LIFTING LUG CALC(VERTICAL VESSEL)( Ref: Compress & Pressure Vessel Handbook by Dennis Moss).

1.0 LIFTING LUG CALCULATION

1.1 Geometry Inputs

Lifting Lug Material :

Length of Lifting Lug, L = mm

Width of Lifting Lug, B = mm

Thickness of Lifting Lug, t = mm

Pin Hole Diameter, d = mm = cm

Lug Diameter at Pin, D = mm = cmWeld Size, tw = mm

Weld Length, b1 = mm

Weld Length, d2 = mm

Collar Thickness, tc = mm

Collar Diameter, Dc = mm

Width of Pad, Bp = mm

Length of Pad, Lp = mm

Pad Thickness, tp = mm

Pad Weld Size, twp = mm

Weld Length, L3 = mm

Length to Brace Plate, L1 = mm = cm

MSET ENGINEERING CORPORATION SDN BHDDATE : 10/04/2013

DOC. REF. NO.: MSETe/M2-228/L4-104C

SUBJECT: LIFTING LUG CALC

DOCUMENT TITLE: DESIGN CALCULATION

REVISION: C

JOB NO: M2-228

Figure 1: Lifting Lug Detail

642300

3055

30012

125

SA 36

5.50

32.50

30.00

150400200

15.8812

150325

5016

Page 2

Vessel Empty Weight = kg

Load Factor =

Design Lift Weight, W = kgDist. from C.O.G to Lifting Lug,l1 = mm

Dist. from C.O.G to Tailing Lug,l2 = mm

Dist. from Vessel C.L to Tailing Lug,l3 = mm

Yield Stress at amb Temp.,Sy = kg/cm2

Allow.Tensile Stress, t =0.6Sy = kg/cm2

Allow. Shear Stress, s = 0.4Sy = kg/cm2

Allow. Bearing Stress, p =0.9Sy = kg/cm2

Allow. Bending Stress, b =0.66Sy = kg/cm2

Allow. Weld Shear Stress,allow. = kg/cm2

1.2 Lift Forces

Lift force on lifting & tailing lug during rotational lift (0o 90

o)

2*Ftop = [W* ((l2*cos) +(l3*sin))] / [((l1*cos) + (l2*cos) + (l3*sin))]

Ftail = W - (2*Ftop)

FT = Ftop cos

FL = Ftop sin

o

0

5

10

15

20

25

30

35

40

45

50

55

60

65

70

75

80

85

90

7354

8076

8773

9451

10123

10815

11579

12535

14004

3103

2210

1225

17210

172109594

Table 1: Lifting Load at Various Lift Angle,

3936

(rad)

0

0.0873

0.1745

0.2618

FT(top) (kgf)

1476.400

FL(top) (kgf)

9548

9594

1517.2921011.528

8327

7872

7354

6777

6143

5457

4720

229461.5

3441933434166

940

2528.82

2275.9381669.0212

10165

10276

10400

10542

10710

9566

9463

Figure 2: Lifting & Tailing Force-Loading Diagram

0

839

1687

2536

Ftop (kgf)

9548

9631

9713

9796

5831

6605

0.3491

0.4363

9286

9036

8716

3380

4214

5032

9882

9970

11988

12729

14058

0.5236

0.6109

0.6981

0.7854

0.8727

0.9599

1.0472

1.1345

1.2217

1.3963

1.4835

10064

10913

11169

11509

1.3090

17210 01.5708

Max Force (kgf) 17210

Page 3

Max. Lifting Load, Fv = kgf

1.3 Lifting Lug Stress Calculation

1.3.1 Lug Pin Diameter based on Shear Stress.

Pin Hole Required Diameter, dreqd : (2*Fv /(*s))0.5

= cm = mm

Pin Hole Required Dia. less than Geometry Input, So Pin Hole Dia. is Sufficient

Pin Hole Area (on 2 Lifting Lug), A : 2*((/4)*d2)

= mm2

= cm2

Shear Stress Required, reqd : Fv /A

= kg/cm2

Shear Stress Required less than Allowable Shear Stress, Stress on Hole is Sufficient

1.3.2 Lug Thickness based on Tensile Stress.

Lifting Lug Thickness Required, treqd : Fv /(D*t)= cm = mm

Thickness Required are less than Geometry Input, Thickness used is Sufficient

Lifting Lug Area, A : D*t= mm

2= cm

2

Tensile Stress Required, reqd : Fv /A= kg/cm

2

Tensile Stress Required less than Allowable Tensile Stress, Stress on Lug is Sufficient

1.3.3 Lug Thickness based on Bearing Stress.

Lifting Lug Thickness (Including Collar Plate)

T : t + (2*tc)= mm

Lifting Lug Thickness Required, Treqd : Fv /(d*p)= cm = mm

Thickness Required are less than Geometry Input, Thickness used is Sufficient

Collar Required Thickness, tc reqd : max(0, 0.5*(Treqd -t))

= mm

Collar Thick. Required less than Geometry Input, Thickness used is Sufficient

Bearing Area, Abearing : (d*(t+2tc))

= mm2

= cm2

Bearing Stress Required, reqd : Fv /Abearing= kg/cm

2

Bearing Stress Required less than Allowable Bearing Stress, Stress on Lug is Sufficient

47.52

62.0

9000

0.47

3.093

0.227 2.27

90.00

191.217

2.687 26.87

34.10

504.677

30.93

3410.00

4751.659

362.179

17210

Page 4

1.3.4 Lug Thickness based on Shear Stress.

( Ref: Pressure Vessel Design Manual Handbook by Dennis Moss pg 417).

Net Section at top of Lug(2 lugs), An : 2[t(D-d/2)] + [2tc (Dc-d/2)]

= mm2

= cm2

Shear Stress at top of lug, s : FT(top)/An

= kg/cm2

Shear Stress Required less than Allowable Shear Stress, Stress on Lug is Sufficient

1.3.5 Weak Axis Bending Stress

Section Modulus of Lug, Z : B*t2

/6

= mm3

= cm3

Bending Stress, b : M/Z

= Fsin *L1 /Z , Where F = 0.5W/cos

b = 0.5W(sin/cos)*L1/Z ,Where sin/cos = tan

Max. lift cable angle from Vertical, = arctan((b*Z)/(0.5WL1))

= rad

= deg

1.4 Weld Stress Calculation

Maximum weld shear stress occurs at lift angle,

= deg = radFrom Table 1, lift force,FL(TOP) = kgf

Lifting Lug Weld Area, Aweld : A1 + A2 + A3 + A4(Brace Plate)

= 0.707*tw[(d1+b1)+(2d2+b2)+(d3+b3) + L1]

= mm2

= cm2

Max. weld Shear Stress, t : FL(TOP) cos/ A weld

= kgcm2

Max. weld Shear Stress, s : FL(TOP)/ A weld

= kgcm2

1.5708

197.90

90.0017209.50

86.96

0.00

45.00

10390.00

10.38

92.341

45000.00

103.90

Figure 3: Lifting Lug Weld Area.

8696.10

0.18

Page 5

1.4.1 Torsional Shear:

Weld Centrod:

Weld Areas, Ai : 0.707 *tw*Li

(Weld at Brace Plate)

Weld Centroid Location:x1 = mm y1 = mm

x2 = mm y2 = mm

x3 = mm y3 = mm

x4 = mm y4 = mm

x5 = mm y5 = mm

x6 = mm y6 = mm

x7 = mm y7 = mm

x8 = mm y8 = mm (Location at Brace)

Xbar : (Ai*Xi)/Ai Ybar : (Ai*Yi)/Ai

= mm = mm

Radius to Centroid Locations, ri : sqrt((Xbar -xi)2 +(Ybar-yi)

2)

r1 = mm

r2 = mm

r3 = mm

r4 = mm

r5 = mm

r6 = mm

r7 = mm

r8 = mm

Polar Moment Area, Ji : 0.707 *tw*(Li3)/12

J1 = mm4

J2 = mm4

J3 = mm4

J4 = mm4

J5 = mm4

J6 = mm4

J7 = mm4

J8 = mm4

Parrallel axis theorem, J : (Ji + Ai*ri2)

= mm4

Location

A1A2A3A4A5A6A7

Area(mm2)

1272.60

1060.5

424.20

424.20

424.20

1060.50

1272.60

2545.20

50.00

A8

Ai (mm2)

25.00

150.00 50.00

175.00 25.00

237.50 0.00

75.00

62.50 0.00

8484.00

Table 2: Weld Torsion Area

0.00

300.00 75.00

150.00 467.00

146.25 167.60

173.10

187.36

172.04

117.66

145.47

190.83

179.48

299.42

2386125.00

1380859.38

88375.00

88375.00

88375.00

1380859.38

2386125.00

19089000.00

437455918

Page 6

Radial distance from centroid to weld:

r : sqrt(Xbar2 +((L3+L-L1)- Ybar)

2)

= mm

r : arctan(((L3+L-L1)-Ybar)/Xbar)

= rad

= deg

2 : M*r/J

= (Fr*cos*(L+L3-Ybar))*r/J

= kg/mm2

= kg/cm2

total : sqrt[(t +2sinr)2 + (s + 2cosr)

2]

= kg/cm2

Weld Shear Stress Reqd. less than Allow. Weld Shear Stress. So, Stress is Sufficient

1.4.2 Collar Weld Stress:

Collar Weld Area, Aweld : 2Dc*0.707tw

= mm2

= cm2

Collar Weld Stress, c : Fv/Aweld= kg/cm

2

Collar Weld Shear Stress Required less than Allow. Weld Shear Stress. So, Stress is Sufficient

1.4.3 Pad Weld Stress:

Direct Shear:

Pad Weld Area, Aweld : 0.707twp * (2Lp +Bp)= mm

2= cm

2

Max. weld Shear Stress, t : FT(TOP) cos/ A weld

= kgcm2

Max. weld Shear Stress, s : FT(TOP) sin/ A weld

= kgcm2

6787.20 67.87

0.00

253.56

333.21

1.12

63.97

0.00

0.00

79.96

215.23

Figure 4: Pad Weld Area.

197.90

7995.98

Page 7

1.4.4 Torsional Shear:

Weld Centrod:

Weld Areas, Ai : 0.707 *twp*Li

Weld Centroid Location:x1 = mm y1 = mm

x2 = mm y2 = mm

x3 = mm y3 = mm

Xbarp : (Ai*Xi)/Ai Ybarp : (Ai*Yi)/Ai

= mm = mm

Radius to Centroid Locations, ri : sqrt((Xbar -xi)2 +(Ybar-yi)

2)

r1 = mm

r2 = mm

r3 = mm

Polar Moment Area, Ji : 0.707 *twp*(Li3)/12

J1 = mm4

J2 = mm4

J3 = mm4

Parrallel axis theorem, J : (Ji + Ai*ri2)

= mm4

Radial distance from centroid to weld:

r : sqrt(Xbarp2 +((Lp- Ybarp)

2)

= mm

r : arctan(((Lp)-Ybar)/Xbar)

= rad

= deg

2 : M*rp/Jp

= (Fr*cos*(L+Lp-Ybarp))*rp/Jp

= kg/mm2

= kg/cm2

total : sqrt[(t +2sinr)2 + (s + 2cosr)

2]

= kg/cm2

Weld Shear Stress Reqd. less than Allow. Weld Shear Stress. So, Stress is Sufficient

36.87

0.00

0.00

253.56

206.16

50.00

206.16

5656000

45248000.00

5656000

209272000

250.00

0.64

Table 3: Weld Torsion Area

0.00 100.00

200.00 0.00

400.00 100.00

200.00 50.00

Location Area(mm2)

A1 1696.80

A2 3393.6

A3 1696.80

Ai (mm2) 6787.20

Page 8