ASME VIII div.1 verification document

Transcription

1 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 conical head (L-6.4) 6 July 8 July, a Microprotol..7. July UG-45 checking (L7-8) June 7 July, a Microprotol..7. May April 6 July, a Microprotol..7. Mar Editing modification 5 Feb 5 July, a Microprotol..6. Jan Code release 7 Feb 4 July, Microprotol... Feb Code release + misc developpements Nov 9 July,9 Microprotol.8.8. Oct 9 Add expansion joint calc. +upd. code 5 Mar 9 July,8 Microprotol.8 April 9 Check + add examples 5 Dec 8 July,8 Microprotol.8 Nov 8 Check + new material data base 5 May 8 July,7 Microprotol.7 April 8 Initial issue Date Rev ASME VIII div. Edit. Software release Comments AutoPIPE Vessel (Microprotol) procal V... prodia V... Bentley Systems, Inc.

2 Table of contents Introduction Appendix L- [Thickness Calculation for shells under internal pressure with supplemental loadings ] 4 L-.. L-.. 4 Appendix L- [Vessels under External Pressure ] 5 L-. 5 L-. 6 L-. without stiffening ring 7 L-. with stiffening rings Appendix L-5 [Design of circumferential stiffening ring and attachment weld for a cylindrical shell under External Pressure] 5 L-5. (using stiffening ring of in. x.75 in.) 6 Appendix L-6 [Required thickness for formed heads with pressure on the convex side] 8 L-6. 9 L-6. [t =.5 in.] L-6. [t =.565 in.] L-6. L-6.4 [t =.75 in.] L-6.4 [t =.56 in.] 4 Appendix L-7 [Openings and reinforcements] 5 L-7. 6 L-7. (without reinforcing plate) 9 L-7. (with reinforcing plate of in. wide x.75 in. thick L-7. (with reinforcing plate of.5 in. wide and.75 in. thick) L L L L-7.7 (nozzle thickness = / in.) 4 L-7.7 (nozzle thickness = 7/8 in.) 45 L UG Part UHX 5 UHX-.. Tubesheet Integral with Shell and Channel 5 UHX-.. Tubesheet gasketed with Shell and Channel 56 UHX-..4 Tubesheet gasketed with Shell and Integral with Channel extended as a flange 6 UHX-.. Tubesheet integral with Shell and gasketed with Channel extended as a flange 6 UHX-.. Fixed Tubesheet Exchanger, Configuration a 7 UHX-.. Stationary Tubesheet Gasketed With Shell and Channel; Floating Tubesheet Gasketed, Not extended as a Flange 78 Other calculations 8 Welding Neck Flange ( Taylor Forge Bulletin) 8 ASME VIII Div. App. 6 Unreinforced Bellows 85 AutoPIPE Vessel (Microprotol) procal V... prodia V... Bentley Systems, Inc.

3 Introduction This document is a part of the AutoPIPE Vessel validation procedure intended to demonstrate the application of the ASME VIII div Code through the examples provided in the various parts of Code. AutoPIPE Vessel input data files used are printed front of the paragraph reference : Appendix L- : Appendix L- : Appendix L-5 : Appendix L-6 : Appendix L-7 : Paragraph L-.. L-.. : Paragraph L-. : Paragraph L-. : Paragraph L-. : Paragraph L-5. : Paragraph L-6. : Paragraph L-6 Paragraph L-6 : Paragraph L-6 4 : Paragraph L-7. : Paragraph L-7 without reinforcing plate: Paragraph L-7 with reinforcing plate : Paragraph L-7.4 : Paragraph L-7.5 : Paragraph L-7.6 : Paragraph L-7.7 : Paragraph L UG-45 : L-..emvd L-.emvd L-.emvd L-. without stiffener.emvd L-.emvd L-5.emvd L-6.emvd L-6.emvd for L-6 [t=.5 in.] L-6.emvd for L-6 [t=.55 in.] L-6.emvd L-6 4.emvd for L-6 4 [t=.75 in.] L-6 4.emvd for L-6 4 [t=.56 in.] L-7.emvd L-7 without reinf.emvd L-7 with reinf.emvd in x.75 in L-7 with reinf incr.emvd.5 in x.75 in L-7 4.emvd L-7 5.emvd L-7 6.emvd L-7 7-.emvd (thk = ½ in.) L-7 7- nozzle thk inc.emvd (thk = 7/8 in.) L-7 8.emvd UHX-. Examples of UHX- for U-Tube Tubesheets : UHX-.. Example : UHX-.. Example : UHX-..4 Example 4 : UHX-. Examples of UHX- for Fixed Tubesheets : UHX-.. Example : UHX-.. Example : UHX-. Examples of UHX-4 for Floating Tubesheets : UHX-.. Example : Other calculations : Taylor Forge calculation method for flange : Unreinforced bellows (Annex 6) : UHX---.emvd UHX---.emvd UHX---4.emvd UHX---.emvd UHX---.emvd UHX---.emvd Flange Welding Neck.emvd emvd AutoPIPE Vessel (Microprotol) procal V... prodia V... Bentley Systems, Inc.

4 Appendix L- [Thickness Calculation for shells under internal pressure with supplemental loadings ] L-.. L-.. Conical shell (.) internal pressure. ASME VIII DIV. - a t = minimum required thickness t n = nominal thickness E = Joint efficiency P = internal pressure S = Allowable stress T = Temperature D = inside diameter at large end Ca = corrosion + tolerance σ = circular stress α = Half apex angle Tol % = tolerance for pipes P a = Max. allowable pressure t min = t+ca+tol % shall be t n t a = (t n Tol % )-Ca shall be t P h = Hydrostatic pressure [UG-(g)] t =P(D+Ca)/[cosα(SE-.6P)] σ =P((D+Ca)+.t a cosα)/(et a cosα) P a =SEt a cosα/((d+ca)+.t a cosα) SA87GRCL Plate Schedule : / DN : / t n =.48 in D = in Tol % = / PWHT : No Radiography : Spot α = Cor. = in Tol. = in UG-6(b) =.65 in P (psi) P h (psi) T ( F) S (psi) E t a (in) σ (psi) P a (psi) t (in) t min (in) Operation N MAWP (65 F, Corroded) = 56. psi MAWP (7 F, new) = 64.4 psi Appendix -5(d) Q L = PR L /+f A rl = kq L R L (- /α) tan α / (S s E ) A el = (t s -t) (R L t s ).5 + (t c -t r ) (R L t c /cos α).5 k = max(, y/s r E r ) y = S s E s Reinforcing ring : Plate 5.5 A ring = 7.5 in P (psi) S s (psi) E t (in) t c (in) t r (in) t s (in) R L (in) Operation N k f (max) (lbf/in) f (min) (lbf/in) Q L(max) (lbf/in) Q L(min) (lbf/in) A rl (in ) A el (in ) Operation N the junction is adequately reinforced Appendix -5(e) Q S = PR S /+f A rs = kq S R S (- /α) / (S s E ) A es =.78 (R S t s ).5 [(t s -t) + (t c -t r ) /cos α)] k = max(, y/s r E r ) y = S s E s Reinforcing ring : Plate 5.5 A ring = 7.5 in P (psi) S s (psi) E t (in) t c (in) t r (in) t s (in) R S (in) Operation N k f (max) (lbf/in) f (min) (lbf/in) Q S(max) (lbf/in) Q S(min) (lbf/in) A rs (in ) A es (in ) Operation N the junction is adequately reinforced [UCS-79] : % extreme fiber elongation = 5 t n / R f ( - R f / R o ) =.44 % ( R f = 5.9 in ; R o = + ) AutoPIPE Vessel (Microprotol) procal V... 4 prodia V... Bentley Systems, Inc.

5 Appendix L- [Vessels under External Pressure ] Comment for reading of external pressure curves ASME curves for external pressure have been checked using stored vertex to redraw the curve on a transparency support visually compared to the Code original. Storage AutoPIPE Vessel file is courbvid.emsd, located in AutoPIPE Vessel\Calcul\Data directory. AutoPIPE Vessel uses logarithmic interpolation to determine the value of B. L-. External Pressure - Shell (Section No. ) (in operation) Ends of section : Bottom : top : Support line level :. in Support line level : 9. in Elements considered : modulus of Vacuum Diameter Thickness Tag elasticity curve Temperature (in) (in) (psi) ( F).5 Virole CS- 7 F ASME VIII DIV. External Pressure : P = 5 psi Design Temperature : 7 F Allowable stress : S = psi modulus of elasticity : E = psi Unsupported shell length : 9 in Pipe, tolerance on the new thickness : c = / Diameter of section : D o = in Vacuum curve : CS- Checked thickness : t =.5 in UG-8 (c) Cylindrical shell with straight circular section L = 9 in L/D o =. D o /t = B D o /t 4 : A (Subpart Section II Part D Fig.G) =.49 D o /t : P a = D t D o /t<4 : A =..67 S min., ( D ) = / D o /t< : P a = min o / t.8 B ; Do t Do t Do t B (Subpart Section II Part D or AE/) = psi P a = 4.96 psi < P INSUFFICIENT THICKNESS Minimum required thickness =. in Comments See Comment for reading of external pressure curves. Rounded value in ASME example of D o /t = 54 is used. o AutoPIPE Vessel (Microprotol) procal V... 5 prodia V... Bentley Systems, Inc.

6 L-. External Pressure - Hemispherical head (Section No.)(in operation) Elements considered : modulus of Vacuum Diameter Thickness Tag elasticity curve Temperature (in) (in) (psi) ( F) NFA- F ASME VIII DIV. a UG- External Pressure : P = psi modulus of elasticity : E = psi Material : SB9-A9-H Corrosion : in Vacuum curve : NFA- Tolerance : in Nominal thickness : t n =.5 in External Diameter : D o = 7 in Checked thickness : t =.5 in outside radius : R o = 6.5 in outside height : h o = / Axis ratio : D o /(h o ) = / (c) Hemispherical heads. 5 UG-8 (d) : A = =.7 R o t B (Subpart Section II Part D or.65e/(r o /t)) = psi P a = B = 4.6 psi P R t o Comments See Comment for reading of external pressure curves. AutoPIPE Vessel (Microprotol) procal V... 6 prodia V... Bentley Systems, Inc.

7 L-. without stiffening ring External Pressure Cone (Section N )(in operation) Ends of section : Bottom : Cone-to-cylinder junction without stiffening ring Support line level : 5. in top : Cone-to-cylinder junction without stiffening ring Support line level : 8. in Elements considered : modulus of Vacuum Diameter Thickness Tag elasticity curve Temperature (in) (in) (psi) ( F) 5. Cône de calandre CS- 65 F ASME VIII DIV. a External Pressure : P = 5 psi Design Temperature : 65 F Allowable stress : S = 5 psi modulus of elasticity : E = 5 5 psi Unsupported shell length : in half opening angle of conical shell : α = 9.98 Checked thickness : t =.5 in Vacuum curve : CS- Element diameter at large end : D L =.5 in Element diameter at small end : D s = 5.75 in UG-(f) Conical shell with straight circular section L = in Fig. UG-. L e = 8.9 in L e /D L =.4 t e = t cos(α) =.8 in D L /t e = B D L /t e : A (Subpart Section II Part D Fig.G) =.447 D L /t e : P a = D L t e D L /t e < : A =..67 S min., ( D ) = / D L /t e < : P a = MIN o / t.8 B ; DL te DL te DL t B (Subpart Section II Part D or AE/) = psi P a = 67.6 psi P e AutoPIPE Vessel (Microprotol) procal V... 7 prodia V... Bentley Systems, Inc.

8 External Pressure Large cylinder-to-cone junction (Section No. ) (in operation) ASME VIII DIV. - a APPENDIX -8 Junction without knuckle, without stiffener Internal corroded radius of knuckle : r t = in Angle : α = 9.98 Shell adjacent to the junction, element No. : 4 Calculation length of cylinders element : L L = 5 in Cone adjacent to junction, element number : 5 Calculation length of cones element : L= in External Pressure : P = 5 psi Cylindrical shell Material : SA56GR7 Temperature : 65 F Nominal stress : S s = 7 5 psi modulus of elasticity : E s = 5 5 ksi Vacuum curve : CS- Longitudinal Joint Efficiency : E =.85 Nominal thickness : t sn =.5 in Corrosion : in Checked thickness : t s =.5 in Tolerance : in External Diameter : D L =.5 in External radius : R L =.5 in Conical shell Material : SA56GR6 Temperature : 65 F Nominal stress : S c = 5 psi modulus of elasticity : E c = 5 5 ksi Vacuum curve : CS- Nominal thickness : t cn =.5 in Corrosion : in Checked thickness : t c =.5 in Tolerance : in Stiffener Type and dimensions : / Material : / Nominal stress : S r = / Temperature : / Vacuum curve : / modulus of elasticity : E r = / Cross-sectional area : A s = / Diameter of shell at centroid elevation : D e = / Checking junction s area P/S s E =.4 = 5.9 < α Reinforcement of large end intersection k = f = 49.9 lbf/in Q L = PR L / + f = 78.5 lbf/in kq LRL tan α PRL QL A rl = =.48 in SsE 4 A QL α el =.55 D Lts ( ts + tc cosα) =.566 in A el + A s =.566 in A rl Checking the junction s moment of inertia RL tan α LL RL Rs M = + + = 5.69 in f R tan α = 49.9 lbf/in F L = PM + f tan α = lbf/in L c = L ( RL + Rs ) L LLts Lctc + = 5.5 in A TL = + + As = 5.7 in B = A (Subpart Section II Part D FIG.G) =.68 I ' = 64.9 in 4 < I s ' 4 FL D A TL L = psi I s = AD A L TL = / I s = AD A L TL = in AutoPIPE Vessel (Microprotol) procal V... 8 prodia V... Bentley Systems, Inc.

9 Comments Angle of cone : α = arc tg[((-5)/) /] = ( in ASME example) tg a = [(-5)/) /] =.5769(value of ASME based on angle of ) P/S s E = 5/(75x.85) =.6 According to Table -8., P/S s E =. = 5 P/S s E =.5 = 7 For P/S s E =.6, = 5 + (7-5) x [(.6-.)/(.5-.)] = (ASME Example value is 5.9 ). No additional area of reinforcement k = f obtains by load due to wind and external load. No detail in ASME example. Q L = 5x.5/ = lbf/in x78.54x.5x x A rl = =.4798 in 4 75x A el =.55.5x.5(.5.5 cos( )) + =.5685 in A rl Junction area checked.5x M = + + = in x.5x.5769 F L =5 x x.5769 = lbf/in = in Lc = ( ) ( ) 5x x.5 A TL = + = in (rounded value in ASME example) x.5 B = x = A from Fig CS- =.68 (see Comment for reading of external pressure curves )..68x.5 x5.655 As there is no stiffener : I s = = in 4.9 Inertia of shell : Length to be considered : L = (./) x (.5x.5) = 8.75 in I sh = (8.75 x.5 ) / =.44 in 4 Inertia of cone : Length to be considered on shell : L = (./) x (.5x.5) = 8.75 in Length to be considered on cone: H = L/ cos(α) = 8.75 /cos(9.98) =. in I co = (H tc cos(α) )/+(H tc sin(α) )/ = 8.7 in 4 Position of centers of inertia from external line of shell : Shell = ts / =.65 in Cone = (tc/) +(H sin(a)/ + (tc/)(-cos(α)) =.655 in Section of shell and cone = (.5x8.75) + (.5x.) =.565 in Position of center of inertia of the combined section = [(.65x.5x8.75) + (.655x.5x.)] /.565 =.96 in Inertia of combined section : I = ( ) x(.5x8.75) + ( ) x(.5x.)= 64.4 in 4 Is > I large cylinder to cone junction not verified AutoPIPE Vessel (Microprotol) procal V... 9 prodia V... Bentley Systems, Inc.

10 External Pressure Small cylinder-to-cone junction (Section No. ) (in operation) ASME VIII DIV. - a APPENDIX -8 Junction without knuckle, without stiffener Internal corroded radius of knuckle : r t = in Angle : α = 9.98 Shell adjacent to the junction, element No. : 6 Calculation length of cylinders element : L s = 75 in Cone adjacent to junction, element number : 5 Calculation length of cones element : L= in External Pressure : P = 5 psi Cylindrical shell Material : SA56GR7 Temperature : 65 F Nominal stress : S s = 7 5 psi modulus of elasticity : E s = 5 5 psi Vacuum curve : CS- Longitudinal Joint Efficiency : E = Nominal thickness : t sn =.75 in Corrosion : in Checked thickness : t s =.75 in Tolerance : in External Diameter : D s = 5.75 in External radius : R s = 5.75 in Conical shell Material : SA56GR6 Temperature : 65 F Nominal stress : S c = 5 psi modulus of elasticity : E c = 5 5 psi Vacuum curve : CS- Nominal thickness : t cn =.5 in Corrosion : in Checked thickness : t c =.5 in Tolerance : in Stiffener Type and dimensions : / Material : / Nominal stress : S r = / Temperature : / Vacuum curve : / modulus of elasticity : E r = / Cross-sectional area : A s = / Diameter of shell at centroid elevation : D e = / Checking junction s area k = f = 6.58 lbf/in Q s = PR s / + f = lbf/in kqsrs tan α A rs = =.58 in A SsE es =.55 D sts (( ts t) + ( tc tr ) cosα) =.765 in Required thicknesses of portions at junction : Shell : t =.5 in Cone : t r =.7 in A es + A s =.765 in A rs Checking the junction s moment of inertia Rs tan α Ls RL Rs N = + + = 54. in f 6R tan α = 6.58 lbf/in F s = PN + f tan α = lbf/in L c = L ( RL + Rs ) s Lsts Lctc + = 5.5 in A Ts = + + As = 8.9 in B = A (Subpart Section II Part D FIG.G) =.9 I ' =.7 in 4 < I s ' 4 Fs Ds = psi A Ts I s = AD A s Ts = / I s = AD A s Ts = 5.6 in AutoPIPE Vessel (Microprotol) procal V... prodia V... Bentley Systems, Inc.

11 Comments No additional area of reinforcement k = f obtains by load due to wind and external load. No detail in ASME example. Q s = 5x5.75/ = lbf/in x696.46x5.75x.5769 A rs = =.586 in 75x 5.75x N = + + = 54. in 6x5.75x.5769 F S =5 x x.5769 = lbf/in f obtains by load due to wind and external load. No detail in ASME example. 75x x.5 A TS = + = 8.9 in (rounded value in ASME example) x5.75 B = x = A from Fig CS- =.9 (see Comment for reading of external pressure curves )..9x5.75 x8.9 As there is no stiffener : I s = =5.54 in 4.9 Inertia of combined section : I =.7 in 4 Is > I large cylinder to cone junction not verified AutoPIPE Vessel (Microprotol) procal V... prodia V... Bentley Systems, Inc.

12 L-. with stiffening rings External Pressure Conical shell (Section No. ) (in operation) Ends of section : Bottom : top : Cone-to-cylinder junction with stiffening ring No. ) Cone-to-cylinder junction with stiffening ring No. ) Support line level : 5. in Support line level : 8. in Elements considered : modulus of Vacuum Diameter Thickness Tag elasticity curve Temperature (in) (in) (psi) ( F) 5. Cône de calandre CS- 65 F ASME VIII DIV. - a External Pressure : P = 5 psi Design Temperature : 65 F Allowable stress : S = 5 psi modulus of elasticity : E = 5 5 psi Unsupported shell length : in half opening angle of conical shell : α = 9.98 Checked thickness : t =.5 in Vacuum curve : CS- Element diameter at large end : D L =.5 in Element diameter at small end : D s = 5.75 in UG-(f) Conical shell with straight circular section L = in Fig. UG-. L e = 8.9 in L e /D L =.4 t e = t cos(α) =.8 in D L /t e = B D L /t e : A (Subpart Section II Part D Fig.G) =.447 D L /t e : P a = D. D L /t e < : A =.67 S min., ( D / ) = / D L /t e < : P a = MIN o t.8 B ; DL te DL te DL t B (Subpart Section II Part D or AE/) = psi P a = 67.6 psi P L t e e AutoPIPE Vessel (Microprotol) procal V... prodia V... Bentley Systems, Inc.

13 External Pressure Large cylinder-to-cone junction (Section No. ) (in operation) ASME VIII DIV. - a APPENDIX -8 Junction without knuckle, reinforced by stiffener No. Internal corroded radius of knuckle : r t = in Angle : α = 9.98 Shell adjacent to the junction, element No. : 4 Calculation length of cylinders element : L L = 5 in Cone adjacent to junction, element number : 5 Calculation length of cones element : L= in External Pressure : P = 5 psi Cylindrical shell Material : SA56GR7 Temperature : 65 F Nominal stress : S s = 7 5 psi modulus of elasticity : E s = 5 5 ksi Vacuum curve : CS- Longitudinal Joint Efficiency : E =.85 Nominal thickness : t sn =.5 in Corrosion : in Checked thickness : t s =.5 in Tolerance : in External Diameter : D L =.5 in External radius : R L =.5 in Conical shell Material : SA56GR6 Temperature : 65 F Nominal stress : S c = 5 psi modulus of elasticity : E c = 5 5 ksi Vacuum curve : CS- Nominal thickness : t cn =.5 in Corrosion : in Checked thickness : t c =.5 in Tolerance : in Stiffener Type and dimensions : WT8x Material : SA56GR6 Nominal stress : S r = 4 5 psi Temperature : 65 F Vacuum curve : CS- modulus of elasticity : E r = 5 5 psi Cross-sectional area : A s = 5.8 in Diameter of shell at centroid elevation : D e = in Checking junction s area P/S s E =.4 = 5.9 < α Reinforcement of large end intersection k =.69 f = 5. lbf/in Q L = PR L / + f = 78.5 lbf/in kq LRL tan α PRL QL A rl = =.649 in SsE 4 A el =.55 D Lts ( ts + tc cosα) =.566 in QL α A el + A s = in A rl Checking the junction s moment of inertia RL tan α LL RL Rs M = + + = 5.69 in f R tan α = 5. lbf/in F L = PM + f tan α = lbf/in L c = L ( RL + Rs ) L LLts Lctc + = 5.5 in A TL = + + As = in B = A (Subpart Section II Part D FIG.G) =.6 I ' = in 4 I s ' Comments Same calculation as calculation without stiffener except for : k = y/sr Er = 75x55/45x55 =.6895 As = area of stiffener f = 5. lbf/in 4 FL D A TL L = psi I s = AD A L TL = / I s = AD A L TL = 46.7 in AutoPIPE Vessel (Microprotol) procal V... prodia V... Bentley Systems, Inc.

14 External Pressure Small cylinder-to-cone junction (Section No. ) (in operation) ASME VIII DIV. - a APPENDIX -8 Junction without knuckle, reinforced by stiffener No. Internal corroded radius of knuckle : r t = in Angle : α = 9.98 Shell adjacent to the junction, element No. : 6 Calculation length of cylinders element : L s = 75 in Cone adjacent to junction, element number : 5 Calculation length of cones element : L= in External Pressure : P = 5 psi Cylindrical shell Material : SA56GR7 Temperature : 65 F Nominal stress : S s = 7 5 psi modulus of elasticity : E s = 5 5 psi Vacuum curve : CS- Longitudinal Joint Efficiency : E = Nominal thickness : t sn =.75 in Corrosion : in Checked thickness : t s =.75 in Tolerance : in External Diameter : D s = 5.75 in External radius : R s = 5.75 in Conical shell Material : SA56GR6 Temperature : 65 F Nominal stress : S c = 5 psi modulus of elasticity : E c = 5 5 psi Vacuum curve : CS- Nominal thickness : t cn =.5 in Corrosion : in Checked thickness : t c =.5 in Tolerance : in Stiffener Type and dimensions : Bar.5.75 Material : SA56GR6 Nominal stress : S r = 4 5 psi Temperature : 65 F Vacuum curve : CS- modulus of elasticity : E r = 5 5 psi Cross-sectional area : A s =. in Diameter of shell at centroid elevation : D e = in Checking junction s area k =.69 f = 6.5 lbf/in Q s = PR s / + f = lbf/in kqsrs tan α A rs = =.74 in A SsE es =.55 D sts (( ts t) + ( tc tr ) cosα) =.765 in Required thicknesses of portions at junction : Shell : t =.5 in Cone : t r =.7 in A es + A s =.78 in A rs Checking the junction s moment of inertia Rs tan α Ls RL Rs N = + + = 54. in f 6R tan α = 6.5 lbf/in F s = PN + f tan α = lbf/in L c = L ( RL + Rs ) s Lsts Lctc + = 5.5 in A Ts = + + As = 9.45 in B = A (Subpart Section II Part D FIG.G) =.6 I ' = 4.64 in 4 < I s ' Comments Same calculation as calculation without stiffener except for : k = y/sr Er = 75x55/45x55 =.6895 As = area of stiffener f = 6.5 lbf/in 4 Fs Ds = psi A Ts I s = AD A s Ts = / I s = AD A s Ts = 5.6 in AutoPIPE Vessel (Microprotol) procal V... 4 prodia V... Bentley Systems, Inc.

15 Appendix L-5 [Design of circumferential stiffening ring and attachment weld for a cylindrical shell under External Pressure] Comment for reading of external pressure curves ASME curves for external pressure have been checked using stored vertex to redraw the curve on a transparency support visually compared to the Code original. Storage AutoPIPE Vessel file is courbvid.emsd, located in AutoPIPE Vessel \Calcul\Data directory. AutoPIPE Vessel uses logarithmic interpolation to determine the value of B. AutoPIPE Vessel (Microprotol) procal V... 5 prodia V... Bentley Systems, Inc.

16 L-5. (using stiffening ring of in. x.75 in.) Ends of section : Bottom : Support line level :. in top : Stiffening ring (ring No. ) Support line level : 4. in Elements considered : modulus of Vacuum Diameter Thickness Tag elasticity curve Temperature (in) (in) (psi) ( F).5 Virole CS- 7 F ASME VIII DIV. External Pressure : P = 5 psi Design Temperature : 7 F Allowable stress : S = 4 psi modulus of elasticity : E = psi Unsupported shell length : 4 in Pipe, tolerance on the new thickness : c = / Diameter of section : D o = 69 in Vacuum curve : CS- Checked thickness : t =.5 in UG-8 (c) Cylindrical shell with straight circular section L = 4 in L/D o =.7 D o /t = B D o /t 4 : A (Subpart Section II Part D Fig.G) =.478 D o /t : P a = D t. D o /t<4 : A =.67 S min., ( D / ) = / D o /t< : P a = min o t.8 B ; Do t Do t Do t B (Subpart Section II Part D or AE/) = psi P a = psi < P INSUFFICIENT THICKNESS Minimum required thickness =.7 in Ends of section : Bottom : Stiffening ring (ring No. ) Support line level : 4. in top : Support line level : 8. in Elements considered : modulus of Vacuum Diameter Thickness Tag elasticity curve Temperature (in) (in) (psi) ( F).5 Virole CS- 7 F ASME VIII DIV. External Pressure : P = 5 psi Design Temperature : 7 F Allowable stress : S = 4 psi modulus of elasticity : E = psi Unsupported shell length : 4 in Pipe, tolerance on the new thickness : c = / Diameter of section : D o = 69 in Vacuum curve : CS- Checked thickness : t =.5 in UG-8 (c) Cylindrical shell with straight circular section L = 4 in L/D o =.7 D o /t = B D o /t 4 : A (Subpart Section II Part D Fig.G) =.478 D o /t : P a = D t. D o /t<4 : A =.67 S min., ( D / ) = / D o /t< : P a = min o t.8 B ; Do t Do t Do t B (Subpart Section II Part D or AE/) = psi P a = psi < P INSUFFICIENT THICKNESS Minimum required thickness =.7 in o o AutoPIPE Vessel (Microprotol) procal V... 6 prodia V... Bentley Systems, Inc.

17 ASME VIII DIV. a Shell External Pressure : P = 5 psi Temperature : 7 F Material : SA85GRC modulus of elasticity : E = psi Vacuum curve : CS- Corrosion : in Nominal thickness : t n =. in Tolerance : in Checked thickness : t =. in Calculation length of previous element : L = 4 in Calculation length of next element : L = 4 in Stiffener Type and dimensions : Plate.75 modulus of elasticity : E = psi Cross-sectional area : A s = 7.5 in Material : SA6 Vacuum curve : CS- Diameter of shell at centroid elevation : D o = 69 in UG-9 Stiffened elements of cylindrical shells x = MIN{ (.55 Do t s ); ( L ) } =.997 in t =. in x = MIN{ (.55 o t ); ( L ) } B = 4 P Do = 8.5 psi L s = t + As / Ls A (Subpart Section II Part D FIG.G or B/E) =. I = 6.54 in 4 I s D s =.997 in t =. in L + L = 4 in t eq =. in ( ) D o Ls t + As / Ls A I s = = D o Ls t + As 4 I s = 6. in 4.9 ( L ) / s A = / Comments ASME example checks only stiffening ring. The thickness of shell is not sufficient (no information about this in ASME example). Index for x,t and L is used for shell before the stiffener and index for x,t and L is used for shell after the stiffener. t and t should be read.5 in, t eq is the average thickness calculated as follow : t eq = (L e +L e )/(L +L ) AutoPIPE Vessel (Microprotol) procal V... 7 prodia V... Bentley Systems, Inc.

18 Appendix L-6 [Required thickness for formed heads with pressure on the convex side] Comment for reading of external pressure curves ASME curves for external pressure have been checked using stored vertex to redraw the curve on a transparency support visually compared to the Code original. Storage AutoPIPE Vessel file is courbvid.emsd, located in AutoPIPE Vessel \Calcul\Data directory. AutoPIPE Vessel uses logarithmic interpolation to determine the value of B. AutoPIPE Vessel (Microprotol) procal V... 8 prodia V... Bentley Systems, Inc.

19 L-6. External pressure Elliptical Head (Section No.)(in operation) Elements considered : modulus of Vacuum Diameter Thickness Tag elasticity curve Temperature (in) (in) (psi) ( F) CS- 7 F ASME VIII DIV. a UG- External Pressure : P = 5 psi modulus of elasticity : E = psi Material : SA85GRC Corrosion : in Vacuum curve : CS- Tolerance : in Nominal thickness : t n =.56 in External Diameter : D o = 69 in Checked thickness : t =.56 in outside radius : R o = / outside height : h o = 4.5 in Axis ratio : D o /(h o ) = (d) Elliptical heads K o (Table UG-.) =.894 Equivalent outside radius R o = K o.d o = 5.94 in (a)()(a) : E = P a(a) =.67 P = 57.7 psi. 5 B UG-8 (d) : A = =.465 P a(d) = =.4 psi R o t R t B (Subpart Section II Part D or.65e/(r o /t)) = psi o (a)()(b) P a = MIN (P a(a), P a(d) ) =.4 psi P Comments AutoPIPE Vessel checks UG-(a) () (a) In ASME example value of K from Table UG-7 is used and this is not correct. AutoPIPE Vessel uses Table UG-. (UG- FORMED HEADS, PRESSURE ON CONVEX SIDE) to determine K. That gives a different value of R O See Comment for reading of external pressure curves. AutoPIPE Vessel (Microprotol) procal V... 9 prodia V... Bentley Systems, Inc.

20 L-6. [t =.5 in.] External pressure Torispherical Head (Section No.)(in operation) Elements considered : modulus of Vacuum Diameter Thickness Tag elasticity curve Temperature (in) (in) (psi) ( F). Fond CS- 7 F ASME VIII DIV. a UG- External Pressure : P = 5 psi modulus of elasticity : E = psi Material : SA85GRC Corrosion : in Vacuum curve : CS- Tolerance : in Nominal thickness : t n =.5 in External Diameter : D o = 69 in Checked thickness : t =.5 in outside radius : R o = 69 in outside height : h o = / Axis ratio : D o /(h o ) = / (e) Torispherical heads (a)()(a) : E = P a(a) =.67 P = 8.68 psi. 5 UG-8 (d) : A = =.7 P a(e) = R o t B (Subpart Section II Part D or.65e/(r o /t)) = psi B R o =.59 psi t (a)()(b) : P a = MIN (P a(a), P a(e) ) =.59 psi < P INSUFFICIENT THICKNESS Comments AutoPIPE Vessel checks UG-(a) () (a) See Comment for reading of external pressure curves. AutoPIPE Vessel (Microprotol) procal V... prodia V... Bentley Systems, Inc.

21 L-6. [t =.565 in.] External Pressure Torispherical Head (Section No.)(in operation) Elements considered : modulus of Vacuum Diameter Thickness Tag elasticity curve Temperature (in) (in) (psi) ( F) CS- 7 F ASME VIII DIV. a UG- External Pressure : P = 5 psi modulus of elasticity : E = psi Material : SA85GRC Corrosion : in Vacuum curve : CS- Tolerance : in Nominal thickness : t n =.56 in External Diameter : D o = 69.5 in Checked thickness : t =.56 in outside radius : R o = 69.6 in outside height : h o = / Axis ratio : D o /(h o ) = / (e) Torispherical heads (a)()(a) : E = P a(a) =.67 P =.6 psi. 5 UG-8 (d) : A = =.46 P a(e) = R o t B (Subpart Section II Part D or.65e/(r o /t)) = psi B R o = 7. psi t (a)()(b) : P a = MIN (P a(a), P a(e) ) = 7. psi P Comments AutoPIPE Vessel checks UG-(a) () (a) t n and t should be read.565 See Comment for reading of external pressure curves. AutoPIPE Vessel (Microprotol) procal V... prodia V... Bentley Systems, Inc.

22 L-6. External Pressure Hemispherical head (Section No.)(in operation) Elements considered : modulus of Vacuum Diameter Thickness Tag elasticity curve Temperature (in) (in) (psi) ( F) CS- 7 F ASME VIII DIV. a UG- External Pressure : P = 5 psi modulus of elasticity : E = psi Material : SA85GRC Corrosion : in Vacuum curve : CS- Tolerance : in Nominal thickness : t n =. in External Diameter : D o = 69 in Checked thickness : t =. in outside radius : R o = 84.5 in outside height : h o = / Axis ratio : D o /(h o ) = / (c) Hemispherical heads. 5 UG-8 (d) : A = =.46 R o t B (Subpart Section II Part D or.65e/(r o /t)) = psi P a = B =.57 psi P R t o Comments t n and t should be read.5 See Comment for reading of external pressure curves. AutoPIPE Vessel (Microprotol) procal V... prodia V... Bentley Systems, Inc.

23 L-6.4 [t =.75 in.] External Pressure Conical Head (Section No. )(in operation) Ends of section : Bottom : Cone-to-cylinder junction without stiffening ring Support line level : 5. in top : Support line level : in Elements considered : modulus of Vacuum Diameter Thickness Tag elasticity curve Temperature (in) (in) (psi) ( F). Cône CS- 7 F ASME VIII DIV. a External Pressure : P = 5 psi Design Temperature : 7 F Allowable stress : S = psi modulus of elasticity : E = psi Unsupported shell length : 4.65 in half opening angle of conical shell : α =.5 Checked thickness : t =.75 in Vacuum curve : CS- Element diameter at large end : D L = 69.5 in Element diameter at small end : D s = in UG-(f) Conical shell with straight circular section L = 4.64 in Fig. UG-. L e =. in L e /D L =.64 t e = t cos(α) =.69 in D L /t e = B D L /t e : A (Subpart Section II Part D Fig.G) =.65 D L /t e : P a = D L t e D L /t e < : A =..67 S min., ( D ) = / D L /t e < : P a = MIN o / t.8 B ; DL te DL te DL t B (Subpart Section II Part D or AE/) = psi P a = 8.9 psi P e Comments See Comment for reading of external pressure curves. The cone to cylinder junction at large end is ignored like in ASME example. AutoPIPE Vessel (Microprotol) procal V... prodia V... Bentley Systems, Inc.

24 L-6.4 [t =.56 in.] External Pressure Conical Head (Section No. ) (in operation) Ends of section : Bottom : Cone-to-cylinder junction without stiffening ring Support line level : 5. in top : Support line level : 9.5 in Elements considered : modulus of Vacuum Diameter Thickness Tag elasticity curve Temperature (in) (in) (psi) ( F). Cône CS- 7 F ASME VIII DIV. a External Pressure : P = 5 psi Design Temperature : 7 F Allowable stress : S = psi modulus of elasticity : E = psi Unsupported shell length : 4.5 in half opening angle of conical shell : α =.5 Checked thickness : t =.56 in Vacuum curve : CS- Element diameter at large end : D L = 69.6 in Element diameter at small end : D s = in UG-(f) Conical shell with straight circular section L = 4.5 in Fig. UG-. L e =.77 in L e /D L =.64 t e = t cos(α) =.5 in D L /t e = B D L /t e : A (Subpart Section II Part D Fig.G) =.78 D L /t e : P a = D L t e D L /t e < : A =..67 S min., ( D ) = / D L /t e < : P a = MIN o / t.8 B ; DL te DL te DL t B (Subpart Section II Part D or AE/) = psi P a = 9.4 psi P e Comments See Comment for reading of external pressure curves. The cone to cylinder junction at large end is ignored like in ASME example. ASME example uses rounded values. Le =L/ = 4.5/ =.765 in; Le / D L =.765/69.6 =.655 ; te = t cos(α) =.56x.988 =.5 in D L / te = 69.6/.5 = 5.5 A =.78 ; B = psi Pa = 4/ [B/(D L /te)] = 4/ x [469.67/5.5) = 9.4 psi P AutoPIPE Vessel (Microprotol) procal V... 4 prodia V... Bentley Systems, Inc.

25 Appendix L-7 [Openings and reinforcements] AutoPIPE Vessel (Microprotol) procal V... 5 prodia V... Bentley Systems, Inc.

26 L-7. Isolated Opening(s) Figures for all configurations from FIG. UG-7. And FIG UG-4. Shell ( α = ) or Cone ( α > ) : in longitudinal plane. Nozzle with or without pad, set-in or set-on Selfreinforcing nozzle, set-in or set-on t n t rn t x t n δ < 9 L β δ >9 Projection L<.5t x t e β t n γ L.5t x t e= Self height Projection L h t p t x d t e d R t R t t r Cylndrical or conical shell : circumferential plane Head : in the plane that contains the axis of the nozzle and the longitudinal axis of vessel. Nozzle with or without pad, set-in or set-on Selfreinforcing nozzle, set-in or set-on t n t rn t x t n t δ < 9 L β δ >9 t r Projection t L<.5t x t e β t n γ L.5t x t e= Self height Projection R h t e R h L α d t p α d t x AutoPIPE Vessel (Microprotol) procal V... 6 prodia V... Bentley Systems, Inc.

27 Opening [ in operation Int.P. ] (Process) ASME VIII DIV. Nozzle without pad on Shell (No. ) Set In Pressure : P = 5 psi Temperature : 5 F Shell Material :SA56GR55 Allowable stress : S v = 7 psi Joint efficiency : E = Corrosion + tolerance : Ca v = in Allowable stress : S = 7 psi Ext. Diameter : D o =.75 in Nominal thickness :.75 in Tolerance for seamless pipe : / Nozzle Neck Material : SA56GR55 Allowable stress : S n = 5 psi Joint efficiency : Corrosion + tolerance : Ca n = in Tolerance for seamless pipe : / Ext. Diameter : D on = 5.5 in Nominal thickness :.75 in External Projection : in Internal Projection : in Schedule : Inclination : Eccentricity : in Flange Material : / Type : / Rating : / Height : / / Pad Material : / Allowable stress : S p = / Height : / Width : / Ext. Diameter : D op = / Weld Outside : leg 4 =.75 in outer reinforcement : leg 4 = / Inside : leg 4 = / fr =min(,s n /S v ) = fr = min(,s n /S v ) = fr = min(,min(s n, S p )/S v ) = fr 4 = min(,s p /S v ) = Required thickness of the nozzle neck UG-7 t rn = P R n / (S n E-.6P) =.7 in R n = in E = The nozzle neck thickness is adequate per UG-7. Required thickness of the nozzle neck UG-45 t a = t rn +Ca n =.4 in ; t b = max[t UG-7, UG-6(b)]+Ca v =.77 in ; t b = Table UG-45+Ca n =.6 in t UG-45 = max [t a, min [t b, t b ] ] =.6 in The nozzle neck thickness is adequate per UG-45. Dimensions FIG. UG-4 angle of plane with longitudinal axis : Longitudinal plane : θ = Circumferential plane : θ = 9 angle of each side / vessel wall : δ = 9 δ = 9 δ = / δ = / β = deflection angle / normal line d = diameter of the finished opening 4 in R n = radius of the finished opening in t i = thickness of internal projection / t p = width of reinforcing pad / t x = thickness of selfreinforcing / L = height of selfreinforcing / / Configuration of the reinforcement : / / t e = thickness or height of the reinforcement in in t n = thickness of nozzle.75 in.75 in h = height of the internal projection in in Reinforcement checking UG-7 opening [ in operation Int.P. ] Required thicknesses UG-7(a) t r =.768 in [ UG-7(c) ] t =.75 in E = t rn = P R n / (S n E-.6P) =.7 in R n = in E = Longitudinal plane : θ = Circumferential plane : θ = 9 Limits of reinforcement UG-4 : δ = 9 δ = 9 δ = / δ = / UG-4 (b) : max [d, R n +t n +t ] = 4 in 4 in UG-4 (c) : min [.5t,.5t n +t e ] =.98 in.98 in Area required UG-7 (c) : Longitudinal plane : θ = Circumferential plane : θ = 9 F = Correction factor FIG.UG-7 A = d t r F + t n /cos(β) t r F (-f r ).7 in AutoPIPE Vessel (Microprotol) procal V... 7 prodia V... Bentley Systems, Inc.

28 Longitudinal plane : θ = Circumferential plane : θ = 9 Lengths and heights of calculation of the areas : δ = 9 δ = 9 δ = / δ = / L = min [ UG-4(b)-Radius, length available ] in in L = min [ UG-4(c), height available ].98 in.98 in L = min [ h,.5t,.5t i ] = in in L 5 = min [ UG-4 (b)-r on, t p, length available] in in Area available (in Longitudinal plane : θ = Circumferential plane : θ = 9 ) : δ = 9 δ = 9 δ = / δ = / A = L (E t-t r F) - t n /cos(β) (E t-t r F) (-f r ) A = L (t n -t rn ) fr A = L t i f r A 4 = leg 4 / f r.7.7 A 4 = leg 4 / f r4 A 4 = leg 4 / f r A 5 = L 5 t e f r4 A + A + A + A 4 + A 4 + A 4 + A 5 =.98 A/.98 A/.877 A The opening is adequately reinforced per UG-7. Weld sizes check UW-6(c). opening [ in operation Int.P. ] t n =.75 leg4 t c,outward Fig. UW-6.(d) full penetration weld Minimum throat required actual min[¼ in.(6 mm);.7 t t min ]=.5 in c,outward t min = min[ ¾ in.(9 mm) ; t, t n ].7 leg 4 =.65 in min[¼ in.(6 mm);.7 t t min ]= / t =.75 tc,inward c,inward t min = min[ ¾ in.(9 mm) ; t, t n ] leg4 Weld sizes are adequate.7 leg 4 Ca n = / Weld loads check UG-4(b). Strength calculations for attachments welds are not required for this opening in accordance with UW-5(b). AutoPIPE Vessel (Microprotol) procal V... 8 prodia V... Bentley Systems, Inc.

29 L-7. (without reinforcing plate) Opening [ in operation Int.P. ] ASME VIII DIV. Nozzle without pad on Shell (No. ) Set In Pressure : P = 5 psi Temperature : 7 F Shell Material :SA56GR55 Allowable stress : S v = 4 psi Joint efficiency : E = Corrosion + tolerance : Ca v = in Allowable stress : S = 4 psi Ext. Diameter : D o = 6,5 in Nominal thickness :,75 in Tolerance for seamless pipe : / Nozzle Material : SA56GR55 Allowable stress : S n = 6 6 psi Joint efficiency : Corrosion + tolerance : Ca n = in Tolerance for seamless pipe : / Ext. Diameter : D on =,75 in Nominal thickness :,5 in External Projection : in Internal Projection : in Schedule : Inclination : Eccentricity : in Flange Material : SA5 Type : WN Rating : (ASME B6.5) Height : 5, in NPS " Pad Material : / Allowable stress : S p = / Height : / Width : / Ext. Diameter : D op = / Weld Outside : leg 4 =,75 in outer reinforcement : leg 4 = / Inside : leg 4 = / fr =min(,s n /S v ) = fr = min(,s n /S v ) = fr = min(,min(s n, S p )/S v ) =.9 fr 4 = min(,s p /S v ) =.9 Required thickness of the nozzle neck UG-7 t rn = P R n / (S n -.6P) =,89 in R n = 5,875 in E = The nozzle neck thickness is adequate per UG-7. Required thickness of the nozzle neck UG-45 t a = t rn +Ca n =.89 in ; t b = max[t UG-7, UG-6(b)]+Ca v =.5 in ; t b = Table UG-45+Ca n =.8 in t UG-45 = max [t a, min [t b, t b ] ] =,8 in The nozzle neck thickness is adequate per UG-45. Dimensions FIG. UG-4 angle of plane with longitudinal axis : Longitudinal Plane : θ = Circumferential Plane : θ = 9 angle of each side / vessel wall : δ = 9 δ = 9 δ = / δ = / β = deflection angle / normal line d = diameter of the finished opening,75 in R n = radius of the finished opening 5,875 in t i = thickness of internal projection / t p = width of reinforcing pad / t x = thickness of selfreinforcing / L = height of selfreinforcing / / Configuration of the reinforcement : / / t e = thickness or height of the reinforcement in in t n = thickness of nozzle,5 in,5 in h = height of the internal projection in in Reinforcement checking UG-7 opening [ in operation Int.P. ] Required thicknesses UG-7(a) t r =.5 in [ UG-7(c) ] t =,75 in E = t rn = P R n / (S n E-.6P) =,89 in R n = 5,875 in E = Longitudinal Plane : θ = Circumferential Plane : θ = 9 Limits of reinforcement UG-4 : δ = 9 δ = 9 δ = / δ = / UG-4 (b) : max [d, R n +t n +t ] =,75 in,75 in UG-4 (c) : min [.5t,.5t n +t e ] =,5 in,5 in Area required UG-7 (c) : Longitudinal Plane : θ = Circumferential Plane : θ = 9 F = Correction factor FIG.UG-7 A = d t r F + t n /cos(β) t r F (-f r ) 6,8 in² AutoPIPE Vessel (Microprotol) procal V... 9 prodia V... Bentley Systems, Inc.

30 Longitudinal Plane : θ = Circumferential Plane : θ = 9 Lengths and heights of calculation of the areas : δ = 9 δ = 9 δ = / δ = / L = min [ UG-4 (b)-radius, length available] 5,875 in 5,875 in L = min [ UG-4 (c), height available],5 in,5 in L = min [ h,.5t,.5t i ] = in in L 5 = min [ UG-4 (b), t p, length available ] in in Longitudinal Plane : θ = Circumferential Plane : θ = 9 Area available (in²) : δ = 9 δ = 9 δ = / δ = / A = L (E t-t r F) - t n /cos(β) (E t-t r F) (-f r ),9,9 A = L (t n -t rn ) fr,5,5 A = L t i f r A 4 = leg 4 / f r,7,7 A 4 = leg 4 / f r4 A 4 = leg 4 / f r A 5 = L 5 t e f r4 A + A + A + A 4 + A 4 + A 4 + A 5 =,876 <A/,876 <A/,75 <A The opening is not adequately reinforced per UG-7. Weld sizes check UW-6(c). opening [ in operation Int.P. ] t n =,5 leg4 t c,outward FIG. UW-6.(d) full penetration weld Minimum throat required actual min(¼ in. (6 mm),.7 t t min ) =,5 in c,outward t min = min( ¾ in. (9 mm), t, t n ).7 leg 4 =,65 in min(¼ in. (6 mm),.7 t t min ) = / t =,75 tc,inward c,inward t min = min( ¾ in. (9 mm), t, t n ) leg4 Weld sizes are adequate.7 leg 4 = / Weld loads check UG-4(b) Strength calculations for attachments welds are not required for this opening in accordance with UW-5(b). AutoPIPE Vessel (Microprotol) procal V... prodia V... Bentley Systems, Inc.

31 L-7. (with reinforcing plate of in. wide x.75 in. thick Opening [ in operation Int.P. ] ASME VIII DIV. Nozzle with pad (,75 ) on Shell (No. ) Set In Pressure : P = 5 psi Temperature : 7 F Shell Material :SA56GR55 Allowable stress : S v = 4 psi Joint efficiency : E = Corrosion + tolerance : Ca v = in Allowable stress : S = 4 psi Ext. Diameter : D o = 6,5 in Nominal thickness :,75 in Tolerance for seamless pipe : / Nozzle Material : SA56GR55 Allowable stress : S n = 6 6 psi Joint efficiency : Corrosion + tolerance : Ca n = in Tolerance for seamless pipe : / Ext. Diameter : D on =,75 in Nominal thickness :,5 in External Projection : in Internal Projection : in Schedule : Inclination : Eccentricity : in Flange Material : SA5 Type : WN Rating : (ASME B6.5) Height : 5, in NPS " Pad Material : SA56GR6 Allowable stress : S p = psi Height :,75 in Width : in Ext. Diameter : D op = 8,75 in Weld outward : leg 4 =,75 in outer reinforcement : leg 4 =,5 in inward : leg 4 = / fr =min(,s n /S v ) = fr = min(,s n /S v ) = fr = min(,min(s n, S p )/S v ) =.9 fr 4 = min(,s p /S v ) =.9 Required thickness of the nozzle neck UG-7 t rn = P R n / (S n -.6P) =,89 in R n = 5,875 in E = The nozzle neck thickness is adequate per UG-7. Required thickness of the nozzle neck UG-45 t a = t rn +Ca n =.89 in ; t b = max[t UG-7, UG-6(b)]+Ca v =.5 in ; t b = Table UG-45+Ca n =.8 in t UG-45 = max [t a, min [t b, t b ] ] =,8 in The nozzle neck thickness is adequate per UG-45. Dimensions FIG. UG-4 angle of plane with longitudinal axis : Longitudinal Plane : θ = Circumferential Plane : θ = 9 angle of each side / vessel wall : δ = 9 δ = 9 δ = / δ = / β = deflection angle / normal line d = diameter of the finished opening,75 in R n = radius of the finished opening 5,875 in t i = thickness of internal projection / t p = width of reinforcing pad in t x = thickness of selfreinforcing / L = height of selfreinforcing / / Configuration of the reinforcement : sketch (b-) sketch (b-) t e = thickness or height of the reinforcement,75 in,75 in t n = thickness of nozzle,5 in,5 in h = height of the internal projection in in Reinforcement checking UG-7 opening [ in operation Int.P. ] Required thicknesses UG-7(a) t r =.5 in [ UG-7(c) ] t =,75 in E = t rn = P R n / (S n E-.6P) =,89 in R n = 5,875 in E = Longitudinal Plane : θ = Circumferential Plane : θ = 9 Limits of reinforcement UG-4 : δ = 9 δ = 9 δ = / δ = / UG-4 (b) : max [d, R n +t n +t ] =,75 in,75 in UG-4 (c) : min [.5t,.5t n +t e ] =,65 in,65 in Area required UG-7 (c) : Longitudinal Plane : θ = Circumferential Plane : θ = 9 F = Correction factor FIG.UG-7 A = d t r F + t n /cos(β) t r F (-f r ) 6,8 in² AutoPIPE Vessel (Microprotol) procal V... prodia V... Bentley Systems, Inc.

32 Longitudinal Plane : θ = Circumferential Plane : θ = 9 Lengths and heights of calculation of the areas : δ = 9 δ = 9 δ = / δ = / L = min [ UG-4 (b)-radius, length available] 5,875 in 5,875 in L = min [ UG-4 (c), height available],65 in,65 in L = min [ h,.5t,.5t i ] = in in L 5 = min [ UG-4 (b), t p, length available ] in in Longitudinal Plane : θ = Circumferential Plane : θ = 9 Area available (in²) : δ = 9 δ = 9 δ = / δ = / A = L (E t-t r F) - t n /cos(β) (E t-t r F) (-f r ),9,9 A = L (t n -t rn ) fr,667,667 A = L t i f r A 4 = leg 4 / f r,65,65 A 4 = leg 4 / f r4,45,45 A 4 = leg 4 / f r A 5 = L 5 t e f r4,8,8 A + A + A + A 4 + A 4 + A 4 + A 5 =,8 <A/,8 <A/ 6,6 <A The opening is not adequately reinforced per UG-7. Weld sizes check UW-6(c). opening [ in operation Int.P. ] t n =,5 FIG. UW-6. (d)+(a-) full penetration weld leg 4 Minimum throat required actual t c,inner leg 4 min(¼ in. (6 mm),.7 t t min ) =,5 in c,inner.7 leg t min = min( ¾ in. (9 mm), t, t n ) 4 =,65 in t c,outer t e =,75.5 t t min =,875 in c,outer t min = min(¾ in. (9 mm)., t e, t).7 leg 4 =,88 in t =,75 t c min(¼ in. (6 mm),.7 t t min ) = / c leg 4 t min = min( ¾ in. (9 mm), t, t n ).7 leg 4 = / Weld sizes are adequate Weld loads check UG-4(b). opening [ in operation Int.P. ] FIG. UG-4. (a) full penetration weld Allowable strengths UW-5(c) + UG-4(a) + UG-45(c) + L-7 Outer fillet weld in shear : s w,outer = π/4 D op leg 4.49 min( S p, S v ) = lbf Inner fillet weld in shear : s w,inner = π/4 D on leg 4.49 min( S p, S n ) = 4 89 lbf Inside fillet weld in shear : s c = π/4 D on leg 4.49 min( S n, S v ) = lbf Lower groove weld in tension : s g,lower = π/4 D on t.74 min( S n, S v ) = lbf Upper groove weld in tension : s g,upper = π/4 D on t e.74 min( S n, S p ) = 6 68 lbf Nozzle wall in shear : s n = π/4 (D on t n ) t n.7 S n = lbf Longitudinal plane : θ = Circumferential plane : θ = 8 Loads to be carried by welds Fig. UG-4.(a) δ = 9 δ = 9 δ = δ = Total : W = [ A A + t n f r ( E t F t r )] S v 7 6 lbf 7 6 lbf Path - : W - = (A +A 5 +A 4 +A 4 ) S v lbf lbf Path - : W - = (A +A +A 4 +A 4 +t n t f r ) S v 5 85 lbf 5 85 lbf Path - : W - = (A +A +A 5 +A 4 +A 4 +A 4 +t n t f r ) S v 9 lbf 9 lbf Longitudinal plane : θ = Circumferential plane : θ = 8 Check strength paths δ = 9 δ = 9 δ = δ = Path - : min(w;w - ) s w,outer + s n yes yes Path - : min(w;w - ) s w,inner +s g,upper +s g,lower +s c yes yes Path - : min( W, W - ) s w,outer +s g,lower +s c yes yes Strength of welded joints is adequate AutoPIPE Vessel (Microprotol) procal V... prodia V... Bentley Systems, Inc.

33 L-7. (with reinforcing plate of.5 in. wide and.75 in. thick) Opening [ in operation Int.P. ] ASME VIII DIV. Nozzle with pad (,75,5) on Shell (No. ) Set In Pressure : P = 5 psi Temperature : 7 F Shell Material :SA56GR55 Allowable stress : S v = 4 psi Joint efficiency : E = Corrosion + tolerance : Ca v = in Allowable stress : S = 4 psi Ext. Diameter : D o = 6,5 in Nominal thickness :,75 in Tolerance for seamless pipe : / Nozzle Material : SA56GR55 Allowable stress : S n = 6 6 psi Joint efficiency : Corrosion + tolerance : Ca n = in Tolerance for seamless pipe : / Ext. Diameter : D on =,75 in Nominal thickness :,5 in External Projection : in Internal Projection : in Schedule : Inclination : Eccentricity : in Flange Material : SA5 Type : WN Rating : (ASME B6.5) Height : 5, in NPS " Pad Material : SA56GR6 Allowable stress : S p = psi Height :,75 in Width :,5 in Ext. Diameter : D op = 9 in Weld Outside : leg 4 =,75 in outer reinforcement : leg 4 =,5 in Inside : leg 4 = / fr =min(,s n /S v ) = fr = min(,s n /S v ) = fr = min(,min(s n, S p )/S v ) =.9 fr 4 = min(,s p /S v ) =.9 Required thickness of the nozzle neck UG-7 t rn = P R n / (S n -.6P) =,89 in R n = 5,875 in E = The nozzle neck thickness is adequate per UG-7. Required thickness of the nozzle neck UG-45 t a = t rn +Ca n =.89 in ; t b = max[t UG-7, UG-6(b)]+Ca v =.5 in ; t b = Table UG-45+Ca n =.8 in t UG-45 = max [t a, min [t b, t b ] ] =,8 in The nozzle neck thickness is adequate per UG-45. Dimensions FIG. UG-4 angle of plane with longitudinal axis : Longitudinal Plane : θ = Circumferential Plane : θ = 9 angle of each side / vessel wall : δ = 9 δ = 9 δ = / δ = / β = deflection angle / normal line d = diameter of the finished opening,75 in R n = radius of the finished opening 5,875 in t i = thickness of internal projection / t p = width of reinforcing pad,5 in t x = thickness of selfreinforcing / L = height of selfreinforcing / / Configuration of the reinforcement : sketch (b-) sketch (b-) t e = thickness or height of the reinforcement,75 in,75 in t n = thickness of nozzle,5 in,5 in h = height of the internal projection in in Reinforcement checking UG-7 opening [ in operation Int.P. ] Required thicknesses UG-7(a) t r =.5 in [ UG-7(c) ] t =,75 in E = t rn = P R n / (S n E-.6P) =,89 in R n = 5,875 in E = Longitudinal plane : θ = Circumferential plane : θ = 9 Limits of reinforcement UG-4 : δ = 9 δ = 9 δ = / δ = / UG-4 (b) : max [d, R n +t n +t ] =,75 in,75 in UG-4 (c) : min [.5t,.5t n +t e ] =,65 in,65 in Area required UG-7 (c) : Longitudinal plane : θ = Circumferential plane : θ = 9 F = Correction factor FIG.UG-7 A = d t r F + t n /cos(β) t r F (-f r ) 6,8 in² AutoPIPE Vessel (Microprotol) procal V... prodia V... Bentley Systems, Inc.

34 Longitudinal plane : θ = Circumferential plane : θ = 9 Lengths and heights of calculation of the areas : δ = 9 δ = 9 δ = / δ = / L = min [ UG-4 (b)-radius, length available] 5,875 in 5,875 in L = min [ UG-4 (c), height available],65 in,65 in L = min [ h,.5t,.5t i ] = in in L 5 = min [ UG-4 (b), t p, length available ],5 in,5 in Longitudinal plane : θ = Circumferential plane : θ = 9 Area available (in²) : δ = 9 δ = 9 δ = / δ = / A = L (E t-t r F) - t n /cos(β) (E t-t r F) (-f r ),9,9 A = L (t n -t rn ) fr,667,667 A = L t i f r A 4 = leg 4 / f r,65,65 A 4 = leg 4 / f r4,45,45 A 4 = leg 4 / f r A 5 = L 5 t e f r4,8,8 A + A + A + A 4 + A 4 + A 4 + A 5 =,5 A/,5 A/ 6, A The opening is adequately reinforced per UG-7. Weld sizes check UW-6(c). opening [ in operation Int.P. ] t n =,5 FIG. UW-6. (d)+(a-) full penetration weld leg 4 Minimum throat required actual t c,inner leg 4 min(¼ in. (6 mm),.7 t t min ) =,5 in c,inner.7 leg t min = min( ¾ in. (9 mm), t, t n ) 4 =,65 in t c,outer t e =,75.5 t t min =,875 in c,outer t min = min(¾ in. (9 mm)., t e, t).7 leg 4 =,88 in t =,75 t c min(¼ in. (6 mm),.7 t t min ) = / c leg 4 t min = min( ¾ in. (9 mm), t, t n ).7 leg 4 = / Weld sizes are adequate Weld loads check UG-4(b). opening [ in operation Int.P. ] FIG. UG-4. (a) full penetration weld Allowable strengths UW-5(c) + UG-4(a) + UG-45(c) + L-7 Outer fillet weld in shear : s w,outer = π/4 D op leg 4.49 min( S p, S v ) = 6 lbf Inner fillet weld in shear : s w,inner = π/4 D on leg 4.49 min( S p, S n ) = 4 89 lbf Inside fillet weld in shear : s c = π/4 D on leg 4.49 min( S n, S v ) = lbf Lower groove weld in tension : s g,lower = π/4 D on t.74 min( S n, S v ) = lbf Upper groove weld in tension : s g,upper = π/4 D on t e.74 min( S n, S p ) = 6 68 lbf Nozzle wall in shear : s n = π/4 (D on t n ) t n.7 S n = lbf Longitudinal plane : θ = Circumferential plane : θ = 8 Loads to be carried by welds Fig. UG-4.(a) δ = 9 δ = 9 δ = δ = Total : W = [ A A + t n f r ( E t F t r )] S v 7 6 lbf 7 6 lbf Path - : W - = (A +A 5 +A 4 +A 4 ) S v lbf lbf Path - : W - = (A +A +A 4 +A 4 +t n t f r ) S v 5 85 lbf 5 85 lbf Path - : W - = (A +A +A 5 +A 4 +A 4 +A 4 +t n t f r ) S v 948 lbf 948 lbf Longitudinal plane : θ = Circumferential plane : θ = 8 Check strength paths δ = 9 δ = 9 δ = δ = Path - : min(w;w - ) s w,outer + s n yes yes Path - : min(w;w - ) s w,inner +s g,upper +s g,lower +s c yes yes Path - : min( W, W - ) s w,outer +s g,lower +s c yes yes Strength of welded joints is adequate AutoPIPE Vessel (Microprotol) procal V... 4 prodia V... Bentley Systems, Inc.

35 L-7.4 Opening [ in operation Int.P. ] ASME VIII DIV. Nozzle Self Reinforcing (,5 γ = 5 ) on Shell (No. ) Set-on Pressure : P = 45 psi Temperature : 8 F Shell Material :SA56GR55 Allowable stress : S v = 4 psi Joint efficiency : E = Corrosion + tolerance : Ca v =,6 in Allowable stress : S = 4 psi Ext. Diameter : D o = in Nominal thickness : in Tolerance for seamless pipe : / Nozzle Material : SA5 Allowable stress : S n = psi Joint efficiency : Corrosion + tolerance : Ca n =,6 in Tolerance for seamless pipe : / Ext. Diameter : D on = 9,5 in Nominal thickness :,75 in External Projection : in Internal Projection : in Schedule : Inclination : Eccentricity : in Flange Material : SA5 Type : LN Rating : (ASME B6.5) 6 height :.5 in NPS 6" Pad Material : / Allowable stress : S p = / Height : in Width :,5 in Ext. Diameter : D op = 6 in Weld Outside : leg 4 =,75 in outer reinforcement : leg 4 = / Inside : leg 4 = / fr =min(,s n /S v ) = fr = min(,s n /S v ) = fr = min(,min(s n, S p )/S v ) = fr 4 = min(,s p /S v ) = Required thickness of the nozzle neck UG-7 t rn = P R n / (S n -.6P) =,97 in R n = 8,6 in E = The nozzle neck thickness is adequate per UG-7. Required thickness of the nozzle neck UG-45 t a = t rn +Ca n =,54 in ; t b = max[t UG-7, UG-6(b)]+Ca v =,895 in ; t b = Table UG-45+Ca n =,9 in t UG-45 = max [t a, min [t b, t b ] ] =,95 in The nozzle neck thickness is adequate per UG-45. Dimensions FIG. UG-4 angle of plane with longitudinal axis : Longitudinal Plane : θ = Circumferential Plane : θ = 9 angle of each side / vessel wall : δ = 9 δ = 9 δ = / δ = / β = deflection angle / normal line d = diameter of the finished opening 6,5 in R n = radius of the finished opening 8,6 in t i = thickness of internal projection / t p = width of reinforcing pad / t x = thickness of selfreinforcing 4,975 in L = height of selfreinforcing in in Configuration of the reinforcement : sketch (e-) sketch (e-) t e = thickness or height of the reinforcement.5 in.5 in t n = thickness of nozzle,6875 in,6875 in h = height of the internal projection in in Reinforcement checking UG-7 opening [ in operation Int.P. ] Required thicknesses UG-7(a) t r =,88 in [ UG-7(c) ] t =,975 in E = t rn = P R n / (S n E-.6P) =,97 in R n = 8,6 in E = Longitudinal plane : θ = Circumferential plane : θ = 9 Limits of reinforcement UG-4 : δ = 9 δ = 9 δ = / δ = / UG-4 (b) : max [d, R n +t n +t ] = 6,5 in 6,5 in UG-4 (c) : min [.5t,.5t n +t e ] = 4,844 in 4,844 in Area required UG-7 (c) : Longitudinal plane : θ = Circumferential plane : θ = 9 F = Correction factor FIG.UG-7 A = d t r F + t n /cos(β) t r F (-f r ) 9,554 in² AutoPIPE Vessel (Microprotol) procal V... 5 prodia V... Bentley Systems, Inc.

36 Longitudinal plane : θ = Circumferential plane : θ = 9 Lengths and heights of calculation of the areas : δ = 9 δ = 9 δ = / δ = / L = min [ UG-4 (b)-radius, length available] 8,6 in 8,6 in L = min [ UG-4 (c), height available] 4,844 in 4,844 in L = min [ h,.5t,.5t i ] = in in L 5 = min [ UG-4 (c), t e, height available ].5 in.5 in Longitudinal plane : θ = Circumferential plane : θ = 9 Area available (in²) : δ = 9 δ = 9 δ = / δ = / A = L (E t-t r F) - t n /cos(β) (E t-t r F) (-f r ),844,844 A = L (t n -t rn ) fr 6,76 6,76 A = L t i f r A 4 = leg 4 / f r,8,8 A 4 = leg 4 / f r4 A 4 = leg 4 / f r A 5 = L 5 (t x -t n ) f r 8,97 8,97 A + A + A + A 4 + A 4 + A 4 + A 5 = 6,84 A/ 6,84 A/,647 A The opening is adequately reinforced per UG-7. Weld sizes check UW-6(c). opening [ in operation Int.P. ] t n =,688 leg 4 FIG. UW-6.(a) full penetration weld Minimum throat required actual min(¼ in. (6 mm),.7 t t min )=,5 in c t min = min( ¾ in. (9 mm), t, t n ).7 leg 4 =,55 in t =,97 tc Weld sizes are adequate Weld loads check UG-4(b) Strength calculations for attachments welds are not required for this opening in accordance with UW-5(b). AutoPIPE Vessel (Microprotol) procal V... 6 prodia V... Bentley Systems, Inc.

37 Comments t e 4 48'.7957 Ø6 Ø6 According to FIG UG-4 (e-) t e limited to self reinforcement height : +.5 =.5 in Calculation of A 5 area : a) part of cylindrical reinforcement :.5 x = 6.5 in b) part of cone :.5 x.5 / =.475 in A 5 = = in AutoPIPE Vessel (Microprotol) procal V... 7 prodia V... Bentley Systems, Inc.

38 L-7.5 Opening [ in operation Int.P. ] ASME VIII DIV. Nozzle with pad (,5 6,5) on Shell (No. ) Set In Pressure : P = 5 psi Temperature : 4 F Shell Material :SA56GR7 Allowable stress : S v = 7 psi Joint efficiency : E = Corrosion + tolerance : Ca v =,5 in Allowable stress : S = 7 psi Ext. Diameter : D o = 87 in Nominal thickness : in Tolerance for seamless pipe : / Nozzle Material : SA56GR7 Allowable stress : S n = 7 psi Joint efficiency : Corrosion + tolerance : Ca n =,5 in Tolerance for seamless pipe : / Ext. Diameter : D on = 6 in Nominal thickness :,75 in External Projection : in Internal Projection : in Schedule : Inclination : Eccentricity : in Flange Material : SA5 Type : WN Rating : (ASME B6.5) height : 5, in NPS " Pad Material : SA56GR6 Allowable stress : S p = 7 psi Height :,5 in Width : 6,5 in Ext. Diameter : D op = 8,5 in Weld Outside : leg 4 =,75 in outer reinforcement : leg 4 =,875 in Inside : leg 4 = / fr =min(,s n /S v ) = fr = min(,s n /S v ) = fr = min(,min(s n, S p )/S v ) = fr 4 = min(,s p /S v ) = Required thickness of the nozzle neck UG-7 t rn = P R on / (S n +.4P) =,878 in R on = 8 in E= The nozzle neck thickness is adequate per UG-7. Required thickness of the nozzle neck UG-45 t a = t rn +Ca n =,58 in ; t b = max[t UG-7, UG-6(b)]+Ca v =,88 in ; t b = Table UG-45+Ca n =,578 in t UG-45 = max [t a, min [t b, t b ] ] =,578 in The nozzle neck thickness is adequate per UG-45. Dimensions FIG. UG-4 angle of plane with longitudinal axis : Longitudinal plane : θ = Circumferential plane : θ = 9 angle of each side / vessel wall : δ = 9 δ = 9 δ = / δ = / β = deflection angle / normal line d = diameter of the finished opening 5 in R n = radius of the finished opening 7.5 in t i = thickness of internal projection / t p = width of reinforcing pad 6,5 in t x = thickness of selfreinforcing / L = height of selfreinforcing / / Configuration of the reinforcement : sketch (b-) sketch (b-) t e = thickness or height of the reinforcement,5 in,5 in t n = thickness of nozzle,5 in,5 in h = height of the internal projection in in Reinforcement checking UG-7 opening [ in operation Int.P. ] Required thicknesses UG-7(a) t r =,5578 in [ UG-7(c) ] t =,75 in E = t rn = P R on / (S n E+.4P) =,878 in R on = 8 in E = Longitudinal plane : θ = Circumferential plane : θ = 9 Limits of reinforcement UG-4 : δ = 9 δ = 9 δ = / δ = / UG-4 (b) : max [d, R n +t n +t ] = 5 in 5 in UG-4 (c) : min [.5t,.5t n +t e ] =,75 in,75 in Area required UG-7 (c) : Longitudinal plane : θ = Circumferential plane : θ = 9 F = Correction factor FIG.UG-7 A = d t r F + t n /cos(β) t r F (-f r ),68 in² ] AutoPIPE Vessel (Microprotol) procal V... 8 prodia V... Bentley Systems, Inc.

39 Longitudinal Plane : θ = Circumferential Plane : θ = 9 Lengths and heights of calculation of the areas : δ = 9 δ = 9 δ = / δ = / L = min [ UG-4 (b)-radius, length available] 7,5 in 7,5 in L = min [ UG-4 (c), height available],75 in,75 in L = min [ h,.5t,.5t i ] = in in L 5 = min [ UG-4 (b), t p, length available ] 6,5 in 6,5 in Longitudinal Plane : θ = Circumferential Plane : θ = 9 Area available (in²) : δ = 9 δ = 9 δ = / δ = / A = L (E t-t r F) - t n /cos(β) (E t-t r F) (-f r ),44,44 A = L (t n -t rn ) fr,584,584 A = L t i f r A 4 = leg 4 / f r,7,7 A 4 = leg 4 / f r4,8,8 A 4 = leg 4 / f r A 5 = L 5 t e f r4 9,88 9,88 A + A + A + A 4 + A 4 + A 4 + A 5 =,665 <A/,665 <A/, <A The opening is not adequately reinforced per UG-7. Weld sizes check UW-6(c). opening [ in operation Int.P. ] t n =,49 FIG. UW-6. (d)+(a-) full penetration weld leg 4 Minimum throat required actual t c,inner leg 4 min[¼ in.(6 mm);.7 t t min ]=,5 in c,inner.7 leg t min = min[ ¾ in.(9 mm) ; t e, t n ] 4 =,65 in t c,outer t e =,5.5 t t min =,75 in c,outer t min = min[ ¾ in.(9 mm) ; t e, t].7 leg 4 =,65 in t =,75 t c min[¼ in. (6 mm);.7 t t min ]= / c leg 4 t min = min[ ¾ in.(9 mm) ; t, t n ].7 leg 4 Ca n = / Weld sizes are adequate Weld loads check UG-4(b). opening [ in operation Int.P. ] FIG. UG-4. (a) full penetration weld Allowable strengths UW-5(c) + UG-4(a) + UG-45(c) + L-7 Outer fillet weld in shear : s w,outer = π/4 D op leg 4.49 min( S p, S v ) = 7 lbf Inner fillet weld in shear : s w,inner = π/4 D on leg 4.49 min( S p, S n ) = 64 lbf Inside fillet weld in shear : s c = π/4 D on leg 4.49 min( S n, S v ) = lbf Lower groove weld in tension : s g,lower = π/4 D on t.74 min( S n, S v ) = 946 lbf Upper groove weld in tension : s g,upper = π/4 D on t e.74 min( S n, S p ) = 9 97 lbf Nozzle wall in shear : s n = π/4 (D on t n ) t n.7 S n = 58 7 lbf Longitudinal plane : θ = Circumferential plane : θ = 8 Loads to be carried by welds Fig. UG-4.(a) δ = 9 δ = 9 δ = δ = Total : W = [ A A + t n f r ( E t F t r )] S v 4 69 lbf 4 69 lbf Path - : W - = (A +A 5 +A 4 +A 4 ) S v 4 7 lbf 4 7 lbf Path - : W - = (A +A +A 4 +A 4 +t n t f r ) S v 947 lbf 947 lbf Path - : W - = (A +A +A 5 +A 4 +A 4 +A 4 +t n t f r ) S v 5 6 lbf 5 6 lbf Longitudinal plane : θ = Circumferential plane : θ = 8 Check strength paths δ = 9 δ = 9 δ = δ = Path - : min(w;w - ) s w,outer + s n yes yes Path - : min(w;w - ) s w,inner +s g,upper +s g,lower +s c yes yes Path - : min( W, W - ) s w,outer +s g,lower +s c yes yes Strength of welded joints is adequate AutoPIPE Vessel (Microprotol) procal V... 9 prodia V... Bentley Systems, Inc.

40 Comments Calculation of t r,n is normally done in AutoPIPE Vessel with formula of external diameter and consequently gives a different thickness than in ASME example. t rn = 5x8 / (7+.4x5) =,8777 in t r = 5x4.75 / (7-.6x5) =,55784 in Required area to be reinforced : A = d t r F + t n /cos(β) t r F (-f r ) = 5x =.676 in (ASME example value is.4 in ) Available areas on each side : A = 7.5x( ) =.44 in (ASME example value is.85/ =.45 in ) A =.75x( ) =.586 in (ASME example value is./ =.65 in ) A = in A 4 =.75 /=.7 in (ASME example value of the sum of A 4 and A 4 is.96/ =.45 in ) A 4 =.875 /=.88 in ASME example value of the sum of A 4 and A 4 is.96/ =.45 in ) A 4 = in A + A + A + A 4 + A 4 = A =.4779 in (ASME example value is 4.97/ =.485 in ) A 5 = 6.5x.5 = in (ASME example value is 8.4/ = 9. in ) Total of available areas in AutoPIPE Vessel calculation : =.6654 in <.676/ =.685 in Total of available areas in ASME example is : =.685 in <.4/ =.7 in ASME example conclusion is : This is equal to the required area; therefore, opening is adequatly reinforced. ASME calculation is not correct. There are too many rounded values resulting in an important error. AutoPIPE Vessel (Microprotol) procal V... 4 prodia V... Bentley Systems, Inc.

41 L-7.6 Opening [ in operation Int.P. ] ASME VIII DIV. Nozzle without pad on Elliptical Head (No. ) Set In Pressure : P = 5 psi Temperature : 4 F Shell Material :SA56GR6 Allowable stress : S v = 7 5 psi Joint efficiency : E = Corrosion + tolerance : Ca v = in Allowable stress : S = 7 5 psi Ext. Diameter : D o = 4 in Nominal thickness :,88 in Tolerance for seamless pipe : / Nozzle Material : SA6GRB Allowable stress : S n = psi Joint efficiency : Corrosion + tolerance : Ca n = in Tolerance for seamless pipe :,5 % Ext. Diameter : D on = 8,65 in Nominal thickness :,5 in NPS 8" External Projection : 9,96 in Internal Projection :,6 in Schedule : Inclination : Eccentricity : in Flange Material : / Type : / Rating : / height : / Pad Material : / Allowable stress : S p = / Height : / Width : / Ext. Diameter : D op = / Weld Outside : leg 4 =,5 in outer reinforcement : leg 4 = / Inside : leg 4 =,5 in fr =min(,s n /S v ) =.686 fr = min(,s n /S v ) =.686 fr = min(,min(s n, S p )/S v ) =.686 fr 4 = min(,s p /S v ) = Required thickness of the nozzle neck Appendix - t rn = P R on / (S n +.4P) =,56 in R on = 4, in E= The nozzle neck thickness is adequate per Appendix -. Required thickness of the nozzle neck UG-45 t a = t rn +Ca n =.54 in ; t b = max[t UG-, UG-6(b)]+Ca v =. in ; t b = Table UG-45+Ca n =.8 in t UG-45 = max [t a, min [t b, t b ] ] =, in The nozzle neck thickness is adequate per UG-45. Dimensions FIG. UG-4 angle of plane with longitudinal axis : Longitudinal plane : θ = Circumferential plane : θ = 9 angle of each side / vessel wall : δ = 9 δ = 9 δ = / δ = / β = deflection angle / normal line d = diameter of the finished opening 8,5 in R n = radius of the finished opening 4,6 in t i = thickness of internal projection,5 in t p = width of reinforcing pad / t x = thickness of selfreinforcing / L = height of selfreinforcing / / Configuration of the reinforcement : / / t e = thickness or height of the reinforcement in in t n = thickness of nozzle,5 in,5 in h = height of the internal projection,6 in,6 in Reinforcement checking UG-7 opening [ in operation Int.P. ] Required thicknesses UG-7(a) t r =.9 in [ UG-7(a)(c) + UG-7(d) ] t =,875 in K (Table UG-7) =,9 E = t rn = P R on / (S n E+.4P) =,56 in R on = 4, in E = Longitudinal plane : θ = Circumferential plane : θ = 9 Limits of reinforcement UG-4 : δ = 9 δ = 9 δ = / δ = / UG-4 (b) : max [d, R n +t n +t ] = 8,5 in 8,5 in UG-4 (c) : min [.5t,.5t n +t e ] =,469 in,469 in Area required UG-7 (c) : Longitudinal plane : θ = Circumferential plane : θ = 9 F = Correction factor FIG.UG-7 A = d t r F + t n /cos(β) t r F (-f r ),756 in² AutoPIPE Vessel (Microprotol) procal V... 4 prodia V... Bentley Systems, Inc.

42 Longitudinal plane : θ = Circumferential plane : θ = 9 Lengths and heights of calculation of the areas : δ = 9 δ = 9 δ = / δ = / L = min [ UG-4 (b)-radius, length available] 4,8 in 4,8 in L = min [ UG-4 (c), height available],469 in,469 in L = min [ h,.5t,.5t i ] =,469 in,469 in L 5 = min [ UG-4 (b), t p, length available ] in in Longitudinal plane : θ = Circumferential plane : θ = 9 Area available (in²) : δ = 9 δ = 9 δ = / δ = / A = L (E t-t r F) - t n /cos(β) (E t-t r F) (-f r ),8,8 A = L (t n -t rn ) fr,6,6 A = L t i f r,8,8 A 4 = leg 4 / f r,, A 4 = leg 4 / f r4 A 4 = leg 4 / f r,, A 5 = L 5 t e f r4 A + A + A + A 4 + A 4 + A 4 + A 5 =,567 A/,567 A/,5 A The opening is adequately reinforced per UG-7. Weld sizes check UW-6(c). opening [ in operation Int.P. ] tn =,5 leg4 tc,outward FIG. UW-6.(d) full penetration weld Minimum throat required actual min[¼ in.(6 mm);.7 t t min ]=, in c,outward t min = min[ ¾ in.(9 mm) ; t, t n ].7 leg 4 =,75 in min[¼ in.(6 mm);.7 t t min ]=, in t =,88 t c,inward c,inward t min = min[ ¾ in.(9 mm) ; t, t n ] leg 4 Weld sizes are adequate.7 leg 4 =,75 in Weld loads check UG-4(b) Strength calculations for attachments welds are not required for this opening in accordance with UW-5(b). Comments AutoPIPE Vessel does not take into account weld attachment following FIG.UW-6.(i) and consequently does not check weld loading. AutoPIPE Vessel (Microprotol) procal V... 4 prodia V... Bentley Systems, Inc.

43 L-7.7 (nozzle thickness = ½ in.) Opening A [ in operation Int.P. ] ASME VIII DIV. Nozzle without pad on Shell (No. ) Set-in Pressure : P = psi Temperature : 5 F Shell Material :SA55GR6 Allowable stress : S v = 8 psi Joint efficiency : E = Corrosion + tolerance : Ca v = in Allowable stress : S = 8 psi Ext. Diameter : D o = in Nominal thickness :,5 in Tolerance for seamless pipe : / Nozzle Material : SA55GR6 Allowable stress : S n = 5 psi Joint efficiency : Corrosion + tolerance : Ca n = in Tolerance for seamless pipe : / Ext. Diameter : D on = 5 in Nominal thickness :,5 in External Projection : in Internal Projection : in Schedule : Inclination : Eccentricity : in Flange Material : / Type : / Rating : / height : / Pad Material : / Allowable stress : S p = / Height : / Width : / Ext. Diameter : D op = / Weld outward : leg 4 =,5 in outer reinforcement : leg 4 = / inward : leg 4 = / fr =min(,s n /S v ) = fr = min(,s n /S v ) = fr = min(,min(s n, S p )/S v ) = fr 4 = min(,s p /S v ) = Required thickness of the nozzle neck UG-7 t rn = P R n / (S n -.6P) =,89 in R n = in E= The nozzle neck thickness is adequate per UG-7. Required thickness of the nozzle neck UG-45 t a = t rn +Ca n =.9 in ; t b = max[t UG-7, UG-6(b)]+Ca v =.6 in ; t b = Table UG-45+Ca n =.6 in t UG-45 = max [t a, min [t b, t b ] ] =,6 in The nozzle neck thickness is adequate per UG-45. Dimensions FIG. UG-4 angle of plane with longitudinal axis : Longitudinal plane : θ = Circumferential plane : θ = 9 angle of each side / vessel wall : δ = 9 δ = 9 δ = 4,4 δ = 6,66 β = deflection angle / normal line 46,66 d = diameter of the finished opening 4 in 6,66 in R n = radius of the finished opening in,8 in t i = thickness of internal projection / / t p = width of reinforcing pad / / t x = thickness of selfreinforcing / / L = height of selfreinforcing / / / / Configuration of the reinforcement : / / / / t e = thickness or height of the reinforcement in in in in t n = thickness of nozzle,5 in,5 in,5 in,5 in h = height of the internal projection in in in in Reinforcement checking UG-7 opening A [ in operation Int.P. ] Required thicknesses UG-7(a) t r =.64 in [ UG-7(c) ] t =,5 in E = t rn = P R n / (S n E-.6P) =,89 in R n = in E = Longitudinal plane : θ = Circumferential plane : θ = 9 Limits of reinforcement UG-4 : δ = 9 δ = 9 δ = 4,4 δ = 6,66 UG-4 (b) : max [d, R n +t n +t ] = 4 in 4 in 6,66 in 6,66 in UG-4 (c) : min [.5t,.5t n +t e ] =,5 in,5 in,5 in,5 in Area required UG-7 (c) : Longitudinal plane : θ = Circumferential plane : θ = 9 F = Correction factor FIG.UG-7,5 A = d t r F + t n /cos(β) t r F (-f r ) 4,545 in²,67 in² AutoPIPE Vessel (Microprotol) procal V... 4 prodia V... Bentley Systems, Inc.

44 Longitudinal plane : θ = Circumferential plane : θ = 9 Lengths and heights of calculation of the areas : δ = 9 δ = 9 δ = 4,4 δ = 6,66 L = min [ UG-4 (b)-radius, length available] in in,6 in,6 in L = min [ UG-4 (c), height available],5 in,5 in,5 in,5 in L = min [ h,.5t,.5t i ] = in in in in L 5 = min [ UG-4 (b), t p, length available ] in in in in Longitudinal plane : θ = Circumferential plane : θ = 9 Area available (in²) : δ = 9 δ = 9 δ = 4,4 δ = 6,66 A = L (E t-t r F) - t n /cos(β) (E t-t r F) (-f r ),77,77,946,946 A = L (t n -t rn ) fr,45,45,45,45 A = L t i f r A 4 = leg 4 / f r,5,5,5,5 A 4 = leg 4 / f r4 A 4 = leg 4 / f r A 5 = L 5 t e f r4 A + A + A + A 4 + A 4 + A 4 + A 5 =,4 <A/,4 <A/,5 A/,5 A/,67 <A 7,44 A The opening is not adequately reinforced per UG-7. Weld sizes check UW-6(c). opening A [ in operation Int.P. ] tn =,5 leg4 tc,outward FIG. UW-6.(d) full penetration weld Minimum throat required actual min[¼ in.(6 mm);.7 t t min ]=,5 in c,outward t min = min[ ¾ in.(9 mm) ; t, t n ].7 leg 4 =,5 in min[¼ in.(6 mm);.7 t t min ]= / t =,5 t c,inward c,inward t min = min[ ¾ in.(9 mm) ; t, t n ] leg 4 Weld sizes are adequate.7 leg 4 = / Weld loads check UG-4(b) Strength calculations for attachments welds are not required for this opening in accordance with UW-5(b). Comments Differences are due to the fact that AutoPIPE Vessel calculates d using the nominal thickness of the shell (.5 in.) instead of the calculated value t r. t r = (x5)/(8-.6*) =.64 in (ASME value is.4in) Angles are different and consequently d. AutoPIPE Vessel calculation : Rm = 5 + (.5/) = 5.75 in α = arc cos((+)/5.75) = 7.66 α = arc cos((-)/5.75) = α = =. d = x5.75x (-cos(α/) ) = 6.66 in ASME calculation is approximative taking account the rounding of t r value. UG parts is based on the use of the internal diameter and figure UG-7. shows extra thickness for reinforcement outside. If thickness is calculated according to Appendix -,we can consider probably that extra thickness for reinforcement is inside. Consequently, d may be different for the same geometry following that the thickness is calculated with the internal or the external diameter. AutoPIPE Vessel (Microprotol) procal V prodia V... Bentley Systems, Inc.

45 L-7.7 (nozzle thickness = 7/8 in.) Opening A [ in operation Int.P. ] ASME VIII DIV. Nozzle without pad on Shell (No. ) Set In Pressure : P = psi Temperature : 5 F Shell Material :SA55GR6 Allowable stress : S v = 8 psi Joint efficiency : E = Corrosion + tolerance : Ca v = in Allowable stress : S = 8 psi Ext. Diameter : D o = in Nominal thickness :,5 in Tolerance for seamless pipe : / Nozzle Material : SA55GR6 Allowable stress : S n = 7 psi Joint efficiency : Corrosion + tolerance : Ca n = in Tolerance for seamless pipe : / Ext. Diameter : D on = 5,75 in Nominal thickness :,875 in External Projection : in Internal Projection : in Schedule : Inclination : Eccentricity : in Flange Material : / Type : / Rating : / height : / Pad Material : / Allowable stress : S p = / Height : / Width : / Ext. Diameter : D op = / Weld Outside : leg 4 =,5 in outer reinforcement : leg 4 = / Inside : leg 4 = / fr =min(,s n /S v ) = fr = min(,s n /S v ) = fr = min(,min(s n, S p )/S v ) = fr 4 = min(,s p /S v ) = Required thickness of the nozzle neck UG-7 t rn = P R n / (S n -.6P) =, in R n = in E= The nozzle neck thickness is adequate per UG-7. Required thickness of the nozzle neck UG-45 t a = t rn +Ca n =. in ; t b = max[t UG-7, UG-6(b)]+Ca v =.6 in ; t b = Table UG-45+Ca n =.45 in t UG-45 = max [t a, min [t b, t b ] ] =.45 in The nozzle neck thickness is adequate per UG-45. Dimensions FIG. UG-4 angle of plane with longitudinal axis : Longitudinal plane : θ = Circumferential plane : θ = 9 angle of each side / vessel wall : δ = 9 δ = 9 δ = 4,4 δ = 6,66 β = deflection angle / normal line 46,66 d = diameter of the finished opening 4 in 6,66 in R n = radius of the finished opening in,8 in t i = thickness of internal projection / / t p = width of reinforcing pad / / t x = thickness of selfreinforcing / / L = height of selfreinforcing / / / / Configuration of the reinforcement : / / / / t e = thickness or height of the reinforcement in in in in t n = thickness of nozzle,875 in,875 in,875 in,875 in h = height of the internal projection in in in in Reinforcement checking UG-7 opening A [ in operation Int.P. ] Required thicknesses UG-7(a) t r =.64 in [ UG-7(c) ] t =,5 in E = t rn = P R n / (S n E-.6P) =, in R n = in E = Longitudinal plane : θ = Circumferential plane : θ = 9 Limits of reinforcement UG-4 : δ = 9 δ = 9 δ = 4,4 δ = 6,66 UG-4 (b) : max [d, R n +t n +t ] = 4,75 in 4,75 in 6,66 in 6,66 in UG-4 (c) : min [.5t,.5t n +t e ] =,88 in,88 in,88 in,88 in Area required UG-7 (c) : Longitudinal plane : θ = Circumferential plane : θ = 9 F = Correction factor FIG.UG-7,5 A = d t r F + t n /cos(β) t r F (-f r ) 4,545 in²,67 in² AutoPIPE Vessel (Microprotol) procal V prodia V... Bentley Systems, Inc.

46 Longitudinal plane : θ = Circumferential plane : θ = 9 Lengths and heights of calculation of the areas : δ = 9 δ = 9 δ = 4,4 δ = 6,66 L = min [ UG-4 (b)-radius, length available],75 in,75 in,6 in,6 in L = min [ UG-4 (c), height available],88 in,88 in,88 in,88 in L = min [ h,.5t,.5t i ] = in in in in L 5 = min [ UG-4 (b), t p, length available ] in in in in Longitudinal plane : θ = Circumferential plane : θ = 9 Area available (in²) : δ = 9 δ = 9 δ = 4,4 δ = 6,66 A = L (E t-t r F) - t n /cos(β) (E t-t r F) (-f r ),864,864,946,946 A = L (t n -t rn ) fr,649,649,649,649 A = L t i f r A 4 = leg 4 / f r,5,5,5,5 A 4 = leg 4 / f r4 A 4 = leg 4 / f r A 5 = L 5 t e f r4 A + A + A + A 4 + A 4 + A 4 + A 5 =,68 A/,68 A/ 4,79 A/ 4,79 A/ 5,75 A 9,49 A The opening is adequately reinforced per UG-7. Weld sizes check UW-6(c). opening A [ in operation Int.P. ] tn =,875 leg4 tc,outward FIG. UW-6.(d) full penetration weld Minimum throat required actual min[¼ in.(6 mm);.7 t t min ]=,5 in c,outward t min = min[ ¾ in.(9 mm) ; t, t n ].7 leg 4 =,5 in min[¼ in.(6 mm);.7 t t min ]= / t =,5 t c,inward c,inward t min = min[ ¾ in.(9 mm) ; t, t n ] leg 4 Weld sizes are adequate.7 leg 4 = / Weld loads check UG-4(b) Strength calculations for attachments welds are not required for this opening in accordance with UW-5(b). Same as for L7-7 (nozzle thickness = ½ in) Comments AutoPIPE Vessel (Microprotol) procal V prodia V... Bentley Systems, Inc.

47 L UG-45 Opening [ in operation Int.P. ] ASME VIII DIV. Nozzle with pad (,5,75) on Shell (No. ) Set In Pressure : P = psi Temperature : 65 F Shell Material :SA56GR7 Allowable stress : S v = 7 5 psi Joint efficiency : E = Corrosion + tolerance : Ca v =,5 in Allowable stress : S = 7 5 psi Ext. Diameter : D o = 4,5 in Nominal thickness :,56 in Tolerance for seamless pipe : / Nozzle Material : SA6GRB Allowable stress : S n = psi Joint efficiency : Corrosion + tolerance : Ca n =,5 in Tolerance for seamless pipe :,5 % Ext. Diameter : D on =,75 in Nominal thickness :,594 in NPS " External Projection :,48 in Internal Projection : in Schedule : 8 Inclination : Eccentricity : in Flange Material : / Type : / Rating : / height : / Reinforcement Material : SA56GR6 Allowable stress : S p = 5 psi Height :,5 in Width :,75 in Ext. Diameter : D op = 6,5 in Weld Outside : leg 4 =,57 in outer reinforcement : leg 4 =,75 in Inside : leg 4 = / fr =min(,s n /S v ) =.686 fr = min(,s n /S v ) =.686 fr = min(,min(s n, S p )/S v ) =.686 fr 4 = min(,s p /S v ) =.857 Required thickness of the nozzle neck Appendix - t rn = P R on / (S n +.4P) =, in R on = 5,75 in E= The nozzle neck thickness is adequate per Appendix -. Required thickness of the nozzle neck UG-45 t a = t rn +Ca n =.58 in ; t b = max[t UG-7, UG-6(b)]+Ca v =.49 in ; t b = Table UG-45+Ca n =.444 in t UG-45 = max [t a, min [t b, t b ] ] =,444 in The nozzle neck thickness is adequate per UG-45. Dimensions FIG. UG-4 angle of plane with longitudinal axis : Longitudinal plane : θ = Circumferential plane : θ = 9 angle of each side / vessel wall : δ = 9 δ = 9 δ = / δ = / β = deflection angle / normal line d = diameter of the finished opening 9,8 in R n = radius of the finished opening 4,96 in t i = thickness of internal projection / t p = width of reinforcing pad,75 in t x = thickness of selfreinforcing / L = height of selfreinforcing / / Configuration of the reinforcement : sketch (b-) sketch (b-) t e = thickness or height of the reinforcement,5 in,5 in t n = thickness of nozzle,469 in,469 in h = height of the internal projection in in Reinforcement checking UG-7 opening [ in operation Int.P. ] Required thicknesses UG-7(a) t r =.659 in [ UG-7(c) ] t =,475 in E = t rn = P R on / (S n E+.4P) =, in R on = 5,75 in E = Longitudinal plane : θ = Circumferential plane : θ = 9 Limits of reinforcement UG-4 : δ = 9 δ = 9 δ = / δ = / UG-4 (b) : max [d, R n +t n +t ] = 9,8 in 9,8 in UG-4 (c) : min [.5t,.5t n +t e ] =,94 in,94 in Area required UG-7 (c) : Longitudinal plane : θ = Circumferential plane : θ = 9 F = Correction factor FIG.UG-7 A = d t r F + t n /cos(β) t r F (-f r ),698 in² AutoPIPE Vessel (Microprotol) procal V prodia V... Bentley Systems, Inc.

48 Longitudinal plane : θ = Circumferential plane : θ = 9 Lengths and heights of calculation of the areas : δ = 9 δ = 9 δ = / δ = / L = min [ UG-4 (b)-radius, length available] 4,96 in 4,96 in L = min [ UG-4 (c), height available],94 in,94 in L = min [ h,.5t,.5t i ] = in in L 5 = min [ UG-4 (b), t p, length available ],75 in,75 in Longitudinal plane : θ = Circumferential plane : θ = 9 Area available (in²) : δ = 9 δ = 9 δ = / δ = / A = L (E t-t r F) - t n /cos(β) (E t-t r F) (-f r ),4,4 A = L (t n -t rn ) fr,5,5 A = L t i f r A 4 = leg 4 / f r,48,48 A 4 = leg 4 / f r4,6,6 A 4 = leg 4 / f r A 5 = L 5 t e f r4,79,79 A + A + A + A 4 + A 4 + A 4 + A 5 =,88 A/,88 A/,759 A The opening is adequately reinforced per UG-7. Weld sizes check UW-6(c). opening [ in operation Int.P. ] t n =,469 FIG. UW-6. (d)+(a-) full penetration weld leg 4 Minimum throat required actual t c,inner leg 4 min[¼ in.(6 mm);.7 t t min ]=,5 in c,inner.7 leg t min = min[ ¾ in.(9 mm) ; t e, t n ] 4 =,65 in t c,outer t e =,5.5 t t min =,87 in c,outer t min = min[ ¾ in.(9 mm) ; t e, t].7 leg 4 =,65 in t =,47 t c min[¼ in. (6 mm);.7 t t min ]= / c leg 4 t min = min[ ¾ in.(9 mm) ; t, t n ].7 leg 4 = / Weld sizes are adequate Weld loads check UG-4(b). opening [ in operation Int.P. ] FIG. UG-4. (a) full penetration weld Allowable strengths UW-5(c) + UG-4(a) + UG-45(c) + L-7 Outer fillet weld in shear : s w,outer = π/4 D op leg 4.49 min( S p, S v ) = 5 77 lbf Inner fillet weld in shear : s w,inner = π/4 D on leg 4.49 min( S p, S n ) = 8 67 lbf Inside fillet weld in shear : s c = π/4 D on leg 4.49 min( S n, S v ) = lbf Lower groove weld in tension : s g,lower = π/4 D on t.74 min( S n, S v ) = 8 lbf Upper groove weld in tension : s g,upper = π/4 D on t e.74 min( S n, S p ) = lbf Nozzle wall in shear : s n = π/4 (D on t n ) t n.7 S n = 8 lbf Longitudinal plane : θ = Circumferential plane : θ = 8 Loads to be carried by welds Fig. UG-4.(a) δ = 9 δ = 9 δ = δ = Total : W = [ A A + t n f r ( E t F t r )] S v 6 8 lbf 6 8 lbf Path - : W - = (A +A 5 +A 4 +A 4 ) S v 6 9 lbf 6 9 lbf Path - : W - = (A +A +A 4 +A 4 +t n t f r ) S v 7 75 lbf 7 75 lbf Path - : W - = (A +A +A 5 +A 4 +A 4 +A 4 +t n t f r ) S v 9 95 lbf 9 95 lbf Longitudinal plane : θ = Circumferential plane : θ = 8 Check strength paths δ = 9 δ = 9 δ = δ = Path - : min(w;w - ) s w,outer + s n yes yes Path - : min(w;w - ) s w,inner +s g,upper +s g,lower +s c yes yes Path - : min( W, W - ) s w,outer +s g,lower +s c yes yes Strength of welded joints is adequate AutoPIPE Vessel (Microprotol) procal V prodia V... Bentley Systems, Inc.

49 UG 45 NOZZLE NECK THICKNESS case of pipe nozzle Outer Diameter of nozzle =.75 in Nominal thickness of nozzle =.594 in Pipe (yes =) = Tolerance (.5 % nominal thickness for pipe) =.745 in Tolerance (other than pipe) in Corrosion allowance =.5 in Design pressure = psi Allowable stress = psi Minimum calculated shell thickness (internal pressure) =.659 in Minimum calculated shell thickness (external pressure) = in Standard nozzle thickness =.65 in before release Thickness according UG45B =.499 in (Mini shell thk +CA with E=) Thickness according UG6B =.875 in (/6 in + CA) Thickness according UG45B = in (Ext pressure pres.thk +CA) Thickness according UG45B4 = in Standard thk * CA Thickness according UG45A =.5876 in (Mini nozzle thk +CA) Minimum nozzle neck thickness requirement : Max ( Min (Max ( UG45B,UG6B,UG45B ),UG45B4),UG45A) mini =.4448 in Minimum undertoleranced thickness of nozzle neck =.5975 in thickness OK per UG 45 release ta =.5876 in tb =.499 in tb = in TABLE UG-45 (undertoleranced standard thickness) =.9 in tb =.444 in tb = min(tb,max(tb,tb)) =.444 in tug45 =.444 in Minimum undertoleranced thickness of nozzle neck.5975 in thickness OK per UG 45 AutoPIPE Vessel (Microprotol) procal V prodia V... Bentley Systems, Inc.

50 Part UHX General comment ASME examples have not been updated. AutoPIPE Vessel examples are issued from ASME VIII div. -a Consequently, where W* is used for bolting connection and if W* is null, values of Q and resulting values are different. AutoPIPE Vessel (Microprotol) procal V... 5 prodia V... Bentley Systems, Inc.

51 UHX-.. Tubesheet Integral with Shell and Channel Tubesheet, Loading conditions [corroded normal condition]. ASME VIII DIV. Tubesheet a Tubes Shell Tubeside Tubeside Shellside [UHX-] Pressure P t =4 psi P s =- psi Corrosion c t = in c s = in in in Material SA4GR6 SATP6 SA4GR6 SA4GR6 Temperature 5 F (T =/) 5 F (T t,m=/) 5 F (T s,m=/) 5 F (T c =/) Allowable Stress S = 8 psi S a = psi S t = 8 psi S s = 8 psi S c = 8 psi Yield Strength S y = psi S y,t = psi S y,s = psi S y,c = psi modulus of elasticity E = 5 8. ksi E t = 5 8. ksi E s = 5 8. ksi E c = 5 8. ksi Poisson s ratio ν =. ν t =. ν s =. ν c =. Diameter A =.99 in d t =.75 in.9 in. in Nominal thicknesses.5 in t t =.65 in.8 in. in Tolerance in pattern Square N t =76 L = / OTL=.6 in p= in t c t s h p h D c D s Configuration a D s =.9 in t s =.8 in h =.5 in D c =. in t c =. in h p =.5 in h g = in Extra thickness (periphery) : Tubeside : in Shellside : in Tubesheet characteristics Diameter of perforated region D = r +d t =.6 in r = 5.45 in Tube expansion depth ratio ρ = l t,x /h = l t,x = in Effective Tube Pitch basic ligament efficiency : µ = (p- d t )/p =.5 p * p effective ligament efficiency : µ * = (p * - d * )/ p * =.49 = =.5 in 4MIN[ AL,( 4DO p) ] d * = max[(d t -t t E t /E S t /S ρ).(d t -t t )]=.75 in largest center-to-center distance between adjacent tube rows : U L =.5 in π DO Unperforated Area : A L = 6. in² Effective elastic constants E * = 49 5 psi ν * =,54 (Fig. UHX-., Fig. UHX-.4) Conditions of applicability Minimum thickness : TEMA 9th Ed. RCB 7- U L 4p Parameters ρ s = D s /D =.68 ρ c = D c /D =.6 M TS = D /6 [(ρ s -)(ρ s +)P s -(ρ c -)(ρ c +)P t ] β s = 4 ( ν s ) ( Ds + ts ) ts =.9 in - β c = 4 ( c ) ( Dc + tc ) tc ν =.94 in - k s = β s E s t s / 6(-ν s ) = 4.5 lbf k c = β c E c t c / 6(-ν c ) = lbf λ s = 6D s k s [+hβ s +(h β s /)] / h = psi λ c = 6D c k c [+hβ c +(h β c /)] / h = 48 6 psi δ s = [D s / (4E s t s )] (-ν s /) = in /lbf δ c = [D c / (4E c t c )] (-ν c /) = in /lbf ω s = ρ s k s β s δ s (+h β s ) =.499 in ω c = ρ c k c β c δ c (+h β c ) = in W s =. lbf W c =. lbf W ms =. lbf W mc =. lbf W max = max[w s, W c ] W mmax = max[w ms, W mc ] h g = max[(h g -c t ),()] = in K = A/D =.5 F =(-ν * )/E * (λ s +λ c +E ln K)= 9.44 bending moments M * =M TS +ω c P t -ω s P s M p = (M * - D / F (P s -P t ))/(+F) M = max( M p ; M ) M = M p + D /64 (+ν * ) (P s -P t ) Case W * P s (psi) P t (psi) M TS (lb.in/in) M * (lb.in/in) M p (lb.in/in) M (lb.in/in) M (lb.in/in) AutoPIPE Vessel (Microprotol) procal V... 5 prodia V... Bentley Systems, Inc.

52 Bending stresses in the Tubesheet : σ = 6 M / [µ * (h-h g ) ] σ shall be S b = S Shear stresses in the Tubesheet : τ = /(4µ) (D /h p ) P s -P t τ = /(4µ) ({4A p /C p }/h p ) P s -P t if P s -P t >.Sµ h p /D τ shall be S τ =.8S where : C p = 8.5 in and A p = 68.5 in² Case σ (psi) S b (psi) τ (psi) S τ (psi) Axial tube stress a = D / x s = -N t (d t /a ) x t = -N t ((d t -t t )/a ) σ t,o = [P t ( x t ) P s ( x s )] / (x t x s ) [UW-] Tube-To-Tubesheet Welds Fig. (c) a f =.75 in a g =.75 in a c = a f + a g F f =min(.55π a f (d t +.67a f ) S w ; F t )= lbf A t = π (d t -t t )t t f w = S t / S w = f f =-F g /(f d F t ) F g =min(.85π a g (d t +.67a g ) S w ; F t )= lbf L a = σ t,o A t F d = min (L actual ; F t ) f d =. S w = min (S t ; S) F t = π (d t -t t ) S t = lbf [UW-.4] Case (-) : L max =F t Case (4-7) : L max =F t L a shall be L max [UW-.6] a r = [ ( (.75d t ) +.7t t (d t -t t )f w f d ) d t ] a c shall not be < max(a r,t t ) Case σ t,o (psi) F d (lbf) f d f f a r (in) L a (lbf) L max (lbf) Shell stresses calculation Axial Membrane * 6 ν D σ stress s,m = Ds 4ts ( Ds + ts ) Ps bending σ s,b = hβ + s D k ( ) s β sδ + p + s sps 6 M P P * t stress ts E h σ Total axial s shall be S mb,s =,5S s σ stress s = σ s,m + σ s,b otherwise perform the elastic-plastic calculation procedure if σ s S PS,s = S,s = 54 psi Case σ s,b (psi) σ s,m (psi) σ s (psi) S mb,s (psi) The shell shall have a uniform thickness adjacent to the Tubesheet for a minimum length of l s. l s =. 8 D s + ts =,688 in Channel stresses calculation Membrane stress σ c,m = Dc 4tc ( Dc + tc ) Pt bending stress 6 t * ν * E hβ + σ c,b = c k β δ P 6 M + ( P P ) c c D h D c c c + p s t σ Total axial c shall be S mb,c =,5S c σ stress c = σ c,m + σ c,b otherwise perform the elastic-plastic calculation procedure if σ c S PS,c = S,c = 54 psi Case σ c,b (psi) σ c,m (psi) σ c (psi) S mb,c (psi) The channel shall have a uniform thickness adjacent to the Tubesheet for a minimum length of l c. Error(s) and/or warning(s) The thickness is acceptable The stresses in the shell and/or channel integral with tubesheet are acceptable l c =. 8 D + t =,54 in c c AutoPIPE Vessel (Microprotol) procal V... 5 prodia V... Bentley Systems, Inc.

53 UHX-. Configuration cylinder AutoPIPE Vessel checking a UHX-. ν factors. shell Ps = - psi Ds =.9 in ts =.8 in Gs = in Ss = 8 psi Sy,s = psi Es = 58 psi Sps,s = psi channel Pt = 4 psi Dc =. in tc =. in Gc = in Sc = 8 psi Sy,c = psi Ec = 58 psi Sps,c = psi tubesheet h =.5 in d= in Do =.6 in A =.99 in G = in C = in W* = hg = in equal fillet and groove welds ct = in expansion % cs = in S = 8 psi E = 58 psi tube Nt = 76 tubes pitch : (9 ) p = in dt =.75 in minimum U radius.5 in tt =.65 in number of pitch for Cp 4 stt = 8 psi Sy,t = psi EtT = 58 psi UHX-.5 UL =.5 in µ =.5 d* =.75 in UHX-.5 LL =.6 in µ = p* =.579 in AL = 6. in ρ = h'g = in ltx = in ro = 5.45 in Fig. UHX (pitch 9 ) h/p =.5 α = α = E*/E = α = α = α4 = AutoPIPE Vessel (Microprotol) procal V... 5 prodia V... Bentley Systems, Inc.

54 .5 ν* =.5999 β = β = β = β = β4 = case Ps = psi Pt = 4 psi case Ps = - psi Pt = psi case Ps = - psi Pt = 4 psi Step Do =.6 in Step 7 µ =.5 case Mp = lb.in / in - µ = Mo = lb.in / in h'g = in M = lb.in / in case Mp = 7.9 lb.in / in Step ρs =.6845 Mo = lb.in / in ρc = M = 7.9 lb.in / in case MTs = lb.in / in case Mp = lb.in / in case MTs = lb.in / in Mo = lb.in / in case MTs = lb.in / in M = lb.in / in Step h/p =.5 Step 8 E*/E = case σ = psi ν* =.5999 σ S OK case σ = 6.48 psi Step 4 βs =.854 βc = σ S OK ks =.996 kc = case σ = psi λs = λc = σ S OK δs = 7.44E-6 δc =.98954E-6 ωs =.4995 ωc= Step 5 K =.54 Step 9 F = case τ = 7.85 psi τ.8 S OK Step 6 case τ = psi case M* = lb.in / in τ.8 S OK case M* = lb.in / in case τ = 9.79 psi case M* = lb.in / in τ.8 S OK Step case σs,m = psi σs,b = psi σs = σs,m + σs,b = psi.5 Ss OK σc,m = psi σc,b = psi σc = σc,m + σc,b = psi.5 Sc OK case σs,m = psi σs,b = psi σs = σs,m + σs,b = psi.5 Ss OK σc,m = psi σc,b = psi σc = σc,m + σc,b = psi.5 Sc OK case σs,m = psi σs,b = psi σs = σs,m + σs,b = psi.5 Ss OK σc,m = psi σc,b = psi AutoPIPE Vessel (Microprotol) procal V prodia V... Bentley Systems, Inc.

55 σc = σc,m + σc,b = psi.5 Sc OK Comments for discrepancies between AutoPIPE Vessel and ASME example Elasticity modulus for Stainless Steel 6 (6Cr-Ni-Mo) has been input because read value from Table TM- of Section II Part D (GroupG at 5 F) is 5,9 6 psi. Some of values in ASME example have been rounded like parameters, AutoPIPE Vessel calculation gives for example : ρ s =.9/.6 =.68 ; ρ c =./.6 =.65 M TS =.6 /6 [(.68-)(.68 +)x--(.65-)(.65 +)x4] = Consequently, results are slightly different. AutoPIPE Vessel (Microprotol) procal V prodia V... Bentley Systems, Inc.

56 UHX-.. Tubesheet gasketed with Shell and Channel Tubesheet, Loading conditions [corroded normal condition]. ASME VIII DIV. Tubesheet a Tubes Shell Tubeside Tubeside Shellside [UHX-] Pressure P t =5 psi P s =-5 psi Corrosion c t =,5 in c s = in in in Material SA85GRC SB-C76- H55 SA56GR6 SA56GR6 Temperature F (T =/) F (T t,m=/) F (T s,m=/) F (T c =/) Allowable Stress S = 5 7 psi S a = 5 7 psi S t = psi S s = 7 psi S c = 7 psi Yield Strength S y = 6 5 psi S y,t = 6 psi S y,s = 8 psi S y,c = 8 psi modulus of elasticity E = 8, ksi E t = 5 4 ksi E s = 8, ksi E c = 8, ksi Poisson s ratio ν =. ν t =. ν s =. ν c =. Diameter A = in d t =.65 in in in Nominal thicknesses.45 in t t =.65 in.75 in.75 in Tolerance in pattern Rotated Triangular N t =86 L = / OTL=6.8 in p=.75 in h p D c G c Configuration d D s = in G s = 9 in h =.8 in D c = in G c = 9 in h p =.8 in h g = in t s =.75 in t c =.75 in Extra thickness (periphery) : Tubeside = in Shellside = in Tubesheet characteristics Diameter of perforated region D = r +d t = 6.8 in r = 8.87 in Tube expansion depth ratio ρ = l t,x /h = l t,x =.8 in Effective Tube Pitch basic ligament efficiency : µ = (p- d t )/p =,67 p * p effective ligament efficiency : µ * = (p * - d * )/ p * =,8 = =.85 in 4MIN[ AL,( 4DO p) ] d * = max[(d t -t t E t /E S t /S ρ),(d t -t t )]=,58 in largest center-to-center distance between adjacent tube rows : U L =.75 in π DO Unperforated Area : A L = 9,4 in² Effective elastic constants E * = psi ν * =.58 (Fig. UHX-., Fig. UHX-.4) Conditions of applicability Minimum thickness : TEMA 9th Ed. RCB 7- h D s G s U L 4p Parameters ρ s = G s /D =. ρ c = G c /D =. M TS = D /6 [(ρ s -)(ρ s +)P s -(ρ c -)(ρ c +)P t ] β s = 4 ( ν s ) ( Ds + ts ) ts = / β c = 4 ( c ) ( Dc + tc ) tc ν = / k s = β s E s t s / 6(-ν s ) = lbf k c = β c E c t c / 6(-ν c ) = lbf λ s = 6D s k s [+hβ s +(h β s /)] / h = psi λ c = 6D c k c [+hβ c +(h β c /)] / h = psi δ s = [D s / (4E s t s )] (-ν s /) = in /lbf δ c = [D c / (4E c t c )] (-ν c /) = in /lbf ω s = ρ s k s β s δ s (+h β s ) = in ω c = ρ c k c β c δ c (+h β c ) = in W s =.78 6 lbf W c =.78 6 lbf W ms =. lbf W mc = lbf W max = max[w s, W c ] W mmax = max[w ms, W mc ] h g = max[(h g -c t ),()] = in K = A/D =.9 F =(-ν * )/E * (λ s +λ c +E ln K)=.4 AutoPIPE Vessel (Microprotol) procal V prodia V... Bentley Systems, Inc.

57 bending moments M * =M TS +ω c P t -ω s P s +((G c -G s )/πd )W * M p = (M * - D / F (P s -P t ))/(+F) M = max( M p ; M ) M = M p + D /64 (+ν * ) (P s -P t ) Case W * P s (psi) P t (psi) M TS (lb.in/in) M * (lb.in/in) M p (lb.in/in) M (lb.in/in) M (lb.in/in) W mc W ms W mmax Bending stresses in the Tubesheet : σ = 6 M / [µ * (h-h g ) ] σ shall be S b = S Shear stresses in the Tubesheet : τ = /(4µ) (D /h p ) P s -P t τ = /(4µ) ({4A p /C p }/h p ) P s -P t if P s -P t >.Sµ h p /D τ shall be S τ =.8S in which : C p = 54,5 in and A p = 89. in² Case σ (psi) S b (psi) τ (psi) S τ (psi) Axial tube stress a = D / x s = -N t (d t /a ) x t = -N t ((d t -t t )/a ) σ t,o = [P t ( x t ) P s ( x s )] / (x t x s ) Tube-to-Tubesheet joint S min = min( S ; S t ) Welded tubes : S t,j = min[ ( S min g / t t ) ; S t ] (Weld : g = in) S t,j = 8 psi Expanded joint no groove : S t,j =.5 S min min[ ( l t,x / d t ) ;.6 ] σ t,o shall be S t,j ( groove(s) ) one groove : S t,j =.6 S min with grooves > : S t,j =.8 S min Error(s) and/or warning(s) The thickness is acceptable AutoPIPE Vessel checking UHX-. Configuration d cylinder UHX-. ν factors. shell Ps = -5 psi Ds = in ts =.75 in Gs = 9 in Ss = 7 psi Sy,s = 8 psi Es = 8 psi Sps,s = psi channel Pt = 5 psi Dc = in tc =.75 in Gc = 9 in Sc = 7 psi Sy,c = 8 psi Ec = 8 psi Sps,c = psi tubesheet hnew =.45 in h =.8 in d= in AutoPIPE Vessel (Microprotol) procal V prodia V... Bentley Systems, Inc.