Design Calculations. CTC My Address My City. Revision : 16/02/10. Example B102

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1 Revision : 16/2/1 2 16/2/1 1 6/11/9 Rev. Date Description Aut. Chk. App. QA Job Tag : Description : Job Name : Drawing No : Vessel Tag : Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

2 Update this field to get the table of contents. Table of Contents Revision : 16/2/1 Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

3 Input data list Design Parameters. Design pressure code : CODAP 21 Div.2 Add. 1/12 Design and optimize : Yes Local Load Design Method : EN 13445:29 V5 (213-7) Design check : No Flange Standard : ASME B /B With Stiffeners : Yes Piping standard in acc. With : ASME B36.1M-24/B36.19M-24 Plate associated with stiffeners : Yes Apply DIN 188 part 4 : No Support rings as stiffening : No MAWP calculation req'd. : No Min. distance between stiffeners : 3 mm Specific Gravity : 8 Gas Pressure in Vessel : Yes Default Values. Rounded Up Dist. Flange / Axis : 5 mm Dist. Insulation / Flange : 75 mm Extension for Welded Tubes : / Safety factor for flanges in operation/test : 1 1 Rule limiting available area in opening reinforcement f(t) : 1 Friction Factor for Bolt Torque - Thread / Nut supporting surface : Geometry Definition. No. Type Tag Designation Thk. (*) Corr. Tol. Temp.. (mm) (mm) (mm) ( C) 1 [5] Elliptical Head 3.1 Head [1] Shell 31.5 Barrel [1] Shell 31.6 Barrel [2] Cone 3.24 Cone [1] Shell 31.7 Barrel [5] Elliptical Head 3.12 Head (*) minimum input thickness. Nozzle Definition. No. Tag Location Set-in Ori. Inc. Exc. (mm) ( ) ( ) (mm) Designation Nozzle Type Flange 1 S Outlet A Process [13] 2 H 3, Manhole H Manhole [13] Welding Neck (Class type 11) Welding Neck (Class type 11) Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

4 List of Materials. Shell Shells / heads : SA24GR316L Nozzles Nozzle Necks : Nozzle flange : SA16GRB, SA516GR6 SA15 Support Saddles, brackets, legs or skirt : SA516GR6 SA24GR316L ASME II (Plate, Stainless Steel, 212) S3163 P-No. : 8 Group No. : 1 Vacuum curve: C4-12 Specific gravity: 8 Elongation: 4 % Poisson Factor:.31 Chemical comp. (%) Cr Ni Modulus of Elasticity (ASME II part D table TM) C MPa C 65 7 MPa Thermal expansion coefficients (ASME II part D table TE) C mm/mm/ C C mm/mm/ C Strength C MPa C 525 MPa 387 Yield strength.2% C MPa C MPa Yield strength 1% C MPa C MPa Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

5 SA516GR6 ASME II (Plate, Carbon Steel, 212) K21 P-No. : 1 Group No. : 1 Vacuum curve: C4-2 Specific gravity: 7.85 Poisson Factor:.3 Chemical comp. (%) C Mn.3 1 Modulus of Elasticity (ASME II part D table TM) C MPa Thermal expansion coefficients (ASME II part D table TE) C mm/mm/ C C mm/mm/ C Strength C MPa Yield strength.2% C MPa C MPa SA16GRB ASME II (Seamless pipe, Carbon Steel, 212) K36 P-No. : 1 Group No. : 1 Vacuum curve: C4-2 Specific gravity: 7.85 Min. Temp.: 68 F Poisson Factor:.3 Chemical comp. (%) C Mn Modulus of Elasticity (ASME II part D table TM) C MPa Thermal expansion coefficients (ASME II part D table TE) F in/in/ F F , 1,5 1,1 1,15 1,2 1,25 1,3 in/in/ F Strength C MPa Yield strength.2% C MPa C MPa SA15 ASME II (Forging, Carbon Steel, 212) K354 P-No. : 1 Group No. : 2 Vacuum curve: C4-2 Specific gravity: 7.85 Min. Temp.: 68 F Poisson Factor:.3 Modulus of Elasticity (ASME II part D table TM) C MPa Thermal expansion coefficients (ASME II part D table TE) C mm/mm/ C C mm/mm/ C Strength C MPa Yield strength.2% C MPa C MPa Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

6 Codes, Guidelines and Standards Implemented. Pressure vessel design code: CODAP 21 Div.2 Add. 1/12 Local load design method: EN 13445:29 V5 (213-7) WRC 17 (22-1) Standard of flange ratings: ASME B Standard for pipes: ASME B36.1M-24/B36.19M-24 Material standard(s) and update(s): ASME II 212 SA24GR316L Plate ASME II 212 SA516GR6 Plate ASME II 212 SA16GRB Seamless pipe ASME II 212 SA15 Forging Units: SI g = m/s 2 [ Weight (N) = Mass (kg) g ] Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

7 Design Conditions. Compartment 1 / / Internal pressure :.9 MPa / / Required MAWP : / / Design Temperature : 18 C / / Height of liquid : mm / / Operating fluid spec. gravity : 1 / / Corrosion : 1.5 mm / / External pressure : -.1 MPa / / External temperature : 18 C / / Test Pressure : / / Test fluid spec. gravity : 1 / / Insulation Thickness : mm / / Weight/density of insulation : 35 kg/m 3 / / Construction Category : B1 / / Nominal stress : 1 / / Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

8 Allowable stresses and safety factors CODAP Division 2 GA4 f R m R t m R t p,2 R t p1, σ R σ 1% Nominal stress at design temperature. Minimum guaranteed tensile strength at room temperature. Minimum guaranteed tensile strength at design temperature. Minimum guaranteed yield strength.2 % at design temperature. Minimum guaranteed yield strength 1 % at design temperature. Average stress to cause rupture by creep in 1, hours at design temperature. Average stress to cause 1% elongation by creep in 1, hours hours at design temperature. Excluding bolting Bolting Compartment 1 Nominal stress at design temperature f Category B1 Normal Conditions f 1 Exceptional and test conditions Creep Steel (M2, M3 A<3%, M4, M5, M6) MIN ( R t p,2 / 1.5 ; R m / 2.4 ).95 R t p,2 ΜΙΝ{σ R/1.6 ; σ 1%} Stainless steel (M3 A 3%) (R t p1, / 1.5) MIN ( R t p1, / 1.2 ; R t m / 3 ).95 R t p1, ΜΙΝ{σ R/1.6 ; σ 1%} Copper alloy R t m / 4 R t m / 3 ΜΙΝ{σ R/1.6 ; σ 1%} Aluminum Alloy MIN ( R t p,2 / 1.5 ; R m / 2.4 ).95 R t p,2 ΜΙΝ{σ R/1.6 ; σ 1%} Nickel alloy MIN ( R t p,2 / 1.5 ; R m / 2.4 ).95 R t p,2 ΜΙΝ{σ R/1.6 ; σ 1%} Titanium and Zirconium R t m / 3 R t m / 2.2 ΜΙΝ{σ R/1.6 ; σ 1%} Steel (M2,M4,M5,M6) MIN ( R t p,2 / 3 ; R m / 5 ) R t p,2 / 2 ΜΙΝ{σ R/1.6 ; σ 1%} Stainless steel (M3) R t m / 5 R t m / 3 ΜΙΝ{σ R/1.6 ; σ 1%} Cast materials.79 f Mechanical properties have been calculated on the basis of standard thickness limits. Users should check that thicknesses comply with any usage restrictions given in Part M, based on building classification and division. Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

9 Hydraulic Test Pressure CODAP I : P e = MAX [ 1,43 P s ; 1,25 P s ( f E / f t ) max ] P s = Design Pressure f E = allowable stress at room temperature, normal operating conditions f t = allowable stress under normal operating conditions For each component P s f E f t e c P e (MPa) (MPa) (MPa) (mm) (mm) (MPa) Elliptical Head (1) Shell (2) Shell (3) Cone (4) Shell (5) Elliptical Head (6) Nozzle S Nozzle H Neck Pad / / / /.9 Flange Bolting / / / Neck Pad / / / /.9 Flange Bolting / / / Compartment 1 / / Test Pressure at the Top : MPa / / For vertical vessels with a test in horizontal position : P e = P e + P e P e = additional hydrostatic pressure corresponding to the height of the vertical compartment. Compartment 1 / / Design Pressure P s :.9 MPa / / Test Pressure at the Top : MPa / / Hydrostatic pressure P e : / / / Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

10 Hydrostatic Pressure Type of components Specific Gravity liquid level Operating hydrostatic height Hydrostatic pressure Specific Gravity liquid level Horizontal hydrostatic height Test Hydrostatic pressure liquid level Vertical hydrostatic height Hydrostatic pressure (mm) (mm) (MPa) (mm) (mm) (MPa) (mm) (mm) (MPa) Shell(s) ,48. 1, , ,48. 1, , ,46. 1, , ,5. 4, ,46. 2, ,. 2, ,46. 2, Opening(s) 1 S 1 /.. 1 / 1, / 5, H 1 /.. 1 / 2, / 1, Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

11 Element(s) of geometry under internal pressure Elliptical head (3.1) Internal pressure. CODAP 21 Div.2 Add. 1/12 e n = nominal thickness f = Allowable stress e = minimum required thickness h i h e L.T P = internal pressure h c z = Weld joint efficiency T = Temperature σ = circular stress P max = Max. allowable pressure R = equivalent inside radius P h = Hydrostatic pressure D i = Internal Diameter c = corrosion + tolerance D e = External Diameter = 1,5 mm K = Axis ratio = D i /2h i = 1.9 h e = outside height = mm Tol % = tolerance for pipes e n,min = (e+c)/tol % shall be e n e u = (e n Tol % ) c shall be e SA24GR316L Plate Schedule : / NPS : / e n = 1. mm Tol % = / PWHT : Yes Radiography : Full Seamless Cor. = 1.5 mm Tol. = mm C3.1.4 Conditions of applicability : 1.7 K 2.2 D e 12.5e Analysis thickness e u.1d e Equivalent knuckle radius : r = D i [.5/K.8] e s = PR/(2fz-.5P) e y = β (.75R+.2D i )P/f e b =.433 (.75R+.2D i ) (D i /r).55 (P/f).667 required thickness : e = max[e s, e y, e b ] Operation Horizontal test Vertical test Operation Horizontal test Vertical test Operation Horizontal test Vertical test N X X N X X N X X MAWP (18 C, Corroded) = 1.18 MPa C Butt-welded with Shell. L.T. slope 1/3 e c, D i D e Equivalent crown radius : R = D i [.44 K+.2] β Table C c P (MPa) P h (MPa) T ( C) f (MPa) z D i (mm) r (mm) R (mm) , , , , , , e c β e s (mm) e y (mm) e b (mm) e (mm) e u (mm) σ (MPa) P max (MPa) e n,min (mm) e D i l c l = h c D C a MAWP (2 C, new) = 1.92 MPa D = shell inside diameter = 1,48. mm e n,s = shell nominal thickness 1. mm f s = allowable stress of the shell c s = (corrosion + tolerance) Shell = 1.5 mm+. mm Shell analysis thickness : e u,s = e n,,s c s Straight length : h c = 5. mm Straight flange analysis thickness :e c = e n c e c, = PD i /(2f P) l c,max =.2 ( D i + ec, ) ec, d) Straight Flange Thickness e c shall be e e) If l > l c,max : e1) Straight Flange Thickness e c shall be e c, e2) If l c > l c,max : analysis thickness at the end should not be < e c, Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

12 Operation N Horizontal test X Vertical test X With D i Corroded f s (MPa) e c, (mm) l c,max (mm) e c,min (mm) Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

13 Conical shell (3.24) under internal pressure. CODAP 21 Div.2 Add. 1/12 Paragraph C2.3 e n = nominal thickness = 2 mm Knuckle radius at large end r 1,t = 15 mm P = Design Pressure α = Half angle = Flare radius at small end r 2,t = mm f = Nominal stress T = Temperature Large end diameter = 2,5 mm (outside) z = Weld joint efficiency Cone height = 1,5 mm Small end diameter = 1,5 mm (outside) c = corrosion + tolerance Cone Length L cône = 1, mm Radiography : 1% Material : SA24GR316L [Plate] PWHT : Yes C2.3.2 Scope of application. α 6 r 1,t.3D m,1 e 1,cône,u.cos(α) / D m,1 >.1 (e 1,cône,u = e n c) D m / cos(α) 5 e r 2,t.1D m,2 C2.3.4 Required thickness of cone. e = P D e /(2f z+p) 1/cos(α) P (MPa) T ( C) f (MPa) e (mm) D e (mm) z c (mm) σ (MPa) Operation N.9 Horizontal test X Vertical test X MAWP (18 C, Corroded) = 1.51 MPa ,5. 2,5. 2, MAWP (2 C, new) = 2.27 MPa e 1,cône,u (mm) C2.3.5 Large end junction with a knuckle LT l 1,cyl LT e j = PDm,1β ρ γ = 1+ f 2 f γ 1.2( 1+.2 ρ) min,1 = min(f, f 1,cyl ) min,1 l 1,cône ρ = λ r D 1,t m,1 e j 1+ 1 α cosα λ = 2.5 r1,t Di, e 1,cyl r 1,t l k 1 β = max 1, 3 D e j tg α cosα P fmin,1 6 m,1 α D m, D i,1 D k α e 1,cône l k =.5 D e m,1 1,cône cosα D k = D i,1 2 r 1,t (1 cos α) - 2 l k sin α e 1,cône,u α l 1,cyl = max 1.4 D m,1 e1,cyl r1,t + tg,. 5 Dm,1 e1, cyl 2 2 e k = D m,1 e1,cône e D e 1,cône,u α m,1 1,cône l 1,cône = max 1.4 r + 1,t tg,.7 cosα 2 2 cosα e cyl = Operation Horizontal test Vertical test Operation Horizontal test Vertical test Operation Horizontal test Vertical test N X X N X X N X X PDk 1 fz P cosα 2 1, cyl 2 f 1,cyl P D z i,1 1,cyl P e 1,cyl = max (e j, e cyl ) e 1,cône = max (e j, e k ) D i,1 (mm) D m,1 (mm) f 1,cyl (MPa) f min,1 (MPa) λ γ ρ 2,463. 2, ,463. 2, ,463. 2, β z 1,cyl e cyl (mm) e j (mm) e 1,cyl (mm) l k (mm) D k (mm) , , , e k (mm) e 1,cône (mm) l 1,cyl (mm) l 1,cône (mm) Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

14 C2.3.7 Small end junction without a flare D m,2 S cyl e 2,cyl,u l l 2,cyl 2,cône e 2,cône,u S G s s.35335s s = e 2,cône / e 2,cyl k s = s s f min,2 = min ( f, f 2cyl ) k s = min [ 1, k s + s (1-k s ) (P / f min,2 /.1)] P P P a 1 + a3 + a + 5 a 7 fmin,2 fmin,2 fmin,2 k = MIN, ( 1) P + P 1 + P a 2 a 4 a 6 fmin,2 fmin,2 fmin,2 Parameters a 1, a 2 : Table C F 1 = k k s [ S (f z.5 P) + S cyl (f 2,cyl z 2,cyl.5 P) ] F 1 P G 3 l 2,cône,n = D m e,2 cos α 2,cône l 2,cyl,n = D m,2 e 2, cyl Operation Horizontal test Vertical test Operation Horizontal test Vertical test Operation Horizontal test Vertical test Operation Horizontal test Vertical test N X X N X X N X X N X X e 2,cône (mm) e 2,cyl (mm) s f 2cyl (MPa) f min,2 (MPa) z 2,cyl k s k s k S (mm 2 ) S cyl (mm 2 ) G (mm 2 ) , , , , , , , , ,431.7 D m,2 (mm) l 2,cyl,n (mm) l 2,cône,n (mm) l 2,cyl (mm) l 2,cône (mm) 1, , , e 2,cyl,u (mm) e 2,cône,u (mm) F 1 (N) P G (N) , , ,146,92 556, ,146, ,697.3 Application of Paragraph C2.3.3 General case : l 2,cyl = l 2,cyl,n When the length interferes with the area of influence around the joint between a cylinder and a Tubesheet or a flange, use a reduced value : l 2,cyl = l 2,cyl,r The software does not restrict the length l 2,cyl Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

15 Elliptical head (3.12) Internal pressure. CODAP 21 Div.2 Add. 1/12 e n = nominal thickness f = Allowable stress e = minimum required thickness h i h e L.T P = internal pressure h c z = Weld joint efficiency T = Temperature σ = circular stress P max = Max. allowable pressure R = equivalent inside radius P h = Hydrostatic pressure D i = Internal Diameter c = corrosion + tolerance D e = External Diameter = 2,5 mm K = Axis ratio = D i /2h i = 1.9 h e = outside height = mm Tol % = tolerance for pipes e n,min = (e+c)/tol % shall be e n e u = (e n Tol % ) c shall be e SA24GR316L Plate Schedule : / NPS : / e n = 2. mm Tol % = / PWHT : Yes Radiography : Full Seamless Cor. = 1.5 mm Tol. = mm C3.1.4 Conditions of applicability : 1.7 K 2.2 D e 12.5e Analysis thickness e u.1d e Equivalent knuckle radius : r = D i [.5/K.8] e s = PR/(2fz-.5P) e y = β (.75R+.2D i )P/f e b =.433 (.75R+.2D i ) (D i /r).55 (P/f).667 required thickness : e = max[e s, e y, e b ] Operation Horizontal test Vertical test Operation Horizontal test Vertical test Operation Horizontal test Vertical test N X X N X X N X X MAWP (18 C, Corroded) = 1.54 MPa C Butt-welded with Shell. L.T. slope 1/3 e c, D i D e Equivalent crown radius : R = D i [.44 K+.2] β Table C c P (MPa) P h (MPa) T ( C) f (MPa) z D i (mm) r (mm) R (mm) , , , , , ,15.76 e c β e s (mm) e y (mm) e b (mm) e (mm) e u (mm) σ (MPa) P max (MPa) e n,min (mm) e D i l c l = h c D C a MAWP (2 C, new) = 2.31 MPa D = shell inside diameter = 2,46. mm e n,s = shell nominal thickness 2. mm f s = allowable stress of the shell c s = (corrosion + tolerance) Shell = 1.5 mm+. mm Shell analysis thickness : e u,s = e n,,s c s Straight length : h c = 5. mm Straight flange analysis thickness :e c = e n c e c, = PD i /(2f P) l c,max =.2 ( D i + ec, ) ec, d) Straight Flange Thickness e c shall be e e) If l > l c,max : e1) Straight Flange Thickness e c shall be e c, e2) If l c > l c,max : analysis thickness at the end should not be < e c, Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

16 Operation N Horizontal test X Vertical test X With D i Corroded f s (MPa) e c, (mm) l c,max (mm) e c,min (mm) Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

17 Cylindrical shell under internal pressure. CODAP 21 Div.2 Add. 1/12 C2.1 e = minimum required thickness e n = nominal thickness z = Weld joint efficiency P = internal pressure f = Nominal stress T = Temperature D e, D i = outside, inside diameter c = corrosion + tolerance σ = circular stress D m = average diameter Tol % = tolerance for pipes P a = maximum allowable pressure e n,min = (e+c)/tol % shall be e n e u = (e n Tol % ) c shall be e P h = Hydrostatic pressure C D m shall be 5e formula C e = P. (D i +2c)./ (2f.z P) σ = (P. (D i +2c) / e u + P) / (2 z) formula C e = P.D e./ (2f.z+P) σ = (P.D e / e u P) / (2 z) Shell (2) : 31.5 (Barrel) SA24GR316L Plate Schedule : / NPS : / e n = 1. mm D i = 1,48. mm Tol % = / PWHT : Yes Radiography : Spot D m = 1,49. mm D e = 1,5. mm Cor. = 1.5 mm Tol. = mm Operation N.9 Horizontal test X Vertical test X MAWP (18 C, Corroded) = 1 MPa P (MPa) P h (MPa) T ( C) f (MPa) z e u (mm) σ (MPa) P a (MPa) e (mm) MAWP (2 C, new) = 1.64 MPa e n,min (mm) Shell (3) : 31.6 (Barrel) SA24GR316L Plate Schedule : / NPS : / e n = 2. mm D i = 1,46. mm Tol % = / PWHT : Yes Radiography : Spot D m = 1,48. mm D e = 1,5. mm Cor. = 1.5 mm Tol. = mm Operation N.9 Horizontal test X Vertical test X MAWP (18 C, Corroded) = 2.19 MPa P (MPa) P h (MPa) T ( C) f (MPa) z e u (mm) σ (MPa) P a (MPa) e (mm) MAWP (2 C, new) = 3.29 MPa e n,min (mm) Shell (5) : 31.7 (Barrel) SA24GR316L Plate Schedule : / NPS : / e n = 2. mm D i = 2,46. mm Tol % = / PWHT : Yes Radiography : Spot D m = 2,48. mm D e = 2,5. mm Cor. = 1.5 mm Tol. = mm Operation N.9 Horizontal test X Vertical test X MAWP (18 C, Corroded) = 1.31 MPa P (MPa) P h (MPa) T ( C) f (MPa) z e u (mm) σ (MPa) P a (MPa) e (mm) MAWP (2 C, new) = 1.97 MPa e n,min (mm) Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

18 Element(s) of geometry under external pressure External Pressure Elliptical Head (Section No. 1) (in operation) Elements considered : modulus of Vacuum Diameter Thickness Tag elasticity curve Temperature (mm) (mm) (MPa) ( C) Head 1, , C CODAP C4 External Pressure : P =.1 MPa modulus of elasticity : E = 182, MPa Factor : K= 1 Allowable stress : f = MPa Vacuum curve : C4-12 Material : SA24GR316L Thickness as new : e n = 1 mm Corrosion : 1.5 mm Checked thickness : e = 8.5 mm Tolerance : mm External Diameter : D e = 1,5 mm inside crown radius : R i = / Internal Diameter : D i = D e -2e = / Inside radius of knuckle : r c = / outside radius : R e = / Axis ratio : D i /(2h 2 ) = 1.9 C4.2.3 Elliptical heads C 1 =.45[D i /(2h 2 )] =.855 β = ( Graph C3.1.5 or Table C c )=.6334 R e = C 1 D e = 1,282.5 mm 1.2P R 1.2P e s = e y = β(.75r +.2Di ) 1.7 <= D i /(2h 2 ) <= f.5p f.1d e e.8d e e min = MAX(e y ;e s ) =.92 mm e. 125 A = =.8 B R e e P a = K =.2967 MPa P Re e B (Chart C4-12 or AE/2 ) = MPa Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

19 External Pressure Shell (Section No. 2) (in operation) Ends of section : Bottom : Head (component No. 1) Support line level : mm top : Cone-to-cylinder junction without stiffening ring Support line level : 5. mm Elements considered : Tag Head (Straight flange) Barrel Barrel Diameter Thickness modulus of Vacuum elasticity curve Temperature (mm) (mm) (MPa) ( C) 1, , C C 1, , C C 1, , C C CODAP C4 External Pressure : P =.1 MPa Design Temperature : 18 C Factor : K= 1 modulus of elasticity : E = 182, MPa Unsupported shell length : mm Pipe, tolerance on the new thickness : c 1 = / Diameter of section : D e = 1,5 mm Vacuum curve : C4-12 Checked thickness : e = 8.5 mm Allowable stress : f = MPa C4.2.1 Cylindrical shell with straight circular section L = mm L/D e =.42 D e /e = A (Chart C ) =.15 B ((Chart C4-12 or AE/2 ) = MPa P a =.378 MPa P D e / e 1 : P a = 4 3 B De K e f 1 D e / e < 1 : P a = MIN.833 BK ; 1 De e De e De e Minimum required thickness = 3.44 mm Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

20 External Pressure Conical shell (Section No. 3) (in operation) Ends of section : Bottom : top : Cone-to-cylinder junction without stiffening ring Support line level : 5. mm Cone-to-cylinder junction without stiffening ring Support line level : 1, mm Elements considered : modulus of Vacuum Diameter Thickness Tag elasticity curve Temperature (mm) (mm) (MPa) ( C) Cone , C CODAP C4 External Pressure : P =.1 MPa Design Temperature : 18 C Factor : K= 1 modulus of elasticity : E = 182, MPa Unsupported shell length : 1,474.4 mm half opening angle of conical shell : α = Diameter of section : D e = 2,5 mm Vacuum curve : C4-12 Checked thickness : e = 18.5 mm Allowable stress : f = MPa C4.2.4 Conical shell with straight circular section H = 1,474.4 mm H tgα L eq = L eq /D eq =.45 H 1 = 1, mm D e D D eq = e = 2,64.3 mm D cosα eq /e = A (Chart C ) =.19 B (Chart C4-12 or AE/2 ) = MPa D eq /e 1 : P a = 4 3 B Deq K e f D eq /e < 1 : P a = MIN.833 BK ; Deq e D eq P a =.487 MPa P 1 1 e Deq e Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

21 External Pressure Large cylinder-to-cone junction (Section No. 3) (in operation) CODAP C4 Junction with knuckle, without stiffener Internal corroded radius of knuckle : r t = mm Angle : α = Shell adjacent to the junction, element No. : 5 Calculation length of cylinder section : L= 2, mm Cone adjacent to junction, element number : 4 Calculation length of cone section : H= 1,474.4 mm External Pressure : P =.1 MPa Factor : K= 1 Cylindrical shell Material : SA24GR316L Temperature : 18 C Nominal stress : f 1,cyl = MPa modulus of elasticity : E = 182, MPa Vacuum curve : C4-12 Thickness as new : e n = 2 mm Corrosion : 1.5 mm Checked thickness : e cyl = 18.5 mm Tolerance : mm External Diameter : D e,1 = 2,5 mm average diameter : D m,1 = 2,481.5 mm Conical shell Material : SA24GR316L Temperature : 18 C Nominal stress : f = MPa modulus of elasticity : E = 182, MPa Vacuum curve : C4-12 Thickness as new : e n = 2 mm Corrosion : 1.5 mm Checked thickness : e cone = 18.5 mm Tolerance : mm Stiffener Type and dimensions : / Material : / Nominal stress : f a = / Temperature : / Vacuum curve : / modulus of elasticity : E = / Cross-sectional area : A r = / Diameter of shell at centroid elevation : D e = / C r t.1d e,1 e j = (formula C ) = 1.87 mm If r t <.1D e,1 : l 1,cone = Dm,1 ev cosα and l 1,cyl = Dm,1 ev (e v = e j ) If.1D e,1 r t.1d e,1 : l 1,cone = Dm,1 et cosα and l 1,cyl =.5 Dm,1 et (e t = e j ) The actual thickness of the shell, along a length l 1,cyl = 34.9 mm, shall be e j Straight Flange Thickness l 1,cone = 7.6 mm, shall be e j C B = 3 Q D 1 1 e,1 2 = 8.31 MPa Q 1 = L + H H De,1 P + tg α = N/mm 4 hj eeq + Ar K 2 3D 4 e,1 A (Chart C4-12 or 2B/E ; C ) =.1 I n = ( h e A ) A 12 I (C ) = 24,624,49 mm 4 I n 2 e,1 j eq r h j = 1, mm e eq = 18.5 mm D + = 1,66,344 mm 4 C Moment of inertia x 1 =MIN{.55 De,1 e1 ; (Fig. C / C ) } = mm e 1 = 18.5 mm x 2 =MIN{.55 De,1 e2 cosα ; (Fig. C / C ) } = mm e 2 = 18.5 mm Fig. C l 3 = / distance from centroid to junction = /.55 De,1 e3 = / e 3 = / distance from centroid to stiffener edge = / C4.2.8 Manufacturing rules for ring stiffeners h = / Flat bars : Angles : Type T, I or H : b = / h b 16 h e a 5 h e a 5 e a = / e s = / b ea De es b ea De es b e a + 16es b e a + 32es Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

22 External Pressure Small cylinder-to-cone junction (Section No. 3) (in operation) CODAP C4 Junction without knuckle, without stiffener Internal corroded radius of knuckle : r t = mm Angle : α = Shell adjacent to the junction, element No. : 3 Calculation length of cylinder section : L= mm Cone adjacent to junction, element number : 4 Calculation length of cone section : H= 1,474.4 mm External Pressure : P =.1 MPa Factor : K= 1 Cylindrical shell Material : SA24GR316L Temperature : 18 C Nominal stress : f 2,cyl = MPa modulus of elasticity : E = 182, MPa Vacuum curve : C4-12 Thickness as new : e n = 2 mm Corrosion : 1.5 mm Checked thickness : e cyl = 18.5 mm Tolerance : mm External Diameter : D e,2 = 1,5 mm average diameter : D m,2 = 1,481.5 mm Conical shell Material : SA24GR316L Temperature : 18 C Nominal stress : f = MPa modulus of elasticity : E = 182, MPa Vacuum curve : C4-12 Thickness as new : e n = 2 mm Corrosion : 1.5 mm Checked thickness : e cone = 18.5 mm Tolerance : mm Stiffener Type and dimensions : / Material : / Nominal stress : f a = / Temperature : / Vacuum curve : / modulus of elasticity : E = / Cross-sectional area : A r = / Diameter of shell at centroid elevation : D e = / C l 1,cone (calculated at large end junction) = mm δ = L cone (figures C , C , C ) = 1, mm { D e cosα } l 2,cone = MIN ( L l ); cone 1,cone m,2 cone = mm l 2,cyl = m,2 ecyl Dm,2 = 8.71 k = (graphic C ) =.82 Dm,2 econe cosα D = mm figures C : G = 37,15.3 mm 2 S = 3,18.5 mm 2 S cyl = 3,594.8 mm 2 coefficient C2.3.7 : k =.837 k s = 1 k s = 1 k k S f.5p + S f.5p + A f. 5P = 579,628.3 N P.G = 37,1.53 N formula C : s[ ( ) cyl( 2,cyl ) r ( a )] C B = 3 Q D 1 2 e,2 2 L H = MPa Q 2 = H De,2 P tg α = N/mm 2 4 hj eeq + Ar K 2 2 2cos α 3De,2 cos α 4 2 e,2 j eq r A A ((Chart C4-12 or 2B/E ; C ) =.1 I n = ( h e A ) 12 I (C ) = 41,413.6 mm 4 I n h j = 1,94.1 mm e eq = 18.5 mm D + = 335,485.8 mm 4 C Moment of inertia x 1 =MIN{.55 De,2 e1 ; (Fig. C / C ) } = mm e 1 = 18.5 mm x 2 =MIN{.55 De,2 e2 cosα ; (Fig. C / C ) } = mm e 2 = 18.5 mm Fig. C l 3 = / distance from centroid to junction = /.55 De,2 e3 = / e 3 = / distance from centroid to stiffener edge = / C4.2.8 Manufacturing rules for ring stiffeners h = / Flat bars : Angles : Type T, I or H : b = / h b 16 h e a 5 h e a 5 e a = / e s = / b ea De es b ea De es b e a + 16es b e a + 32es Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

23 External Pressure Shell (Section No. 4) (in operation) Ends of section : Bottom : Cone-to-cylinder junction without stiffening ring Support line level : 1, mm top : Head (component No. 6) Support line level : 4, mm Elements considered : Tag Barrel Head (Straight flange) Diameter Thickness modulus of Vacuum elasticity curve Temperature (mm) (mm) (MPa) ( C) 2, , C C 2, , C C CODAP C4 External Pressure : P =.1 MPa Design Temperature : 18 C Factor : K= 1 modulus of elasticity : E = 182, MPa Unsupported shell length : 2, mm Pipe, tolerance on the new thickness : c 1 = / Diameter of section : D e = 2,5 mm Vacuum curve : C4-12 Checked thickness : e = 18.5 mm Allowable stress : f = MPa C4.2.1 Cylindrical shell with straight circular section L = 2, mm L/D e =.897 D e /e = A (Chart C ) =.1 B ((Chart C4-12 or AE/2 ) = MPa P a =.455 MPa P D e / e 1 : P a = 4 3 B De K e f 1 D e / e < 1 : P a = MIN.833 BK ; 1 De e De e De e Minimum required thickness = 7.76 mm Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

24 External Pressure Elliptical Head (Section No. 5) (in operation) Elements considered : modulus of Vacuum Diameter Thickness Tag elasticity curve Temperature (mm) (mm) (MPa) ( C) Head 2, , C CODAP C4 External Pressure : P =.1 MPa modulus of elasticity : E = 182, MPa Factor : K= 1 Allowable stress : f = MPa Vacuum curve : C4-12 Material : SA24GR316L Thickness as new : e n = 2 mm Corrosion : 1.5 mm Checked thickness : e = 18.5 mm Tolerance : mm External Diameter : D e = 2,5 mm inside crown radius : R i = / Internal Diameter : D i = D e -2e = / Inside radius of knuckle : r c = / outside radius : R e = / Axis ratio : D i /(2h 2 ) = 1.9 C4.2.3 Elliptical heads C 1 =.45[D i /(2h 2 )] =.855 β = ( Graph C3.1.5 or Table C c )=.6325 R e = C 1 D e = 2,137.5 mm 1.2P R 1.2P e s = e y = β(.75r +.2Di ) 1.7 <= D i /(2h 2 ) <= f.5p f.1d e e.8d e e min = MAX(e y ;e s ) = 1.52 mm e. 125 A = =.11 B R e e P a = K =.473 MPa P Re e B (Chart C4-12 or AE/2 ) = MPa Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

25 External Pressure - Summary (in operation) Section No. 1 Component(s) Diameter (mm) Thickness (mm) Length : mm ok (1) 1 [5] 1,5 1 Section No. 2 Component(s) Diameter (mm) Thickness (mm) Length : mm 1 [5] 1,5 1 ok (1) 2 3 [1] [1] 1,5 1,5 1 2 Section No. 3 Component(s) Diameter (mm) Thickness (mm) Length : 1,474.4 mm ok (1) 4 [2] 2 Section No. 4 Component(s) Diameter (mm) Thickness (mm) Length : 2, mm 5 [1] 2,5 2 ok (1) 6 [5] 2,5 2 Section No. 5 Component(s) Diameter (mm) Thickness (mm) Length : mm ok (1) 6 [5] 2,5 2 (1) : # = unchecked element (revise design) = unchecked element, without external pressure (P=) ok = checked element Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

26 Vessel under combination loading - Definitions Model X R A M A R B Beam B Y Beam A M B The vessel is modeled as two cantilever beams. Two periods and two deflections are computed. R A,M A : Reactions at the support of the beam above anchor. R B,M B : Reactions at the support of the beam below anchor. Moments and loads used to compute brackets or anchor Wind load cases Wind loads act in the same direction. Moment M = max ( M A, M B, M A - M B ) Load R = R A + R B Earthquake load cases Seismic loads could act in opposite directions. Moment M = M A + M B Load R = R A + R B Other cases Moment M = M A + M B Load R = R A + R B Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

27 Nomenclature used in the following forms. Stresses and Distortions (a) [(b)] (c) Load combinations : (d) (a) = load case (e.g. Operation (extreme wind) ). (b) = pressure case: [Int.P.] = internal, [Test P.] = test, [Ext.P.] = external, [P = ] = no pressure. (c) = compartment: index 1,2 or 3. (d) = only in the wind and earthquake design cases ( D = dead load, W = wind Load, E = seismic load, E h /E v = effect of horizontal/vertical load seismic forces, "+" means "be combined with" ). Summary of stresses and strains by geometrical component Component Max. deflection Max. rotation (e) (1) (1) (1) (1) (1) (f) / (g) (2) % (e) = type of component. (f) = Component sequence number. (g) = Tag. (1) = Maximum values: see below for details of the calculation of these values (2) = Stress / Acceptance criteria (3) = thickness (corroded or non-corroded, based on the design case under consideration). (4) = minimum required thickness obtained by iteration under design case conditions. Stress calculation (For each geometrical component) Component Elevation E lt / E lc / E c (e) (f) / (g) (8) (5)/(6)/(7) D i cos(α) (9) (1) M F P (11) (12) (13) M max F max σ eqmax σ z Stab. t t min P max P a (14) (15) σ M σ F σ P σ θ (16) (17) (18) (19) (1) (2) % σ z+ σ z σ z+ σ z (1) (3) (4) Stability (5) = weld joint factor applied to longitudinal tensile stress (if required by design code, otherwise equal to 1). (6) = weld joint factor applied to longitudinal compressive stress (if required by design code, otherwise equal to 1). (7) = weld joint factor applied to circumferential stress (if required by design code, otherwise equal to 1). (8) = Location of the calculation point (9) = inside diameter (corroded or uncorroded, based on the design case under consideration). (1) = cosine of the half apex angle for a conical section. (11) = bending moment at the base of the section. (12) = axial load. (13) = pressure (external with a negative sign). (14) = maximum allowable pressure obtained by iteration under design case conditions. (15) = allowable external pressure. (16) = stress due to bending moment : σ M = 32M.D o / [π (D o 4 D i 4 ) cos(α)] ; D o = Outside diameter. (17) = stress due to axial force (ex: weight) : σ F = 4F / [π (D o 2 D i 2 ) cos(α)] ; D o = Outside diameter. (18) = longitudinal stress due to pressure : σ P =P D i 2 / [ (D o 2 D i 2 ) cos(α)] ; D o = Outside diameter. (19) = circumferential stress due to pressure, positive if tensile : σ θ = P D i / [ 2t cos(α)] (2) (21) = meridional stress (longitudinal in a cylindrical shell), positive if tensile : σ z = σ P σ F ± σ M (22) (23) = meridional stress (longitudinal in a cylindrical shell), positive if tensile, without including the stress resulting from external pressure in the stability criterion check when the section is subject to simultaneous longitudinal compression and external pressure : σ z = σ F ± σ M (24) = See acceptance criteria (25) (26) = general primary membrane stress intensity simplified (without an applied torque) determined directly from the stress component as follow : σ eq = max [ ( σ θ / E c σ z / E lt ) ; ( σ θ / E c +.5 P / E c ) ; ( σ z / E lt +.5 P / E c ) ]. (27) = allowable tensile stress. Non-Pressure components: test and exceptional allowable stress at temperature or in accordance with normal condition option. Pressure components: allowable stress, multiplied by a coefficient if required (ASME UG23 or PD 55 A.3.6B or in accordance with wind or earthquake code) (28) = allowable compressive stress : CODAP C stress acceptance criteria under internal pressure (P ) : σ eq S T σ z S T E lt σ z < σ z S C E lc stress acceptance criteria under external pressure (P < ) : σ eq S T σ z S T E lt σ z < σ z S C E lc Limits for compressive stresses are also included to guard against buckling. Application of DIN 188 may restrict the value of allowable compressive stresses. The calculation of membrane stress intensity is based on the maximum shear stress criterion (Guest-Tresca). (2) (21) (22) (23) (24) σ eq+ σ eq (25) (26) S T S C (27) (28) Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

28 Operating Allowable stresses and safety factors Operating CODAP Division 2 GA4 f R m R t m R t p,2 R t p1, σ R σ 1% Nominal stress at design temperature. Minimum guaranteed tensile strength at room temperature. Minimum guaranteed tensile strength at design temperature. Minimum guaranteed yield strength.2 % at design temperature. Minimum guaranteed yield strength 1 % at design temperature. Average stress to cause rupture by creep in 1, hours at design temperature. Average stress to cause 1% elongation by creep in 1, hours hours at design temperature. Excluding bolting Compartment 1 Nominal stress at design temperature f Category B1 Normal Conditions f 1 Exceptional and test conditions Creep Steel (M2, M3 A<3%, M4, M5, M6) MIN ( R t p,2 / 1.5 ; R m / 2.4 ).95 R t p,2 ΜΙΝ{σ R/1.6 ; σ 1%} Stainless steel (M3 A 3%) (R t p1, / 1.5) MIN ( R t p1, / 1.2 ; R t m / 3 ).95 R t p1, ΜΙΝ{σ R/1.6 ; σ 1%} Copper alloy R t m / 4 R t m / 3 ΜΙΝ{σ R/1.6 ; σ 1%} Aluminum Alloy MIN ( R t p,2 / 1.5 ; R m / 2.4 ).95 R t p,2 ΜΙΝ{σ R/1.6 ; σ 1%} Nickel alloy MIN ( R t p,2 / 1.5 ; R m / 2.4 ).95 R t p,2 ΜΙΝ{σ R/1.6 ; σ 1%} Titanium and Zirconium R t m / 3 R t m / 2.2 ΜΙΝ{σ R/1.6 ; σ 1%} Steel (M2,M4,M5,M6) MIN ( R t p,2 / 3 ; R m / 5 ) R t p,2 / 2 ΜΙΝ{σ R/1.6 ; σ 1%} Bolting Stainless steel (M3) R t m / 5 R t m / 3 ΜΙΝ{σ R/1.6 ; σ 1%} Cast materials.79 f Mechanical properties have been calculated on the basis of standard thickness limits. Users should check that thicknesses comply with any usage restrictions given in Part M, based on building classification and division. Pressure / Temperature Operating Type of components Liquid liquid level hydrostatic height Hydrostatic pressure Pressure Temperature Specific Gravity (mm) (mm) (MPa) (MPa) ( C) Compartment 1 Compartment 2 Compartment 3 Design Pressure.9 MPa MPa MPa Design Temperature 18 C C C Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

29 Test Allowable stresses and safety factors Test CODAP Division 2 GA4 f R m R t m R t p,2 R t p1, σ R σ 1% Nominal stress at design temperature. Minimum guaranteed tensile strength at room temperature. Minimum guaranteed tensile strength at design temperature. Minimum guaranteed yield strength.2 % at design temperature. Minimum guaranteed yield strength 1 % at design temperature. Average stress to cause rupture by creep in 1, hours at design temperature. Average stress to cause 1% elongation by creep in 1, hours hours at design temperature. Excluding bolting Compartment 1 Nominal stress at design temperature f Category B1 Normal Conditions f 1 Exceptional and test conditions Creep Steel (M2, M3 A<3%, M4, M5, M6) MIN ( R t p,2 / 1.5 ; R m / 2.4 ).95 R t p,2 ΜΙΝ{σ R/1.6 ; σ 1%} Stainless steel (M3 A 3%) (R t p1, / 1.5) MIN ( R t p1, / 1.2 ; R t m / 3 ).95 R t p1, ΜΙΝ{σ R/1.6 ; σ 1%} Copper alloy R t m / 4 R t m / 3 ΜΙΝ{σ R/1.6 ; σ 1%} Aluminum Alloy MIN ( R t p,2 / 1.5 ; R m / 2.4 ).95 R t p,2 ΜΙΝ{σ R/1.6 ; σ 1%} Nickel alloy MIN ( R t p,2 / 1.5 ; R m / 2.4 ).95 R t p,2 ΜΙΝ{σ R/1.6 ; σ 1%} Titanium and Zirconium R t m / 3 R t m / 2.2 ΜΙΝ{σ R/1.6 ; σ 1%} Steel (M2,M4,M5,M6) MIN ( R t p,2 / 3 ; R m / 5 ) R t p,2 / 2 ΜΙΝ{σ R/1.6 ; σ 1%} Bolting Stainless steel (M3) R t m / 5 R t m / 3 ΜΙΝ{σ R/1.6 ; σ 1%} Cast materials.79 f Mechanical properties have been calculated on the basis of standard thickness limits. Users should check that thicknesses comply with any usage restrictions given in Part M, based on building classification and division. Pressure / Temperature Test Type of components Liquid liquid level hydrostatic height Hydrostatic pressure Pressure Temperature Specific Gravity (mm) (mm) (MPa) , , , ,5. 4, ,. 2, (MPa) ( C) Compartment 1 Compartment 2 Compartment 3 Design Pressure MPa MPa MPa Design Temperature 2 C 2 C 2 C Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

30 Vessel under combination loading - Design case Operation (Corroded inertias) (Corroded Weight) Weight and projected areas Load Weight (dan) Projected area (m 2 ) Load Weight (dan) Projected area (m 2 ) Shell components 5, Nozzle / Brackets / Summary Total weight : 5, dan Total loaded area : 1.51 m 2 Period and Center of Gravity Mode Center of Gravity Period A , mm Period B A : Above anchor B : Below anchor Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

31 Stresses and Distortions - Operation (Corroded inertias) (Corroded Weight) [Int.P.] 1 Load combinations : D Supports [Int.P.] 1 Spring Rate Reactions Displacement Location No. Rotation deflection Vertical Horizontal Moment deflection Rotation (mm) (dan mm/rad) (dan/mm) (dan) (dan) (dan m) (mm) (rad) 1 3,278. / 5,568.9 Graphs of bending moments, stresses and deflections [Int.P.] 1 Bending moments Stresses σ eq,max Deflections 1, mm 1, mm 1, mm 1 dan m 2 MPa 1 mm Maximum moment : dan m A : Above anchor B : Below anchor Maximum stress ( σ eq,max ) : 92.9 MPa Deflections (mm) maximum Allowable A 722 B 3,278 Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

32 Summary of stresses and strains by geometrical component [Int.P.] 1 Max. Max. M Component deflection rotation max F max σ eqmax (dan m) (dan) (MPa) (mm) (rad) Shell / 31.5 (89.9%) Shell / 31.6 (41.3%) Cone ,858 4 / 3.24 (6.89%) Shell 5 / , (68.72%) σ z (MPa) (44.53%) (2.6%) (35.45%) (34.11%) Stab. t (mm) t min (mm) / / / / Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

33 Stresses and Distortions - Operation (Corroded inertias) (Corroded Weight) [Ext.P.] 1 Load combinations : D Supports [Ext.P.] 1 Spring Rate Reactions Displacement Location No. Rotation deflection Vertical Horizontal Moment deflection Rotation (mm) (dan mm/rad) (dan/mm) (dan) (dan) (dan m) (mm) (rad) 1 3,278. / 5,568.9 Graphs of bending moments, stresses and deflections [Ext.P.] 1 Bending moments Stresses σ eq,max Deflections 1, mm 1, mm 1, mm 1 dan m 1 MPa 1 mm Maximum moment : dan m A : Above anchor B : Below anchor Maximum stress ( σ eq,max ) : 1.2 MPa Deflections (mm) maximum Allowable A 722 B 3,278 Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

34 Summary of stresses and strains by geometrical component [Ext.P.] 1 Max. Max. M Component deflection rotation max F max σ eqmax (dan m) (dan) (MPa) (mm) (rad) Shell / 31.5 (9.88%) Shell / 31.6 (4.44%) Cone ,858 4 / 3.24 (6.67%) Shell 5 / , (7.52%) σ z (MPa) 4.34 (4.94%) 1.91 (2.18%) 3.31 (3.77%) 3.46 (3.94%) Stab. t (mm) t min (mm) During test (Corroded inertias) (Corroded Weight) Weight and projected areas Projected Weight Load area (dan) (m 2 ) Load Weight (dan) Projected area (m 2 ) Shell components 5, Nozzle / Brackets / Liquid (Compartment) 17, / Summary Total weight : 22, dan Total loaded area : 1.51 m 2 Period and Center of Gravity Mode Center of Gravity Period A / 2, mm Period B A : Above anchor B : Below anchor Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

35 Stresses and Distortions - During test (Corroded inertias) (Corroded Weight) Load combinations : D Supports Spring Rate Reactions Displacement Location No. Rotation deflection Vertical Horizontal Moment deflection Rotation (mm) (dan mm/rad) (dan/mm) (dan) (dan) (dan m) (mm) (rad) 1 3,278. / 22,748.7 Graphs of bending moments, stresses and deflections Bending moments Stresses σ eq,max Deflections 1, mm 1, mm 1, mm 1 dan m 1 MPa 1 mm Maximum moment : dan m A : Above anchor B : Below anchor Maximum stress ( σ eq,max ) : 2.4 MPa Deflections (mm) maximum Allowable A / B / Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

36 Summary of stresses and strains by geometrical component Component Max. Max. M deflection rotation max F max (dan m) (dan) (mm) (rad) Shell 2 / ,539 Shell 3 / ,891 Cone 4 / ,38 Shell 5 / ,483 σ eqmax (MPa) 2.4 (1.47%) 1.26 (.77%) 1.59 (.97%) 1.42 (.87%) σ z (MPa) 2.4 (1.47%) 1.26 (.77%) 1.59 (.97%) 1.42 (.87%) Stab. t (mm) t min (mm) / / / / Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

37 Vessel under combination loading - Summary Period Critical speed Center of Gravity Max. deflection (s) (m/s) (mm) (mm) A / B A / B A / B Operation (Corroded inertias).5 /.43 / 2, / (Corroded Weight) During test (Corroded inertias) (Corroded Weight).9 /.85 / 2, / (+) with seismic load downside (-) with seismic load downside A :Above anchor B : Below anchor Governing case (stresses and distortions) Element No. Type Diameter Thickness / / / / No calculation of perpendicular wind action is planned, as it corresponds to Karman vortex action. Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

38 Maximum Allowable Working Pressure Maximum Allowable Pressure(Geometry). Type / Mark Diameter Thickness Max. allowable pressure Max. All. Ext. Pressure Hydrostatic pressure Operating Test Operating Test Operating Test (mm) (mm) (MPa) (MPa) (MPa) (MPa) (MPa) (MPa) 1[5] 3.1 1, / [1] , / [1] , / [2] / [1] , / [5] , / Maximum Allowable Pressure (Nozzles). Neck Flange Hydrostatic pressure Tag Operating Test Operating Test Operating Test (MPa) (MPa) (MPa) (MPa) (MPa) (MPa) S H Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

39 Maximum Allowable Working Pressure (Maximum pressure to overload stresses) Operating Vertical test Type / Mark Hydrostatic pressure normal wind Extreme Wind Earthquake Hydrostatic pressure 1st comp. 2nd comp.. 3rd comp. (MPa) (MPa) (MPa (MPa) (MPa) (MPa) (MPa) (MPa) 2[1] / /. / / / 3[1] / /. / / / 4[2] / /. / / / 5[1] / /. / / / Bentley AutoPIPE Vessel (Microprotol) procal V prodia2 V Bentley Systems, Inc.

ASME VIII div.1 verification document

ASME VIII div.1 verification document ASME VIII div. verification document August July, a AutoPIPE Vessel... No changes 5 Mar July, a Microprotol..7.6 Feb Same as Rev 9 including Bentley Inc. 4 Oct 9 July, a Microprotol..7.5 Oct Including