1 Tempered Water Cooler E-3107

8/12/2019 1 Tempered Water Cooler E-3107

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CLIENT : THIRUMALAI CHEMICALS LIMITED,

RANIPET

PROJECT : MA PLANT-EQPT DESIGN

ITEM : TEMPERED WATER COOLER (E-3107)

Design Code : ASME SEC VIII DIV 1-2010 / TEMA-CLASS "C"

Type as per TEMA : AEMDwg No : 0546-E3107-L1 R3

Design Doc No : PPC/TCL/Dsn-E3107 R0

1 EQUIPMENT DIMENSION

Shell Inner diameter Di= 540 mm

Tube plate to Tube plate length L = 4260 mm

Installation Horizontal

Shell volume Vs= 1.0 CuM

End connection type Tori spherical

End Connection ID DEi= 540 mm

Inner Crown Radius L = 400 mm

Inner Knuckle Radius r = 75 mm

End Connection height Hi= 140 mm

End Connection volume - 1no VDE= 0.021 CuM

Total volume V = 1.0 CuM

= 997 Litres

2 DESIGN DATA-EQUIPMENT

Design code =

ASME SEC VIII

DIV I /TEMA

CLASS C

Inspection by = -

SHELL SIDE

Service medium-Shell side = Tempered water

Specific gravity-Shell side = 1

Specific gravity considered in design-Shell side s = 1

Operating pressure PO= 3.00 Kg/Sqcm(g)

Operating temperature T = 60 Deg C

Design pressure-Internal P = 490.332 Kpa(g)

= 0.49 Mpa(g)

= 5.00 Kg/Sqcm(g)

= 71 Psi(g)

Design pressure-External Pe = Nil

Design temperature = 90 Deg C

= 194 Deg F

Hydrotest Pressure = 6.50 Kg/Sqcm(g)

Corrosion allowance CA = 3 mm

Radiography = Spot

Weld joint efficiency j = 0.85

Post weld heat treatment = No

Insulation Yes

DESIGN PRESSURE WITH STATIC HEAD

Design Pressure PD= 5.00 Kg/Sqcm(g)

Static head H = 540 mm

= 0.05 Kg/Sqcm(g)

Max design pressure Pd = 5.06 Kg/Sqcm(g)

= 72 Psi(g)

TUBE SIDE

Service medium-Tube side = Cooling water

Specific gravity-Tube side = 1

Specific gravity considered in design-Tube side s = 1

Operating pressure PO= 3.00 Kg/Sqcm(g)

MECHANICAL DESIGN OF TEMPERED WATER COOLER

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Operating temperature T = 42 Deg C

Design pressure-Internal P = 490.332 Kpa(g)

= 0.49 Mpa(g)

= 5.0 Kg/Sqcm(g)

= 71 Psi(g)

Design pressure (On Tubes)-External Pe = 72 Psi

Design temperature = 60 Deg C

= 140 Deg F

Hydrotest Pressure = 6.50 Kg/Sqcm(g)

Corrosion allowance CA = 3 mm

Radiography = Spot

Weld joint efficiency j = 0.85Weld joint efficiency on dished end jd = 1

Post weld heat treatment = No

Insulation No

DESIGN PRESSURE WITH STATIC HEAD

Design Pressure PD= 5.00 Kg/Sqcm(g)

Static head H = 540 mm

= 0.05 Kg/Sqcm(g)

Max design pressure Pd = 5.06 Kg/Sqcm(g)

= 72 Psi(g)

3 NOZZLE SCHEDULE

a ON SHELL SIDE

a Tempered water inlet N1 = 300 NB

b Tempered water outlet N2 = 300 NB

c Drain N5 = 25 NPTb ON TUBE SIDE

d Cooling water Inlet N3 = 150 NB

e Cooling water Outlet N4 = 150 NB

f Side drain N6 = 25 NPT

4 MATERIAL OF CONSTRUCTION AND ALLOWABLE STRESSES

Material

Allow. Stress,

(@Design

temp) Psi

SHELL SIDE

Shell = SA 285 Gr C 18300Nozzle neck = SA 106 Gr B 17100

Nozzle flange = SA 105 20000

TUBE SIDE

Channel Shell = SA 285 Gr C 18300

Dished end = SA 285 Gr C 18300

Tube Plate = SA 285 Gr C 18300

Channel Flange = SA 285 Gr C 18300

Channel Cover = SA 285 Gr C 18300

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Tubes =

BS 3059 Part 1

ERW 13400

Nozzle neck = SA 106 Gr B 17100

Nozzle flange = SA 105 20000

Blind flange = SA 105 20000

Coupling = SA 105 -

Note : BS 3059 PART 1 is considered to be equivalent to SA 179

5 SHELL SIDE THICKNESS CALCULATION (INTERNAL PRESSURE)-UG-27

a SHELL

Joint Efficiency, E : 0.85

Inner diameter-Corroded Dic= 546 mmMin. Shell thick, ts : ts = PRi/(SE-0.6P)+Ca

= 4.3 mm

Min shell thk reqd as per TEMA (CB 3.13) = 7.9 mm

Shell thickness as per dwg Tsi= 8 mm

Shell OD DO= 556 mm

Selected thickness is safe for the internal pressure

6 TUBE SIDE THICKNESS CALCULATION (INTERNAL PRESSURE)-UG-27

a CHANNEL SHELL

Joint Efficiency, E : 0.85

Inner diameter-Corroded Dic= 546

Min. Shell thick, ts : ts = PRi/(SE-0.6P)+Ca= 4.27 mm

Min shell thk reqd as per TEMA (RCB 3.13) = 7.9 mm

Shell thickness as per dwg 8 mm

Shell OD DO= 556 mm


TORISPHERICAL DISHED END DESIGN (UG-32)-Internal pressure

Material : = SA 285 Gr C

Inside Diameter IDde= 540 mm

Inside Diameter-Corroded IDdec= 546 mm

= 21.5 Inches

Inner Crown Radius L = 400 mm

Inner Knuckle Radius r = 75 mm

Factor L/r = 5.3

Straight flange SF = 40 mm

Factor M = (1/4)(3+(L/r)^0.5)

= 1.3

Joint Efficiency E = 1.0

Min. Dished end Thk tdmin = PLM/(2SE-0.2P) + CA

= 4.04 mm

Forming Allowance f = 1.5 mm

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Min required Dishes End Thk td = tdmin+f

= 5.54 mm

Selected thickness Tdi = 8 mm


CHANNEL COVER DESIGN (UG-34)

Flange cover material = SA 285 Gr C

Short span/cover diameter d = 556 mm

21.9 in

Corrosion allowance Ca = 3 mm0.1 in

Gasket material = G1

CAF - 3 mm thk

Gasket OD Go= 581 mm

22.9 in

Gasket ID Gi= 561 mm

22.1 in

Gasket load reaction diameter G = 565.1 mm

= 22.2 inBasic gasket seating surface width bo= 10.0 mm

0.4 in

Effective gasket seating surface width b = 0.314 in

Gasket factor m = 2

Gasket seating stress y = 1600 psi

Number of bolts Nb= 20Metric Bolt size M16

Bolt diameter Db= 16 mm

= 0.63 in

Bolt circle diameter Cb= 612 mm

= 24.09 in

Factor depending on the attachment of cover C = 0.3

Maximum allowable stress at design temp S = 18300 psi

Total hydrostatic end force H = 0.785*G^2*P

= 27935 lbs

Total joint-contact surface compression load Hp= 2b*3.14GmP

= 6306 lbs

Required bolt load for operating conditions Wm1 = H+Hp

= 34241 lbs

Required bolt load for gasket seating conditions Wm2= PI()*b*G*y

= 35082 lbs

o a cross-sec ona area o o s a roo o rea

required for operating conditions Am1= Wm1/Sb

= 1.82 sq.ino a cross-sec ona area o o s a roo o rea

required for gasket seating conditions Am2= Wm2/Sa

= 1.87 sq.in

total cross-sectional area of bolts Am= Greater of Am1 and Am2

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= 1.87 sq.incross-sec ona area o e o s usng e roo

diameter of the thread Ab= 0.22 sq.in

Flange design bolt load for operating conditions W = Wm1

= 34240.76 lbs

Flange design bolt load for gasket seating conditions W = (Am + Ab)*Sb/2

= 19607.70 lbsradial distance from gasket load reaction to the bolt

circle hG= (Cb-G)/2

= 0.92 in

Total bolt load for circular heads W = Greater of= 34240.76 lbs

Minimum cover thickness required tc= +(1.9*W*h G

= 0.96 in

= 24.48 mm

Selected thickness Tsi = 35 mm


TUBE THICKNESS CALCULATION

Tube Material =

BS 3059 Part 1

ERW

Tube OD = 25.4 mm

= 1.0 Inch

No. of Tubes = 188Joint Efficiency, E = 1

Min. Tube thick ts = PRo/(SE+0.4P)

= 0.07 mm

Tube thickness = 12 BWG

Tube thickness as per dwg Tsi= 0.109 Inch

= 2.769 mm


Tube length = 4276 mm

DESIGN OF TUBE FOR EXTERNAL PRESSURE (UG-28)

Tube OD do = 25.4 mm

Tube thickness t = 0.11 mm

Tube length Leff = 4276 mmExternal design pressure on Tube Pv = 72 Psi

Ratio LEFF/do = 168.35

Ratio do/t = 233.03

Young's modulus E = 29000000 Psi

External pressure chart to be referred = CS 1

FROM FIG G of code, Factor A = 0.015

FROM FIG CS 1 of code, Factor B = 13900 Psi

Allowable external pressure on Tube Pa = 4B/3(Dot)

= 80 Psi

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Tube thickness is safe for the external pressure

Tube sheet thickness - BendingTube Plate material SA 285 Gr C

Design Pressure P = 71.90 psi

Allow. Stress S = 18300 psi

Shell wall thk/Shell ID = 0.0148

Factor F = 1

Gasket Dia G = 590 mm

Tube Pitch Pt = 31.75 mm

Tube OD do = 25.4 mm

Ligament Eff. e = 1-((0.907)/(Pt/do)^2)

= 0.420

Tube sheet thk T = (FG/3)*(P/eS)^0.5

= 19.0 mm

Inclusive of CA & Groove

T = 19.0 mm

Thickness as per dwg T = 35 mm

Tube Plate thickness is satisfactory as per code

DESCRIPTION SYMBOL VALUE UNIT

Design Conditions

Shell side design pressure Ps= 5.06 Kg/sq.cm

= 72 Psig

Tube side design pressure Pt= 5.06 Kg/sq.cm

= 72 Psig

Shell side design temperature Ts = 90 Deg C

= 194.0 Deg F

Tube side design temperature ts = 60 Deg C

= 140.0 Deg F

Design Temperature T = 90.0 Deg C

194.0 Deg F

Shell side CA Cas= 3 mm

= 0.12 in

Tube side CA Cat= 3 mm

= 0.12 in

TUBE SIDE DATA

Tube material BS 3059 Part 1 ERW

Outside diameter Dto= 25.4 mm

= 1.00 in

Thickness Th= 12 BWG

= 0.11 in

2.77 mm

Tube Length L = 4276 mm

= 168 in

Number of tubes in the shell N = 188

Pitch pt = 32 mm

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(Triangular) = 1.3 in

Mean Tube wall metal temperature Tw= 75 Deg C

= 167.0 Deg F

SHELL SIDE DATA

Shell material CS8

SA 285 Gr.C

Shell OD DO= DO= 556.0 mm

21.9 in

Shell ID Di= Di= 540 mm

= 21.26 in

Corroded dia 22.76 inThickness Ths= 8 mm

= 0.3 in

Corroded thickness 0.43 in

Mean Shell wall metal temperature Tws= 90 Deg C

= 194 Deg F

J = 0

Maximum expansion joint inside diameter DJ= 540 mm21.3 in

Wall thickness/Shell ID Ths/Di = 0.0148

Slope (From Fig R,C,B-7.132) M = 6.67

F = 1.000

TUBESHEETS DATA

Tubesheet material SA 285 Gr C

Design metal temperature T = 60 Deg C

= 140 Deg F

Corrosion allowance (shell side) Cas= 3.0 mm

0.1 in

Pass partition grooves Pgt = 5 mm

= 0.2 in

MATING FLANGE

Flange material SA 285 Gr C

Bolt material SA 193 B7

Flange ID B = 562 mm

= 22.1 in

Flange OD A = 650 mm

25.6 in

Thickness of Hub at small end go= 8.00 mm

0.3 in

Corroded value 0.43 in

Thickness of Hub at back of flange g1= 16.0 mm

0.6 in

Corroded value 0.87

Hub length h = 5.0 mm

0.2 in

Gasket material = G1

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CAF - 3 mm thk

Basic gasket seating surface width bo= 11.1 mm

0.4 in

Effective gasket seating surface width b = 0.331 in

Gasket load reaction diameter G = 571 mm

= 22.5 in

Gasket OD Go= 581.0 mm

22.9 in

Gasket ID Gi= 561.0 mm

22.1 inGasket factor m = 2

Gasket seating stress y = 1600 psi

Number of bolts Nb= 20

Metric Bolt size M16

Bolt diameter Db= 16.00 mm

= 0.63 in

Bolt circle diameter C = 612.0 mm

= 24.09 in

Tube sheet thickness(assumed) Tts= 1 in

33 mm

EQUIVALENT DIFFERENTIAL EXPANSION PRESSURE (R,C,B-7.161)

Tube length between inner tubesheet faces Li = 4210.0 mm

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= 165.7 in

Tube length between outer tubesheet faces Lo = 4276 mm

= 168.3 in

Coefficient of thermal expansion for shell material as = 0.0001 mm/mm/Deg C

= 0.0001 in/in/Deg F

Coefficient of thermal expansion for tube material at = 0.0001 mm/mm/Deg C

= 0.0001 in/in/Deg FMean Shell wall metal temperature Tws= 90 Deg C

= 194 Deg F

Mean Tube wall metal temperature Tw= 75.0 Deg C

= 167.0 Deg FDifferential thermal growth Dl= Lo{as(Tws-70)-at(tw-70)}

= 0.3 in

= 6.4 mmElastic modulus of the shell material at mean metal

temperature Es= 21800000 psi

= 1532729 kg/sq.cmas c mo u u s o e u e ma er a a mean me a

temperature Et = 29000000 psi

= 2038951.0 kg/sq.cm

Elastic modulus of the tube sheet material at mean

metal temperature E = 21800000 psi

1532729 kg/sq.cm

Outside diameter of shell Do= 556 mm

= 103 in

Outside diameter of tube Dto= 25.4 mm= 1.0 in

Thickness of shell Ths= 8.0 mm

= 0.3 in

BWG Th= 12.0

= 2.8 mm

Value in inches = 0.1 in

Gasket load reaction diameter G = 571.0 mm

22.5 in

Spring rate of the expansion joint Sj = 1000.0

OR

= (Do-Ths)*Ths*Es/10Li

= 565666.6

(for shell without expansion joint J = 1.0

(for expansion joint) = Sj*Li/{Sj*Li+PI()*(Do-Ths)*Ths*Es}

0.0010636

J = 0

If Sj < (Do-ts)*ts*Es/10Li, then J = 0

K = Es*Ths*(Do-Ths)/(Et*th*N*(dto-th))

0.1

Fq = 0.25+(F-0.6){300*Ths*Es(G/Tts)^3/K*Li*E}^0.25

6.4 OR

6.4

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Pressure due to Diff.Thermal Expansion Pd = 4*J*Es*Ths*(Dl/Lo)/[(Do-3Ths)(1+J*K*Fq)]

0

UNCORRODED CONDITION

EQUIVALENT BOLTING PRESSURE (R,C,B-7.162)

Internal Design Pressure P = 5.06 kg/sq.cm

72 psi

Allowable bolt stress at Atm. temperature Sa = 25000 psi

1757.7 kg/sq.cm

Allowable bolt stress at design temperature S b = 18800 psi

1321.8 kg/sq.cm

Allowable flange material stress at Atm. temperature Sf = 18300 psi

1286.6 kg/sq.cm

Allowable shell stress at design Temp Ss= 18300 psi

1286.6 kg/sq.cm

Root area of bolts Ab= 2 sq.mm

0.0 sq.in

Nominal thk of shell tn= 0.3 in

(for integral flange) tx= 0.6 in

(for loose flange) 0.6 in

Minimum weld size (smaller of tnor tx) Wm= 0.3 in

Radial dist.from bolt circle to point of intersection of

hub & back of flange R = (C-B)/2-g1

0.4 inTotal Hydrostatic end force H = 0.785*G^2*P

28524.6 lbs

Gasket Load HG= W-H

8886.6 lbs

Radial distance from gasket load reaction to bolt circle hG= (C-G)/2

0.81 in

Hydrostatic end force on area inside of flange HD= 0.785*B^2*P

27632.5 lbs

Radial dist.from bolt circle to the circle on which HDacts hD= R+0.5g1

0.7 in

H-HD HT= 892.1 lbs

a a s . rom e o c rc e o e c rc e on w c Tacts hT= (R+g1+hG)/2

= 0.9 inTotal joint-contact surface compression load HP= 2b*3.14GmP

8886.6 lb

Required Bolt load for operating conditions Wm1= H + HP

37411.2 lbs

Required bolt load for gasket seating conditions Wm2= PI()*b*G*y

37370.7 lbs

Root area of bolts required for operating conditions Am1= Wm1/Sb

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2.0 sq.inoo area o o s requ re or gas e sea ng

conditions Am2= Wm2/Sa

1.5 sq.ino a cross-sec ona area req m or m ,

whichever is greater) AM= 2.0 sq.in

Actual cross-sectional area provided ( > or = Am) Aactual= 0.1 sq.in

Actual Flange Bolt load for the Operating conditions WO= Wm1

37411.2 lbsActual Flange Bolt load for the Gasket seating

conditions WG= (Am+Ab)Sa/2

25649.5 lbs

Flange design bolt (WO or WG, whichever is greater) W = 37411.2 lbs

Moment due to HD MD= HD*hD

18494.2 lb-in

Moment due to HG MG= HG*hG

7172.3 lb-in

Moment due to HT MT= HT*hT

799.0 lb-in

Moment due to Operating conditions MOO= MD+MG+MT

26465.5 lb-in

Moment due to gasket seating conditions MOG= W(C-G)/2

30194.1 lb-in

Actual moment (MOOor MOG, whichever is greater) MO= 30194.1 lb-in

A-Factor hO= (Bg0)^0.5

= 67.1 mm

= 2.6 in

Flange OD/ID Kf= 1.2

L = [txe+1)/Tk+ tx^3/d]

-371.25

Factor involving Kf Tk=

1.3

Factor involving KfFactor involving Kf U =

= 10.0

Y =

13.41

Z = (Kf 2+1)/(Kf 2-1)

= 6.92

A factor for integral type flanges FF= (-E6/((C/2.73)^0.25(1+A)^3/C)

-26.22

Hub stress correction factor f = C36/(1+A)

0.00

Factor for integral type flanges V = E4/[(2.73/C)^0.25(1+A) 3]

Kf 2[(1+8.55246Log10Kf)-

1]/[(1.04720+1.9448Kf 2)(Kf-1)]

Kf 2[(1+8.55246Log10Kf)-1]/[1.36136(Kf 2-1)(Kf-

1)]

[1/(Kf-1)]*[0.66845+5.71690[(Kf 2Log10Kf)/(Kf 2-1)]]

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-3915.76

Factor d = (U/V)*h0*g0

= 0.00 in3

Factor e = F/h0

= 0.4 in-1

Radial flange stress (for loose type flanges) SR= 0.0 psi

Tangential flange stress ST= Sf

18300.0 psi

Longitudinal hub stress (for loose type flanges) SH= 0.0 psi

Calculated Thickness of flange Tc = YMO/STB+Cas+Cat

1.2 in

31.4 mm

Actual Thickness of flange t = 32.0 mm

1.3 Inchqu va en o ng pressure w en u e s e pressure s

acting PBT= 6.2M1/F2DI

3

0.4 psiEquivalent bolting pressure when tube side pressure is

not acting PBS= 6.2M2/F2DI

3

0.4 psi

EFFECTIVE SHELL SIDE DESIGN PRESSURE (R,C,B-7.163)

Maximum expansion joint inside diameter DJ= 540.0 mm21.3 in

Shell side design pressure Ps= 71.9 psi

fS= 1-N(DTO/DI)^2

0.58

PS' = PS(-1/2)(DJ^2/DI^2-1)

PS' = 0.0 psi

PS'

Effective shell design pressure P = 0.0 psi

PBS

OR P = 0.4 psi

PS'-PBS

OR P = -0.4 psi

P = 0.4 psi

EFFECTIVE TUBE SIDE DESIGN PRESSURE (R,C,B-7.164)

f1= 1-N[(DTO-2Th)/DI]^2

0.7 psi

Pt' = PT[1+0.4JK(1.5+f1)]/(1+JKFq)

when J =0 & Pd= 0 Pt' = PT

71.9 psi

Effective tube design pressure P = Pt'-PS'+PBT

72.3 psi

TUBESHEET FORMULA BENDING (R,C,B-7.132)

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Design pressure P = 72.3 psi

Allowable design stress of the tubesheet material at

the design metal temperature S = 18300.0 psi

Tubesheet thickness Tts= (FG/3)*sqrt(P/S)

0.69 in

Tts+ pass

partition

groove depth 0.88 in

= 22.47 mm

Thickness as per dwg for extended tube plate T = 24 mm

THK AS PER DWG IS SATISFACTORY

7 NOZZLE NECK THICKNESS CHECK - UG - 45

SHELL SIDE NOZZLES

a Tempered water inlet N1 = 300 NB

No of nozzles 1

Location of nozzle On shell

Wall thk. Per UG- 45( a ) tr1 :

Nozzle neck size, = 12 NB, Inch

OD of Pipe = 323.9 mm

Material = SA 106 Gr B

Allowable stress = 17100 Psi

Joint Efficiency E = 1

Min. Nozzle thickness ta= PRo/(SE+0.4P)+Ca

= 3.68 mm= 3.7 mm

Wall thk. Per UG- 45 :

Required shell thk for internal pressure tb1= 4.3 mm

= 4.3 mm

Required shell thk for external pressure tb2= 0.0 mm

= 1.6 mm

Wall thk. Per UG- 16( b ) = 1.6 mm

Min pipe wall thk per table UG - 45 tb3= 11.34 mm

The greater of tb1 and tb2 = 4.3 mm

The lesser of tb3 and (greater of tb1 & tb2) tb= 4.30

Required per UG - 45 = Larger of ta or tb :

= 4.30 mm

Nozzle neck thickness as per dwg = Sch 40

= 10.31 mm

THICKNESS AS PER DWG SATISFIES CODE REQUIREMENT

Design Check for RF Pad

Opening size on shell d = 303.2 mm


Min. Shell thickness ts = PRo/(SE+0.4P)+CA

(When E = 1) = 4.1 mm

Minimum shell thk reqd tr = 4.1 mm

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Area required for reinforcement Ar = tr*d

= 1243.2 Sqmm

Excess thickness available in the shell = 3.9 mm

Shell dia availed for nozzle reinforcement ds = 648 mm

RF pad dia made available for reinforcement dp = 0 mm

RF pad thickness tp = 0 mm

Area available for reinforcement = (ds-d)*(Ts-tr)+(dp-d)*tp

= 1343.4 Sqmm

Area available for reinforcement is more than the area

required for reinforcement.Hence opening is

adequately reinforced.

(Note: Area available in welds and nozzle projections are not included in available area)

b Tempered water outlet N2 = 300 NB

No of nozzles 1








Factor y = 0.6

Min. Nozzle thickness tr1 = PRo/(SE+0.4P)+Ca

= 3.68 mm

= 3.7 mm


Required shell thk for internal pressure tb1= 4.3 mm= 4.3 mm

Required shell thk for external pressure tb2= 4.3 mm

= 4.3 mm



The greater of tb1 and tb2 = 4.3 mm

The lesser of tb3 and (greater of tb1 & tb2) tb= 4.30


= 4.30 mm


= 10.31 mm


Design Check for RF PadOpening size on shell d = 303.2 mm


Factor y = 0.6


(When E = 1) = 4.1 mm



= 1243.2 Sqmm

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= 1343.4 Sqmm

Area available for reinforcement is more than the area




c Drain N5 = 25 NPT

No of nozzles 1





Pipe rating = #3000

Since Nozzle size is


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Factor y = 0.6


(When E = 1) = 4.1 mm



= 631.6 Sqmm






= 711.7 SqmmArea available for reinforcement is more than the area




e Cooling water Outlet N4 = 150 NB

No of nozzles 1

Location of nozzle

On RHS

Channel



OD of Pipe = 168.3 mmMaterial = SA 106 Gr B



Factor y = 0.6

Min. Nozzle thickness tr1 = PRo/(SE+0.4P)+Ca

= 3.35 mm

= 3.4 mm


Required channel shell thk for internal pressure tb1= 4.3 mm

= 4.3 mm

Required channel shell thk for external pressure tb2= 0.0 mm

= 1.6 mm



The greater of tb1 and tb2 = 4.3 mmThe lesser of tb3 and (greater of tb1 & tb2) tb= 4.30


= 4.30 mm


= 7.11 mm



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Factor y = 0.6


(When E = 1) = 4.1 mm



= 631.6 Sqmm






= 711.7 Sqmmrea ava a e or re n orcemen s more an e area




f Side drain N6 = 25 NPT

No of nozzles 1

Location of nozzle On LHS Channel




Pipe rating = #3000Since Nozzle size is


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ON SHELL SIDE

N1 = Tempered water inlet SA 106 Gr B 4.30 10.31 Thk safe

N2 = Tempered water outlet SA 106 Gr B 4.3 10.31 Thk safe

N5 = Drain SA 106 Gr B - #3000 Thk safe

ON TUBE SIDE

N3 = Cooling water Inlet SA 106 Gr B 4.30 7.11 Thk safe

N4 = Cooling water Outlet SA 106 Gr B 4.30 7.11 Thk safe

N6 = Side drain SA 106 Gr B - #3000 Thk safe

From above, it may be noted that all available

thicknesses are more than thickness required as per

code. Hence the equipment meets code requirement.

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