V 2151 101 a 205 C_Design Calculation Sheet (v 1101)

7/30/2019 V 2151 101 a 205 C_Design Calculation Sheet (v 1101)

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Project: NOEV Lube Oil Blending Plant

Job No.: AL-2503

Document No.: V-2151-101-A-205

Reference Drawing: V-2151-101-A-201_Rev.B

Vessel Name: Instrument and Utility Air Drum

Vessel Tag No.: V-1101

C 5/27/2013

B 4/20/2013

A 23/03/2013

Rev Date

L.N.B

L.N.B

MECHANICAL CALCULATION SHEET

Description Prepared Approval

Issue for review / approval

Issue for review / approval

Issue for review / approval L.D.T

L.D.T

Vu

L.N.B

L.N.B

L.N.B

Checked

L.N.B



Project: NOEV Lube Oil Blending Plant Job No.: AL-2503 Rev. No

INDEX Page

1. Design Data 2

2. Shell Thickness Calculation 3

3. Head Thickness Calculation 4

4. Nozzle Calculation 4

5. Weld Size Calculation 8

6. Reinforcement 10

7. Weight Calculation Sheet 12

8. Wind Load Analysis 12

9. Seismic Analysis 14

10. Leg Support Base Plate Thickness 17

11. Lifting Lug calculation 18

12. Hydrotest Pressure 21

13. Conclusion 22

MECHANICAL CALCULATION SHEET

Page 1 of



Project: NOEV Lube Oil Blending Plant Job No.: AL-2503

1. Design Data

1.1 Summary of Design Data

1.2 Maximum Allowable Stress Value

SEISMIC FACTOR 0.4 -

BASIC WIND SPEED 39

5289 kg

1666

1661 kg

kg

EMPTY

OPERATING

FULL OF WATER

m/sec

NO mm

INSULATION mmNO

JOINT EFFICIENCY (SHELL / HEAD)

P.W.H.T

-0.85 / 1.0

RADIOGRAPHY SPOT -

CORROSION ALLOWANCE mm1

TEMPERATURE

DESIGN

OPERATING

M.D.M.T -5

AMBIENT

65

oC

oC

oC

mm

-

FIRE PROOFING

UNIT

VESSEL INSIDE DIAMETER 1300 mm

VESSEL LENGTH (T TO T) 2300

DESIGN (INT. / EXT.)

OPERATING

PNEUMATIC TEST

HYDRO. TEST

PRESSURE

1.274

NO

0.8335

0.98 / 0

FLUID

SPECIFIC GRAVITY

SPECIAL SERVICE NO

--

DESIGN DATA

ASME SEC. VIII DIV.1 2010 ED., 2011 ADD.

V-1101

INSTRUMENT AND UTILITY AIR DRUM

TYPE VERTICAL -

MPa G

MPa G

MPa G

MPa G

-INSTRUMENT AIR

CODE

ITEM NAME

ITEM NO.

-

CYCLIC SERVICE NO -

MAIN MATERIALS OF CONSTRUCTION

SHELL / HEAD

SUPPORT LEG

NOZZLE FLANGE

NOZZLE NECK

SA-516 GR.70

SA-106 GR.B / SA-516 GR.70

SA-105

SA-36

-2 : 1 ELLIPSOIDAL HEADTYPE OF HEAD

IMPACT TEST NO -

WEIGHT

ERECTION 1661 kg

NO




Material S : Maximum allowable stress value

Shell SA-516 GR.70 138 MPa

Head SA-516 GR.70 138 MPa

Nozzle Neck SA-106 GR.B 118 MPa

SA-516 GR.70 138 MPa

Nozzle Flange SA-105

Support Leg SA-36 114 MPa

1.3 Nozzle Information

Nozzle Flange: ASME B16.5 Standard

SCH THK.

N1 150 XXS 9.09

N2 150 160 11.13

N3 150 XXS 7.82

N4 150 XXS 7.82

N5 150 160 8.74

N6 150 160 8.74

N7 150 XXS 9.09

N8 150 160 8.74

M1 150 - 10

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

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

Circumferential Stress (Longitudinal Joints)

0.98 x 650.0

138.0 x 0.85 - 0.6 x 0.98

where:

P : internal design pressure P = 0.98 MPa < 0.385SE = 45.161 MPa

R : Inside radius of the shell R = 650.0 mm

S : Maximum allowable stress value S = 138.0 MPa

E : Joint efficiency E = 0.85

Longitudinal Stress (Circumferential Joints)

0.98 x 650.0 637.0

2.0 x 138.0 x 0.85 + 0.4 x 0.98 235.0

where:


Degree of Radiographic Examination: Spot 25%

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

2.3 Minimum required thickness of shell included corrosion allowance

tr = 5.46 + 1.0 = 6.46 mm

2.4 Choose Nominal thickness of shell, ts = 10 mm

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

Type of head: 2:1 Ellipsoidal Head

DN 500 (20")

mm

mm

5.46

2.71=

116.7

=

=

Flange Type

WN RF

WN RF

WN RF

WN RF

WN RF

WN RF

DN 20 (3/4")

DN 20 (3/4")

508

637.0

488

33.4 15.22

60.3

Nozzle inside

diameter, mm

15.22

66.64

11.06

11.06

42.82

42.82

26.7

26.7

60.3

33.4

88.9

42.82

WN RF

WN RF

WN RF

DN 50 (2")

DN 25 (1")

==

=

DN 50 (2") 60.3

DN 50 (2")

Nozzle ClassNozzle Neck Nozzle outside

diameter, mmSize

DN 25 (1")

DN 80 (3")




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

0.98 x 1300.0 1274.0

2.0 x 138.0 x 1.00 - 0.2 x 0.98 275.8

where:

P : internal design pressure P = 0.98 MPa < 0.385SE = 53.13 Mpa

D : Inside diameter of the head skirt D = 1300.0 mm

S : Maximum allowable stress value S = 138.0 MPa


3.2 Minimum required thickness of Head included corrosion allowance

= 4.62 + 1.0 = 5.62 mm

3.3 Minimum required thickness of Head, ts = Min. 5.62 mm

3.4 Minimum thickness as per Data Sheet S-300-1351-001 = 7.8 mm

3.5 Stress Relief (Refer to UCS-79)

Type of head: 2:1 Ellipsoidal Head (Double Curvature)

=> Percent extreme fiber elongation is not exceeded by 5% so that a stress relief is not required

where:

t : Nominal Straight Flange thickness t = 10 mm

D : Inside diameter of the head skirt D = 1300 mm

Rf : Final centerline radius (mean knuckle radius) Rf = 226.0 mm

Ro : Original centerline radius Ro = infinity for straight plate

4. Nozzle Calculation

4.1. Nozzle N3, N4 DN20 (3/4")

Minimum Nozzle neck thickness

where:

S : Maximum allowable stress value, S = 118.0 MPa


Nozzle inside radius Rn = 5.5 mm

tn (min) : minimum required thickness of Nozzle

4.1.1. 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.

0.98 x 5.5 5.42

118.0 x 1.00 - 0.6 x 0.98 117.4

ta = 0.05 + 1.0 = 1.05 mm

4.1.2. = min ( 3.51 , 6.5 ) = 3.5 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).

3.3186 %

mm4.62= =

= 0.05 mm

=

=

= =

ban t t t ,max(min)




tb1 = 6.46 mm

tb2 : for vessels under external pressure

tb2 = 0.0 mm

Max (tb1, tb2) = Max ( 6.46 , 0.0 ) = 6.46 mm

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

(for standard wall pipe)

tb3 = 2.51 + 1.0 = 3.51 mm

=> = max ( 1.05 , 3.51 ) = 3.51 mm

4.1.3. Choose Nozzle actual thickness = 7.82 mm

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

material would include a 12.5% undertolerance

= 0.875 x 7.82 = 6.84 > tn (min) = 3.51 mm

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

4.2. Nozzle N1, N7 DN 25 (1")


where:









0.98 x 7.6 7.46

118.0 x 1.00 - 0.6 x 0.98 117.4

ta = 0.06 + 1.0 = 1.06 mm

4.2.2. = min ( 3.96 , 5.62 ) = 4.0 mm

where:




tb1 = 5.62 mm


tb2 = 0.0 mm

Max (tb1, tb2) = Max ( 5.62 , 0.0 ) = 5.62 mm



tb3 = 2.96 + 1.0 = 3.96 mm

=> = max ( 1.06 , 3.96 ) = 3.96 mm


4.2.4. Nozzle actual thickness is compared with the minimum thickness provided which for pipematerial would include a 12.5% undertolerance

== = 0.06 mm

bant t t ,max(min)

ban t t t ,max(min)

bant t t ,max(min)




= 0.875 x 9.09 = 7.95 > tn (min) = 3.96 mm


4.3. Nozzle N5, N6, N8 DN50 (2")


where:









0.98 x 21.4 20.98

118.0 x 1.00 - 0.6 x 0.98 117.4

ta = 0.18 + 1.0 = 1.18 mm

4.3.2. = min ( 4.42 , 6.5 ) = 4.4 mm

where:




tb1 = 6.46 mm


tb2 = 0.0 mm

Max (tb1, tb2) = Max ( 6.46 , 0.0 ) = 6.46 mm



tb3 = 3.42 + 1.0 = 4.42 mm

=> = max ( 1.18 , 4.42 ) = 4.42 mm




= 0.875 x 8.74 = 7.65 > tn (min) = 4.42 mm


4.4. Nozzle N2 DN80 (3")


where:







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.

= = = 0.18 mm

bant t t ,max(min)

bant t t ,max(min)

ban t t t ,max(min)




0.98 x 33.3 32.65

118.0 x 1.00 - 0.6 x 0.98 117.4

ta = 0.28 + 1.0 = 1.28 mm

4.4.2. = min ( 5.80 , 6.46 ) = 5.8 mm

where:




tb1 = 6.46 mm


tb2 = 0.0 mm

Max (tb1, tb2) = Max ( 6.46 , 0.0 ) = 6.46 mm



tb3 = 4.8 + 1.0 = 5.80 mm

=> = max ( 1.28 , 5.80 ) = 5.80 mm




= 0.875 x 11.13 = 9.74 > tn (min) = 5.80 mm


4.5. Nozzle M1 DN500 (20")

Minimum Nozzle neck thickness (Access opening case)

where:




ta : minimum required thickness of Nozzle





0.98 x 244.0 239.12

138.0 x 0.85 - 0.6 x 0.98 116.7

ta = 2.05 + 1.0 = 3.05 mm

4.5.2. Choose Nozzle actual thickness = 10 mm (Rolling by plate)

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

5.1 Nozzle N3 & N4 to Shell weld joints

5.1.1 Size of weld / Shell thickness

tn (actual) = 7.82 mm

Fillet Leg Length = 8.00 mm

=> tc (actual) = 5.60 mm

= 2.05 mm= =

= = = 0.28 mm

bant t t ,max(min)




t = 10.00 mm

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

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

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 weldtmin = Min ( 19.0 , 7.82 , 10.00 ) = 7.82 mm

0.7tmin = 0.7 x 7.82 = 5.47 mm

=> tc (min) = Min ( 6 , 0.7 t min ) = Min ( 6.00 , 5.47 ) = 5.47 < tc (actual) = 5.6 mm

=> PASS

5.2 Nozzle N1 & N7 to Head weld joints



Fillet Leg Length = 8.00 mm=> tc (actual) = 5.60 mm

t = 7.80 mm


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

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 , 9.09 , 7.80 ) = 7.80 mm

0.7tmin = 0.7 x 7.80 = 5.46 mm


=> PASS

5.3 Nozzle N5, N6, N8 to Shell weld joints





t = 10.00 mm


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

where:


tmin = Min ( 19.0 , 8.74 , 10.00 ) = 8.74 mm

0.7tmin = 0.7 x 8.74 = 6.12 mm


=> PASS

5.4 Nozzle N2 to Shell weld joints








t = 10.00 mm


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

where:


tmin = Min ( 19.0 , 11.13 , 10.00 ) = 10.00 mm

0.7tmin = 0.7 x 10.00 = 7.00 mm

=> tc (min) = Min ( 6 , 0.7 tmin ) = Min ( 6.00 , 7.00 ) = 6.00 < tc (actual) = 6.3 mm

=> PASS

5.5 Nozzle M1 to Shell weld joints





t = 10.00 mm


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

where:


tmin = Min ( 19.0 , 10.0 , 10.00 ) = 10.00 mm

0.7tmin = 0.7 x 10.00 = 7.00 mm

=> tc (min) = Min ( 6 , 0.7 tmin ) = Min ( 6.00 , 7.00 ) = 6.00 < tc (actual) = 6.3 mm

=> PASS

6. Reinforcement

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

6.1 Reinforcement calculation for Manhole M1




Reinforcement material: SA-516 GR.70

Dp : outside diameter of reinforcing element = 850 mm

te : thickness or height of reinforcing element = 10 mm

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

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

A = dtr F + 2tn tr F (1-f r1) = 3151 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 = 1729 mm2

d(E1t - Ftr ) - 2tn(E1t - Ftr )(1 - f r1) = 1728.6 mm2

2(t + tn)(E1t - Ftr ) - 2tn(E1t - Ftr )(1 - f r1) = 141.68 mm2

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

A2 = smaller of below value = 347.6 mm2

5(tn - tr n) f r2t = 347.56 mm2

5(tn - tr n) f r2tn = 347.56 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 = 3420 mm2

where:

d : finished diameter of circular opening or finished dimension = 488 mm

h : distance nozzle projects = 0 mm

t : specified vessel wall thickness = 10 mm

tn : nozzle wall thickness = 10 mm

tr : required thickness of a seamless shell = 6.5 mm

tr n : required thickness of a seamless Nozzle wall = 3.05 mm

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

S : allowable stress value in tension = 138 MPa

Sn : allowable stress in nozzle = 138 MPa

Sp : allowable stress in reinforcing element = 138 MPaSv : allowable stress in vessel = 138 MPa

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

= 5496mm

2 > A = 3151mm

2

RESULT : PASS

7. Weight Calculation Sheet

No. Q'ty

1 Shell 1

2 Head 2

3 Leg Support Angle Bar 4 L 150x15

4 Leg Support Base Plate 4

5 Leg Support Reinforcement Plate 4

6 Lifting Lug 2

7 Name Plate 1

8 Nozzle Neck N1 0.9 PIPE 1",

9 Nozzle Flange N1 1.0 1" WN R



12 Nozzle Neck N3 0.9 PIPE 3/4

13 Nozzle Flange N3 1.0 3/4" WN

14 Nozzle Neck N4 0.1 PIPE 3/4

15 Nozzle Flange N4 1.0 3/4" WN




19 Nozzle Flange N6 1.0 2" WN R20 Nozzle Neck N7 0.1 PIPE 1",



23 Nozzle Flange N8 1 2" WN R

24 Nozzle Neck M1 1 Plate 10

25 Nozzle Flange M1 1 20" WN R

26 Blind Flange M1 1 20" RF 1

27 Reinforcement M1 1 Plate 10

28 Manway davit 1

29 Manway Bolt & Nut 20

30 Manway Gasket 2

Empty Weight

Weight of Fluid at Operating Level

2.7

11.1

1.4

5.52.7

1.0

1.6

9.2

44.5

130.0

21.2

5

9.2

44.5

130.0

82.0

21.2

32.8

2.0

-

-

--

-

-

-

-

-

10

-

Total Weight

(kg)

Thickness

(mm)

Unit Weight

(kg)

718.5

Description

-

-

-

-

-

-

-

6

18

10

20

15

10

10

1.4

5.0

1.9

1.3

4.2

12.1

54.8

150.0

11.1

2.7

11.1

0.9

3.64

0.9

3.64

4.6

82.0

1.9

2.6

17.0

48.2

219.0

300.1

4.6

2.3

3.3

0.9

0.4

0.9

2.7

1.1

2.7

1.1

1.4

0.6

1.1

2.7

-

-

-

-

10

718.5

21.4

1.4

5.5

1661




8. Wind Load Analysis (Refer to Pressure Vessel Design Manual 3rd Ed. 2004 - Dennis R. Moss, Procedure 3-1)

8.1 Design Specification

Wo : Operating Weight of Vessel = 1666 kg

h : Overall Height of Vessel = 3834 mm

D : Outside Vessel Diameter = 1320 mm

De : Vessel Effective Diameter from Table 3-4 = 1.4D = 1848 mm

Le : Vessel Effective Length = 2960 mm

hx : Distance to the center of the projected area = 2350 mm

Structure Category = IV

Exposure Category = B

Cf : Force Coefficient (shape factor) = 0.8 (for cylindrical Vessel)

G : Gust effect factor = 0.8

KZ : Velocity pressure exposure coefficient from Table 3-3a

= 0.57

KZT : Topographic factor = 1

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

I : Importance factor = 1.15

Vessel Support Type Unbraced Angle Legs

Number of Support Legs = 4

Section Designation of Angle Leg mm

l : Leg Length (from Base to bottom tangent line) = 1238 mm

A : Cross Section Area = 4300 mm2 (EN 10056-1: 1998)

r : Least Radius of Gyration = 29.3 mm (EN 10056-1: 1998)

Ix : Leg Property = 8980000 mm4 (EN 10056-1: 1998)

Iy : Leg Property = 8980000 mm4 (EN 10056-1: 1998)

E : Modulus of elasticity = 199000 MPa

8.2 Design Calculation

h/D ratioh/D = = 2.90 < 4

150 x 150 x 15

3834 / 1320

hx




y : Deflection = 1.446 mm

T : Period of Vibration = 0.076 sec < 1 sec

=> The Vessel is considered rigid

Projected area of vessel

Af = Le x De = 2960 x 1848 = 5470080 mm2 = 5.4701 m

2

Velocity pressure at height z above the ground

qz = = 12.772439 psf = 611.54 N/m2

Design Wind force (Shear force)

= 2140.9259 N

Moment at the base plate

M = F x hx = 5031.1759 Nm

9. Seismic Analysis (Refer to Pressure Vessel Design Manual 3rd Ed. 2004 - Dennis R. Moss, Procedure 3-3 & 3-4)

9.1 Design Specification

Wo : Operating Weight of Vessel = 1666 kg

H : Overall Height of Vessel = 3834 mm

D : Outside Diameter of Vessel = 1320 mm

t : Thickness of Vessel = 10 mm

L : Height of Vessel Centroid = 2350 mm

I : Importance factor = 1 (As per Specification)

Soil Profile Type = SD (As per Specification)

Z : Seismic Zone Factor = 0.4 (Choose maximum factor)

Rw : Coefficient (Vertical vessel on unbraced legs) = 2.2

Seismic Source Type from Table 3-9e = A (Assumed)Distance To Fault: = ≥15 km (Assumed)




Na : Near Source Factor from Table 3-9d = 1

Nv : Near Source Factor from Table 3-9d = 1

Ca : Coefficient from Table 3-9a = 0.44

Cv : Coefficient from Table 3-9b = 0.64

Vessel Support Type Unbraced Angle Legs

Number of Support Legs = 4

Section Designation of Angle Leg mm

l : Leg Length (from Base to bottom tangent line) = 1238 mm

A : Cross Section Area = 4300 mm2 (EN 10056-1: 1998)

r : Least Radius of Gyration = 29.3 mm (EN 10056-1: 1998)

Ix : Leg Property = 8980000 mm4 (EN 10056-1: 1998)

Iy : Leg Property = 8980000 mm4 (EN 10056-1: 1998)

I1 : Summation of moments of inertias of all legs perpendicular to F h

= 71840000 mm4

I2 : Summation of moments of inertia of one leg perpendicular to Fh

= 17960000 mm4

e : Eccentricity of Legs = 45 mm

d1 = 1013 mm

C1 : Distance from centroid to extreme fiber = 107.5 mm

E : Modulus of elasticity = 199000 MPa

SL : Allowable Stress of Legs = 114 MPa

SS : Allowable Stress of Shell = 138 MPa

9.2 Design Calculation

y : Deflection = 1.446 mm

T : Period of Vibration = 0.076 sec

Find Base Shear V: Follow Pressure Vessel Design Manual 3rd Ed. 2004 - Dennis R. Moss, Procedure 3-3

V1 = = 4027.0675 N

V2 = = 62324.728 N

V3 = = 8171.8091 N

V4 = = 4754.5071 N

Vs = = 8171.8091 N

V = = 11440.533 N

Horizontal force at top of vessel

Ft = 0 N (T < 0.7 sec)

Horizontal force at C.G of vessel

150 x 150 x 15

(As per 8.2 shown above)

V3

1.4 x Vs




Fh = V - Ft = = 11440.533 N

Vertical force at C.G of vessel

Fv = (1 + Cv)Wo = = 26803.534 N

Overturning moment at base

Mb = LFh + HFt = = 26885252 Nmm

Overturning moment at bottom tangent line

Mt = (L-l)Fh + (H-l)Ft = = 12721872 Nmm

Maximum eccentric load

Horizontal load distribution at each leg

Vertical load distribution at each leg (Case 2)

Dead load

Live load

Vertical load

= 11526.915 N

Bending moment in each leg

= 2805604.9 Nmm

Axial stress in leg

Bending stress in leg

Maximum stress in leg

f = f a + f b = 36.267 MPa < SL = 114 MPa (PASS)

Maximum compressive stress in shell

Shear load in welds attaching legs

2860.1332 N

= 1.576 MPa

=

= 6700.8834 N

-16338.67 N

=

=

= 6825.0388 N

= 2.681 N/mm2

= 33.59 N/mm2

11440.53 - 0

< SS (PASS)MPa138

x




Refer to Pressure Vessel Design Manual 3rd Ed. 2004 - Dennis R. Moss, Procedure 3-5, Table 3-11

Choose Min. Weld size = 5/16 in. = 8 mm

Anchor bolts (Refer to Pressure Vessel Design Handbook 2nd Ed. 1986 - Henry H. Bednar, Chapter 5)

where:

Sa : Allowable Tension Stress in bolts = 138 MPa

Ab : Cross-sectional area of the bolt, in mm2

Mb : Overturning moment at base = 26885252 Nmm

Db : Base Diameter ~ Outside Diameter of Vessel = 1320 mm

W : Operating Weight of Vessel = 1666 kg

N : Number of Support Legs = 4

And Ab ~ π x d2/4 => d = 12.26 mm

Choose Anchor Bolt Diameter M24, SA-193 Gr.B7 is satisfactory in this case.

10. Support Base Plate Thickness (Refer to Pressure Vessel Design Manual, third Edition, Procedure 3-12)

Moment at Base - Operating Condition

Moment, M (kN-m)

Wind

Earthquake a = 210 mm

Sum b = 210 mm

n = 30 mm

Minimum Base Plate Thickness Required m = 30 mm

3.19 mm

where

Bearing pressure

P

a x b

Axial load

M 31.92 x 10^6

B

Fb = 150 MPa Allowable bending stress = 0.6 x Fy

Fy = 250 MPa Yield strength

0.5654

P = = 24935

= MPa

=1280

f c = =24935

44100

N

5.031

26.89

31.92

=16338.66551

2 x 280= 29176 N/m

=> Ab = 117.98341 mm2

= kips/in0.1666

b

c

F

L f t

23

hw

w




B = 1280 mm Anchor Bolt Circle Diameter (B.C.D)

L = Max (n, m) = 30 mm

Choose Base Plate Thickness = 20 mm

11. Lifting Lug Calculation

Equipment weight We = 1661 kg

Lifting Lug material SA-36

11.1 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 = 32595 N

Force

Fz = 0.5 P = 16298 N

Fx = Fz / tg β = 0 N

Max tensile force in Wire Rope

Ps = Fz / sin β = 16298 N

Lifting lug configuration (Base on D-000-1351-0005 - Standard Drawing for Lifting Lug)

where :

SWL = Safe working load

d = Hole Diameter

Rh = Hole Radius

R = Main plate radius

T = Main plate thickness

B = Base width

H = 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

Choose Shackle

Shackle load Ps = 16298 N = 1.661 tonne

Choose Shackle with SWL = 3.2 tonne




As per Table shown above :

Shackle jaw width W = 27 mm

Shackle pin size D = 19 mm

Choose Lug Configuration

d = 30 mm

Rh = d/2 = 15 mm

R = 50 mm

T = 20 mm

B = 150 mm

H = 60 mm

D = 19 mm

Fy = 250 MPa

Stress in Lifting Lug

Bearing Stress

Bearing = 42.89 MPa Bearing = Ps/(T x D)

Allowable = 225 MPa Allowable = 0.9 x Fy

Safety Factor = 5.25 => PASS

Shear Stress

Shear = 11.64 MPa Shear = Ps/(2(R-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 = 24 mm

Plate thickness = 20 mm

Tensile = 33.95 MPa Tensile = Ps/(Effective width*plate thickness)

Allowable = 112.5 MPa Allowable = 0.45 Fy (AISC Section D3.2)


Bending Stress

Section modulus Z = 75000 mm3

Z = B2

x T / 6

Area of lug base A = 3000 mm2

A = B x T

Bending = 5.43 MPa Bending = (Fx*H / Z) + (Fz / A)

Allowable = 150 MPa Allowable = 0.6 Fy


Stress in Weld Joint




Weld type : T-Butt weld, Full Penetration

Critial weld length K = 20 mm (Assumed equal to the thickness of lug)

Section modulus of weld Zw = 150000 mm Zw = B x K / 3

Area of weld Aw = 6000 mm Aw = 2 x K x B

Applied by force FxBending S1 = 0.0 MPa Bending S1 = Fx*H/Zw

Shear S2 = 0.0 MPa Shear S2 = Fx/Aw

Combined = 0.00 MPa Combined = (S12

+ S22)0.5


=> PASS

Applied by force Fz

Tensile S3 = 2.72 MPa Tensile S3 = Fz/Aw



11.2 Check for β = 80 degrees (Considering Tolerance 10 degrees)

Angle β = 80.0 degree

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

Design Load P = 2x9.81xWe = 32595 N

Force

Fz = 0.5 P = 16298 N

Fx = Fz / tg β = 2874 N

Max tensile force in Wire Rope

Ps = Fz / sin β = 16549 N

Choose Shackle

Shackle load Ps = 16549 N = 1.687 tonne

Choose Shackle with SWL = 3.2 tonne

Stress in Lifting Lug

Bearing Stress

Bearing = 43.55 MPa Bearing = Ps/(T x D)



Shear Stress

Shear = 11.82 MPa Shear = Ps/(2(R-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 = 24 mm

Plate thickness = 20 mm

Tensile = 34.48 MPa Tensile = Ps/(Effective width*plate thickness)

Allowable = 112.5 MPa Allowable = 0.45 Fy (AISC Section D3.2)





Bending Stress

Section modulus Z = 75000 mm3

Z = B2

x T / 6

Area of lug base A = 3000 mm2

A = B x T

Bending = 7.73 MPa Bending = (Fx*H / Z) + (Fz / A)



Stress in Weld Joint

Weld type : T-Butt weld, Full Penetration

Critial weld length K = 20 mm (Assumed equal to the thickness of lug)

Section modulus of weld Zw = 150000 mm Zw = B2

x K / 3

Area of weld Aw = 6000 mm Aw = 2 x K x B

Applied by force Fx

Bending S1 = 1.1 MPa Bending S1 = Fx*H/Zw

Shear S2 = 0.5 MPa Shear S2 = Fx/Aw

Combined = 1.25 MPa Combined = (S12

+ S22)0.5



Applied by force Fz

Tensile S3 = 2.72 MPa Tensile S3 = Fz/Aw



Choose Lug Configuration as shown above is satisfactory

12. Hydrotest Pressure

Design Temperature = 65 degrees C

Test Temperature = A.T.M

Internal Design Pressure P = 9.8 bar

Max. Allowable Stress at Design Temperature Sd = 138 MPa

Max. Allowable Stress at Test Temperature St = 138 MPa

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

Ph = 1.3 x 9.8 (138/138) = 12.74 bar = 1.274 MPaG

13. Conclusion

Shell thickness:

Thickness required: 6.46 mm

Thickness actual: 10 mm

Head thickness:

Min. Thickness required: 5.62 mm

Nozzle thickness:

Nozzle N3, N4 DN20 (3/4")


Thickness actual: 7.82 mm

Nozzle N1, N7 DN 25 (1")






Nozzle N5, N6, N8 DN50 (2")



Nozzle N2 DN80 (3")



Nozzle M1 DN500 (20")



Weld size:

Nozzle N3 & N4 to Shell weld joints

tc (actual) = 5.60 => Leg length = 8 mm

Nozzle N1 & N7 to Head weld joints


Nozzle N5, N6, N8 to Shell weld joints


Nozzle N2 to Shell weld joints


Nozzle M1 to Shell weld joints


Nozzle reinforcement:

Manhole reinforcement size:

Outside diameter = 850 mm

Thickness = 10 mm

Leg Support Base Plate Thickness



Hydro test pressure: 12.7 bar = 1.274 MPaG



1 bar = 14.5038 psi

Shell material SA-516 1 bar = 100kPa

Shell I/D (mm) 1300 1 bar = 0.987 atm

Head material SA-516 1 Mpa = 145.038 psi

Head type Elip 2:1

Design temperature (Degree C) 65

Max. Allowable stress (Mpa) 138.0

Corrosion allow. 1

Shell length (mm) 2300

Strainght flange of head 50

Volume of Shell (T to T) (m^3) 3.05

Volume of 1 Head (m^3) 0.29

Total Volume (m^3) 3.63

Design Pressure (Psi) 142.1

Shell radius (inch) 25.59

Max. Allowable stress (Psi) 20015.20

Weld joint Efficiency 1.00

Min. Cal. thick of Shell (mm) 5.64

Min. Cal. Head thickness (mm) 5.62

Nom. Shell thickness (mm) 9.00

Nom. Head thickness (mm) 10.00

N1 1" WN RF

Tinh khoi luong N2 2" WN RF

VESSEL ID 1300.00 N3 3/4" WN RF

SHELL THK 9.00 N4 3/4" WN RF

SHELL LENGTH 2300.00 N5 2" WN RF

FABRI. HEAD PLATE THK. 10.00 N6 2" WN RF

HEAD WEIGHT 154.2 N7 1" WN RF

SHELL WEIGHT 668.2 N8 2" WN RF

VESSEL BODY NET WEIGHT (KG) 976.7 M1 20" WN RF

Lifting lug 2.00

Nozzles (kg) 284.40

Name Plate 2.00

4 Support Leg 177.746738

Manhole davit 10

Total weight (kg) 1,452.8

Water 3628.02

Full water weight 5,080.85

Nozzle Size Flange Type



SCH THK. Flange, B Flange, Bolt Nut Neck

150 80 4.55 1.4 3

150 80 5.54 2.7 2

150 160 5.56 0.9 1

150 160 5.56 0.9 1

150 80 5.54 2.7 2

150 80 5.54 2.7 2

150 80 4.55 1.4 1

150 80 5.54 2.7 2

150 STD 9.53 245 10

260.4 24

WEIGHTClass

Nozzle Neck

V 2151 101 a 205 C_Design Calculation Sheet (v 1101)

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Transcript of V 2151 101 a 205 C_Design Calculation Sheet (v 1101)