Padeye calculation based on the latest noble denton code AISC 9 ed

1. COMPANY
PROJECT
SUBJECT
1. Summary Result
Shackle and Sling
Sling Stress Ratio
Shackle Stress Ratio
Padeye
Dimensional Check
Outside Radius Check
Pin Hole Diameter Check
Total Padeye Thickness Check
Total Cheeck Plate Thickness Check
Stress Check around the Hole
Bearing Stress Check
Shear Stress Check
Shear Stress Check at Weld (Cheek Plate 1 - Main Plate)
Shear Stress Check at The Base of Padeye
Tension Failure
Tearout Failure
Stress Check at the End of Padeye
Von Mises Stress Ratio
Sling Selection
Sling Type Cable Laid Sling
Sling Diameter mm
Shackle Selection
Shackle Type Green Pin P-6033
Shackle WLL MT
Padeye Selection
Main Plate Thickness mm Main Plate Radius mm
End Main Plate Thickness mm
Cheek Plate 1 Thickness mm Cheek Plate 1 Radius mm
Cheek Plate 2 Thickness mm Cheek Plate 2 Radius mm
Pin Hole Diameter mm
2. Code and Reference
a. TEP - 9001 - DBS - ST - BP5 - 0001 Structural Design Basis
b. AISC - ASD 9th
Ed. Manual of Steel Construction, Allowable Stress Design
c. DNVGL - ST - N001 Marine Operation and marine warranty
d. Sling Catalogue
e. Shackle Catalaogue Green Pin Catalogue
3. Load Comparison
SACS applicable Load = MT
Design Load for Padeye Check = MT OK
0 0
221
289
700
75 400
75 350
597
600
60
0.72
0.75
0.37
0.40
1.12
0.88
0.59
0.56
NOT OK
OK
23/09/2016 REFERENCE
Description Unity Check
1.33
OK
OK

2. COMPANY
PROJECT
SUBJECT
23/09/2016 REFERENCE
4. Shackle and Sling Design
Sling Force
Maximum Sling Static Load (SSL) = MT = kN
Dynamic Amplification Factor (DAF) = Design Basis
Skew Factor (SKL) = Ch. 8.9.4
Consequences Factor (CF) =
Load Factor = DAF x SKL x CF = Design Basis
Ch. 8.9.4
Design Sling Load (DSL) = MT = kN
Sling Selection
Nominal Safety Factor for Sling (γsf) = DNVGL-ST-N0001
γf γc γr γw γm = 4.9 sect 16.4.3.1
2.3 γr γw = 4.5
DNVGL-ST-N0001
Lifting Factor γf = sect 16.4.4.1
Consequences Factor γc = sect 16.4.5.1
Sling Reduction Factor γr = (Maximum of γs and γb) sect 16.4.6.1
Termination Factor γs = sect 16.4.7
Bending Factor γb = sect 16.4.8
Sling Bending Diameter = mm Shackle Catalogue
Wear Application Factor γw = sect 16.4.10
Material Factor γm = sect 16.4.9
The width available for the sling shall be not less than 1.3d (limited to 1.25d + 25 mm), where d is nominal DNVGL-ST-N0001
sling diameter in mm. sect 16.4.9.1
1.3d = mm OK
1.25d + 25 mm = mm
Minimum Breaking Load MBL = SSL x γsf/CF = MT = kN
Sling Type = Cable Laid Sling
Sling Diameter = mm
Sling MBL = MT
Sling UC = > NOT OK
Shackle Selection
Shackle Type = Green Pin P-6033 Green Pin
Catalogue
Working Limit Load WLL = MT
Derrated Factor φ =
Pin Diameter b = mm
Inside Jaw Width e = mm
Inside Length f = mm
Width Bow g = mm
Criteria Shackle Selection DNVGL-ST-N0001
The shackle WLL should not be less than the static sling load sect 16.5.2
Working Limit Load WLL x φ = MT
Maximum Sling Load P = MT
WLL > P > OK
The shackle dynamic load is to be less than the minimum of the following values DNVGL-ST-N0001
Shackle WLL x DAF x φ = MT sect 16.5.2
Shackle MBL / 3.0 = MT
Shackle MBL = 5 x WLL = MT Green Pin
Catalogue
Shackle Unity Check = OK0.88
751
678.7608
600
746.6369
1131
3393.804
540
289
2461.5
1.33
700
215
315
380
1.10
1.50
3263.374
97%
375.7
386.25
32014
Max
1.30
1.30
1.77
1.25
1.77
1.00
1.30
1.43
858 8417
4.94
600 5886
1.10

3. COMPANY
PROJECT
SUBJECT
23/09/2016 REFERENCE
5. Padeye
Criteria Padeye
Main plate height, Mp,h = mm
pin hole diameter (dh) = mm
radius of main plate (Rm) = mm
radius of cheek plate 1 (Rc1) = mm
radius of cheek plate 2 (Rc2) = mm
main plate thickness (tm) = mm
Yield Stress (Fy) of Main Plate = MPa
Yield Stress (Fy) of Cheek Plate 1 = MPa
Yield Stress (Fy) of Cheek Plate 2 = MPa
cheek plate (1) thk, tce1 = mm
cheek plate (1) thk, tce2 = mm
DNVGL-ST-N0001
1. The outside radius of the padeye main plate shall be no less than the diameter of the pin hole. sect 16.9.5.1
Rm > dh --> OK
2. Pin-holes should be bored / reamed, and should be designed to suit the shackle proposed. sect 16.9.5.2
The pin hole diameter shall be 2 mm or 3% larger than the diameter of the shackle pin,
whichever is the greater, up to a maximum of 6 mm
b + 2 mm = mm Min Pin Hole Diameter mm
b + (3% x b) = mm Max Pin Hole Diameter mm
b + 6 mm = mm Status
3. The pad eye thickness at the hole shall not be less than 75% the inside width of the shackle sect 16.9.5.4
Rm + 2 Rc1 + 2 Rc2 = mm NOT OK
0.75 x e = mm
4. The total thicknesses of cheek plates on one side of the main plate should not exceed 100% sect 16.9.5.5
of the main plate thickness. The cheek plates should be symmetric either side of the main plate.
tce1 + tce2 = mm OK
tm = mm
Padeye Design Forces
Padeye Cordinate X = m Location of Padeye =
Y = m
Z = m
X = m X = m
Y = m Y = m
Z = m Z = m
Hook Cordinate
(FEED)
Hook Cordinate
(SACS)
-10.00
-15.00
48.80
-0.37
-0.47
74.56
-0.26
-0.03
80.32
Row C-2
75
217.0
221.5
221.0
225
236
75
75
325
325
325
75
0
221
221
OK
1000
221
400
350
0
DSF
fz
fy
θ

4. COMPANY
PROJECT
SUBJECT
23/09/2016 REFERENCE
To FEED Cordinate To SACS Cordinate
Lx = m Lx = m
Ly = m Ly = m
Lz = m Lz = m
Lxy = (Lx
2
+ Ly
2
)0.5
= m Lxy = (Lx
2
+ Ly
2
)0.5
= m
Lxyz = (Lx
2
+ Ly
2
+ Lz
2
)0.5
= m Lxy = (Lx
2
+ Ly
2
+ Lz
2
)0.5
= m
β1 = deg β2 = deg
β = β2 - β1 = deg
Out of Plane Angle = degree
Design Sling Force (DSF) = MT
F (Out of Plane) = MAX DSF x sin β = MT = kN sect 16.9.3.1
3% x SSL
Stress Check arround the hole
Bearing Stress Check
Bearing Force, Fb = kN
Bearing Area, Ab = mm2
b x (t m + 2 t ce1 + 2t ce2 )
Bearing Stress, Fb/Ab = MPa
Allowable Bearing Stress, 0.9 x Fy = MPa AISC Sect J8
UC = OK
Shear Stress Check
Shear Force, Fs = kN
Shear Area, As (γ - γ) = mm2
[(R m - 0.5d h )t m +(R c1 - 0.5d h )2t ce1 +(R c2 - 0.5d h )2t ce2 ] x 2
Shear Stress, Fs/As = MPa
Allowable Shear Stress, 0.4 x Fy = MPa AISC Sect F4
UC = OK
Shear Stress Check at Weld (Cheek Plate 1 - Main Plate)
Shear Force at Cheeck Plate 1, Fscheek 1 = kN
SQRT( (DSF x t ce1 /(t m + 2 t ce1 + 2t ce2 )) 2
+ (3% DSF) 2
)
DNVGL-ST-N0001
sect 16.9.5.6
73
130
0.56
2817
Cheek plate welds shall be proportioned and designed with due regard to possible uneven bearing
across the padeye/cheek plate thickness due to combined nominal (3%) and actual lateral loads
48375
174
292.5
0.59
8417
115275
4.6
858
68.1
17
31
26
10
15
56
4.6
667.90
8417
18
36
10
15
32
60
fz
fy
θ
γ
γ
β
β
C
Mp h
α
α

5. COMPANY
PROJECT
SUBJECT
23/09/2016 REFERENCE
Fillet Weld Size, tw1 = mm
Fillet yield Strength, Fyw = MPa (70 ksi)
Weld Shear Area, Aw1 = mm2
0.707 x Π x R c1 x t w1
Shear Stress at Weld, Fscheek1/Aw1 = MPa
Allowable Shear Stress, 0.3 x Fyw = MPa
UC = OK
Shear Stress Check at The Base of Padeye
Shear Force, FsBase = kN DSF sin θ θ = 60 deg
Shear Area, AsBase = mm2
Shear Stress = MPa
Allowable Shear Stress, 0.4 x fy = MPa AISC Sect F4
UC = OK
Tension and Tearout Failure
Tension Force, Ft = kN
Area at Cross Section, At (α - α) = mm2
[(R m - 0.5d h )t m +(R c1 - 0.5d h )2t ce1 +(R c2 - 0.5d h )2t ce2 ] x 2
Tension Stress, Ft/At = MPa
Allowable Tensile Stress, 0.6 x fy = MPa AISC Sect D1
UC = OK
Tearout Area, As (β - β) = mm2
t m ( Π R c1 x 2R m )
Tearout Stress, Fs/As = MPa
Allowable Shear Stress, 0.45 x fy = MPa AISC Sect D3.1
UC = OK
Stress Check at the end of padeye
Main plate height, Mph = mm
Main plate thickness, Mpt = mm
Stiffener Plate 1 width, t1w = mm
Stiffener Plate 1 thickness, t1t = mm
Stiffener Plate 2 width, t2w = mm
Stiffener Plate 2 thickness, t2t = mm
Stiffener Plate 3 width, t3w = mm
Stiffener Plate 3 thickness, t3t = mm
Stiffener Plate 4 width, t4w = mm
Stiffener Plate 4 thickness, t4t = mm
Depth 1, d1 = mm
Depth 2, d2 = mm
Depth 3, d3 = mm
Centre of pinhole to base of padeye, C = mm
Neutral Axis, na = mm from top of stiffener 1
440
0
550
542.35
0.00
0.00
0.00
550.00
40.00
0
0.40
1000
60
400.00
40.00
0.00
73
195
0.37
142467
59
146
75000
97
130
0.75
8417
115275
482
27209
104
145
0.72
7289
35
taw taw

6. COMPANY
PROJECT
SUBJECT
23/09/2016 REFERENCE
About x - x axis
About y - y axis
Ixx = mm4
Iyy = mm4
Forces on Padeyes
Centre of pinhole to base of padeye, C = mm
Sling Load (DSF) = kN
Out-pane Load (F) = kN
Fx = F = kN
Fy = DSF x Sin θ = kN
Fz = DSF x Cos θ = kN
Mx = = Nmm
My = = Nmm
Check Axial and Shear Stress along a section base of the padeye
fs = fvx + fxy
fvy = MPa
fvx = MPa
fbx = MPa fs =
fby = MPa
faz = MPa
fvy = MPa
fvx = MPa
fbx = MPa fs =
fby = MPa
faz = MPa
At Point B
121.49
0.00
84.35 121.49
0.00
30.94
7289
4208
3.58.E+09
3.67.E+08
At Point A
0.00
8.79
84.35 8.79
23.02
30.94
2.22.E+10
7.34.E+09
550
8417
668
668
TOTAL 98000 1.04.E+07 2.89.E+09 7.34.E+09
Area Main 60000 0 0.00.E+00 0.00.E+00 1.80.E+07
Area T4 22000 305 6.71.E+06 2.05.E+09 5.20.E+09
Area T3 0 0 0.00.E+00 0.00.E+00 0.00.E+00
2.12.E+09
Area T2 0 30 0.00.E+00 0.00.E+00 0.00.E+00
A (mm2
) X(mm) AX (mm3
) AX2
(mm4
) Iyy (mm4
)
Area T1 16000 230 3.68.E+06 8.46.E+08
TOTAL 136000 7.38.E+07 1.73.E+10 5.01.E+09
Area Main 60000 500 3.00.E+07 1.08.E+08 5.00.E+09
Area T4 44000 980 4.31.E+07 8.43.E+09 5.87.E+06
Area T3 0 0 0.00.E+00 0.00.E+00 0.00.E+00
Area T2 0 0 0.00.E+00 0.00.E+00 0.00.E+00
Area T1 32000 20 6.40.E+05 8.73.E+09 4.27.E+06
A (mm2
) Y(mm) AY (mm3
) AY2
(mm4
) Ixx (mm4
)

7. COMPANY
PROJECT
SUBJECT
23/09/2016 REFERENCE
fvy = MPa
fvx = MPa
fbx = MPa fs =
fby = MPa
faz = MPa
fvy = MPa
fvx = MPa
fbx = MPa fs =
fby = MPa
faz = MPa
fvy = MPa
fvx = MPa
fbx = MPa fs =
fby = MPa
faz = MPa
fvy = MPa
fvx = MPa
fbx = MPa fs =
fby = MPa
faz = MPa
Compute Von Mises combined stress, fc = [ (faz + fbx +fby)2
+ 3fs2
]0.5
Allowable combined stress, 0.66 x Fy = MPa
At Point F 125.57 0.59 OK
At Point D 0.00 0.00 OK
At Point E 233.68 1.09 NOT OK
At Point B 239.94 1.12 NOT OK
At Point C 0.00 0.00 OK
214.50
fc (Mpa) UC Status
At Point A 139.16 0.65 OK
At Point F
0.00
8.79
70.67 8.79
23.02
30.94
At Point E
121.49
0.00
70.67 121.49
0.00
30.94
At Point D
0.00
0.00
0.00 0.00
0.00
0.00
At Point C
0.00
0.00
0.00 0.00
0.00
0.00