v 2151 102 a 216 c design calculation sheet (filter)

7/30/2019 V 2151 102 a 216 C Design Calculation Sheet (Filter)

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Project : NOEV Lube Oil Blending Plant

Job Number : AL-2524

Document Number : V-2151-102-A-216

Reference Drawing : V-2151-102-A-201_Rev.C & V-2151-102-A-215_Rev.B

Package Name : Filter

Tag Number : F-901A/B, F-902A/B, F-903A/B, F-904A/B, F-905A/B, F-906A/B

C 27-May-2013

B 20-May-2013

A 27-Mar-2013

Rev Date

L.A.V

Checked

L.N.B

L.N.B

L.N.B

DESIGN CALCULATION SHEET

Description Prepared Approval

Issue for review / approval

Issue for review / approval

Issue for review / approval L.D.T

L.D.T

L.D.T

L.A.V

L.A.V



Project: NOEV Lube Oil Blending Plant Job No.: AL-2524 Rev. No

INDEX PAGE

1. Design Data 2

2. Shell Thickness Calculation 2

3. Bottom Head Thickness Calculation 3

4. Top Head Thickness & Swing Bolt Diameter Calculation 3

5. Nozzle Calculation 4

6. Weld Size Calculation 7

7. Reinforcement 8

8. Weight Calculation Sheet 109. Wind load Analysis 10

10. Seismic Analysis 11

11. Skirt Support design for Wind/Seismic 12

12. Lifting Lug Calculation 17

13. Hydrotest Pressure 20

14. Conclusion 21

DESIGN CALCULATION SHEET

Page 1 of



Project: NOEV Lube Oil Blending Plan Job No.: AL-2524 Rev. No

1. Design Data

Design Code : ASME Sec VIII Div.1 2010 Ed., 2011a add.

Code Stamp: No

Service: Lube Oil

Design pressure

Internal pressure P = 11.8 bar = 1.18 MPa

External pressure 0.0 bar = 0.0 MPa

Working pressure 4.8 bar = 0.48 MPa

Design temperature 105.0 degree C

Working temperature 40 degree C

Corrosion allowance 0.0 mm

Vessel inside diameter 396 mm (O/D = 406 mm)

Vessel length (T to T) 1020 mm

Bottom Head type: 2:1 Ellipsoidal Head

MinimumDesignMetalTemperature 6.0 degree C

Material

Shell SA-240M TP304/304L

Head SA-240M TP304/304L

Nozzle Flange SA-182M F304/304L or SA-240M TP304/304L

Nozzle Neck (Pipe) SA-312M TP304/304L

Skirt Support SA-240M TP304/304L

Nozzle Flange: ASME B16.5 Standard

SCH THK.

N1 150 40S 5.49

N2 150 40S 5.49

N3 150 80S 3.91

N4 150 80S 3.91

HH 150 - 5

2. Shell Thickness Calculation (Refer to UG-27)

2.1 Minimum required thickness of shell exclusive corrosion allowance (t):

Circumferential Stress (Longitudinal Joints)

1.18 x 198.0

115.0 x 0.85 - 0.6 x 1.18

where:

P : internal design pressure P = 1.18 MPa < 0.385SE = 37.634 MPa

R : Inside radius of the shell R = 198.0 mm

S : Maximum allowable stress value S = 115.0 MPa

E : Joint efficiency E = 0.85

Longitudinal Stress (Circumferential Joints)

1.18 x 198.0 233.6

2.0 x 115.0 x 0.85 + 0.4 x 1.18 196.0

where:

DN 80 (3") SO RF 88.9 77.92

DN 20 (3/4") SO RF 26.7 18.88

DN 20 (3/4") SO RF 26.7 18.88

DN 400 (16") SO RF 406 396

==

= =

97.0

Nozzle Size Flange Type ClassNozzle Neck Nozzle outside

diameter, mm

Nozzle inside

diameter, mm

DN 80 (3") SO RF 88.9 77.92

mm

mm

2.41

= 1.19

=233.6

Page 2 o





Degree of Radiographic Examination: Spot

2.2 Minimum Thickness of Pressure retaining Components (UG-16 (b)) = 2.5 mm

2.3 Choose Nominal thickness of shell, ts = 5 mm

3. Bottom Head Thickness Calculation (Refer to UG-32)

Type of head: 2:1 Ellipsoidal Head

3.1 Minimum required thickness of Head exclusive corrosion allowance (t):

1.18 x 396.0 467.3

2.0 x 115.0 x 1.00 - 0.2 x 1.18 229.8

where:

P : internal design pressure P = 1.18 MPa < 0.385SE = 44.275 MPa

D : Inside diameter of the head skirt D = 396.0 mm



3.2 Minimum required thickness of Head included corrosion allowance

= 2.03 + 0.0 = 2.03 mm

3.3 Minimum required thickness of Head, ts = Min. 2.03 mm

3.4 MDMT

Refer to UG-20 (f): MDMT = -29 degree C

4. Top Head Calculation (Refer to ASME B16.5)

4.1 Thickness of Top Head

Thickness of Top Head selected base on thickness of Blind Flange DN400 (16") ASME B16.5 Pressure Rating 150

Material: SA-240 TP304/304L (Material Group 2.3)

=> Top Head thickness = 37 mm (included raise face)

4.2 Swing Bolt diameter

Bolt material SA-193 GR.B8

Allowable stress of bolt material = 112.8 MPa (refer to ASME Section II, Part D)

Compress force on Top Head, F = A x P = N

Tensile force per one bolt, f = F / n = 9083 N

Tensile strenght per one bolt, τ = f / Ab = 45.18 MPa < 112.8 MPa

Result : PASS

where

A = 123163 mm2 area of Top head resist internal pressure

P = 1.18 MPa internal design pressure

n = 16 quantity of bolt

145332.3

= = mm2.03=

Page 3 o




db = 16 mm diameter of bolt

Ab = 201.1 mm^2 section area of bolt

5. Nozzle calculation (Refer to UG-45)

5.1 Nozzle Neck N1, N2_DN 80 (3")

Minimum Nozzle neck thickness

where:



Nozzle inside radius Rn = 38.96 mm

tn (min) : minimum required thickness of Nozzle

5.1.1 ta : minimum neck thickness required for internal and external pressure using UG-27 and UG-28

(plus corrosion allowance), as applicable. The effects of external forces and moments from supplemental

loads (see UG-22) shall be considered. Shear stresses caused by UG-22 loadings shall not exceed 70%

of the allowable tensile stress for the nozzle material.

1.18 x 38.96 45.973

115.0 x 1.00 - 0.6 x 1.18 114.3

ta = 0.40 + 0.0 = 0.40 mm

5.1.2 = min ( 4.80 , 2.50 ) = 2.50 mm

where:

tb1 : for vessels under internal pressure, the thickness (plus corrosion allowance) required for pressure

(assuming E = 1.0) for the shell or head at the location where the nozzle neck or other connection

attaches to the vessel but in no case less than the minimum thickness specified for the material in UG-16(b).

tb1 = 2.50 mm

tb2 : for vessels under external pressure (not applicable to this vessel)tb2 = 0 mm

Max (tb1, tb2) = Max ( 2.50 , 0.0 ) = 2.50 mm

tb3 : the thickness given in Table UG-45 plus the thickness added for corrosion allowance.

(for standard wall pipe)

tb3 = 4.8 + 0.0 = 4.80 mm

=> = max ( 0.40 , 2.50 ) = 2.50 mm

5.1.3 Choose Nozzle Neck thickness = 5.49 mm (SCH 40S)

5.1.4 Nozzle actual thickness is compared with the minimum thickness provided which for pipe

material would include a 12.5% undertolerance

= 0.875 x 5.49 = 4.80 > tn (min) = 2.50 mm

Result: the actual thickness provided meets the rules of UG-45 <PASS>

5.2 Nozzle Neck N3_DN 20 (3/4")


= = = 0.40 mm

bant t t ,max(min)

bant t t ,max(min)

bant t t ,max(min)

Page 4 o




where:









1.18 x 9.44 11.139

115.0 x 1.00 - 0.6 x 1.18 114.3

ta = 0.10 + 0.0 = 0.10 mm

5.2.2 = min ( 2.51 , 2.50 ) = 2.50 mm

where:




tb1 = 2.50 mm

tb2 : for vessels under external pressure (not applicable to this vessel)

tb2 = 0 mm

Max (tb1, tb2) = Max ( 2.50 , 0.0 ) = 2.50 mm



tb3 = 2.51 + 0.0 = 2.51 mm

=> = max ( 0.10 , 2.50 ) = 2.50 mm




= 0.875 x 3.91 = 3.42 > tn (min) = 2.50 mm


5.3 Nozzle Neck N4_DN 20 (3/4")


where:







= 0.10 mm= =

bant t t ,max(min)

bant t t ,max(min)

Page 5 o






1.18 x 9.4 11.139

115.0 x 1.00 - 0.6 x 1.18 114.3

ta = 0.10 + 0.0 = 0.10 mm

5.3.2 = min ( 2.51 , 37.0 ) = 2.51 mm

where:




tb1 = 37.00 mm

tb2 : for vessels under external pressure (not applicable to this vessel)

tb2 = 0 mm

Max (tb1, tb2) = Max ( 37.00 , 0.0 ) = 37.0 mm



tb3 = 2.51 + 0.0 = 2.51 mm

=> = max ( 0.10 , 2.51 ) = 2.51 mm




= 0.875 x 3.91 = 3.42 > tn (min) = 2.51 mm


6. Weld size calculation (Refer to UW-16)

6.1 Nozzle N1 & N2 to Shell weld joints

6.1.1 Size of weld / Shell thickness

tn (actual) = 5.49 mm

Fillet Leg Length = 6.00 mm

=> tc (actual) = 4.20 mm

t = 5.00 mm

6.1.2 Check for full penetration groove weld and fillet cover weld shown in Fig above

tc (min) = Min ( 6 , 0.7 tmin )

where:

tmin = the smaller of 19 mm or the thickness of the thinner of the parts joined by a fil let, single-bevel, or single-J weld

tmin = Min ( 19.0 , 5.49 , 5.00 ) = 5.49 mm

0.7tmin = 0.7 x 5.49 = 3.84 mm

=> tc (min) = Min ( 6 , 0.7 tmin ) = Min ( 6.00 , 3.84 ) = 3.84 < tc (actual) = 4.2 mm

= 0.10 mm= =

bant t t ,max(min)

Page 6 o



Project: NOEV Lube Oil Blending Plan Job No.: AL-2524 Rev. N

=> PASS

6.2 Nozzle N3 to Bottom Head weld joint





t = 2.03 mm


tc (min) = Min ( 6 , 0.7 tmin )

where:

tmin = the smaller of 19 mm or the thickness of the thinner of the parts joined by a fillet, single-bevel, or single-J weld

tmin = Min ( 19.0 , 3.91 , 2.03 ) = 3.91 mm

0.7tmin = 0.7 x 3.91 = 2.74 mm


=> PASS

6.3 Nozzle N4 to Top Head weld joint





t = 37.00 mm


tc (min) = Min ( 6 , 0.7 tmin )

where:

tmin = the smaller of 19 mm or the thickness of the thinner of the parts joined by a fillet, single-bevel, or single-J weld

tmin = Min ( 19.0 , 3.91 , 37.00 ) = 3.91 mm

0.7tmin = 0.7 x 3.91 = 2.74 mm


=> PASS

7. Reinforcement

7.1 Reinforcement for Nozzle N3, N4_DN 20 (3/4")

Refer to UG-36C (3) reinforcements are not required for Nozzle 2" and smaller

7.2 Reinforcement for Nozzle N1, N2_DN 80 (3")

Reinforcement material: SA-240 TP304/304L

Dp : outside diameter of reinforcing element = 150 mm

te : thickness or height of reinforcing element = 5 mm

A : total cross-sectional area of reinforcement required in the plane under consideration

Page 7 o



Project: NOEV Lube Oil Blending Plan Job No.: AL-2524 Rev.

(includes consideration of nozzle area through shell if Sn /Sv < 1.0)

A = dtr F + 2tn tr F (1-f r1) = 194.8 mm2

A1 : area in excess thickness in the vessel wall available for reinforcement

(includes consideration of nozzle area through shell if Sn /Sv<1.0)

A1 = larger of below value = 195 mm2

d(E1t - Ftr ) - 2tn(E1t - Ftr )(1 - f r1) = 194.8 mm2

2(t + tn)(E1t - Ftr ) - 2tn(E1t - Ftr )(1 - f r1) = 52.45 mm2

A2 : area in excess thickness in the nozzle wall available for reinforcement (see Fig. UG-37.1)

A2 = smaller of below value = 74.5 mm2

5(tn - tr n) f r2t = 74.5 mm2

5(tn - tr n) f r2tn = 81.8 mm2

A3 : area available for reinforcement when the nozzle extends inside the vessel wall

A3 = min (5t ti f r2, 5ti ti f r2, 2h ti f r2) = 0 mm2

A5 : cross-sectional area of material added as reinforcement

A5 = (DP - d - 2tn)te f r4 = 305.5 mm2

where:

d : finished diameter of circular opening or finished dimension = 77.92 mm

h : distance nozzle projects = 0 mm

t : specified vessel wall thickness = 5 mm

tn : nozzle wall thickness = 5.49 mm

tr : required thickness of a seamless shell = 2.5 mm

tr n : required thickness of a seamless Nozzle wall = 2.5 mm

ti : nominal thickness of internal projection of nozzle wall = 0 mm

S : allowable stress value in tension = 115.0 MPa

Sn : allowable stress in nozzle = 115.0 MPa

Sp : allowable stress in reinforcing element = 115.0 MPa

Sv : allowable stress in vessel = 115.0 MPa

Page 8



Project: NOEV Lube Oil Blending Plan Job No.: AL-2524

F : correction factor = 1

E1 = 1

f r1 = 1

f r2 = Sn /Sv = 1

f r3 = Min (Sn/S or Sp/S) = = 1

f r4 = Sp /Sv = 1

A1 + A2 + A3 + A5 = 575 mm2 > A = 195 mm2

RESULT : PASS

8. Weight Calculation Sheet

No.Thickness

(mm)Q'ty

Unit

Weight

(kg)

Total

Weight

(kg)

1 Shell 5.0 1 54.2 54.18

2 Bottom Head 5.0 1 8.87 8.87

3 HH Flange 37 1 40.65 40.65

4 HH Cap & Swing Bolts 37 1 99.07 99.07

6 Hinge Backet 16 1 1.85 1.85

7 Hinge Backet 8 2 0.22 0.45

8 Skirt Support 5 1 13.75 13.75

9 Base Plate 8 1 3.85 3.85

10 Gusset Plate 5 4 0.06 0.25

12 Lifting Lug 16 2 0.96 1.93

13 Nozzle N1 - Neck - 0.15 11.52 1.73 3" SCH 40S

14 Nozzle N1 - Flange - 1 3.70 3.70 3" 150#

15 Nozzle N2 - Neck - 0.15 11.52 1.73 3" SCH 40S

16 Nozzle N2 - Flange - 1 3.70 3.70 3" 150#

17 Nozzle N3 - Neck - 0.46 2.00 0.92 3/4" SCH 80S

18 Nozzle N3 - Flange - 1 0.90 0.90 3/4" 150#

19 Nozzle N4 - Neck - 0.15 2.00 0.30 3/4" SCH 80S

20 Nozzle N4 - Flange - 1 0.90 0.90 3/4" 150#

28 Filter Components - 1 10.00 10.00

Empty Weight 248.7

Weight of Liquid at Operating Level 123.5

Weight of Full Water 139.55

Total Weight of Liquid at Operating Level 372.2

Total Weight of Full Water 388.3

9. Wind load Analysis (Refer to Pressure Vessel Handbook 10th Edition - By Eugene F. Megyesy)

Ea

Description Unit Remark

Ea

Ea

Ea

Ea

Ea

Ea

Ea

Ea

Ea

Ea

Ea

m

Ea

m

Ea

m

Ea

m




9.1 Design Data

D : Outside Vessel Diameter = 406 mm

H : Overall Height of Vessel = 1430 mm (Base on GA Drawing)

h ~ H/2 : Distance to the center of the projected area = 715 mm

hT : Distance from base to the skirt to head joint = 288 mm

Exposure Category = B

V : Wind Basic Speed = 39 m/sec = 87.24 mph

G : Gust factor combined with Exposure Coefficient = 0.6

Cf : Shape factor = 0.8

I : Importance factor = 1.08 (As per Specification)

9.2 Design Calculation

Projected area of vessel

Af = D x H = = 580580 mm2

= 0.5806 m2

Velocity pressure

qz = 0.00256 x (IV)2 = 22.727 psf = 1088.2 N/m

2

Design Wind force (Shear force)

F = qz x G x Cf x Af = 303.25 N

Moment at the base plate

M = F x h = 216826 Nmm = 216.83 Nm

Moment at the skirt to head joint

MT = M - hT(F - 0.5 x qz x D x hT) = 147.81 Nm

10. Seismic Analysis (Refer to Pressure Vessel Handbook 10th Edition - By Eugene F. Megyesy)

406 x 1430

Page 10 o




10.1 Design Data

W : Operating Weight of Vessel = 372.2 kg = 3651.5 N


H : Overall Height of Vessel = 1430 mm = 4.6916 ft.

X : Distance from top tangent line to the skirt to head joint = 1142 mm (Base on GA Drawing)

Z : Seismic zone factor = 0.4 (Choose Max. Factor)

I : Occupancy Importance coefficient = 1

Rw : Numerical coefficient = 4

Ct : Numerical coefficient = 0.035

S : Site coefficient for soil characteristics = 1.35 (As per Specification)

10.2 Design Calculation

Fundamental period of vibration

T = Ct x H3/4

= 0.112 sec < 0.7 sec

Numberical coefficient

Choose C = 2.75

Total seismic shear

Total horizontal seismic force at top of the vessel

Ft = 0 N ( for T≤ 0.7 sec )

Maximum moment (at the base)

= 957.3 Nm

2.75

= 1004.2=0.4 x 1 x 2.75

4x 3651.5 N

= >7.2812 =1.25×

/3

Page 11 o




With X = 1142 mm > H/3 = 476.67 mm

Thus

Moment at the skirt to head joint

= 668.1 Nm

11. Skirt Support design for Wind/Seismic (Refer to Pressure Vessel Handbook 10th Edition - By Eugene F. Megyesy)

Moment at base in Wind Case

Mw = 216.83 Nm

Moment at the skirt to head joint in Wind Case

MwT = 147.81 Nm

Moment at base in Seismic Case

Ms = 957.3 Nm

Moment at the skirt to head joint in Seismic Case

MsT = 668.1 Nm

Maximum Moment at base in Skirt Support Design

M = = 957.3 Nm

Maximum Moment at the skirt to head joint in Skirt Support Design

MT = = 668.1 Nm

11.1 Design of Skirt thickness



R : Outside Vessel Radius = 203 mm

E : Efficiency of skirt to head joint = 0.6 (butt weld as figure above)

S : Allowable Stress value of the head or skirt material = 115 MPa

MT : Maximum Moment at the skirt to head joint = 668.1 Nm

The required skirt thickness

= 0.94 mm

Use 5 mm thickness plate for skirt.

11.2 Design of Anchor Bolt and Base Plate

Max(Mw , Ms)

Max(MwT , MsT)

Head

Skirt

Page 12 o





D = d : Diameter of anchor bolt circle = 425 mm

dB : Anchor Bolt Size

r : Radius of anchor bolt circle = 212.5 mm

n : Ratio of modulus of elasticity of steel and concrete = 12 (Table E)

f c : Allowable compression strength of concrete = 7.5 MPa (As per Specification)

l1 : Actual Cantilever outside = 45 mm

l2 : Dimension as shown on sketch above = 22.5 mm

l3 : Dimension as shown on sketch above = 27.5 mm

l : Actual Width of Base Plate = 45 mm

S : Allowable stress value of Base plate material = 115 MPa

Sa : Allowable tensile stress in bolts = 138 MPa

M : Maximum Moment at base = 957.3 Nm

Assume 45mm wide Base Ring and a compressive stress at the bolt circle, f cb = 0.8 f c = 6 MPa

Then the constants from Table D are:

Cc = 1.64

Ct = 2.333

j = 0.783

z = 0.427

Required area of anchor bolts

Using 4 anchor bolts, the required root area for one bolt is A = 634.84 / 4 = 158.71 mm2

A ~πdB

2

/4=> d

B= 14.215 mm

Choose Anchor Bolt Size M16 (5/8 in.)

Tensile load on the anchor bolts

Thickness of a ring

=1

1 + 138/(12 x 6)= 0.34

= 7.5 x2 x 0.34 x 425

= 6.50 MPa2 x 0.34 x 425 + 45

= = 634.84 mm22π x

12 x 957.3 - 3651.5 x 0.427 x 425

2.333 x 138 x 0.783 x 425

N=957.3 - 3651.5 x 0.427 x 425

0.783 x 425= 885.42

Page 13 o




= 0.48 mm

Tensile stress in the anchor bolts

Compressive load on the concrete

= = 4536.9 N

Width of the base ring

= = 44.52 mm

Compressive stress in the concrete at the bolt circle

Checking value of k which was calculated with assumed value of f cb = 6 MPa and Sa = 138 MPa

Then the constant from Table D are:

Cc = 1.884

Ct = 2.113

j = 0.785

z = 0.404

Tensile load on the anchor bolts

Tensile stress in the anchor bolts

Compressive load on the concrete

= = 4641.7 N

Compressive stress in the concrete at the bolt circle

Compressive stress in the anchor bolts

=990.15

0.48 x 212.5 x 2.113= 4.64 MPa

990.15 + 3651.5

= = 0.23 MPa4641.7

(44.52 + 12 x 0.48) x 212.5 x 1.884

=

= 0.259

=885.42

0.48 x 212.5 x 2.333= 3.76 MPa

MPa

=

885.42 + 3651.5

45 - 0.48

=4536.9

(44.52 + 12 x 0.48) x 212.5 x 1.64

=1

1 + 3.76/(12 x 0.259)0.453

957.3 -3651.5 x 0.404 x 425

0.785 x 425= N990.15

Page 14 o




= = 2.77 MPa

Compressive stress in the concrete at the outer edge of the base ring

Required thickness of base ring (without gussets)

= 3.69 mm

To decrease the thickness of the base ring, use gusset plates.

Using 4 gusset plates, the distance between the gussets,

= 333.79 mm

Ratio

= = 0.1348

Interpolate from table F:

= )2 = 245.8 Nmm

Base ring thickness with gusset

Using thickness of the base plate is 8 mm

12. Lifting Lug Calculation

0.47085 x 0.26 x (45

= 3.58 mm

12 x 0.231

0.26 MPa== 0.23 x2 x 0.453 x 425 + 45

2 x 0.453 x 425

45 / 333.79

Page 15 o




Equipment weight We = 248.7 kg

Lifting Lug material SA-240M TP304/304L

12.1 Check for β = 90 degrees

Angle β = 90.0 degree

Considered a load factor of 2.0 applied to the structure gravity loads

Design Load P = 2x9.81xWe = 4879.9 N

Force

Fz = 0.5 P = 2440 N

Fx = Fz / tg β = 0 N

Max tensile force in Wire Rope

Ps = Fz / sin β = 2440 N

Lifting lug configuration

where :

SWL = Safe working load

Rh = Hole radius

T = Main plate thickness

h = Base width

b = Distance from edge of taper to center of hole

c = Distance from base of plate to center of hole

D = Shackle pin diameter

Fy = Yield Strength of lifting lug material

The dimension T should equal 60 - 85% of shackle jaw width.

The pin hole diameter should be 3 mm greater than the selected shackle pin size

The main plate radius is approximately R = 3 R h

Choose Shackle

Shackle load Ps = 2440 N = 0.249 tonne

Choose Shackle with SWL = 1.5 tonne

Shackle jaw width W = 19 mm

Shackle pin size D = 13 mm

Page 16 o




Choose Lug Configuration

Rh = 8 mm

a = 18 mm

T = 16 mm

h = 35 mm

b = 50 mm

c = 25 mm

Fy = 170 MPa

Stress in Lifting Lug

Bearing Stress

Bearing = 11.73 MPa Bearing = Ps/(T x D)

Allowable = 153 MPa Allowable = 0.9 x Fy

Safety Factor = 13.04 => PASS

Shear Stress

Shear = 7.62 MPa Shear = Ps/(2(a-Rh)*T)



Tensile Stress

From Section D3.2 of AISC, the distance used in calculations, across the hole, is the minimum of 4 times

the plate thickness at the pinhole or 0.8 times the hole diameter.

Effective width = 12.8 mm

Plate thickness = 16 mm

Tensile = 11.91 MPa Tensile = Ps/(Effective width*plate thk.) Allowable = 76.5 MPa Allowable = 0.45 Fy (AISC Section D3.2)


Bending Stress

Section modulus Z = 3266.7 mm3

Z = h2

x T / 6

Area of lug base A = 560 mm2

A = h x T

Bending = 18.67 MPa Bending = (Fz*c / Z) + (Fx / A)

Allowable = 102 MPa Allowable = 0.6 Fy


Stress in Weld Joint

Weld type : T-Butt weld, Full Penetration

Critial weld length K = 16 mm (Assumed equal to the thickness of lug)

Section modulus of weld Zw = 6533 mm Zw = h2

x K / 3

Area of weld Aw = 1120 mm Aw = 2 x K x h

Applied by force Fz

Bending S1 = 9.3 MPa Bending S1 = Fz*c/Zw

Shear S2 = 2.2 MPa Shear S2 = Fz/Aw

Page 17 o




Combined = 9.59 MPa Combined = (S12

+ S22)0.5



Applied by force Fx

Tensile S3 = 0.00 MPa Tensile S3 = Fx/Aw


=> PASS

12.2 Check for β = 85 degrees (Considering Tolerance 5 degrees)

Angle β = 85.0 degree

Considered a load factor of 2.0 applied to the structure gravity loads

Design Load P = 2x9.81xWe = 4879.9 N

Force

Fz = 0.5 P = 2440 N

Fx = Fz / tg β = 213 N

Max tensile force in Wire Rope

Ps = Fz / sin β = 2449 N

Choose Shackle

Shackle load Ps = 2449 N = 0.250 tonne

Choose Shackle with SWL = 1.5 tonne

Stress in Lifting Lug

Bearing Stress

Bearing = 11.78 MPa Bearing = Ps/(T x D)



Shear Stress

Shear = 7.65 MPa Shear = Ps/(2(a-Rh)*T)



Tensile Stress

From Section D3.2 of AISC, the distance used in calculations, across the hole, is the minimum of 4 times

the plate thickness at the pinhole or 0.8 times the hole diameter.

Effective width = 12.8 mm

Plate thickness = 16 mm

Tensile = 11.96 MPa Tensile = Ps/(Effective width*plate thk.)

Allowable = 76.5 MPa Allowable = 0.45 Fy (AISC Section D3.2)


Bending Stress

Section modulus Z = 3266.7 mm3

Z = h2

x T / 6

Area of lug base A = 560 mm2

A = h x T

Bending = 19.05 MPa Bending = (Fz*c / Z) + (Fx / A)


Page 18 o





Stress in Weld Joint

Weld type : T-Butt weld, Full Penetration

Critial weld length K = 16 mm (Assumed equal to the thickness of lug)

Section modulus of weld Zw = 6533 mm Zw = h2

x K / 3

Area of weld Aw = 1120 mm Aw = 2 x K x h

Applied by force Fz

Bending S1 = 9.3 MPa Bending S1 = Fz*c/Zw

Shear S2 = 2.2 MPa Shear S2 = Fz/Aw

Combined = 9.59 MPa Combined = (S12

+ S22)0.5



Applied by force Fx

Tensile S3 = 0.19 MPa Tensile S3 = Fx/Aw



Choose Lug Configuration as shown above is satisfactory

13. Hydrotest Pressure (Refer to ASME Section VIII, Division 1, UG-99 (b))

Design Temperature = 105 degrees C

Test Temperature = A.T.M

Internal Design Pressure P = 1.18 MPa

Max. Allowable Stress at Design Temperature Sd = 115 MPa

Max. Allowable Stress at Test Temperature St = 115 MPa

Hydrotest Pressure Ph = 1.3 x P x (St/Sd)

Ph = 1.3 x 1.18 (115/115) = 1.534 MPa

14. Conclusion

Shell thickness:

Thickness required: 2.50 mm

Thickness actual: 5 mm

Bottom Head thickness:

Min. Thickness required: 2.03 mm

Top Head thickness:

Min. Thickness required: 37.00 mm

Swing bolt diameter : 16 mm

Nozzle thickness:

Nozzle Neck N1, N2_DN 80 (3")


Thickness actual: 5.49 mm

Nozzle Neck N3_DN 20 (3/4")

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Nozzle Neck N4_DN 20 (3/4")



MDMT for all items of equipment:

MDMT = 6 degree C

Nozzle reinforcement:

Nozzle Neck N1, N2_DN 80 (3")

Material SA-240 TP304/304L

Outside diameter = 150 mm

Thickness = 5 mm

Skirt thickness:



Anchor Bolt:

Anchor Bolt Size: M16 (5/8 in.)

Base Plate:



Hydrotest Pressure: 1.534 MPa = 15.34 bar

Page 20 o



ASME B16.5

SA-240 TP304

SA-312 TP304

v 2151 102 a 216 c design calculation sheet (filter)

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