ASME VIII UHX TUBESHEET CALCS
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INTEGRAL TUBESHEET OPTIMIZATION SHEET ASME VIII Div. 1 UHX RULES FOR SHELL AND TUBE HEAT EXCHANGERS U tube configuration (a),tubesheet integral both sides, with channel type hemispherical 1 A= outside diameter of tubesheet 1422.40 mm 2 r o =radius to outermost tube hole center 563.00 mm 3 d t =nominal outside diameter of tubes 19.05 mm 4 D o =equivalent diameter of outer tube limit circle 1145.05 mm 5 D S = inside diameter of shell 1411.70 mm 6 D C = inside diameter of channel 1219.20 mm 7 E=Modulus of elasticity of tubesheet at tubesh DT 1955300 bar 8 S=Allowable stress of tubesheet material at tubesh DT 1290 bar 9 E C =Modulus of elasticity of channel at channel DT 1955300 bar 10 E S =Modulus of elasticity of shell at shell DT 1955300 bar 11 E tT =Modulus of elasticity of tubes at tubesheeet DT 1955300 bar 12 S tT =Allowable stress of tubes material at tubesh DT 1290 bar 13 h= uncorroded tubesheet thickness 238.60 mm 14 h g =tube side pass partition groove depth 0.00 mm 15 c t = tubesheet corrosion allowance on the tube side/shell side 0.00 mm 16 p= tube pitch 25.4 mm 17 tube layout pattern triangular 18 l tx =expanded length of tube in tubesheet 0.00 mm 19 ʌ=tube expansion depth ratio =l tx /h 0.0000 20 h g = MAX [( h g Ͳc t ),0] 0.00 mm 21 ʅ=basic ligament efficiency for shear =(pͲd t )/p 0.25 22 t t = nominal tube wall thickness 2.413 mm 23 d*=effective tube hole diameter=max[( d t Ͳ2t t (Et T /E)(S tT /S)ʌ,d t Ͳ2t t )] 19.0500 mm 24 A total area of untubed lanes 69870 00 mm 2 24 A L = total area of untubed lanes 69870.00 mm 25 p*=effective tube pitch= p/ [1Ͳ4MIN(A L, 4D o p)/ʋD o 2 )] 1/2 26.3082 mm 26 ʅ*=effective ligament efficiency for bending=(p*Ͳd*)/p* 0.2759 27 [hͲ2c t ]/p= 9.3937 28 E*/E (function of h/p and ʅ*) = 0.2497 29 ʆ* =effective Poisson ratio of tubesh in perforated region 0.3722 30 E*= effective modulus of elas of tubesh in perforated region 488330.6622 bar 31 ʌ s =D s /D o 1.2329 32 ʌ c =D c /D o 1.0648 33 P s = shell side internal design pressure 0 bar 34 P t =tube side internal design pressure 186 bar 35 M TS =D o 2 /16 {[ (ʌ s Ͳ1)(ʌ s 2 +1)P s Ͳ(ʌ c Ͳ1)(ʌ c 2 +1)P t ]} Ͳ2106024.62 bar* mm 2 36 t s = shell thickness 16.00 mm 37 t c =channel thickness 129.56 mm 38 v s =Poisson's ratio of shell material 0.300 39 v c =Poisson's ratio of channel material 0.300 40 S c =Allowable stress of channel material at DT 1290 bar 41 S s =Allowable stress of shell material at DT 1290 bar 42 ɴ S = 4 я12(1Ͳv s 2 )/я (D s +t s )t s 0.012028 mm 1 43 k s =ɴ s E s t s 3 / 6(1Ͳv s 2 ) 1764240.933 N 44 ʄ s =[ 6D s k s /(hͲc t )3] [1+(hͲc t ) ɴ s +(hͲc t ) 2 ɴ s 2 /2] 8787.260 N/mm 2 45 ɷ s =D s 2 /4E s t s [1Ͳv s /2] 0.135366 mm 3 /N 46 ʘ s = ʌ s k s ɴ s ɷ s[ 1+(hͲc t )ɴ s ] 13704.07537 mm 2 PStylianopoulos Pressure Vessel Engineer Page 1 of 3, 9/29/2011
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ASME VIII UHX TUBESHEET CALC TABLE
Transcript of ASME VIII UHX TUBESHEET CALCS
INTEGRAL TUBESHEET OPTIMIZATION SHEET ASME VIII Div. 1 UHX RULES FOR SHELL AND TUBE HEAT EXCHANGERS
U tube configuration (a),tubesheet integral both sides, with channel type hemispherical1 A= outside diameter of tubesheet 1422.40 mm
2 ro =radius to outermost tube hole center 563.00 mm
3 dt=nominal outside diameter of tubes 19.05 mm
4 Do=equivalent diameter of outer tube limit circle 1145.05 mm
5 DS = inside diameter of shell 1411.70 mm
6 DC= inside diameter of channel 1219.20 mm
7 E=Modulus of elasticity of tubesheet at tubesh DT 1955300 bar
8 S=Allowable stress of tubesheet material at tubesh DT 1290 bar
9 EC=Modulus of elasticity of channel at channel DT 1955300 bar
10 ES=Modulus of elasticity of shell at shell DT 1955300 bar
11 EtT=Modulus of elasticity of tubes at tubesheeet DT 1955300 bar
12 StT=Allowable stress of tubes material at tubesh DT 1290 bar
13 h= uncorroded tubesheet thickness 238.60 mm
14 hg=tube side pass partition groove depth 0.00 mm
15 ct= tubesheet corrosion allowance on the tube side/shell side 0.00 mm
16 p= tube pitch 25.4 mm
17 tube layout pattern triangular
18 ltx =expanded length of tube in tubesheet 0.00 mm
19 =tube expansion depth ratio =ltx/h 0.0000
20 hg = MAX [( hg ct ),0] 0.00 mm
21 =basic ligament efficiency for shear =(p dt)/p 0.25
22 tt= nominal tube wall thickness 2.413 mm
23 d*=effective tube hole diameter=max[( dt 2tt(EtT/E)(StT/S) ,dt 2tt)] 19.0500 mm
24 A total area of untubed lanes 69870 00 mm224 AL= total area of untubed lanes 69870.00 mm
25 p*=effective tube pitch= p/ [1 4MIN(AL,4Dop)/ Do2)]1/2 26.3082 mm
26 *=effective ligament efficiency for bending=(p* d*)/p* 0.275927 [h 2ct]/p= 9.3937
28 E*/E (function of h/p and *) = 0.2497
29 * =effective Poisson ratio of tubesh in perforated region 0.3722
30 E*= effective modulus of elas of tubesh in perforated region 488330.6622 bar31 s=Ds/Do 1.2329
32 c=Dc/Do 1.0648
33 Ps= shell side internal design pressure 0 bar
34 Pt=tube side internal design pressure 186 bar
35 MTS=Do2/16 {[ ( s 1)( s
2+1)Ps ( c 1)( c2+1)Pt]} 2106024.62 bar* mm2
36 ts= shell thickness 16.00 mm
37 tc=channel thickness 129.56 mm
38 vs=Poisson's ratio of shell material 0.300
39 vc=Poisson's ratio of channel material 0.300
40 Sc=Allowable stress of channel material at DT 1290 bar
41 Ss=Allowable stress of shell material at DT 1290 bar
42 S = 4 12(1 vs2)/ (Ds+ts)ts 0.012028 mm 1
43 ks = s Ests3/ 6(1 vs
2) 1764240.933 N
44 s =[ 6Dsks/(h ct)3] [1+(h ct) s +(h ct)2
s2/2] 8787.260 N/mm2
45 s = Ds2/4Ests [1 vs/2] 0.135366 mm3/N
46 s = sks s s[1+(h ct) s] 13704.07537 mm2
PStylianopoulos Pressure Vessel Engineer Page 1 of 3, 9/29/2011
INTEGRAL TUBESHEET OPTIMIZATION SHEET ASME VIII Div. 1 UHX RULES FOR SHELL AND TUBE HEAT EXCHANGERS
hemispherical47 c = 4 12(1 vc
2)/ (Dc+tc)tc 0.004349 mm 1
48 kc = c Ects3/ 6(1 vc
2) 338684441.491 N
49 c =[ 6Dckc/(h ct)3] [1+(h ct) c +(h ct)2
c2/2] 469819.419 N/mm2
50 c = Dc2/4Ectc [1 vc/2], Dc
2/4Ectc [(1 vc )/2] for hemispherical channel 0.005134 mm3/N
51 c = ckc c c[1+(h ct) c] 16405.207 mm2
52 K=A/Do 1.2422
53 F=(1 v*)/E* (E lnK + c+ s) 6.6980
54 M*=MTS + cPt sPsmoment on unperforated tubesheet rim 945343.8173 bar* mm2
55 Mp=[M* (Do2/32)F(Ps Pt)]/(1+F) moment at the periphery 6753805.38 bar* mm2
56 Mo=Mp+(Do2/64)(3+v*)(PS Pt) moment at the center 6096034.395 bar* mm2
57 M=MAX [ ABS(M ),ABS(Mo)] max tubesheet bending moment 6753805.379 bar* mm2
58 = 6M/ *(h 2ct hg')2 tubesheet bend stress 2580.00 bar
59 =(1/4 )[Do/(h 2ct] ABS( Ps Pt) outer tubesheet shear stress 892.62 bar
60 Sall =2S 2580.0 bar ok
61 all=0.8S 1032.0 bar ok
62 s,m= Ds2Ps/4ts(Ds+ts) 0.00 bar
63 s,b=(6ks/ts2){ S SPs+6[(1 v*)/E*][Do/(h ct)
3][ 1+(h ct) s/2][Mp+9Do2/32)(Ps Pt)]} 567.70 bar
64 s =l sml+ l sbl 567.70 bar
65 Ssall =1.5Ss 1935.00 bar ok
66 c,m= Dc2Pc/4tc(Dc+tc) 395.54 bar
67 c,b=(6kc/tc2){ c cPc 6[(1 v*)/E*][Do/(h ct)
3][ 1+(h ct) c/2][Mp+9Do2/32)(Ps Pt)]} 1539.46 bar
68 c =l cml+ l cbl 1935.00 bar
69 Scall =1.5Sc 1935.00 ok
70 Length of uniform shell thickness l 1 8D t 201 64
U tube configuration (a),tubesheet integral both sides, with channel type
70 Length of uniform shell thickness, leq,s= 1.8Dsts = 201.64 mm
71 Length of uniform channel thickness, leq,c= 1.8Dctc = 533.23 mm
72 Number of tubes, N= 189073 Shell side design Pressure Ps= 10.00 barg
74 Tube side design Pressure Pc= 186.00 barg
75 Shell side minimum thickness= 16.00 mm
76 Channel side minimum thickness= 44.59 mm77 Objective function to be minimized = Dstsleq,s+ Dctcleq,c+[ ( 2/4) N dt2/4]h 529532546 mm3
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INTEGRAL TUBESHEET OPTIMIZATION SHEET ASME VIII Div. 1 UHX RULES FOR SHELL AND TUBE HEAT EXCHANGERS
hemispherical
( ) E*/E (E il t l T i l P tt )
U tube configuration (a),tubesheet integral both sides, with channel type
FIG UHX 11.3 CURVES FOR THE DETERMINATION OF E*/E AND * (EQUILATERAL TRIANGULAR PATTERN)
h/p=0.1
h/p=0.25
h/p=0.5
h/p=2
0.2759, 0.2497
0.0
0.1
0.2
0.3
0.4
0.5
0.6
0.7
0.8
0.1 0.2 0.3 0.4 0.5 0.6
E*/E
*
(a) E*/E (Equilateral Triangular Pattern)
(b) * (Equilateral Triangular Pattern)
h/p=0.1
h/p=0.15
h/p=0.25
h/p=0.5
h/p=1
h/p=2
0.2759, 0.3722
0.0
0.1
0.2
0.3
0.4
0.5
0.6
0.7
0.1 0.2 0.3 0.4 0.5 0.6
*
*
PStylianopoulos Pressure Vessel Engineer Page 3 of 3, 9/29/2011
