Download - V 2154 101 a 215_Mechanical Calculation (v 430 v 431)Update

Project: NOEV LUBE OIL BLENDING PLANT

Job No.: AL-2499

Document No.: V-2154-101-A-215

Reference Drawing: V-2154-101-A-202_Rev.C

Vessel Tag No.: V430 / V431

A 05/04/2013

Rev Date

L.N.B

MECHANICAL CALCULATION SHEET

Description Prepared Approval

Issue for review / approval L.D.T L.A.V

Checked

Project: NOEV LUBE OIL BLENDING PLANT Job No.: AL-2499 Rev. No.: A

INDEX Page

1. Design Data 2

2. Shell Thickness Calculation 2

3. Bottom Head Thickness Calculation 3

4. Top Head Thickness Calculation 3

5. Auxiliary Stiffener Calculation 4

6. Main Stiffener Calculation 5

7. Coil Half-Pipe Calculation 6

8. Lug Support 7

9. Nozzle Calculation 11

10. Welding 14

11. Lifting Lug Calculation 17

12. Vibration Calculation 20

13. Conclusion 31

MECHANICAL CALCULATION SHEET

Page 1 of 31


1. Design Data

Design Code : None

Service: Blending Vessel

Design pressure

Max. Internal pressure - (Full 4.18 meters of Water) P = 0.41 barg = 0.041 MPa

External pressure 0.0 barg = 0.0 MPa

Working pressure 0.0 barg = 0.0 MPa

Design temperature 180 degrees C

Working temperature 60 ~ 80 degrees C

Corrosion allowance 0.0 mm

Vessel inside diameter 3950 mm (O/D = 3966 mm)

Vessel length (Flat Head to T.L) 2730 mm

Material

Shell SA-240 TP304 / 304L

Flat Top Head SA-240 TP304 / 304L

Bottom Cone Head SA-240 TP304 / 304L

Nozzle Neck SA-312 TP304 / 304L

Support SA-240 TP304 / 304L

2. Shell Thickness Calculation (Refer to API 650 10th Edition, Appendix S.3.2)

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

where:

td : Design shell thickness, in mm

tt : Hydrostatic test shell thickness, in mm

D : nominal diameter of the tank = 3.958 m

H : Design Liquid Level = 4.18 m

G : Specific Gravity of the Liquid = 1.0

(Shall not be less than 1.0)

E : Joint effeciency = 0.85

CA : Corrosion allowance = 0.0 mm

Sd : Allowable Stress for design condition = 128 MPa

St : Allowable Stress for the hydrostatic test condition = 155 MPa

Plate of dimension width 1.5 m is selected for first shell course

With the tank height of 2.73 m, the second shell course will be 1.23 m width.

2.2 First Shell Course:

4.9 x 3.958 x ( 4.18 -0.3) x 1.0

4.9 x 3.958 x ( 4.18 -0.3)

Minimum Shell Thickness shall not be less than 5 mm (Refer to API 650 10th Edition, Clause 3.6.1.1)

Choose Nominal thickness of shell, ts1 = 8 mm

td1 = + 0.00 = 0.692 mm128 x 0.85

tt1 = = 0.571 mm155 x 0.85

Page 2 of 31


2.3 Second Shell Course:

4.9 x 3.958 x ( 1.2 -0.3) x 1.0

4.9 x 3.958 x ( 1.2 -0.3)

Minimum Shell Thickness shall not be less than 5 mm (Refer to API 650 10th Edition, Clause 3.6.1.1)

Choose Nominal thickness of shell, ts2 = 8 mm

3. Bottom Head Thickness Calculation (Refer to ASME Section VIII, Division 1, UG-32)

Type of head: Cone Head

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

0.0410 x 3950.0

where:

P : internal design pressure = 0.041 MPa < = 36.65 MPa

D : Inside diameter of the head skirt = 3950.0 mm

S : Maximum allowable stress value = 112.0 MPa

E : Joint efficiency = 0.85

α : one-half of the included angle of = 60 degrees

the cone at the centerline of head

3.2 Minimum required thickness of Head included corrosion allowance

= 1.70 + 0.0 = 1.70 mm

3.3 Minimum required thickness of Head, tb = Min. 8.0 mm

4. Top Head Thickness Calculation (Refer to Roark's Formulas for Stress and Strain)

Type of head: Flat Head

Assume square plate (axb) 600x600 mm with all edges simply supported

and uniform loads over entire plate.

Top Head Self-Weight = 790.634 kg

F = m x g = 7756.12 N

Area (A) = πD2/4 = 12.35 m

2

P1 = F/A = 0.628 kPa

Structural Weight = 200 kg (Including weight of nozzles, manhole on Top Head - 200 kg)

F = m x g = 1962 N

Area (A) = πD2/4 = 12.35 m

2

P2 = F/A = 0.159 kPa

Concentrated Load = 250 kg (Assumed)

F = m x g = 2452.5 N

Area (A) = πD2/4 = 12.35 m

2

P3 = F/A = 0.199 kPa

Total Dead Load (P) = P1+P2+P3 = 0.99 kPa

Total Live Load (L) = 1.2 kPa (As per API 650 10th Edition, Clause 3.10.2.1)

Total Uniform Load (q) = P + L = 2.19 kPa

0.385SE

= mm1.70= =162.0

95.22 x cos(60) x (112 x 0.85 - 0.6 x 0.041)

td2 = + 0.00 = 0.166 mm128 x 0.85

tt2 = = 0.137 mm155 x 0.85

60

0

600

Page 3 of 31


Edges of Plate (a x b) = 600 x 600 mm

a/b = 1

β = 0.2874

α = 0.0444

Elastic Modulus (E) = 1.93E+08 kPa

Allowable Stress ([ϭ]) = 112000 kPa (Refer to ASME Section II, Part D, Table 1A)

Required Plate thickness (Refer to Roark's Formulas, Table 11.4, Case 1a)

Choose thickness of Top Head Plate = 8 mm

Max. Deflection (Refer to Roark's Formulas, Table 11.4, Case 8a)

Max. Stress in plate

5. Auxiliary Stiffener Calculation

Length of stiffener L = 1600 mm

Width of Plate that using stiffener Wp = 1200 mm (Assumed)

Uniform load wa = q x Wp = 2.622 kN/m

Select stiffener properties as below

Area moment of inertia (As per Roark's Formulas, Table A.1, Case 4: Tee section):

where:

t : The thickness of Top Head = 8 mm

I = = 604446 mm4

= 1.42 mm

= 0.13 mm

= 3533 kPa [ϭ] 112000

t/2 = (ACCEPTED)<

kPa (ACCEPTED)<

4 mm

=

𝑡 =𝛽𝑞𝑏2

𝜎

𝑦𝑚𝑎𝑥 =𝛼𝑞𝑏4

𝐸𝑡3

𝜎𝑝 =𝛽𝑞𝑏2

𝑡2

60

1600

8

Page 4 of 31


b : Effective area (about 32 x t) = 256 mm

tw : The thickness of Stiffener = 8 mm

d : Stiffener height = 60 mm

= 2528 mm2

Elastic modulus (E) = kPa

Plastic section modulus (Zx)

Max. deflection at the center of stiffener (Refer to Roark's Formulas, Table 8.1, Case 2e )

-5 x 2.622 x 7804

Unity Check (UC) ratio calculation

M : Maximum bending moment caused by uniform load wa = 0.839 KN.m

S : Bending Stress caused by M = 41559 KPa

UC ratio : = 0.371 < 1

=> (ACCEPTED)

6. Main Stiffener Calculation

Length of stiffener L = 3900 mm

Width of Plate that using stiffener Wp = 1000 mm (Assumed)

Uniform load wa = q x Wp = 2.185 kN/m

Agitator Concentrated load W = 430 kg = 4.218 kN

Select stiffener properties as below

b3 : Effective area (about 32 x d3) = 256 mm

d3 : The thickness of Top Head = 8 mm

d2 : Web height = 200 mm

b2 : Web thickness = 8 mm

b1 : Bottom flange length = 70 mm

d1 : Bottom flange thickness = 8 mm

= 10.456 mm

= 20191 mm3

193000000

= -1.918 mm=384 x 193000 x 604446

M =𝑤𝑎𝑙

2

8

S =𝑀

𝑍𝑥

𝑈𝐶 =𝑆

𝜎

3900

Page 5 of 31

Vula

Rectangle


PART Area (a) y a x y h h2

bd3/12

mm2

mm mm3

mm mm2

mm4

1 560 4 2240 140.78 19817.8 2986.6667

2 1600 108 172800 36.78 1352.45 5333333.3

3 2048 212 434176 -67.22 4519.11 10922.667

TOTAL 4208 609216 5347242.7

Therefore,

Distance from bottom to Neutral axis

C = 609216 / 4208 = 144.776 mm

Area moment of inertia

I = 22517020.228 + 5347243 = 27864263 mm4

Section Modulus

Z = I/C = 192465.1 mm3

Max. deflection at the center of stiffener (Refer to Roark's Formulas, Table 8.1, Case 2e )

-4.2183 x 39003

x 39004

Unity Check (UC) ratio calculation

M : Maximum bending moment caused by uniform load W = 8.267 KN.m

S : Bending Stress caused by M = 42955 KPa

UC ratio : = 0.384 < 1

=> (ACCEPTED)

7. Coil Half-Pipe Calculation (Refer to ASME Section VIII, Division 1, Nonmandatory Appendix EE)

7.1 Because of the same thickness of shell and cone head, the half-pipe calculation shall be considered for shell only.

ts : Thickness of the shell = 8 mm = 1/3 in

R : Inside shell radius = 1975 mm

D = 2R : Inside shell diameter = 3950 mm = 155.5 in

Half-pipe jacket is DN80

S : Allowable tensile stress of shell = 112.0 MPa

S1 : Allowable tensile stress of coil half-pipe = 112.0 MPa

P : Internal Pressure in vessel = 0.041 MPa (Positive pressure inside the shell)

P1 : Design Pressure in coil = 0.98 MPa (Positive pressure inside the half-pipe)

From Fig. EE-2, with D = 155.5 in. and t = 1/3 in., so K = 80

Actual longitudinal tensile pressure in shell

S' = PR/2ts = 5.06 MPa

Permissible coil pressure

P' = F / K = (1.5S - S') / K = 2.04 MPa > P1 = 0.98 MPa

=> PASS

The thickness of shell is satisfactory for pressure inside Half-pipe

Choose Half-pipe DN80, SCH. 40

=384 x 193000 x 27864263

mm

22517020.228

-5 x 2.185

48 x193000 x 27864263+

mm4

a x h2

9255139.661

= -2.193

2163919.305

11097961.26

S =𝑀

𝑍𝑥

𝑈𝐶 =𝑆

𝜎

M =𝑊𝑙

4+𝑤𝑎𝑙

2

8

Page 6 of 31


Half-pipe thickness included 12.5% undertolerance

t = 0.875 x 5.49 = 4.8 mm

Inside half-pipe radius

r = 88.9/2 - 4.8 = 39.65 mm

The required half-pipe thickness

=> PASS

The minimum fillet weld size is equal to

= 1.414 x 0.411 = 0.581 mm

Choose Fillet weld size = 5 mm

7.2 Hydrotest Pressure for Coil Half-pipe (Refer to ASME Section VIII, Division 1, UG-99)

Min. Test Pressure = 1.3 x Design Pressure = 1.3 x 0.98 = 1.27 MPa

8. Lug Support (Refer to Pressure Vessel Handbook 10th Edition)

8.1 Wear plate

W : Weight of Vessel (Full of Water) = 48230 kg (As per Specification + Agitator weight)

n : Number of lugs = 8

Q = W/n : Load on one lug = 6028.8 kg

R : Radius of shell = 1983 mm

H : Lever arm of load = 152 mm

2A : 1st Dimension of wear plate = 550 mm

2B : 2nd Dimension of wear plate = 550 mm

t : Wall thickness of shell = 8.0 mm

tw : Wear plate thickness (approximate shell thickness) = 8.0 mm

P : Internal Pressure at Wear plate location = 0.00 MPa

Shell material : SA-240 TP304 / 304L

Allowable stress value : 112.0 MPa

Joint Efficiency : 0.85

Shape factors C :

1983 275

8.0 275R/t ;

= 0.411 mm

= = 248 = 1B/A =

𝑧 = 2 × 𝑇

Page 7 of 31

Vula

Rectangle


C1 = 1

C2 = 1

C3 = 1

C4 = 1

The factors K

K1 = 8.3

K2 = 0.014

K3 = 14

K4 = 0.01

Longitudinal Stress :

= 66.20 MPa

Stress due to internal pressure:

PR

2t

The sum of tensional stresses:

66.20 + 0.00 = 66.20 MPa

It does not exceed the stress value of the girth seam:

112.0 x 0.85 = 95.2 MPa (ACCEPTED)

Circumferential Stress:

= 59.49 MPa

Stress due to internal pressure:

PR

t

The sum of tensional stresses:

59.49 + 0.00 = 59.49 MPa

It does not exceed the stress value of shell material multiplied by 1.5 :

112.0 x 1.50 = 168 MPa (ACCEPTED)

Choose wear plate = 550x550x8 mm

= 0.14

=

= =0 x 1983

2 x 8

0 x 1983

0.00 MPa

= 0.00 MPa8

𝐷 =𝐴

𝑅

3 𝐵

𝐴=

275

1983

3 275

275

𝑆1 = ±𝑄𝐻

𝐷𝑅2𝑡𝐶1𝐾1 + 6

𝐾2𝑅

𝐶2𝑡+

𝐷

2 1.17 + 𝐵/𝐴×𝑅2

𝐻𝐴

𝑆2 = ±𝑄𝐻

𝐷𝑅2𝑡𝐶3𝐾3 + 6

𝐾4𝑅

𝐶4𝑡

Page 8 of 31


8.2 Gussets

Q : Vertical load per lug = 6028.8 kg = 59142 N

n : Number of gussets per lug = 2 (Double Gusset)

b = 352 mm

h = 350 mm

tg : Gusset thickness = 20 mm

θ = 60 degrees

Fy : Minimum Yield Strength of gusset material = 170 MPa

Fa : Allowable axial Stress = 68 MPa (0.4 Fy)

Fb : Allowable bending Stress = 102 MPa (0.6 Fy)

Qa = Q.sinθ : Axial load on gusset = 51219 N

Qb = Q.cosθ : Bending load on gusset = 29571 N

A = tg.C : Cross-sectional area of assumed column = 3048.4 mm2

Axial stress

=> PASS

Bending Stress

=> PASS

Choose dimensions of Double Gusset as shown above

= 152.42 mm

MPa= 8.401 MPa < Fa = 68

: Bending moment = 6E+06 Nmm

= 77440

Mpa= 77.163 MPa < Fb = 102

= 404.15 mm

: Section modulus mm3

Page 9 of 31

Vula

Rectangle


8.3 Base Plate for Double Gusset

l : Base plate width = 280 mm

a : Bearing width = 50 mm (Assumed)

l1 = 210 mm

φ : Bolt hole diameter = 38 mm

8.3.1 Bending (Assume to be between simply supported and fixed)

8.3.2 Bearing

8.3.3 Thickness required base plate

where Mb is bending moment

Choose the actual thickness base plate tb = 25 mm

8.4 Compression Plate for Double Gusset

e = 152 (Refer to figure of 8.2 Gussets)

Ev : Modulus of elasticity of vessel = 193721 MPa

Es : Modulus of elasticity of compression plate = 193721 MPa

t : Shell Vessel thickness = 8.0 mm

R : Inside Radius of vessel = 1975.0 mm

tc : Assumed Compression Plate thickness = 25.0 mm

y : Compression Plate width = 208.0 mm

x : Distance between loads = 420.0 mm

Fy : Minimum Yield Strength of gusset material = 170 MPa

Fb : Allowable bending Stress = 102 MPa (0.6 Fy)

Concentrated load on Double Gusset

Foundation modulus

Moment of inertial of Compression plate

= 12842 N (Assumed)

(Uniform load on base plate)

= 19.69 mm

= 0.3973 N/mm3

= 2E+06 Nmm

= 4.2244 Nmm2

= 18630 Nmm

Page 10 of 31

Vula

Rectangle

Vula

Rectangle

Vula

Rectangle


Section modulus of Compression plate

Damping factor

Internal bending moment in Compression plate

Bending stress

=> PASS

Choose Compression Plate thickness, tc = 25.0 mm

9. Nozzle calculation

9.1 Shell Nozzle N2 (DN40) (Refer to API 650 10th Edition, Appendix S)

9.1.1 Minimum Nozzle Neck thickness

Base on table S.3.3.1

Minimum thickness of Nozzle Neck = 5.08 mm (SCH 80S)

Corrosion Allowance (C.A) = 0.00 mm

Minimum thickness of Nozzle Neck including C.A = 5.08 mm

9.1.2 Choose Nozzle actual thickness = 5.08 mm (SCH 80S)

9.2 Flat Top Head Nozzle N1, N3 (DN50) (Refer to API 650 10th Edition, Appendix S)







9.3 Flat Top Head Nozzle N9 (DN80) (Refer to API 650 10th Edition, Appendix S)

Mpa

= 1E+07 Nmm

= 62.308 MPa < Fb =

= 2E+07 mm4

= 180267 mm3

= 0.0004

102

Page 11 of 31

Vula

Rectangle








9.4 Flat Top Head Nozzle N6, N10 (DN100) (Refer to API 650 10th Edition, Appendix S)







9.5 Flat Top Head Nozzle N4 (DN250) (Refer to API 650 10th Edition, Appendix S)



Minimum thickness of Nozzle Neck = 6 mm




9.6. Cone Bottom Head Nozzle N5 (DN100) (Refer to ASME Section VIII, Division 1 & API 650 10th Edition, Appendix S)

9.6.1 Minimum Nozzle neck thickness (Refer to ASME Section VIII, Division 1)

where:

S : Maximum allowable stress value, S = 112 MPa

E : Joint efficiency E = 1.00

Nozzle inside radius Rn = 97.18 mm

tn (min) : minimum required thickness of Nozzle

9.6.1.1 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.

ban ttt ,max(min)

Page 12 of 31


0.041 x 97.2 3.9849

112.0 x 1.00 - 0.6 x 0.0 112.0

ta = 0.04 + 0.0 = 0.04 mm

9.6.1.2 = min ( 5.27 , 8.0 ) = 5.27 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 = 8.00 mm

tb2 : for vessels under external pressure

tb2 = 0.00 mm

Max (tb1, tb2) = Max ( 8.00 , 0.00 ) = 8.0 mm

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

(for standard wall pipe)

tb3 = 5.27 + 0.0 = 5.27 mm

=> = max ( 0.04 , 5.3 ) = 5.27 mm

9.6.2. Minimum Nozzle neck thickness (Refer to API 650 10th Edition, Appendix S)





Choose Nozzle actual thickness = 6.02 mm

9.6.3. Choose Nozzle actual thickness = 6.02 mm (SCH 40S)

9.7 Coil Half-pipe Steam Nozzle N7A/B/C & N8A/B/C (DN25) (Refer to ASME Section VIII, Division 1)

Minimum Nozzle neck thickness

where:

S : Maximum allowable stress value, S = 112 MPa

E : Joint efficiency E = 1.00

Nozzle inside radius Rn = 24.30 mm

tn (min) : minimum required thickness of Nozzle

9.7.1 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.

= = = 0.04 mm

ban ttt ,max(min)

ban ttt ,max(min)

Page 13 of 31


0.980 x 24.3 23.814

112.0 x 1.00 - 0.6 x 0.980 111.4

ta = 0.21 + 0.0 = 0.21 mm

9.7.2 = min ( 2.96 , 5.49 ) = 2.96 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 = 5.49 mm

tb2 : for vessels under external pressure

tb2 = 5.49 mm

Max (tb1, tb2) = Max ( 5.49 , 5.49 ) = 5.49 mm

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

(for standard wall pipe)

tb3 = 2.96 + 0.0 = 2.96 mm

=> = max ( 0.21 , 2.96 ) = 2.96 mm

9.7.3 Choose Nozzle actual thickness = 4.55 mm (SCH 80)

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

material would include a 12.5% undertolerance

= 0.875 x 4.55 = 3.98 > tn (min) = 2.96 mm

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

10. Welding

10.1 Shell Nozzle N2 (DN40) - (Refer to API 650 10th Edition, Clause 3.6)

As per Fig. 3-4B and Table 3-6

Flanged Nozzles in pipe sizes NPS 2 (DN50) or smaller

do not required reinforcing plates

Diameter of the hole in the shell plate, DR = 51 mm

Size of Fillet Weld, A = 6 mm

= = = 0.21 mm

ban ttt ,max(min)

Page 14 of 31


10.2 Flat Top Head Nozzle N1, N3 (DN50) - (Refer to API 650 10th Edition, Clause 3.6)

As per Fig. 3-16 - Flanged Roof Nozzles

where :

DP : Diameter of Hole in Roof Plate (Table 3-14)

DP = 65 mm

10.3 Flat Top Head Nozzle N9 (DN80) - (Refer to API 650 10th Edition, Clause 3.6)


where :


DP = 92 mm

Refer to Table 3-14: Reinforcing plates are not required on nozzle DN 80

10.4 Flat Top Head Nozzle N6, N10 (DN100) - (Refer to API 650 10th Edition, Clause 3.6)


where :


DP = 120 mm

Refer to Table 3-14: Reinforcing plates are not required on nozzle DN 100

10.5 Flat Top Head Nozzle N4 (DN250) - (Refer to API 650 10th Edition, Clause 3.6)


& Table 3-14

where :

DP : Diameter of Hole in Reinforcing Plate

DP = 280 mm

DR : Outside Diameter of Reinforcing Plate

DR = 550 mm

10.6 Cone Bottom Head Nozzle N5 (DN100)

10.6.1 Size of weld, Nozzle thickness & Shell thickness

tn = 6.02 mm (Nozzle thickness)

tc (actual) = 6.00 mm (Refer to fabrication detail drawing)

t = 8.00 mm (Min. Bottom Head thickness after forming)

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

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

where:

Page 15 of 31

Vula

Rectangle


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 , 6.02 ) = 6.02 mm

0.7tmin = 0.7 x 6.02 = 4.21 mm

=> tc (min) = Min ( 6 , 0.7 tmin ) = Min ( 6.00 , 4.21 ) = 4.21 < tc (actual) = 6.00 mm

=> PASS

10.7 Coil Half-pipe Steam Nozzle N7A/B/C & N8A/B/C

10.7.1 Size of weld, Nozzle thickness & Shell thickness

tn = 4.55 mm (Nozzle thickness)

tc (actual) = 4.00 mm (Refer to fabrication detail drawing)

t = 0.00 mm (Coil Half-pipe thickness)

10.7.2 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 fillet, single-bevel, or single-J weld

tmin = Min ( 19.0 , 4.55 ) = 4.55 mm

0.7tmin = 0.7 x 4.55 = 3.19 mm

=> tc (min) = Min ( 6 , 0.7 tmin ) = Min ( 6.00 , 3.19 ) = 3.19 < tc (actual) = 4.00 mm

=> PASS

10.8 Cone Bottom Head Welded Joint

Weld type : Butt weld, Full Penetration

Critical weld length K = 8 mm (Assumed equal to the thickness of shell)

Inside Diameter of Tank D = 3950 mm

Area of weld Aw = 99274 mm2 Aw = πDK

Allowable Stress of Shell material = 112.0 MPa

Applied by force Total Weight Load (TWL)

Weight Load of Water inside the tank Ww = 391419 N (Estimate)

Weight Load of Cone Bottom Head Wb = 8063.8 N (Estimate)

TWL = 399483 N TWL = Ww + Wb

Tensile Stress on Welded Joint

Tensile = 4.02 MPa Tensile = TWL / Aw

Allowable = 112.0 MPa

Safety Factor = 27.8 => PASS

Page 16 of 31


11. Lifting Lug Calculation

Equipment weight We = 7900 kg

Angle β = 90.0 degree

Lifting Lug material SA-240 TP304 / 304L

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

Design Load P = 2x9.81xWe = 154998 N

Force

Fz = 0.5 P = 77499 N

Fx = Fz / tg β = 0 N

Max tensile force in Wire Rope

Ps = Fz / sin β = 77499 N

11.1 Lifting lug configuration

where :

SWL = Safe working load

Rh = Hole radius

r = Cheek plate radius

R = Main plate radius

Tp = Main plate thickness

t = Cheek plate thickness

T = Total 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

a = Taper angle

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

Cheek plate radius is approximately r = R - 1.5t

The main plate radius is approximately R = 3 R h

The cheek plate thickness (t) should be less than or equal to the plate thickness (Tp).

11.1.1 Choose Shackle

Shackle load Ps = 77499 N = 7.9 tonne

Choose Shackle with SWL = 9.5 tonne

Page 17 of 31


As per Table shown above :

Shackle jaw width W = 46 mm

Shackle pin size D = 32 mm

11.1.2 Choose Lug Configuration

Rh = 18 mm

r = 40 mm

R = 50 mm

Tp = 25 mm

t = 8 mm

T = 41 mm

h = 167 mm

b = 190 mm

c = 140 mm

a = 90 degrees

D = 32 mm

Fy = 170 MPa

11.2 Stress in Lifting Lug

Bearing Stress

Bearing = 59.07 MPa Bearing = Ps/(T x D)

Allowable = 153 MPa Allowable = 0.9 x Fy


Shear Stress

Shear = 33.64 MPa Shear = Ps/(4(r-Rh)*t+2(R-Rh)*Tp)

Allowable = 68 MPa Allowable = 0.4 x Fy


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 = 28.8 mm

Plate thickness = 41 mm

Tensile = 65.63 MPa Tensile = Ps/(Effective width*plate thickness)

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


Bending Stress

Section modulus Z = 116204.2 mm3 Z = h

2 x Tp / 6

Area of lug base A = 4175 mm2 A = h x Tp

Bending = 93.37 MPa Bending = (Fz*c / Z) + (Fx / A)

Page 18 of 31


Allowable = 102 MPa Allowable = 0.6 Fy


11.3 Stress in Weld Joint

Weld type : T-Butt weld, Full Penetration

Critial weld length K = 25 mm (Assumed equal to the thickness of lug)

Section modulus of weld Zw = 232408 mm3

Zw = h2 x K / 3

Area of weld Aw = 8350 mm2

Aw = 2 x K x h

Applied by force Fz

Bending S1 = 46.7 MPa Bending S1 = Fz*c/Zw

Shear S2 = 9.3 MPa Shear S2 = Fz/Aw

Combined = 47.60 MPa Combined = (S12 + S2

2)0.5



Applied by force Fx

Tensile S3 = 0.00 MPa Tensile S3 = Fx/Aw


=> PASS

Choose Lug Configuration as shown above is satisfactory

Page 19 of 31

of 31

12. Vibration Calculation

Simulation of BENDING VESSEL Date: Tuesday, April 02, 2013 Designer: Solidworks Study name: VIBRATION DUE TO AGITATOR Analysis type: Dynamic

Table of Contents Description .......................................... 20

Model Information ............................... 21

Study Properties ................................. 22

Units.................................................... 22

Material Properties .............................. 23

Loads and Fixtures ............................. 24

Contact Information ............................ 25

Mesh Information ................................ 26

Resultant Forces ................................... 8

Study Results ........................................ 9

Conclusion .......................................... 11

Description BENDING VESSEL

of 31

Model Information

Model name: BENDING VESSEL Current Configuration: Default

Solid Bodies

Document Name and Reference

Treated As Volumetric Properties Document Path/Date

Modified

Boss-Extrude10

Solid Body

Mass:4905.75 kg Volume:0.613219 m^3 Density:8000 kg/m^3

Weight:48076.4 N

C:\Users\TRAN THE THAO\Desktop\ANH VU\3D\2\BENDING VESSEL (V 430-V

431).SLDPRT Apr 02 22:22:37 2013

Revolve1

Solid Body

Mass:306.91 kg Volume:0.0383637 m^3 Density:8000 kg/m^3

Weight:3007.72 N

C:\Users\TRAN THE THAO\Desktop\ANH VU\3D\2\BENDING

VESSEL 2.2.SLDPRT Apr 02 20:55:43 2013

of 31

Study Properties

Study name VIBRATION DUE TO AGITATOR

Analysis type Dynamic

Mesh type Solid Mesh

Thermal Effect: On

Thermal option Include temperature loads

Zero strain temperature 298 Kelvin

Include fluid pressure effects from SolidWorks Flow Simulation

Off

Solver type FFEPlus

Inplane Effect: Off

Soft Spring: Off

Inertial Relief: Off

Incompatible bonding options Automatic

Large displacement Off

Compute free body forces On

Friction Off

Use Adaptive Method: Off

Result folder SolidWorks document (C:\Users\TRAN THE THAO\Desktop\ANH VU\3D\2)

Units

Unit system: SI (MKS)

Length/Displacement mm

Temperature Kelvin

Angular velocity Rad/sec

Pressure/Stress N/m^2

of 31

Material Properties

Model Reference Properties Components

Name: A-240 TP304/304 L

Model type: Linear Elastic Isotropic

Default failure criterion:

Max von Mises Stress

Yield strength: 1.28e+008 N/m^2 Tensile strength: 5.15e+008 N/m^2 Elastic modulus: 2e+011 N/m^2 Poisson's ratio: 0.26

Mass density: 8000 kg/m^3 Shear modulus: 7.93e+010 N/m^2

SolidBody 1(Boss-Extrude10)(BENDING VESSEL (V 430-V 431)-1), SolidBody 1(Revolve1)(BENDING VESSEL 2.2-1)

Curve Data:N/A

of 31

Loads and Fixtures

Fixture name Fixture Image Fixture Details

Fixed-1

Entities: 8 face(s) Type: Fixed Geometry

Resultant Forces

Components X Y Z Resultant

Reaction force(N) 49.2291 719982 -15.8973 719982

Reaction Moment(N·m)

0 0 0 0

Load name Load Image Load Details

Force-1 (Full Water)

Entities: 3 face(s) Type: Apply normal force

Value: 500000 N

Bending Moment (Agitator)

Entities: 14 face(s) Type: Apply torque

Value: 158 N·m

Dynamic Load (Due to agitator)

Entities: 1 face(s) Type: Apply normal force

Value: -860 N

of 31

Gravity-1

Reference: Top Plane Values: 0 0 -9.81

Units: SI

Contact Information

Contact Contact Image Contact Properties

Global Contact

Type: Bonded Components: 1

component(s) Options: Compatible

mesh

of 31

Mesh Information

Mesh type Solid Mesh

Mesher Used: Standard mesh

Automatic Transition: Off

Include Mesh Auto Loops: Off

Jacobian points 4 Points

Element Size 123.544 mm

Tolerance 6.17719 mm

Mesh Quality High

Remesh failed parts with incompatible mesh Off

Mesh Information - Details

Total Nodes 192800

Total Elements 97185

Maximum Aspect Ratio 2206.3

% of elements with Aspect Ratio < 3 6.9

% of elements with Aspect Ratio > 10 49.9

% of distorted elements(Jacobian) 0

Time to complete mesh(hh;mm;ss): 00:01:41

Computer name: TRANTHETHAO-PC

of 31

Mesh Control Information:

Mesh Control Name Mesh Control Image Mesh Control Details

Control-1

Entities: 1 component(s) Units: mm Size: 70

Ratio: 1.5

Control-2

Entities: 1 component(s) Units: mm Size: 40

Ratio: 1.5

Resultant Forces

Reaction Forces

Selection set Units Sum X Sum Y Sum Z Resultant

Entire Model N 49.2291 719982 -15.8973 719982

Reaction Moments

Selection set Units Sum X Sum Y Sum Z Resultant

Entire Model N·m 0 0 0 0

of 31

Study Results

Name Type Min Max

Stress1 VON: von Mises Stress 0.000236212 N/mm^2 (MPa) Node: 17656

101.848 N/mm^2 (MPa) Node: 192580

BENDING VESSEL-VIBRATION DUE TO AGITATOR-Stress-Stress1

Name Type Min Max

Displacement1 URES: Resultant Displacement

0 mm Node: 16910

14.4683 mm Node: 182622

of 31

BENDING VESSEL-VIBRATION DUE TO AGITATOR-Displacement-Displacement1

Name Type Min Max

Strain1 ESTRN: Equivalent Strain 2.4083e-009 Element: 75937

0.000335032 Element: 94615

BENDING VESSEL-VIBRATION DUE TO AGITATOR-Strain-Strain1

of 31

Name Type Min Max

Factor of Safety1 Automatic 0.551475 Node: 55133

541887 Node: 17656

BENDING VESSEL-VIBRATION DUE TO AGITATOR-Factor of Safety-Factor of Safety1

Conclusion - Von Misses Stress=101.8 (Mpa) < Allowable Stress=112(Mpa)

- Safety factor = Allowable Stress / Actual Stress= 112 / 101.8 = 1.1 > 1.

- Bending Vessel is Safety.


13. Conclusion

Shell thickness:

First Shell course

Thickness required: 5.00 mm

Thickness actual: 8 mm

Second Shell course


Thickness actual: 8 mm

Bottom Head thickness:

Min. Thickness required: 8.00 mm

Top Head thickness:

Thickness actual: 8.00 mm

Auxiliary Stiffener size: 60 x 8 mm

Main Stiffener size: T-200x8 + 70x8 mm (Refer to GA Drawing for more details)

Nozzle thickness:

Shell Nozzle N2 (DN40)


Thickness actual: 5.08 mm (SCH 80S)

Flat Top Head Nozzle N1, N3 (DN50)



Flat Top Head Nozzle N9 (DN80)



Flat Top Head Nozzle N6, N10 (DN100)



Flat Top Head Nozzle N4 (DN250)



Cone Bottom Head Nozzle N5 (DN100)



Coil Half-pipe Steam Nozzle N7A/B/C & N8A/B/C (DN25)


Thickness actual: 4.55 mm (SCH 80)

Page 31 of 31

Download - V 2154 101 a 215_Mechanical Calculation (v 430 v 431)Update

Top Related