

G 0.0435 G 3 P + 0.5 S B AB hG E T3

(

P = SE t2 /d2 c - 1.9 W hG / d3 c

)

MM