DESIGN DESIGN RULES FOR CLAM CLAM P CONN ECTION ECTION S
ASM ASM E VIII VIII Div.1 A-24
Hub M aterial/Fig aterial/Fig
SA-266-2/ 24.1(a)
Design Pressure
Clamp M aterial/Fig aterial/Fig SA-266-2/ 24.2(a)
Design Design Temperat ure
SA-516-70
Cover M aterial aterial
Corrosion allowance
8 0. 0 . 0 0 b ar ar g 150.00 C 1 .5 0 m m
1 A = o u t si d e d i a m e t e r o f h u b
1 3 9 0 .8 0 m m
cross-sectional -sectional area of th e bolt s per clam clam p lug 2 A bl =tot al cross A C=total effective clamp cross-sectional are 3 =A 1 +A 2 +A 3
5232.10 m m 2
4 5 6 7 8 9 10
A 1 =partial clam clam p area =( Cw -2 Ct )Ct
13664.00 m m 2
A 2 =partial clam clam p area =(π/2)*Ct
23379.73 m m 2
A 3 =partial clam clam p area =( Cw -C g )l c m
=
4162.50 m m 2 -
required for t he operating conditions=W m 1 / 2 Sb required for gasket gasket seating=W m 2 / 2 Sa
0.00 m m 2
A m 3 =tot al crosscross-se sectional ctional area of t he bo lts per clamp lug required for ass assem bly conditions=W m 3 / 2 Sa
4941.57 m m 2
A m l =tot al required cross-s cross-sectional ectional area of th e bolts per clamp lug taken as the greater o f A m 1 ,A m 2 ,A m 3
1 3 B= i n si d e d i a m e t e r o f h u b B c =radial distance distance from connection centerline to center of bo lts 14 [Fig.24-1 [Fig.24-1 sketch (e)]
4941.57 m m 2 5 .0 0 m m 10.00 m m 1 2 3 0 .8 0 m m 905.00 m m
C= diamet er of effective clam clam p-hub r eaction eaction circle circle =(A+Ci )/ 2
1377.80 m m
inside diameter of clamp 1 6 Ci= inside g=
1364.80 m m .
clamp thickness thickness (C (Ct shall be equal to or greater t hat r ) 1 8 Ct = effective clamp clamp w idht 1 9 Cw = clamp 20
1613.48 m m 2
A m 2 =tot al crosscross-se sectional ctional area of t he bo lts per clamp lug
-su r f a c e se a t i n g w id id h t (T (Ta b l e 2 - 5 . 2 ) 1 1 b = e f f e c t i v e g a sk e t o r j o i n t - c o n t a ct -s gasket or jo int -cont act -surf -surf ace seatin seatin g widh t (Table 2-5.2) 1 2 b o =basic gasket
15
41206.23 m m 2
mm
122.00 m m 356.00 m m
e b =radial distance distance from center of th e bolts to the centro id of the clamp cross section section =B c -( C /i 2 )- l c -X
158.75 m m
f=hu b stress correct ion fact or fr om Fig. 2-7-6.(For 2-7-6.(For values below 2 1 limit of t he figure, use use f=1.0). h / h o =
0.345 g 1 / g o =
1.00 1.460
=thickness of hub neck at small end 2 2 g o =thickness =thickness of hub neck at inter section w ith h ub shoulder 2 3 g 1 =thickness
45.00 m m
=height of hub shoulder shoulder (g 2 shall not be greater than T) 2 4 g 2 =height g =radial distance distance from hub inside diam diam eter B to the hu b shoulder shoulder 25 ring centroid =[Tg1 +h 2 g 2 (2 g 1 +g 2 )]/[2(Tg 1 +h 2 g 2 ) ]
15.00 m m
PSt y l i a n o p o u l o s
Pr e ssu r e V e sse l En g i n e e r
65.00 m m
39.15 m m
1 of 6
DESIGN RULES FOR CLAM P CONN ECTION S
ASM E VIII Div.1 A-24
26
G= diameter at location of gasket load reaction.Except as noted in Fig.24-1 (Set it as OD of cont act face) , G is defin ed in Table 2.5.2
27 h =h u b t ap er len gt h h D =radial distance from effective clam p-hub r eaction circle to 28 the circle on w hich H D acts = [ C-(B+g1 ) ] / 2 29 30
33
80.00 m m 40.25 m m
h G =radial distance from effective clamp -hub reaction circle to the circle on w hich H G acts .For f ull face gaskets geom etr ies,h G =0
0.00 m m
h n =hub neck length [ minimu m length of h n is 0.5g 1 or 1/4 in. (6 mm ), whichever is larger]
31 h o =(Bg o ) 32
1259.00 m m
139.00 m m
.
231.67 m m
h T=radial distance from effective clam p-hub r eaction circle to the circle on w hich H T acts = [C-(B+G)/2] / 2
65.70 m m
h 2 =average thickness of hu b shoulder = -
.
h =axial distance from t he hub face to t he hub shoulder 34 35 36
ring centroid =[T g 1 +h 2 g 2 ]/[2(Tg1 +h 2 g 2 ) ]
19.94 m m
H=tot al hydrostatic end for ce =(π/4)G P
9959357.65 N
H D =hydrostatic end force on bore area =(π/4)B P
9564657.00 N
H G=difference betw een tot al effective axial clam ping preload 37 and the sum of t otal hydrostatic end force and total joint contact surface com pression= [(π/2)W/tan(φ+μ)]-(Η+Ηp)
W =W (95)
298895.92 N
H m =tot al axial gasket seating requ irem ents for m akeup 38 ( πbGy or t he axial seatin g load for self-ener gizing gaskets if significant )
0.00 N
H p = tot al joint cont act surface compression load 39 = 2bxπGmP.For self energized gaskets use H p =0 or actual ret aining load, if significant 40 41 42 43
0.00 N
T=
end for ce on bore area=H-HD
394700.65 N
I c=mo m ent of inert ia of clamp relative to neut ral axis of entire section=(A1 / 3+A 2 / 4)Ct +A 3 l c / 3-A cX
56775688.60 m m
4
414845.45 m m
4
I h =mo m ent of inert ia of hub shoulder relative its neutral axis = (g 1 T )/ 3 +(g 2 h 2 )/3-(g 2 h 2 +g 1 T)h La =distance from W to t he point w here the clamp lug joins the clamp body [Fig.24-1,sketch(e)]
168.00 m m
44 Lh =clamp lug height [Fig.24-1,sketch(e)]
350.00 m m
45 Lw =clamp lug width [Fig.24-1,sketch(e)]
80.00 m m
46 l c =effective clamp lip length
15.00 m m
47 l m =effective clamp lip mom ent arm =lc-(C-Ci )/ 2
8.50 m m
48 m =gasket fact o r f o r t ab le 2.5.1
0.00
PSt yliano poulo s
Pressur e Vessel Engineer
2 of 6
DESIGN RULES FOR CLAM P CONN ECTION S
ASM E VIII Div.1 A-24
49 M D = m o m e n t d u e t o H D ,= H D h D
3 8 49 7 7. 44 N m
50 M F=offset mom ent = H D (g 1 -g 0 )/ 2 51 M G= m o m e n t d u e t o H G ,= H Gh G 52
9 5 64 6 .5 7 N m 0 .0 0 N m
M H = reaction mom ent at hub neck
(See stress calculation)
Nm
.
=M o / {1 +[ 1.8 18/ (Bg1 ) ]x[T-h +(3.305I h ) / ( g1 ( B/ 2 + g ) ) ] }
53 M o =tot al rotation al mom ent o n hub (See stress calculation)
-
54 M P=pressure mom ent= πxPBT(T/2-h ) 55
7 6.7 2 N m
M R=radial clam p equilibriating mom ent =(π/2)W{h -T+[(C-N)tanφ]/2}
- 1 61 8 4. 24 N m
W =W m 1
56 M T= m o m e n t d u e t o H T,= H Th T
2 5 93 1 .8 3 N m
57 N =o u t sid e d iam et er o f h u b n eck
1360.80 m m
58 P=in t ern al d esign p ressu re
80.00 barg
59 Q=reaction shear for ce at hub neck=1.818M H / (Bg 1 )
.
(See str ess calculat i -
"
.,
t
.
.
61 Sa =allow able bolt stress at room tem peratur e
1720.00 b ar
62 Sb =allow able bolt stress at design t emp erature SOH =allow able design stress for hub m aterial at 63 (operating condit ion) design temp erature
1720.00 b ar
64 65 66
1 3 79 .0 0 b a r
SAH =allow able design stress for hub m aterial at
1379.00 b ar
(assembly condition) room temperature SOC =allow able design stress for clam p m aterial at
1379.00 b ar
(operating condit ion) design temp erature SAc =allow able design stress for clamp m aterial at
1379.00 b ar
(assembly condition) room temperature
67 S1 =hub longitud inal stress on ou tside at hub n eck 68 S2 =maximu m Lame' hoop stress at bore of hu b
-
69 S3 =maximu m hub shear stress at shoulder 70 S4 =maximu m radial hub shear stress at the neck
-
71 S5 =clamp longitudinal stress at clamp bo dy inner diam eter 6=
-
73 S7 =maximu m shear stress in clamp lips 74 S8 =clamp lug bending stress
-
75 S9 =effective bearing stress betw een clamp and hub
-
-
76 T = t h ickn ess o f h u b sh o u ld er p er.Fig.24-1 77 78 79 80
PSt yliano poulo s
40.00 m m
W =tot al design bolt load required for operating or assembly condit ion as applicable( See stress calculation ) W e =tot al effective axial clamp ing preload on one clamp lip and hub shoulder (gasket seating or assem bly)= (π/2)W/tan(φ+μ),W=W(95) W m 1 =minimum required t otal bolt load for t he o perating condit ions(See stre ss calculat ion) W m 2 =minim um r equired tot al bolt load for gasket seating (See stress calculation)
Pressur e Vessel Engineer
10258253.57 N 555037.78 N 1749870.89 N
3 of 6
DESIGN RULES FOR CLAM P CONN ECTION S
ASM E VIII Div.1 A-24
81
X=clam p dim ension to n eut ral axis per Fig.24-1,sketch (f)
48.85 m m
={[Cw / 2-C t / 3]Ct -[(Cw -C g ) / 2 ] l c }/ A c
82 y=gasket seat in g st r ess f ro m t ab le 2.5.1 83
0.00 M p a
Z=clamp -hub t aper angle ,deg.For gasket seatin g and prelo ad Z=φ+μ,for operating Z=φ-μ
-
(See stress calculation)
84 a=h u b t r an sit io n an gle ,d eg=45 m ax.
14.00 d eg 5.00 d eg
85 μ=friction angle,deg 5.00
86 φ=clamp shoulder angle,deg. 40 max. (actual/for calc.)
10.00 d eg
BOLT LOAD S Operating condit ion 87 88
M inimum operating bolt loa d, W m 1 for operating condition W m 1 =0.637(H+H P)tan(φ-μ)=
555037.78 N
Total required bolt cross-sectional area per clamp lug m
=
=
m
.
2
Gasket seatin g 89 90
M inimum operating bolt loa d, W m 2 for gasket seatin g W m 2 =0.637H m tan(φ+μ)=
0.00 N
Total required bolt cross-sectional area per clamp lug 0.00 m m 2
A m 2 =W m 2 / 2Sa = Assembly
91 92 93
M inimum operating bolt loa d, W m 3 for assem bly W m 3 =0.637(H+H P)tan(φ+μ)=
1699899.37 N
Total required bolt cross-sectional area per clamp lug A m 3 =W m 3 / 2Sa =
4941.57 m m 2
tot al required cross-sectional area of th e bolt s per clam p lug A m l =max(A m 1 ,A m 2 ,A m 3 )=
4941.57 m m 2 CLAM P CON NECTION DESIGN BO LT LOAD
94 95
Operating condit ion W =W m 1
=
555037.78 N
ssem y W=(A m l +A bl )Sa =
1749870.89 N HUB M OM ENTS
Op erat in g co n d it io n s
Assem b ly
96 M D =
384977.44 N m
97 M G =
0.00 N m
98 M T= 99 M F=
25931.83 N m
M T=
0.00 N m
95646.57 N m
M F=
0.00 N m
100 M P=
76.72 N m
M P=
0.00 N m
101 M R=
-16184.24 N m
M R=
0.00 N m
M D= M G=W e (C-G)/2
0.00 N m 609340.26 N m
Operating condit ion 102 M O =M D +M G +M T+M F+M P+M R=
PSt yliano poulo s
490448.33 N m
Pressur e Vessel Engineer
4 of 6
DESIGN RULES FOR CLAM P CONN ECTION S
ASM E VIII Div.1 A-24
Assembly 103 M o =[(π/4)W(C-G)]/tan(φ+μ)=
609340.26 N
CALCULATI ON OF H UB STRESSES Operating condit ion 104 M H = reaction mom ent at hub neck=
[Nm]
105 Q=r eact io n sh ear fo r ce at h u b n eck=
[N ]
106 107 108 109
Hu b Lo n git u d in al st ress
432620.11 2809903.06 Allo w ab le
[b ar ]
S1 =f{PB / [4(B+g1 )g 1 ]+1.91M H / [ g 1 (B+g 1 )]}= Hu b h o o p st ress
[b ar ]
S2 =P(N +B )/ (N -B )= Hu b axial sh ear st ress
[b ar ]
S3 =0.75W/T(B+2g1 )tanZ=
[Z=φ-μ]
Hu b rad ial sh ear st ress
[b ar ]
= .
=
1949.20
2068.50
819.15
1379.00
874.13
1103.20
162.70
1103.20
Assembly 110 M H = reaction mom ent at hub neck=
[Nm]
111 Q=r eact io n sh ear fo r ce at h u b n eck=
[N ]
112 113 114 115
Hu b Lo n git u d in al st ress
537493.63 3491065.15 Allo w ab le
[b ar ]
S1 =f{PB / [4(B+g1 )g 1 ]+1.91M H / [ g 1 (B+g 1 )]}= Hu b h o o p st ress
[P=0]
[b ar ]
S2 =P(N +B )/ (N -B )=
[P=0]
Hu b axial sh ear st ress
[b ar ]
S3 =0.75W/T(B+2g1 )tanZ=
[Z=φ+μ]
Hu b rad ial sh ear st ress
[b ar ]
S4 =0.477Q/g 1 (B+g 1 )=
1962.54
2068.50
0.00
1379.00
899.83
1103.20
202.14
1103.20
CALCULATI ON OF CLAM P STRESSES Operating condit ion 116 117 118 119 120
PSt yliano poulo s
Clam p Lo ngit ud in al st ress 5=
t+
t+
Clam p t an gen t ial st ress
Allowable
[ bar ] m
t
=
= -μ
[b ar ]
S6 = ( W / 2 ) [ 1 / A c+l e b l (Ct -X)/Ic] Clam p lip sh ear st r ess
[b ar ]
S7 =1.5W/[(Cw -C g )CtanZ]= Clam p lu g b en d in g st ress
[Z=φ-μ]
[b ar ]
S8 = 3 W La / LW Lh Bearing stress at clam p t o h ub cont act S9 =W/(A-Ci )CtanZ
[bar]
[Z=φ-μ]
Pressur e Vessel Engineer
833.73
2068.50
634.99
2068.50
248.89
1103.20
285.45
1379.00
1770.97
2206.40
5 of 6
DESIGN RULES FOR CLAM P CONN ECTION S
ASM E VIII Div.1 A-24
CALCULATI ON OF CLAM P STRESSES Assemb ly condition 121 122 123 124 125
Clam p Lo ngit ud in al st ress
[ bar ]
S5 =(W/2CtanZ)[1/C t +3(Ct +2 l m )/ Ct ]= Clam p t an gen t ial st ress
Allowable [Z=φ+μ]
[ b ar]
S6 = ( W / 2 ) [ 1 / Ac +l e b l (Ct -X)/Ic ] Clam p lip sh ear st ress
[ b ar]
S7 =1.5W/[(Cw -C g )CtanZ]= Clam p lu g b en din g st ress
[Z=φ+μ]
[ bar]
S8 = 3 W La / LW Lh Bearing stress at clam p t o hu b cont act S9 =W/(A-Ci )CtanZ
[bar]
[Z=φ+μ]
126 d=diam ete r, or shor span Fig. UG-34 (m)=O.D. of hub
858.24
2068.50
2001.94
2068.50
256.21
1103.20
899.93
1379.00
1823.03
2206.40
1390.80 m m
127 C=factor depending on assemb ly met hod=
0.30
128 E=joint efficiency=
1.00
130 S=Cover allow able str ess at design tem perat ure = 129
PSt yliano poulo s
Cover minim um t hickness . t =d(CP/ SE) +c =
1379.00 b ar 184.98 m m
Pressur e Vessel Engineer
6 of 6
