Bolt Torque
4
BOLT TORQUE REQUIRED FOR SEALING OF FLANGES Vessel tag = 20V-2960 DESIGN DATA : Flange size = Design pressure, P 20 = 2900.76 = 3770.99 Design temperature = 80 External bending moment, M = 0 = 0 Bolt lubrication ( Yes / No ) = Yes Friction factor between bolt/nut and nut/flange face, K = 0.15 GASKET DATA : Type = Ring Type Diameter of raised face 1124 mm ) = 44.26 OD 1057.3 mm ) = 41.63 ID 987.4 mm ) = 38.88 Min. designs seating stress 124.11 = 18000.67 Gasket factor, m = 5.5 Mod. of Elasticity, Eg ( Table AMG, ASME VIII Div. = 569000 Gasket thickness, tg 41.28 mm ) = 1.63 Gasket width, N 34.95 mm ) = 1.38 Basic gasket width, bo ( = N / 2 ) = 0.69 Effective gasket seating width, b = 0.42 Diam. of gasket load reaction, G = 40.79 BOLTING DATA : Material = Nominal size, D = 3.25 Quantity, n = 32 root diameter of threads, d (TABLE 2-6) = 3.097 pitch diameter of threads, dm (TABLE 2-6) = 3.169 Mod. of Elasticity, Eb = 29573846 X-sectional area of bolts, = = 240.996 4 Length between outer face of flanges, 801.2 mm = 31.54 Thickness of nut, tn ( = 0.8 x D ) = 3.250 Effective length of bolt, l ( = x + tn ) = 34.79331 Equivalent pressure : Pe = 16 M + + P ( Moss, D.R. "Pressure Vessel Design Manual " ) ( @ N / mm 2 ) Test Pressure, PT Radial load, Pr ( @ ( @ ( @ ( @ N / mm 2 ) ( @ ( @ pd 2 n 4Pr pG 3 pG 2
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Transcript of Bolt Torque
BOLT TORQUE REQUIRED FOR SEALING OF FLANGES
Vessel tag = 20V-2960
DESIGN DATA :
Flange size =
Design pressure, P 20 = 2900.76 psi
= 3770.99 psi
Design temperature = 80External bending moment, M = 0 in. - lb
= 0 lb.Bolt lubrication ( Yes / No ) = YesFriction factor between bolt/nut and nut/flange face, K = 0.15
GASKET DATA :
Type = Ring TypeDiameter of raised face 1124 mm ) = 44.26 in.OD 1057.3 mm ) = 41.63 in.ID 987.4 mm ) = 38.88 in.
Min. designs seating stress, y 124.11 = 18000.666 psiGasket factor, m = 5.5Mod. of Elasticity, Eg ( Table AMG, ASME VIII Div. 2 ) = 569000 psiGasket thickness, tg 41.28 mm ) = 1.63 in.Gasket width, N 34.95 mm ) = 1.38 in.Basic gasket width, bo ( = N / 2 ) = 0.69 in.Effective gasket seating width, b = 0.42 in.Diam. of gasket load reaction, G = 40.79 in.
BOLTING DATA :
Material =Nominal size, D = 3.25 in.Quantity, n = 32root diameter of threads, d (TABLE 2-6) = 3.097 in.pitch diameter of threads, dm (TABLE 2-6) = 3.169 in.Mod. of Elasticity, Eb = 29573846 psi
X-sectional area of bolts, Ab = = 240.9964
Length between outer face of flanges, x 801.2 mm = 31.54 in.Thickness of nut, tn ( = 0.8 x D ) = 3.250 in.Effective length of bolt, lb ( = x + tn ) = 34.793307 in.
Equivalent pressure :
Pe = 16 M + + P
( Moss, D.R. "Pressure Vessel Design Manual" )
( @ N / mm2 )
Test Pressure, PT
o C
Radial load, Pr
( @( @( @
( @ N / mm2 )
( @( @
pd2n in.2
4Pr
pG3 pG2
= 2901 psi
Hydrostatic end force :
H =4
= 3790610 lb.
Total joint contact surface compression load :
Hp =
= 1717344 lb.
Min. required bolt load for gasket seating :
Wm2 = p.G.b.y
= 968816 lb
Actual joint area contact for gasket :
Ag = 2.p.G.b
= 108
Decreasing compression force in gasket ( joint relaxation ) :
DF = H1 + ( Ab.Eb.tg / Ag.Eg.lb )
= 587556 lb.
Initial required tightening force ( tension ) :
Fbo = Hp + DF
= 2304901 lb
Total tightening force required to seal joint :
W = greater of Fbo or Wm2
= 2304901 lb
Initial tightening torque required :
T = K.W.dm12.n
pG2Pe
p.G.2b.m.Pe
in.2
= 2853 ft. - lb.= 3866665 N.mm= 3867 Nm
