100 m³ BUTANE TANK CALCULATIONS
Date Page No
: 13.06.2011 : 1/23
ISISAN ISI SAN. VE TİC. A.Ş.
DESIGN CALCULATIONS 100 m3 BUTANE TANK
(B+F MODULES)
PREPARED BY
Yavuz Talaslıoğlu
Önder ÜLKER
100 m³ BUTANE TANK CALCULATIONS
CONTENT
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: 13.06.2011 : 2/23
PAGE
1) DESIGN DATA FOR 100 m³ BUTANE TANK
3
2) THICKNESS CALCULATION FOR SHELL SUBJECTED TO INTERNAL PRESSURE
4
3) THICKNESS CALCULATION FOR HEAD SUBJECTED TO INTERNAL PRESSURE
4
4) THICKNESS CONTROL UNDER EXTERNAL PRESSURE
6
5) OPENING CALCULATIONS OF THE NOZZLES
8
5) LIFTING LUG STRESS CALCULATIONS
14
6) SADDLE STRESS CALCULATIONS
15
100 m³ BUTANE TANK CALCULATIONS
Date Page No
: 13.06.2011 : 3/23
1. DESIGN DATA FOR 100 m³ BUTANE TANK
DESIGN CODE
CODAP 2005 Div2
VOLUME
100 m³
CONSTRUCTION CATEGORY
A
SERVICE
Butane
DESIGN PRESSURE (INTERNAL)
P = 8 bar (0,8 MPa )
HYDRO TEST PRESSURE
Pt = 11,44 bar (1,144 MPa)
EXTERNAL PRESSURE
Pe = 0.05 MPa (0,5 bar )
MATERIAL
P 355
MATERIAL STANDARD
NF EN 10028-3
ALLOWABLE STRESS, f =
204,17 MPa
CORROSION ALLOWANCE, c
c = 1 mm
DESIGN TEMPERATURE
-10°C / 50°C
JOINT EFFICIENCY, z
z =1
RADIOGRAPHIC EXAMINATION
100 %
NUMBER OF TANK
Rp0t .2 Rm , f min 1 , 5 2 , 4
4 pieces
OUTSIDE DIAMETER
De= 2.900 mm
SHELL LENGTH
Lt= 14.350 mm
DEPTH OF HEAD
h2 =.721 mm
EMPTY WEIGHT
- 12,500 kg (approx.)
100 m³ BUTANE TANK CALCULATIONS
Date Page No
: 13.06.2011 : 4/23
2. THICKNESS CALCULATION FOR SHELL SUBJECTED TO INTERNAL PRESSURE f
355 490 , min 1,5 2,4
= min 236,67 ; 204,16 = 204,16 N/mm ²
f 204,16 N/mm² Shell thickness:
e
P De 2 f z P
c
0,8 2.900
e
2 204,16 1 0,8
1
e. = 6,67 mm
3. THICKNESS CALCULATION FOR HEAD SUBJECTED TO INTERNAL PRESSURE
Di =1,9 2 h 2 Di
2.884 mm
1 0,08 529,24 mm r D i Di 2 2 hi
D Di 0,44R i 0,02 2hi
(C3.1.4.1)
2.466,11 mm
(C3.1.4.2)
e MAX e s ; e y ; eb e s
1)
e s
(C3.1.5.1a)
P R 2 f z 0,5 P
0,8 2.466,11 2 204,17 1 0,5 0,8
c
1
e s = 5
,84 mm
(C3.1.5.1b)
100 m³ BUTANE TANK CALCULATIONS
r
2)
Di
0,1
r Di
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: 13.06.2011 : 5/23
0,18
0,2 :
e Y MIN ; 0,04 0,0032 R
1,006
1 N 4 6,2 90Y
1,006
1 6, 2 90 0,0065
4
Z log Y 2,501
10 0,2
0,845
(C3.1.5.1.c8)
(C3.1.5.1.c7)
0,1 r 0,1 0, 2 Di Di r
(C3.1.5.1.c4)
0,1
N 0,1833 Z 3 1,0383 Z 2 1,2943 Z 0,8370 = 1,037
(C3.1.5.1.c3)
0, 2
MAX 0,532 1,843Y 78,375Y 2 ; 0,5=0,525
(C3.1.5.1.c5)
10 0,2
e y
3)
0,1 r 0,1 0, 2 0,61 Di Di r
0,75 R 0,2 Di c
(C3.1.5.1c)
f
e y = 6 ,8 mm
D eb 0,04330,75 R 0,2 Di i r
0, 55
P f
0 , 667
c
eb = 7 ,78 mm
e MAX e s ; e y ; eb
[ (5,84 mm) ; (6,80 mm) ; (7,78 mm) ]
emin = 7,78 mm for head thickness
(C3.1.5.1d)
100 m³ BUTANE TANK CALCULATIONS
Date Page No
4. THICKNESS CONTROL UNDER EXTERNAL PRESSURE Shell thickness ts = 8 mm is taken from internal pressure calculation 1 st Trial Find A and B Factor; D / 2 h 1,9
K = 1 L Lt (2 h2 / 3) 14.831 mm L Do
14.831 2.900
5,1
t 8 1 7 mm
Do t
2.900 7
414
A 0,00003 B=
A E 2
P a
=
from chart C4.9.1. 0,00003 199.900 2
4 B K 3 ( Do / t )
P a P
4 3 1 3 414
Find A and B Factor; D / 2 h 1,9
K = 1 L2 L / 4 3.708 mm
Do
0,01 MPa
0.01 MPa < 0. 05 MPa
2 nd Trial
L
=3
3.708 2.900
1,3
t 8 1 7 mm
therefore ring is required.
: 13.06.2011 : 6/23
100 m³ BUTANE TANK CALCULATIONS
Do t
2.900 7
414
A 0,00011
from chart C4.9.1.
B = 20
from chart C4.9.2.
P a
4 B K 3 ( Do / t )
P a P
4 20 1 3 414
0,064 MPa
0.064 MPa > 0. 05 MPa
Therefore 2 number rings are required.
Date Page No
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100 m³ BUTANE TANK CALCULATIONS
5. OPENING CALCULATIONS OF THE NOZZLES 5.1.FORMULAS
L d=d i
l
et
St
Sr S
,
et
, l
i
R
Dm
G
2 Ri e
Rp0t .2 Rm , f min 1 , 5 2 , 4 d m
2i et
d m'
2i et '
For k o Graph C5.1.3 on pg.772 shall be used
L k 0 Dm e
l MIN l ' MIN
d m et , (l t ) ' ' ' 0.5d m et , (l t )
The following condition shall be fulfilled
S f 0.5 P S t f t 0.5 P S r f r 0.5 P P G
,
lt
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100 m³ BUTANE TANK CALCULATIONS
Date Page No
: 13.06.2011 : 9/23
5.2.K5 NOZZLE P
0,8
Design pressure (N/mm2)
Dm
2886,78
Main diameter of the shell
Ri
1440
Inside radius of the shell
R el. head
2468,1969
Radius of the head
e
7,78
The min. head thickness
et
5,56
Thickness assumed for the branch
e't
5,56
Thickness assumed for the internal protruding branch portion
(σtensile)shell
490
Tensile stress (N/mm2)
(σyield) shell
355
Yield stress (N/mm2)
f
163,3
Allowable stress for the shell (N/mm2)
(σtensile) branch
415
Tensile stress (N/mm2)
(σyield) branch
240
Yield stress (N/mm )
f t
138,3
Allowable stress for the branch (N/mm2)
lt
200
Available length of branch (project length)
l't
0
Length of internal protruding branch portion (project length)
d
60,3
Nozzle outer diameter
di
51,18
Insider diameter of the branch
dm
55,74
Mean diameter of the branch
d'm
55,74
Mean diameter of the internal protruding branch portion
k o
1
Coefficient derived from graph C5.1.3 pg 772
δ
0,37
Value for k o (untile 4 ko is 1)
c
1
Corrosion allowance
L
129,4
Length of the shell contributing to the strength of the opening
l
15,9
l'
0
S
877,1
Ч°
2
3,7
St
126,3
G
198343,7
160.330,4
≥
Projection angle
158.675,0
opening is adequate
100 m³ BUTANE TANK CALCULATIONS
Date Page No
: 13.06.2011 : 10/23
5.3.MANHOLE CODAP Division 1, Volume 2, Part C P
0,8
Design pressure (N/mm2)
Dm
2889
Main diameter of the shell
Ri
1440
Inside radius of the shell
e
10
The shell thickness
et
20
Thickness assumed for the branch
e't
20
Thickness assumed for the internal protruding branch portion
(σtensile)shell
490
Tensile stress (N/mm2)
(σyield) shell
355
Yield stress (N/mm2)
f
163,3
Allowable stress for the shell (N/mm2)
(σtensile) branch
480
Tensile stress (N/mm2)
(σyield) branch
345
Yield stress (N/mm )
f t
160,0
Allowable stress for the branch (N/mm2)
lt
200
Available length of branch (project length)
l't
0
Length of internal protruding branch portion (project length)
d
609,6
Nozzle outer diameter
di
571,6
Insider diameter of the branch
dm
590,6
Mean diameter of the branch
d'm
590,6
Mean diameter of the internal protruding branch portion
k o
1
Coefficient derived from graph C5.1.3 pg 772
δ
3,4
Value for k o (untile 4 ko is 1)
c
1
Corrosion allowance
L
161,2
Length of the shell contributing to the strength of the opening
l
105,9
l'
0
S
1451,2
St
2298,6
G
703956,8
2
opening is
603.314,5
≥
563.165,4
adequate
100 m³ BUTANE TANK CALCULATIONS
Date Page No
: 13.06.2011 : 11/23
5.4.N1-N2-N4 NOZZLES CODAP Division 1, Volume 2, Part C P
0,8
Design pressure (N/mm2)
Dm
2889
Main diameter of the shell
Ri
1440
Inside radius of the shell
e
10
The shell thickness
et
8,56
Thickness assumed for the branch
e't
8,56
Thickness assumed for the internal protruding branch portion
(σtensile)shell
490
Tensile stress (N/mm2)
(σyield) shell
355
Yield stress (N/mm2)
f
163,3
Allowable stress for the shell (N/mm2)
(σtensile) branch
415
Tensile stress (N/mm2)
(σyield) branch
240
Yield stress (N/mm )
f t
138,3
Allowable stress for the branch (N/mm2)
lt
200
Available length of branch (project length)
l't
0
Length of internal protruding branch portion (project length)
d
114,3
Nozzle outer diameter
di
99,18
Insider diameter of the branch
dm
106,74
Mean diameter of the branch
d'm
106,74
Mean diameter of the internal protruding branch portion
k o
1
Coefficient derived from graph C5.1.3 pg 772
δ
0,6
Value for k o (untile 4 ko is 1)
c
1
Corrosion allowance
L
161,2
Length of the shell contributing to the strength of the opening
l
28,4
l'
0
S
1451,2
St
320,2
G
316348,5
280.621,2
≥
2
253.078,8
opening is adequate
100 m³ BUTANE TANK CALCULATIONS
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: 13.06.2011 : 12/23
5.5.N3-N5-N7-K4 NOZZLES CODAP Division 1, Volume 2, Part C P
0,8
Design pressure (N/mm2)
Dm
2889
Main diameter of the shell
Ri
1440
Inside radius of the shell
e
10
The shell thickness
et
5,56
Thickness assumed for the branch
e't
5,56
Thickness assumed for the internal protruding branch portion
(σtensile)shell
490
Tensile stress (N/mm2)
(σyield) shell
355
Yield stress (N/mm2)
f
163,3
Allowable stress for the shell (N/mm2)
(σtensile) branch
415
Tensile stress (N/mm2)
(σyield) branch
240
Yield stress (N/mm )
f t
138,3
Allowable stress for the branch (N/mm2)
lt
200
Available length of branch (project length)
l't
0
Length of internal protruding branch portion (project length)
d
60,3
Nozzle outer diameter
di
51,18
Insider diameter of the branch
dm
55,74
Mean diameter of the branch
d'm
55,74
Mean diameter of the internal protruding branch portion
k o
1
Coefficient derived from graph C5.1.3 pg 772
δ
0,3
Value for k o (untile 4 ko is 1)
c
1
Corrosion allowance
L
161,2
Length of the shell contributing to the strength of the opening
l
15,9
l'
0
S
1451,2
St
138,7
G
276251,8
255.583,3
≥
2
221.001,4
opening is adequate
100 m³ BUTANE TANK CALCULATIONS
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: 13.06.2011 : 13/23
5.6.N6 NOZZLE CODAP Division 1, Volume 2, Part C P
0,8
Design pressure (N/mm2)
Dm
2889
Main diameter of the shell
Ri
1440
Inside radius of the shell
e
10
The shell thickness
et
7,62
Thickness assumed for the branch
e't
7,62
Thickness assumed for the internal protruding branch portion
(σtensile)shell
490
Tensile stress (N/mm2)
(σyield) shell
355
Yield stress (N/mm2)
f
163,3
Allowable stress for the shell (N/mm2)
(σtensile) branch
415
Tensile stress (N/mm2)
(σyield) branch
240
Yield stress (N/mm )
f t
138,3
Allowable stress for the branch (N/mm2)
lt
200
Available length of branch (project length)
l't
0
Length of internal protruding branch portion (project length)
d
88,9
Nozzle outer diameter
di
75,66
Insider diameter of the branch
dm
82,28
Mean diameter of the branch
d'm
82,28
Mean diameter of the internal protruding branch portion
k o
1
Coefficient derived from graph C5.1.3 pg 772
δ
0,4
Value for k o (untile 4 ko is 1)
c
1
Corrosion allowance
L
161,2
Length of the shell contributing to the strength of the opening
l
23,3
l'
0
S
1451,2
St
246,4
G
297428,9
270.444,1
≥
2
237.943,1
opening is adequate
100 m³ BUTANE TANK CALCULATIONS
Date Page No
: 13.06.2011 : 14/23
6. LIFTING LUG STRESS CALCULATIONS
Material
: P355NL1
Pad
: P355NL1
Lug Thickness
: 17 mm
Pad Thickness
: 10 mm
Total Tank Weight
: 15,000 kg (100 m3 Approx. Tank Weight)
Numbers of Lifting Lugs
:1
Note: It is known that there is 3 lifting lugs on the drawing however only one of them is used in Isısan Factory. Design Load (F)
: 15,000 kg ≈ 147.2 kN
Distance, centerline of hole to component (h)
: 70 mm
Diameter of hole (d)
: 90 mm
Radius of lug (r)
: 95 mm
Corrosion (c )
:1
em
K S
345 1.50
230 N mm2 (Sb: allowable bending stress of lug)
100 m³ BUTANE TANK CALCULATIONS
em
em 2
Date Page No
115 N mm2 (S: allowable shear stress of lug)
Required Thickness For Shear t
F 2 ( S ) (r d / 2)
106 c
147.2 2 (11510 ) (95 90 / 2) 3
106 1 = 14.2 mm
Required Thickness For Bending t
6 F h
S b ( L)
10 6 c 2
6 (147.2) 70 230 10
3
(190)
2
10 6 1 = 8 .6 mm
17 mm thickness is ok. 7. SADDLE STRESS CALCULATIONS Saddle material: Saddle construction is: Saddle allowable stress: Saddle yield stress: Saddle distance to datum: Tangent to tangent length: Saddle separation: Vessel radius: Tangent distance left: Tangent distance right: Saddle height: Saddle contact angle: Wear plate thickness: Wear plate width: Wear plate contact angle: Web plate thickness: Base plate length: Base plate width: Base plate thickness: Number of stiffener ribs: Largest stiffener rib spacing: Stiffener rib thickness: Saddle width: Anchor bolt size & type: Anchor bolt material:
S355J2 Centered web Ss = 140 MPa Sy = 355 MPa 2.300 mm L = 14.351,6 mm Ls = 9.650 mm R = 1.450 mm Al = 2.350,8 mm Ar = 2.350,8 mm Hs = 1.700 mm ° = 120 t p = 10 mm W p = 600 mm ° w = 132 ts = 15 mm E = 2.600 mm F = 400 mm t b = 17 mm n= 5 di = 636,83 mm tw = 12,7 mm B = 400 mm 20 mm
: 13.06.2011 : 15/23
100 m³ BUTANE TANK CALCULATIONS
Anchor bolt allowable shear: Anchor bolt corrosion allowance: Anchor bolts per saddle: Base coefficient of friction: =
Date Page No
: 13.06.2011 : 16/23
103,421 MPa 0 mm 2 0,45
Weight on left saddle: operating corr = 5.682,15 kg, test new = 55.512,9 kg Weight on right saddle: operating corr = 5.897,15 kg, test new = 55.728,36 kg Weight of saddle pair = 1.075,01 kg
Notes: (1) Saddle calculations are based on t he method presented in "Stresses in Large Cylindrical Pressure Vessels on Two Saddle Supports" by L.P. Zick.
Load
Vessel condition
Bending + pressure between saddles Bending + pressure at the saddle (MPa) (MPa) allow (+)
S1
(+)
S1
allow
S2
(-)
(-)
(+)
allow (+)
S2
allow
(-)
(-)
Weight Operating 58,545
153,591
0,935
71,674
61,334
153,591
3,724
71,674
Weight Test
319,5
8,836
71,674
106,076
319,5
35,779
71,674
Load
Vessel condition
79,133
Tangential shear (MPa)
S4
S3 Weight Operating 2,982 Weight Test
Circumferential stress (MPa) S4
allow (horns)
(Wear plate)
122,873 -24,174
-40,108
27,911 255,6
-228,448
allow (+/-)
Stress over Splitting (MPa) saddle (MPa) S5
230,386 7,833
-379,019 319,5
74,024
allow
S6
allow
177,5
1,259
93,333
319,5
11,901
319,5
Load Case 1: Weight ,Operating
Longitudinal stress between saddles (Weight ,Operating, right saddle loading and geometry govern) S1 = +- 3*K 1*Q*(L/12) / ( *R 2*t) = 3*0,2956*57.831,34*(14.351,6/12) / ( *1.4452*10) = 0,935 MPa S p = P*R/(2*t)
100 m³ BUTANE TANK CALCULATIONS
Date Page No
= 0,8*1.440/(2*10) = 57,61 MPa Maximum tensile stress S1t = S1 + S p = 58,545 MPa Maximum compressive stress (shut down) S 1c = S1 = 0,935 MPa Tensile stress is acceptable (<=1*S*E = 153,591 MPa) (153,591 MPa) Compressive stress is acceptable (<=1*Sc = 71,674 MPa)
Longitudinal stress at the right saddle (Weight ,Operating) Le = 2*(Left head depth)/3 + L + 2*(Right head depth)/3 = 2*728,23/3 + 14.351,6 + 2*730/3 = 15.323,76 mm w = Wt/Le = 113.554,22*10/15.323,76 = 74,1 N/cm Bending moment at the right saddle: 2
2
2
Mq = w*(2*H*Ar /3 + Ar /2 - (R - H )/4) = 74,1/10000*(2*730*2.350,8/3 + 2.350,8 2/2 - (1.4502 - 7302)/4) = 26.045,7 N-m S2 = +- Mq*K 1 '/ (*R *t) = 26.045,7*1e3*9,3799/ ( *1.445 2*10) = 3,724 MPa 2
S p = P*R/(2*t) = 0,8*1.440/(2*10) = 57,61 MPa Maximum tensile stress S2t = S2 + S p = 61,334 MPa Maximum compressive stress (shut down) S 2c = S2 = 3,724 MPa Tensile stress is acceptable (<=1*S = 153,591 MPa) Compressive stress is acceptable (<=1*Sc = 71,674 MPa)
Tangential shear stress in the shell (right saddle, Weight ,Operating) Qshear = Q - w*(a + 2*H/3) = 57.831,34 - 7,41*(2.350,8 + 2*730/3) = 36.804,75 N S3 = K 2,2*Qshear /(R*t) = K 2,2*36.804,75/(1.445*10) = 2,982 MPa Tangential shear stress is acceptable (<= 0.8*S = 122,873 MPa)
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100 m³ BUTANE TANK CALCULATIONS
Date Page No
: 13.06.2011 : 18/23
Circumferential stress at the right saddle horns (Weight ,Operating) S4 = -Q/(4*(t+t p)*(b+1,56*Sqr(R o*t))) - 3*K 3*Q/(2*(t2+t p2)) 2 2 = -57.831,34/(4*(10+10)*(400+1,56*Sqr(1.450*10))) - 3*0,0529*57.831,34/(2*(10 +10 )) = -24,174 MPa Circumferential stress at saddle horns is acceptable (<=1,5*Sa = 230,386 MPa)
Circumferential stress at the right saddle wear plate horns (Weight ,Operating) S4 = -Q/(4*t*(b+1,56*Sqr(R o*t))) - 3*K 3*Q/(2*t2) 2 = -57.831,34/(4*10*(400+1,56*Sqr(1.450*10))) - 3*0,0434*57.831,34/(2*10 ) = -40,108 MPa Circumferential stress at wear plate horns is acceptable (<=1,5*Sa = 230,386 MPa)
Ring compression in shell over right saddle (Weight ,Operating) S5 = K 5*Q/((t + t p)*(ts + 1,56*Sqr(R o*tc))) = 0,7603*57.831,34/((10 + 10)*(15 + 1,56*Sqr(1.450*20))) = 7,833 MPa Ring compression in shell is acceptable (<= 0,5*S y = 177,5 MPa)
Saddle splitting load (right, Weight ,Operating) Area resisting splitting force = Web area + wear plate area Ae = Heff *ts + t p*W p = 22,3*1,5 + 1*60 = 93,45 cm2 S6 = K 8*Q / Ae = 0,2035*57.831,34 / 9.344,9986 = 1,259 MPa Stress in saddle is acceptable (<= (2/3)*Ss = 93,333 MPa) Load Case 2: Weight ,Test
Longitudinal stress between saddles (Weight ,Test, right saddle loading and geometry govern) S1 = +- 3*K 1*Q*(L/12) / ( *R *t) 2
= 3*0,2956*546.508,57*(14.351,6/12) / ( *1.4452*10) = 8,836 MPa
100 m³ BUTANE TANK CALCULATIONS
S p = P*R/(2*t) = 0,98*1.440/(2*10) = 70,297 MPa
Maximum tensile stress S1t = S1 + S p = 79,133 MPa Maximum compressive stress (shut down) S 1c = S1 = 8,836 MPa
Tensile stress is acceptable (<= 0,9*Sy = 319,5 MPa) (319,5 MPa) Compressive stress is acceptable (<=1*Sc = 71,674 MPa)
Longitudinal stress at the right saddle (Weight ,Test) Le = 2*(Left head depth)/3 + L + 2*(Right head depth)/3 = 2*728,23/3 + 14.351,6 + 2*730/3 = 15.323,76 mm
w = Wt/Le = 1.090.904,24*10/15.323,76 = 711,9 N/cm
Bending moment at the right saddle:
2
2
2
Mq = w*(2*H*Ar /3 + Ar /2 - (R - H )/4) = 711,9/10000*(2*730*2.350,8/3 + 2.350,8 2/2 - (1.4502 - 7302)/4) = 250.218,9 N-m
S2 = +- Mq*K 1 '/ (*R *t) 2
= 250.218,9*1e3*9,3799/ ( *1.445 2*10) = 35,779 MPa
S p = P*R/(2*t) = 0,98*1.440/(2*10) = 70,297 MPa
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100 m³ BUTANE TANK CALCULATIONS
Date Page No
: 13.06.2011 : 20/23
Maximum tensile stress S2t = S2 + S p = 106,076 MPa Maximum compressive stress (shut down) S 2c = S2 = 35,779 MPa
Tensile stress is acceptable (<= 0,9*Sy = 319,5 MPa) Compressive stress is acceptable (<=1*Sc = 71,674 MPa)
Tangential shear stress in the shell (right saddle, Weight ,Test) Qshear = Q - w*(a + 2*H/3) = 546.508,57 - 71,19*(2.350,8 + 2*730/3) = 344.508,2 N
S3 = K 2,2*Qshear /(R*t) = K 2,2*344.508,2/(1.445*10) = 27,911 MPa
Tangential shear stress is acceptable (<= 0.8*S = 255,6 MPa)
Circumferential stress at the right saddle horns (Weight ,Test) 2
2
S4 = -Q/(4*(t+t p)*(b+1,56*Sqr(R o*t))) - 3*K 3*Q/(2*(t +t p )) = -546.508,57/(4*(10+10)*(400+1,56*Sqr(1.450*10))) - 3*0,0529*546.508,57/(2*(10 2+102)) = -228,448 MPa
Circumferential stress at saddle horns is acceptable (<= 0,9*Sy = 319,5 MPa)
Circumferential stress at the right saddle wear plate horns (Weight ,Test) S4 = -Q/(4*t*(b+1,56*Sqr(R o*t))) - 3*K 3*Q/(2*t2) = -546.508,57/(4*10*(400+1,56*Sqr(1.450*10))) - 3*0,0434*546.508,57/(2*10 2) = -379,019 MPa
100 m³ BUTANE TANK CALCULATIONS
Date Page No
Ring compression in shell over right saddle (Weight ,Test) S5 = K 5*Q/((t + t p)*(ts + 1,56*Sqr(R o*tc))) = 0,7603*546.508,57/((10 + 10)*(15 + 1,56*Sqr(1.450*20))) = 74,024 MPa
Ring compression in shell is acceptable (<= 0,5*S y = 319,5 MPa)
Saddle splitting load (right, Weight ,Test) Area resisting splitting force = Web area + wear plate area
Ae = Heff *ts + t p*W p = 22,3*1,5 + 1*60 = 93,45 cm2
S6 = K 8*Q / Ae = 0,2035*546.508,57 / 9.344,9986 = 11,901 MPa
Stress in saddle is acceptable (<= 0,9*Sy = 319,5 MPa)
Shear stress in anchor bolting, one end slotted Maximum seismic or wind base shear = 0 N
Thermal expansion base shear = W* = 63.102,48 * 0,45= 28.396,12 N
Corroded root area for a 20 mm bolt = 2,3484 cm2 ( 2 per saddle )
Bolt shear stress = 28.396,11/(234,8382*2) = 60,459 MPa
: 13.06.2011 : 21/23
100 m³ BUTANE TANK CALCULATIONS
Date Page No
: 13.06.2011 : 22/23
Anchor bolt stress is acceptable (<= 103,421 MPa)
Web plate buckling check (Escoe pg 251) Allowable compressive stress Sc is the lesser of 140 or 128,335 MPa: (128,335)
Sc = K i* *E/(12*(1 - 0,3 )*(di/tw) ) 2
2
2
= 1,28*2*19,99E+04/(12*(1 - 0,3 2)*(636,83/15)2) = 128,335 MPa
Allowable compressive load on the saddle
be = di*ts/(di*ts + 2*t w*(b - 1)) = 25,0719*0,5906/(25,0719*0,5906 + 2*0,5*(15,748 - 1)) = 0,501
F b = n*(As + 2*be*tw)*S c = 5*(4.889,5 + 2*12,73*15)*128,335 = 3.382.439,81 N
Saddle loading of 551.779,72 N is <= F b; satisfactory.
Primary bending + axial stress in the saddle due to end loads (assumes one saddle slotted)
b = V * (H s - xo)* y / I + Q / A = 0 * (1.700 - 1.199,14)* 200 / (1e4*33.887,76) + 57.831,34 / 62.119,6 = 0,931 MPa
The primary bending + axial stress in the saddle < = 140 MPa; satisfactory.
100 m³ BUTANE TANK CALCULATIONS
Date Page No
: 13.06.2011 : 23/23
Secondary bending + axial stress in the saddle due to end loads (includes thermal expansion, assumes one saddle slotted)
b = V * (H s - xo)* y / I + Q / A = 28.396,11 * (1.700 - 1.199,14)* 200 / (1e4*33.887,76) + 57.831,34 / 62.119,6 = 9,325 MPa
The secondary bending + axial stress in the saddle < 2*Sy= 710 MPa; satisfactory.
Saddle base plate thickness check (Roark sixth edition, Table 26, case 7a) where a = 636,83, b = 192,5 mm
t b = (1*q*b2/(1,5*Sa))0,5 2
0,5
= (3*0,531*192,5 /(1,5*140)) = 16,76 mm
The base plate thickness of 17 mm is adequate.
Foundation bearing check Sf = Qmax / (F*E) = 551.779,72 / (400*2.600) = 0,531 MPa
Concrete bearing stress < 11,432 MPa ; satisfactory.