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

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  • 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

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

    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

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

    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

    : 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) = D2/4 = 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) = D2/4 = 12.35 m

    2

    P2 = F/A = 0.159 kPa

    Concentrated Load = 250 kg (Assumed)

    F = m x g = 2452.5 N

    Area (A) = D2/4 = 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

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

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

    a/b = 1

    = 0.2874

    = 0.0444

    Elastic Modulus (E) = 1.93E+08 kPa

    Allowable Stress ([]) = 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 [] 112000

    t/2 = (ACCEPTED) (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 =

    4+

    2

    8

    Page 6 of 31

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

    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 =

    = 2

    Page 7 of 31

    VulaRectangle

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

    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

    =

    3

    =

    275

    1983

    3 275

    275

    1 =

    211 + 6

    2

    2+

    2 1.17 + /2

    2 =

    233 + 6

    4

    4

    Page 8 of 31

  • Project: NOEV LUBE OIL BLENDING PLANT Job