Key Design Engineering

Transcription

1 Key Design Engineering Northfield Dr. East Waterloo, ON N2K 3T6 COMPRESS Pressure Vessel Design Calculations Item: Sample Calculation: 36" ir Receiver Customer: BC Industries Job: KEY-Design-ir Receiver Sample Designer: Michael Rodgers Date: Monday, September 15, 2008

2 Table Of Contents 1. Deficiencies Summary 2. Nozzle Schedule 3. Nozzle Summary 4. Pressure Summary 5. Revision History 6. Settings Summary 7. Thickness Summary 8. Weight Summary 9. Hydrostatic Test 10. Vacuum Summary " Upper 2:1 Semi Elliptical head 12. Straight Flange on 36" Upper 2:1 Semi Elliptical head 13. N4 3000# 1" HC (N " OD 5/8" Shell 15. Legs 3 X 3 X 3/ # 1/2" HC (N " w/ 2" 300# RFWN (N " with 1 " RFWN (N5 19. Straight Flange on 36" Lower 2:1 Semi-Elliptical head " Lower 2:1 Semi-Elliptical head # 1" HC (N6 1/86

3 Deficiencies Summary No deficiencies found. 2/86

4 Nozzle Schedule Nozzle mark Service Size Nozzle Impact Norm Fine Grain Materials Pad Impact Norm Fine Grain Flange N1 3000# 1/2" HC 0.500" Class threaded S-234 WPB No No No N/ N/ N/ N/ N/ N3 2" w/ 2" 300# RFWN 2" Sch 80 (XS S-106 B Smls pipe No No No N/ N/ N/ N/ WN 105 Class 300 N4 N4 3000# 1" HC 1" Class threaded S-234 WPB No No No N/ N/ N/ N/ N/ N5 1 " with 1 " RFWN 1" Sch 80 (XS S-106 B Smls pipe No No No N/ N/ N/ N/ WN 105 Class 300 N6 3000# 1" HC 1" Class threaded S-234 WPB No No No N/ N/ N/ N/ N/ 3/86

5 Nozzle Summary Nozzle mark OD (in t n (in Req t n (in 1? 2? Nom t (in Shell Design t (in User t (in Reinforcement Pad Width (in t pad (in Corr (in a / r (% N Yes Yes 0.5 N/ N/ N/ 0 Exempt N Yes Yes 0.5 N/ N/ N/ 0 Exempt N Yes Yes 0.5* N/ N/ N/ 0 Exempt N Yes Yes 0.5 N/ N/ N/ 0 Exempt N Yes Yes 0.5* N/ N/ N/ 0 Exempt t n : Nozzle thickness Req t n : Nozzle thickness required per UG-45/UG-16 Nom t: Vessel wall thickness Design t: Required vessel wall thickness due to pressure + corrosion allowance per UG-37 User t: Local vessel wall thickness (near opening a : rea available per UG-37, governing condition r : rea required per UG-37, governing condition Corr: Corrosion allowance on nozzle wall * Head minimum thickness after forming 4/86

6 Pressure Summary Pressure Summary for Chamber bounded by 36" Lower 2:1 Semi-Elliptical head and 36" Upper 2:1 Semi Elliptical head Identifier P Design ( psi T Design ( F MWP ( psi MP ( psi MEP ( psi T e external ( F MDMT ( F MDMT Exemption Impact Tested 36" Upper 2:1 Semi Elliptical head Note 1 No Straight Flange on 36" Upper 2:1 Semi Elliptical head Note 2 No 36" OD 5/8" Shell Note 3 No Straight Flange on 36" Lower 2:1 Semi-Elliptical head Note 2 No 36" Lower 2:1 Semi-Elliptical head Note 1 No Legs 3 X 3 X 3/ N/ N/ N/ N/ N/ N/ 3000# 1/2" HC (N Note 4 No 2" w/ 2" 300# RFWN (N Note 5 No N4 3000# 1" HC (N Note 6 No 1 " with 1 " RFWN (N Note 5 No 3000# 1" HC (N Note 6 No Chamber design MDMT is -20 F Chamber rated MDMT is psi Chamber MWP hot & corroded is F Chamber MP cold & new is F Chamber MEP is F Vacuum rings did not govern the external pressure rating. Notes for MDMT Rating: Note # Exemption Details Material impact test exemption temperature from Fig UCS-66 Curve D = -55 F Fig UCS-66.1 MDMT reduction = 33.8 F, (coincident ratio = Rated MDMT is governed by UCS-66(b(2 Material impact test exemption temperature from Fig UCS-66 Curve D = -55 F Fig UCS-66.1 MDMT reduction = 33.1 F, (coincident ratio = Rated MDMT is governed by UCS-66(b(2 Material impact test exemption temperature from Fig UCS-66 Curve B = -7 F Fig UCS-66.1 MDMT reduction = 33.1 F, (coincident ratio = UCS-66 governing thickness = 0.5 in UCS-66 governing thickness = 0.5 in UCS-66 governing thickness = 0.5 in 4. Nozzle is impact test exempt to -155 F per UCS-66(b(3 (coincident ratio = Flange rating governs: UCS-66(b(1(b 6. Nozzle is impact test exempt to -155 F per UCS-66(b(3 (coincident ratio = Design notes are available on the Settings Summary page. 5/86

7 Revision History No. Date Operator Notes 0 9/ 3/2008 dministrator New vessel created SME Section VIII Division 1 [Build 6259] 6/86

8 Settings Summary COMPRESS Build 6259 Units: U.S. Customary Datum Line Location: 0.00" from bottom seam Design SME Section VIII Division 1, 2007 Edition Design or Rating: Minimum thickness: Design for cold shut down only: Design for lethal service (full radiography required: Design nozzles for: Corrosion weight loss: UG-23 Stress Increase: 1.20 Skirt/legs stress increase: 1.0 Minimum nozzle projection: 1" Juncture calculations for α > 30 only: Preheat P-No 1 Materials > 1.25&#34 and <= 1.50" thick: UG-37(a shell tr calculation considers longitudinal stress: Butt welds are tapered per Figure UCS-66.3(a. Hydro/Pneumatic Test Shop Hydrotest Pressure: Test liquid specific gravity: 1.00 Maximum stress during test: Required Marking - UG times vessel MWP 90% of yield Get Thickness from Pressure 1/16" per UG-16(b No No Design P, find nozzle MWP and MP 100% of theoretical loss Yes No No UG-116 (e Radiography: UG-116 (f Postweld heat treatment: RT3 None Code Cases\Interpretations Use Code Case 2547: No pply interpretation VIII : Yes pply interpretation VIII : Yes pply interpretation VIII : Yes pply interpretation VIII : Yes No UCS-66.1 MDMT reduction: No No UCS-68(c MDMT reduction: No Disallow UG-20(f exemptions: No 7/86

9 UG-22 Loadings UG-22 (a Internal or External Design Pressure : UG-22 (b Weight of the vessel and normal contents under operating or test conditions: UG-22 (c Superimposed static reactions from weight of attached equipment (external loads: UG-22 (d(2 Vessel supports such as lugs, rings, skirts, saddles and legs: UG-22 (f Wind reactions: UG-22 (f Seismic reactions: Note: UG-22 (b,(c and (f loads only considered when supports are present. Yes Yes No Yes No No 8/86

10 Thickness Summary Component Identifier Material Diameter (in Length (in Nominal t (in Design t (in Total Corrosion (in Joint E Load 36" Upper 2:1 Semi Elliptical head S OD * Internal Straight Flange on 36" Upper 2:1 Semi Elliptical head S OD Internal 36" OD 5/8" Shell S OD Internal Straight Flange on 36" Lower 2:1 Semi-Elliptical head S OD Internal 36" Lower 2:1 Semi-Elliptical head S OD * Internal Nominal t: Vessel wall nominal thickness Design t: Required vessel thickness due to governing loading + corrosion Joint E: Longitudinal seam joint efficiency * Head minimum thickness after forming Load internal: external: Wind: Seismic: Circumferential stress due to internal pressure governs External pressure governs Combined longitudinal stress of pressure + weight + wind governs Combined longitudinal stress of pressure + weight + seismic governs 9/86

11 Weight Summary Component Metal New* Metal Corroded* Weight ( lb Contributed by Vessel Elements Insulation & Supports Lining Piping + Liquid Operating Liquid Test Liquid 36" Upper 2:1 Semi Elliptical head " OD 5/8" Shell ,154 36" Lower 2:1 Semi-Elliptical head Legs 3 X 3 X 3/ TOTL: 1, , ,698.2 * Shells with attached nozzles have weight reduced by material cut out for opening. Weight ( lb Contributed by ttachments Component Body Flanges Nozzles & Flanges New Corroded New Corroded Packed Beds Ladders & Platforms Trays & Supports Rings & Clips Vertical Loads 36" Upper 2:1 Semi Elliptical head " OD 5/8" Shell " Lower 2:1 Semi-Elliptical head Legs 3 X 3 X 3/ TOTL: Vessel operating weight, Corroded: 1,540 lb Vessel operating weight, New: Vessel empty weight, Corroded: Vessel empty weight, New: Vessel test weight, New: 1,540 lb 1,540 lb 1,540 lb 4,238 lb Vessel center of gravity location - from datum - lift condition Vessel Lift Weight, New: 1,540 lb Center of Gravity: " Vessel Capacity Vessel Capacity** (New: 323 US gal Vessel Capacity** (Corroded: 323 US gal **The vessel capacity does not include volume of nozzle, piping or other attachments. 10/86

12 Hydrostatic Test Shop test pressure determination for Chamber bounded by 36" Lower 2:1 Semi-Elliptical head and 36" Upper 2:1 Semi Elliptical head based on MWP per UG-99(b Shop hydrostatic test gauge pressure is psi at 70 F (the chamber MWP = 375 psi The shop test is performed with the vessel in the horizontal position. Identifier Local test pressure psi Test liquid static head psi UG-99 stress ratio UG-99 pressure factor Stress during test psi llowable test stress psi Stress excessive? 36" Upper 2:1 Semi Elliptical head ( ,401 34,200 No Straight Flange on 36" Upper 2:1 Semi Elliptical head ,356 34,200 No 36" OD 5/8" Shell ,356 34,200 No Straight Flange on 36" Lower 2:1 Semi-Elliptical head ,356 34,200 No 36" Lower 2:1 Semi-Elliptical head ,401 34,200 No 1 " with 1 " RFWN (N ,707 47,250 No 2" w/ 2" 300# RFWN (N ,826 47,250 No 3000# 1" HC (N ,452 47,250 No 3000# 1/2" HC (N ,557 47,250 No N4 3000# 1" HC (N ,444 47,250 No Notes: (1 36" Upper 2:1 Semi Elliptical head limits the UG-99 stress ratio. (2 P L stresses at nozzle openings have been estimated using the method described in PVP-Vol. 399, pages (3 VIII-2, D-151.1(b used as the basis for nozzle allowable test stress. (4 The zero degree angular position is assumed to be up, and the test liquid height is assumed to the top-most flange. The field test condition has not been investigated for the Chamber bounded by 36" Lower 2:1 Semi-Elliptical head and 36" Upper 2:1 Semi Elliptical head. The test temperature of 70 F is warmer than the minimum recommended temperature of F so the brittle fracture provision of UG-99(h has been met. 11/86

13 Vacuum Summary Component Line of Support Elevation above Datum (in Length Le (in 36" Upper 2:1 Semi Elliptical head N/ - 1/3 depth of 36" Upper 2:1 Semi Elliptical head N/ Straight Flange on 36" Upper 2:1 Semi Elliptical head Top Straight Flange on 36" Upper 2:1 Semi Elliptical head Bottom " OD 5/8" Shell Top " OD 5/8" Shell Bottom Straight Flange on 36" Lower 2:1 Semi-Elliptical head Top Straight Flange on 36" Lower 2:1 Semi-Elliptical head Bottom /3 depth of 36" Lower 2:1 Semi-Elliptical head N/ 36" Lower 2:1 Semi-Elliptical head N/ Note For main components, the listed value of 'Le' is the largest unsupported length for the component. 12/86

14 SME Section VIII, Division 1, 2007 Edition 36" Upper 2:1 Semi Elliptical head Component: Ellipsoidal Head Material Specification: S (II-D p.18, ln. 22 Material impact test exemption temperature from Fig UCS-66 Curve D = -55 F Fig UCS-66.1 MDMT reduction = 33.8 F, (coincident ratio = Rated MDMT is governed by UCS-66(b(2 UCS-66 governing thickness = 0.5 in Internal design pressure: P = F External design pressure: P e = F Static liquid head: P s = 0 psi (SG=1, H s =0" Operating head P th = psi (SG=1, H s =39.5" Horizontal test head Corrosion allowance: Inner C = 0" Outer C = 0" Design MDMT = -20 F Rated MDMT = -55 F No impact test performed Material is normalized Material is not produced to fine grain practice PWHT is not performed Do not Optimize MDMT / Find MWP Radiography: Category joints - Spot UW-11(b Type 1 Head to shell seam - Spot UW-11(b Type 1 Estimated weight*: new = lb corr = lb Capacity*: new = 32.6 US gal corr = 32.6 US gal * includes straight flange Outer diameter = 36" Minimum head thickness = 0.5" Head ratio D/2h = 2 (new Head ratio D/2h = 2 (corroded Straight flange length L sf = 2" Nominal straight flange thickness t sf = 0.5" Results Summary The governing condition is internal pressure. Minimum thickness per UG-16 = " + 0" = " Design thickness due to internal pressure (t = " Design thickness due to external pressure (t e = " Maximum allowable working pressure (MWP = psi Maximum allowable pressure (MP = psi Maximum allowable external pressure (MEP = psi K (Corroded K=(1/6*[2 + (D / (2*h 2 ]=(1/6*[2 + (35 / (2* ]=1 13/86

15 K (New K=(1/6*[2 + (D / (2*h 2 ]=(1/6*[2 + (35 / (2* ]=1 Design thickness for internal pressure, (Corroded at 200 F ppendix 1-4(c t = P*D o *K / (2*S*E + 2*P*(K Corrosion = 375*36*1 / (2*20,000* *375*( = " The head internal pressure design thickness is ". Maximum allowable working pressure, (Corroded at 200 F ppendix 1-4(c P = 2*S*E*t / (K*D o - 2*t*(K P s = 2*20,000*0.85*0.5 / (1*36-2*0.5*( = psi The maximum allowable working pressure (MWP is psi. Maximum allowable pressure, (New at 70 F ppendix 1-4(c P = 2*S*E*t / (K*D o - 2*t*(K P s = 2*20,000*0.85*0.5 / (1*36-2*0.5*( = psi The maximum allowable pressure (MP is psi. Design thickness for external pressure, (Corroded at 200 F UG-33(d Equivalent outside spherical radius (R o R o = K o *D o = * 36 = in = / (R o /t = / ( / = From Table CS-2: B=5, psi P a = B/(R o /t = 5, /( / = 15 psi t = " + Corrosion = " + 0" = " Check the external pressure per UG-33(a(1 ppendix 1-4(c t = 1.67*P e *D o *K / (2*S*E + 2*1.67*P e *(K Corrosion = 1.67*15*36*1 / (2*20,000*1 + 2*1.67*15*( = " The head external pressure design thickness (t e is ". Maximum llowable External Pressure, (Corroded at 200 F UG-33(d Equivalent outside spherical radius (R o 14/86

16 R o = K o *D o = * 36 = in = / (R o /t = / ( /0.5 = From Table CS-2: B=14, psi P a = B/(R o /t = 14,962.51/( /0.5 = psi Check the Maximum External Pressure, UG-33(a(1 ppendix 1-4(c P = 2*S*E*t / ((K*D o - 2*t*(K - 0.1* P s2 = 2*20,000*1*0.5 / ((1*36-2*0.5*(1-0.1* = psi The maximum allowable external pressure (MEP is psi. % Extreme fiber elongation - UCS-79(d = (75*t / R f *(1 - R f / R o = (75*0.5 / 6.2*(1-6.2 / = % The extreme fiber elongation exceeds 5 percent. Heat treatment per UCS-56 may be required. See UCS-79(d(4 or (5. 15/86

17 SME Section VIII Division 1, 2007 Edition Straight Flange on 36" Upper 2:1 Semi Elliptical head Component: Straight Flange Material specification: S (II-D p. 18, ln. 22 Material impact test exemption temperature from Fig UCS-66 Curve D = -55 F Fig UCS-66.1 MDMT reduction = 33.1 F, (coincident ratio = Rated MDMT is governed by UCS-66(b(2 UCS-66 governing thickness = 0.5 in Internal design pressure: P = F External design pressure: P e = F Static liquid head: P th = 1.43 psi (SG = 1, H s = 39.5", Horizontal test head Corrosion allowance Inner C = 0" Outer C = 0" Design MDMT = -20 F Rated MDMT = -55 F No impact test performed Material is normalized Material is not produced to Fine Grain Practice PWHT is not performed Radiography: Longitudinal joint - Spot UW-11(b Type 1 Circumferential joint - Spot UW-11(b Type 1 Estimated weight New = 31.6 lb corr = 31.6 lb Capacity New = 8.33 US gal corr = 8.33 US gal OD = 36" Length L c = 2" t = 0.5" Design thickness, (at 200 F ppendix 1-1 t = P*R o / (S*E *P + Corrosion = 375*18 / (20,000* * = " Maximum allowable working pressure, (at 200 F ppendix 1-1 P = S*E*t / (R o *t - P s = 20,000*0.85*0.5 / ( *0.5-0 = psi Maximum allowable pressure, (at 70 F ppendix 1-1 P = S*E*t / (R o *t = 20,000*0.85*0.5 / ( *0.5 = psi External Pressure, (Corroded & at 200 F UG-28(c L / D o = / 36 = D o / t = 36 / = /86

18 From table G: = From table CS-2: B = 2,635 psi P a = 4*B / (3*(D o / t = 4* / (3*(36 / = 15 psi Design thickness for external pressure P a = 15 psi t a = t + Corrosion = = " Maximum llowable External Pressure, (Corroded & at 200 F UG-28(c L / D o = / 36 = D o / t = 36 / 0.5 = From table G: = From table CS-2: B = 12,613 psi P a = 4*B / (3*(D o / t = 4* / (3*(36 / 0.5 = psi % Extreme fiber elongation - UCS-79(d EFE = (50 * t / R f * (1 - R f / R o = (50 * 0.5 / * ( / = % Design thickness = " The governing condition is due to internal pressure. The cylinder thickness of 0.5" is adequate. Thickness Required Due to Pressure + External Loads Condition Pressure P ( psi llowable Stress Before UG-23 Stress Increase ( psi Temperature ( F Corrosion C (in Load Req'd Thk Due to Tension (in Req'd Thk Due to Compression (in S t S c Operating, Hot & Corroded ,000 16, Weight Operating, Hot & New ,000 16, Weight Hot Shut Down, Corroded 0 20,000 16, Weight Hot Shut Down, New 0 20,000 16, Weight Empty, Corroded 0 20,000 16, Weight Empty, New 0 20,000 16, Weight Vacuum ,000 16, Weight Hot Shut Down, Corroded, Weight & Eccentric Moments Only 0 20,000 16, Weight /86

19 llowable Compressive Stress, Hot and Corroded- S chc, (table CS-2 = / (R o / t = / (18 / 0.5 = B = 16,502 psi S = 20,000 / 1.00 = 20,000 psi S chc = min(b, S = 16,502 psi llowable Compressive Stress, Hot and New- S chn S chn = S chc = psi llowable Compressive Stress, Cold and New- S ccn, (table CS-2 = / (R o / t = / (18 / 0.5 = B = 16,502 psi S = 20,000 / 1.00 = 20,000 psi S ccn = min(b, S = 16,502 psi llowable Compressive Stress, Cold and Corroded- S ccc S ccc = S ccn = psi llowable Compressive Stress, Vacuum and Corroded- S cvc, (table CS-2 = / (R o / t = / (18 / 0.5 = B = 16,502 psi S = 20,000 / 1.00 = 20,000 psi S cvc = min(b, S = 16,502 psi Operating, Hot & Corroded, Bottom Seam t p = P*R / (2*S t *E c * P (Pressure = 375*17.5 / (2*20,000*1.00* * 375 = " t m = M / (π*r m2 *S t *E c (bending = 2 / (π* *20,000*1.00*0.85 = 0" t w = W / (2*π*R m *S t *E c (Weight = / (2*π*17.75*20,000*1.00*0.85 = " 18/86

20 t t = t p + t m - t w (total required, tensile = ( = 0.192" t c = t mc + t wc - t pc (total, net tensile = 0 + ( ( = 0.192" Maximum allowable working pressure, Longitudinal Stress P = 2*S t *E c *(t - t m + t w / (R *(t - t m + t w = 2*20,000*1.00*0.85*( ( / ( *( ( = psi Operating, Hot & New, Bottom Seam t p = P*R / (2*S t *E c * P (Pressure = 375*17.5 / (2*20,000*1.00* * 375 = " t m = M / (π*r m2 *S t *E c (bending = 2 / (π* *20,000*1.00*0.85 = 0" t w = W / (2*π*R m *S t *E c (Weight = / (2*π*17.75*20,000*1.00*0.85 = " t t = t p + t m - t w (total required, tensile = ( = 0.192" t c = t mc + t wc - t pc (total, net tensile = 0 + ( ( = 0.192" Maximum allowable working pressure, Longitudinal Stress P = 2*S t *E c *(t - t m + t w / (R *(t - t m + t w = 2*20,000*1.00*0.85*( ( / ( *( ( = psi Hot Shut Down, Corroded, Bottom Seam t p = 0" (Pressure t m = M / (π*r m2 *S c (bending = 2 / (π* *16,502.16*1.00 = 0" t w = W / (2*π*R m *S c (Weight = / (2*π*17.75*16,502.16*1.00 = " t t = t p + t m - t w (total, net compressive 19/86

21 = ( = " t c = t mc + t wc - t pc (total required, compressive = 0 + ( (0 = " Hot Shut Down, New, Bottom Seam t p = 0" (Pressure t m = M / (π*r m2 *S c (bending = 2 / (π* *16,502.16*1.00 = 0" t w = W / (2*π*R m *S c (Weight = / (2*π*17.75*16,502.16*1.00 = " t t = t p + t m - t w (total, net compressive = ( = " t c = t mc + t wc - t pc (total required, compressive = 0 + ( (0 = " Empty, Corroded, Bottom Seam t p = 0" (Pressure t m = M / (π*r m2 *S c (bending = 2 / (π* *16,502.16*1.00 = 0" t w = W / (2*π*R m *S c (Weight = / (2*π*17.75*16,502.16*1.00 = " t t = t p + t m - t w (total, net compressive = ( = " t c = t mc + t wc - t pc (total required, compressive = 0 + ( (0 = " Empty, New, Bottom Seam t p = 0" (Pressure t m = M / (π*r m2 *S c (bending = 2 / (π* *16,502.16*1.00 = 0" t w = W / (2*π*R m *S c (Weight = / (2*π*17.75*16,502.16* /86

22 = " t t = t p + t m - t w (total, net compressive = ( = " t c = t mc + t wc - t pc (total required, compressive = 0 + ( (0 = " Vacuum, Bottom Seam t p = P*R / (2*S c * P (Pressure = -15*17.5 / (2*16,502.16* * 15 = " t m = M / (π*r m2 *S c (bending = 2 / (π* *16,502.16*1.00 = 0" t w = W / (2*π*R m *S c (Weight = / (2*π*17.75*16,502.16*1.00 = " t t = t p + t m - t w (total, net compressive = ( = " t c = t mc + t wc - t pc (total required, compressive = 0 + ( ( = " Hot Shut Down, Corroded, Weight & Eccentric Moments Only, Bottom Seam t p = 0" (Pressure t m = M / (π*r m2 *S c (bending = 2 / (π* *16,502.16*1.00 = 0" t w = W / (2*π*R m *S c (Weight = / (2*π*17.75*16,502.16*1.00 = " t t = t p + t m - t w (total, net compressive = ( = " t c = t mc + t wc - t pc (total required, compressive = 0 + ( (0 = " 21/86

23 N4 3000# 1" HC (N4 SME Section VIII Division 1, 2007 Edition t w(lower = 0 in Leg 41 = in Note: round inside edges per UG-76(c Located on: 36" Upper 2:1 Semi Elliptical head Liquid static head included: 0 psi Nozzle material specification: S-234 WPB (II-D p. 14, ln. 7 Nozzle longitudinal joint efficiency: 1 Nozzle description: 1" Class threaded Nozzle orientation: 45 Calculated as hillside: no Local vessel minimum thickness: 0.5 in End of nozzle to datum line: in Nozzle inside diameter, new: in Nozzle nominal wall thickness: in Nozzle corrosion allowance: 0 in Projection available outside vessel, Lpr: 1 in Distance to head center, R: 8 in 22/86

24 Reinforcement Calculations for Internal Pressure The vessel wall thickness governs the MWP of this nozzle. UG-37 rea Calculation Summary (in 2 For P = F UG-45 Nozzle Wall Thickness Summary (in The nozzle passes UG-45 required available welds t req t min This nozzle is exempt from area calculations per UG-36(c(3(a UG-41 Weld Failure Path nalysis Summary The nozzle is exempt from weld strength calculations per UW-15(b(2 UW-16 Weld Sizing Summary Weld description Required weld throat size (in ctual weld throat size (in Status Nozzle to shell fillet (Leg weld size is adequate Calculations for internal pressure F Nozzle is impact test exempt to -155 F per UCS-66(b(3 (coincident ratio = Nozzle UCS-66 governing thk: in Nozzle rated MDMT: -155 F Limits of reinforcement per UG-40 Parallel to the vessel wall: Normal to the vessel wall outside: (R n + t n + t = in 2.5*(t n - C n + t e = in Nozzle required thickness per UG-27(c(1 t rn = P*R n /(S n *E - 0.6*P = *0.6575/(17,100*1-0.6* = in Required thickness t r from UG-37(a(c t r = P*K 1 *D o /(2*S*E + 0.8*P = *0.9*36/(2*20,000* * = 0.5 in 23/86

25 This opening does not require reinforcement per UG-36(c(3(a UW-16(c Weld Check Fillet weld: t min = lesser of 0.75 or t n or t = in t c(min = lesser of 0.25 or 0.7*t min = in t c(actual = 0.7*Leg = 0.7* = in The fillet weld size is satisfactory. Weld strength calculations are not required for this detail which conforms to Fig. UW-16.1, sketch (a. SME B16.11 Coupling Wall Thickness Check Interpretation VIII has been applied. Wall thickness req'd per SME B : t r1 = in (E =1 Wall thickness per UG-16(b: t r3 = in 24/86

26 vailable nozzle wall thickness new, t n = in The nozzle neck thickness is adequate. Reinforcement Calculations for MP The vessel wall thickness governs the MP of this nozzle. UG-37 rea Calculation Summary (in 2 For P = F UG-45 Nozzle Wall Thickness Summary (in The nozzle passes UG-45 required available welds t req t min This nozzle is exempt from area calculations per UG-36(c(3(a UG-41 Weld Failure Path nalysis Summary The nozzle is exempt from weld strength calculations per UW-15(b(2 UW-16 Weld Sizing Summary Weld description Required weld throat size (in ctual weld throat size (in Status Nozzle to shell fillet (Leg weld size is adequate Calculations for internal pressure F Limits of reinforcement per UG-40 Parallel to the vessel wall: Normal to the vessel wall outside: (R n + t n + t = in 2.5*(t n - C n + t e = in Nozzle required thickness per UG-27(c(1 t rn = P*R n /(S n *E - 0.6*P = *0.6575/(17,100*1-0.6* = in Required thickness t r from UG-37(a(c t r = P*K 1 *D o /(2*S*E + 0.8*P = *0.9*36/(2*20,000* * = 0.5 in This opening does not require reinforcement per UG-36(c(3(a 25/86

27 UW-16(c Weld Check Fillet weld: t min = lesser of 0.75 or t n or t = in t c(min = lesser of 0.25 or 0.7*t min = in t c(actual = 0.7*Leg = 0.7* = in The fillet weld size is satisfactory. Weld strength calculations are not required for this detail which conforms to Fig. UW-16.1, sketch (a. SME B16.11 Coupling Wall Thickness Check Interpretation VIII has been applied. Wall thickness req'd per SME B : t r1 = in (E =1 Wall thickness per UG-16(b: t r3 = in 26/86

28 vailable nozzle wall thickness new, t n = in The nozzle neck thickness is adequate. Reinforcement Calculations for External Pressure UG-37 rea Calculation Summary (in 2 For Pe = F UG-45 Nozzle Wall Thickness Summary (in The nozzle passes UG-45 required available welds t req t min This nozzle is exempt from area calculations per UG-36(c(3(a UG-41 Weld Failure Path nalysis Summary Weld strength calculations are not required for external pressure UW-16 Weld Sizing Summary Weld description Required weld throat size (in ctual weld throat size (in Status Nozzle to shell fillet (Leg weld size is adequate Calculations for external pressure F Limits of reinforcement per UG-40 Parallel to the vessel wall: Normal to the vessel wall outside: (R n + t n + t = in 2.5*(t n - C n + t e = in Nozzle required thickness per UG-28 t rn = in From UG-37(d(1 required thickness t r = in This opening does not require reinforcement per UG-36(c(3(a UW-16(c Weld Check Fillet weld: t min = lesser of 0.75 or t n or t = in t c(min = lesser of 0.25 or 0.7*t min = in t c(actual = 0.7*Leg = 0.7* = in The fillet weld size is satisfactory. 27/86

29 Weld strength calculations are not required for this detail which conforms to Fig. UW-16.1, sketch (a. UG-45 Nozzle Neck Thickness Check Interpretation VIII has been applied. Wall thickness per UG-45(a: Wall thickness per UG-45(b(2: Wall thickness per UG-16(b: Standard wall pipe per UG-45(b(4: The greater of t r2 or t r3 : The lesser of t r4 or t r5 : t r1 = in t r2 = in t r3 = in t r4 = in t r5 = in t r6 = in Required per UG-45 is the larger of t r1 or t r6 = in vailable nozzle wall thickness new, t n = in The nozzle neck thickness is adequate. External Pressure, (Corroded & at 200 F UG-28(c L / D o = / 1.75 = D o / t = 1.75 / = From table G: = From table CS-2: B = 16,063 psi P a = 4*B / (3*(D o / t = 4* / (3*(1.75 / = psi Design thickness for external pressure P a = psi t a = t + Corrosion = = " 28/86

30 36" OD 5/8" Shell SME Section VIII Division 1, 2007 Edition Component: Cylinder Material specification: S (II-D p. 18, ln. 22 Material impact test exemption temperature from Fig UCS-66 Curve B = -7 F Fig UCS-66.1 MDMT reduction = 33.1 F, (coincident ratio = UCS-66 governing thickness = 0.5 in Internal design pressure: P = F External design pressure: P e = F Static liquid head: P th = 1.43 psi (SG = 1, H s = 39.5", Horizontal test head Corrosion allowance Inner C = 0" Outer C = 0" Design MDMT = -20 F Rated MDMT = F No impact test performed Material is not normalized Material is not produced to Fine Grain Practice PWHT is not performed Radiography: Longitudinal joint - Spot UW-11(b Type 1 Top circumferential joint - Spot UW-11(b Type 1 Bottom circumferential joint - Spot UW-11(b Type 1 Estimated weight New = lb corr = lb Capacity New = US gal corr = US gal OD = 36" Length L c = 62" t = 0.5" Design thickness, (at 200 F ppendix 1-1 t = P*R o / (S*E *P + Corrosion = 375*18 / (20,000* * = " Maximum allowable working pressure, (at 200 F ppendix 1-1 P = S*E*t / (R o *t - P s = 20,000*0.85*0.5 / ( *0.5-0 = psi Maximum allowable pressure, (at 70 F ppendix 1-1 P = S*E*t / (R o *t = 20,000*0.85*0.5 / ( *0.5 = psi External Pressure, (Corroded & at 212 F UG-28(c L / D o = / 36 = D o / t = 36 / = /86

31 From table G: = From table CS-2: B = 2,635 psi P a = 4*B / (3*(D o / t = 4* / (3*(36 / = 15 psi Design thickness for external pressure P a = 15 psi t a = t + Corrosion = = " Maximum llowable External Pressure, (Corroded & at 212 F UG-28(c L / D o = / 36 = D o / t = 36 / 0.5 = From table G: = From table CS-2: B = 12,613 psi P a = 4*B / (3*(D o / t = 4* / (3*(36 / 0.5 = psi % Extreme fiber elongation - UCS-79(d EFE = (50 * t / R f * (1 - R f / R o = (50 * 0.5 / * ( / = % External Pressure + Weight Check (Bergman, SME paper P v = W / (2*π*R m + M / (π*r m2 = 1,217.8 / (2*π* / (π* = lb/in α = P v / (P e *D o n = 3 = / (15*36 = m = 1.23 / (L / D o 2 = 1.23 / ( / 36 2 = Ratio P e = (n m + m*α / (n m = ( * / ( = Ratio P e * P e MEP design cylinder thickness is satisfactory. 30/86

32 External Pressure + Weight Check at Bottom Seam (Bergman, SME paper P v = W / (2*π*R m + M / (π*r m2 = 1,217.8 / (2*π* / (π* = lb/in α = P v / (P e *D o n = 3 = / (15*36 = m = 1.23 / (L / D o 2 = 1.23 / ( / 36 2 = Ratio P e = (n m + m*α / (n m = ( * / ( = Ratio P e * P e MEP design cylinder thickness is satisfactory. Design thickness = " The governing condition is due to internal pressure. The cylinder thickness of 0.5" is adequate. Thickness Required Due to Pressure + External Loads Condition Pressure P ( psi llowable Stress Before UG-23 Stress Increase ( psi Temperature ( F Corrosion C (in Location Load Req'd Thk Due to Tension (in Req'd Thk Due to Compression (in S t S c Operating, Hot & Corroded ,000 16, Operating, Hot & New ,000 16, Hot Shut Down, Corroded 0 20,000 16, Hot Shut Down, New 0 20,000 16, Empty, Corroded 0 20,000 16, Empty, New 0 20,000 16, Vacuum ,000 16, Top Weight Bottom Weight Top Weight Bottom Weight Top Weight Bottom Weight Top Weight Bottom Weight Top Weight Bottom Weight Top Weight Bottom Weight Top Weight Bottom Weight Hot Shut Down, Corroded, Weight & Eccentric Moments Only 0 20,000 16, Top Weight Bottom Weight /86

33 llowable Compressive Stress, Hot and Corroded- S chc, (table CS-2 = / (R o / t = / (18 / 0.5 = B = 16,502 psi S = 20,000 / 1.00 = 20,000 psi S chc = min(b, S = 16,502 psi llowable Compressive Stress, Hot and New- S chn S chn = S chc = psi llowable Compressive Stress, Cold and New- S ccn, (table CS-2 = / (R o / t = / (18 / 0.5 = B = 16,502 psi S = 20,000 / 1.00 = 20,000 psi S ccn = min(b, S = 16,502 psi llowable Compressive Stress, Cold and Corroded- S ccc S ccc = S ccn = psi llowable Compressive Stress, Vacuum and Corroded- S cvc, (table CS-2 = / (R o / t = / (18 / 0.5 = B = 16,502 psi S = 20,000 / 1.00 = 20,000 psi S cvc = min(b, S = 16,502 psi Operating, Hot & Corroded, bove Support Point t p = P*R / (2*S t *E c * P (Pressure = 375*17.5 / (2*20,000*1.00* * 375 = " t m = M / (π*r m2 *S t *E c (bending = 219 / (π* *20,000*1.00*1.00 = 0" t w = W / (2*π*R m *S t *E c (Weight = 1,217.8 / (2*π*17.75*20,000*1.00*1.00 = " t t = t p + t m - t w (total required, tensile 32/86

34 = ( = " t c = t mc + t wc - t pc (total, net tensile = 0 + ( ( = " Maximum allowable working pressure, Longitudinal Stress P = 2*S t *E c *(t - t m + t w / (R *(t - t m + t w = 2*20,000*1.00*1.00*( ( / ( *( ( = 1, psi Operating, Hot & New, bove Support Point t p = P*R / (2*S t *E c * P (Pressure = 375*17.5 / (2*20,000*1.00* * 375 = " t m = M / (π*r m2 *S t *E c (bending = 219 / (π* *20,000*1.00*1.00 = 0" t w = W / (2*π*R m *S t *E c (Weight = 1,217.8 / (2*π*17.75*20,000*1.00*1.00 = " t t = t p + t m - t w (total required, tensile = ( = " t c = t mc + t wc - t pc (total, net tensile = 0 + ( ( = " Maximum allowable working pressure, Longitudinal Stress P = 2*S t *E c *(t - t m + t w / (R *(t - t m + t w = 2*20,000*1.00*1.00*( ( / ( *( ( = 1, psi Hot Shut Down, Corroded, bove Support Point t p = 0" (Pressure t m = M / (π*r m2 *S c (bending = 219 / (π* *16,502.16*1.00 = 0" t w = W / (2*π*R m *S c (Weight = 1,217.8 / (2*π*17.75*16,502.16*1.00 = " t t = t p + t m - t w (total, net compressive = ( /86

35 = " t c = t mc + t wc - t pc (total required, compressive = 0 + ( (0 = " Hot Shut Down, New, bove Support Point t p = 0" (Pressure t m = M / (π*r m2 *S c (bending = 219 / (π* *16,502.16*1.00 = 0" t w = W / (2*π*R m *S c (Weight = 1,217.8 / (2*π*17.75*16,502.16*1.00 = " t t = t p + t m - t w (total, net compressive = ( = " t c = t mc + t wc - t pc (total required, compressive = 0 + ( (0 = " Empty, Corroded, bove Support Point t p = 0" (Pressure t m = M / (π*r m2 *S c (bending = 219 / (π* *16,502.16*1.00 = 0" t w = W / (2*π*R m *S c (Weight = 1,217.8 / (2*π*17.75*16,502.16*1.00 = " t t = t p + t m - t w (total, net compressive = ( = " t c = t mc + t wc - t pc (total required, compressive = 0 + ( (0 = " Empty, New, bove Support Point t p = 0" (Pressure t m = M / (π*r m2 *S c (bending = 219 / (π* *16,502.16*1.00 = 0" t w = W / (2*π*R m *S c (Weight = 1,217.8 / (2*π*17.75*16,502.16*1.00 = " 34/86

36 t t = t p + t m - t w (total, net compressive = ( = " t c = t mc + t wc - t pc (total required, compressive = 0 + ( (0 = " Vacuum, bove Support Point t p = P*R / (2*S c * P (Pressure = -15*17.5 / (2*16,502.16* * 15 = " t m = M / (π*r m2 *S c (bending = 219 / (π* *16,502.16*1.00 = 0" t w = W / (2*π*R m *S c (Weight = 1,217.8 / (2*π*17.75*16,502.16*1.00 = " t t = t p + t m - t w (total, net compressive = ( = " t c = t mc + t wc - t pc (total required, compressive = 0 + ( ( = " Hot Shut Down, Corroded, Weight & Eccentric Moments Only, bove Support Point t p = 0" (Pressure t m = M / (π*r m2 *S c (bending = 219 / (π* *16,502.16*1.00 = 0" t w = W / (2*π*R m *S c (Weight = 1,217.8 / (2*π*17.75*16,502.16*1.00 = " t t = t p + t m - t w (total, net compressive = ( = " t c = t mc + t wc - t pc (total required, compressive = 0 + ( (0 = " Operating, Hot & Corroded, Below Support Point t p = P*R / (2*S t *E c * P (Pressure = 375*17.5 / (2*20,000*1.00* * 375 = " 35/86

37 t m = M / (π*r m2 *S t *E c (bending = 0 / (π* *20,000*1.00*1.00 = 0" t w = W / (2*π*R m *S t *E c (Weight = 1,217.8 / (2*π*17.75*20,000*1.00*1.00 = " t t = t p + t m - t w (total required, tensile = ( = " t c = t mc + t wc - t pc (total, net tensile = 0 + ( ( = " Maximum allowable working pressure, Longitudinal Stress P = 2*S t *E c *(t - t m + t w / (R *(t - t m + t w = 2*20,000*1.00*1.00*( ( / ( *( ( = 1, psi Operating, Hot & New, Below Support Point t p = P*R / (2*S t *E c * P (Pressure = 375*17.5 / (2*20,000*1.00* * 375 = " t m = M / (π*r m2 *S t *E c (bending = 0 / (π* *20,000*1.00*1.00 = 0" t w = W / (2*π*R m *S t *E c (Weight = 1,217.8 / (2*π*17.75*20,000*1.00*1.00 = " t t = t p + t m - t w (total required, tensile = ( = " t c = t mc + t wc - t pc (total, net tensile = 0 + ( ( = " Maximum allowable working pressure, Longitudinal Stress P = 2*S t *E c *(t - t m + t w / (R *(t - t m + t w = 2*20,000*1.00*1.00*( ( / ( *( ( = 1, psi Hot Shut Down, Corroded, Below Support Point t p = 0" (Pressure 36/86

38 t m = M / (π*r m2 *S c (bending = 0 / (π* *16,502.16*1.00 = 0" t w = W / (2*π*R m *S c (Weight = 1,217.8 / (2*π*17.75*16,502.16*1.00 = " t t = t p + t m - t w (total, net compressive = ( = " t c = t mc + t wc - t pc (total required, compressive = 0 + ( (0 = " Hot Shut Down, New, Below Support Point t p = 0" (Pressure t m = M / (π*r m2 *S c (bending = 0 / (π* *16,502.16*1.00 = 0" t w = W / (2*π*R m *S c (Weight = 1,217.8 / (2*π*17.75*16,502.16*1.00 = " t t = t p + t m - t w (total, net compressive = ( = " t c = t mc + t wc - t pc (total required, compressive = 0 + ( (0 = " Empty, Corroded, Below Support Point t p = 0" (Pressure t m = M / (π*r m2 *S c (bending = 0 / (π* *16,502.16*1.00 = 0" t w = W / (2*π*R m *S c (Weight = 1,217.8 / (2*π*17.75*16,502.16*1.00 = " t t = t p + t m - t w (total, net compressive = ( = " t c = t mc + t wc - t pc (total required, compressive = 0 + ( (0 = " 37/86

39 Empty, New, Below Support Point t p = 0" (Pressure t m = M / (π*r m2 *S c (bending = 0 / (π* *16,502.16*1.00 = 0" t w = W / (2*π*R m *S c (Weight = 1,217.8 / (2*π*17.75*16,502.16*1.00 = " t t = t p + t m - t w (total, net compressive = ( = " t c = t mc + t wc - t pc (total required, compressive = 0 + ( (0 = " Vacuum, Below Support Point t p = P*R / (2*S c * P (Pressure = -15*17.5 / (2*16,502.16* * 15 = " t m = M / (π*r m2 *S c (bending = 0 / (π* *16,502.16*1.00 = 0" t w = W / (2*π*R m *S c (Weight = 1,217.8 / (2*π*17.75*16,502.16*1.00 = " t t = t p + t m - t w (total, net compressive = ( = " t c = t mc + t wc - t pc (total required, compressive = 0 + ( ( = " Hot Shut Down, Corroded, Weight & Eccentric Moments Only, Below Support Point t p = 0" (Pressure t m = M / (π*r m2 *S c (bending = 0 / (π* *16,502.16*1.00 = 0" t w = W / (2*π*R m *S c (Weight = 1,217.8 / (2*π*17.75*16,502.16*1.00 = " t t = t p + t m - t w (total, net compressive = ( /86

40 = " t c = t mc + t wc - t pc (total required, compressive = 0 + ( (0 = " 39/86

41 Legs 3 X 3 X 3/8 Leg material: 38W Leg description: 3x3x1/4 Equal ngle (Leg in Number of legs: N = 3 Overall length: 36 in Base to girth seam length: 28.8 in Bolt circle: 44 in nchor bolt size: inch coarse threaded nchor bolt material: S-193-B7 nchor bolts/leg: 2 nchor bolt allowable stress: S b = 20,000 psi nchor bolt corrosion allowance: 0 in nchor bolt hole clearance: in Base plate width: 8 in Base plate length: 10 in Base plate thickness: Base plate allowable stress: 24,000 psi Foundation allowable bearing stress: 1,658 psi Effective length coefficient: K = 1.2 Coefficient: C m = 0.85 Leg yield stress: F y = 38,000 psi Leg elastic modulus: E = 29,000,000 psi in ( in required Leg to shell fillet weld: 0.25 in (0.003 in required Legs braced: No 40/86

42 Note: The support attachment point is assumed to be 1 in up from the cylinder circumferential seam. Loading Force attack angle Leg position xial end load lb f Shear resisted lb f xial f a psi Bending f bx psi Bending f by psi Ratio H 1-1 Ratio H 1-2 Governing Condition Weight operating corroded Moment = 18.2 lb-ft Loading Force attack angle Leg position xial end load lb f Shear resisted lb f xial f a psi Bending f bx psi Bending f by psi Ratio H 1-1 Ratio H 1-2 Weight empty corroded Moment = 18.2 lb-ft /86

43 Loading Force attack angle Leg position xial end load lb f Shear resisted lb f xial f a psi Bending f bx psi Bending f by psi Ratio H 1-1 Ratio H 1-2 Weight vacuum corroded Moment = 18.2 lb-ft Leg Calculations (ISC manual ninth edition xial end load, P 1 (Based on vessel total bending moment acting at leg attachment elevation 42/86

44 P 1 = W/N + 48*M t /(N*D = 1,540.24/ *18.2/( 3*36 = lb f llowable axial compressive stress, F a (ISC chapter E Local buckling check (ISC 5-99 b/t = (3/0.25 < (76 / Sqr(38 so Q s = 1 Flexural-torsional buckling (ISC Shear center distance w o = r o 2 = w o 2 + (I z + I w / = ( /1.44 = 2.75 in 2 Torsional constant J = 0.03 in 4 Shear modulus G = 11,165 ksi F ej = G*J / (*r o2 = 11,165,000*0.03 / (1.44* = 85 ksi K*l/r w = 1.2*26.8/ = F ew = π 2 *E/(Kl/r w 2 = π 2 *29,000/( = 380 ksi H = 1 - (w o 2 / r o2 = 1 - ( / = F e = ((F ew + F ej /(2*H*(1 - Sqr(1 - (4*F ew *F ej *H/(F ew + F ej 2 = (( /(2*0.6262*(1 - Sqr(1 - (4*380*85*0.6262/( = 77 ksi Equivalent slenderness ratio Kl/r = π*sqr(e/f e = π*sqr(29,000/77 = C c = Sqr(2*π 2 *E/(F y *Q s = Sqr(2*π 2 *29,000,000/(38,000*1 = K*l/r= 1.2*26.8/ = F a = 1 * (1 - (Kl/r 2 /(2*C c2 *F y / (5/3 + 3*(Kl/r/(8*C c -(Kl/r 3 /(8*C c3 = 1 * (1 - ( /(2* *38,000 / (5/3 + 3*( /(8* ( /(8* = 18,137 psi llowable axial compression and bending (ISC chapter H Note: r is divided by See ISC 6.1.4, pg /86

45 F ' ex = 1*12*π2 *E/(23*(Kl/r 2 = 1*12*π 2 *29,000,000/(23*( = 27,517 psi F ' ey = 1*12*π2 *E/(23*(Kl/r 2 = 1*12*π 2 *29,000,000/(23*( = 108,920 psi F b = 1*0.66*F y = 1*0.66*38,000 = 25,080 psi Compressive axial stress f a = P 1 / = /1.44 = 362 psi Bending stresses f bx = F*cos(α*L/(I x /C x + P 1 *E cc /(I x /C x = 0*abs(cos(120*26.8/(0.5002/ *0.9305/(0.5002/ = 903 psi f by = F*sin(α*L/(I y /C y = 0*sin(120*26.8/(1.98/2.12 = 0 psi ISC equation H 1-1 H 1-1 = f a /F a + C mx *f bx /((1 - f a /F ' ex *F bx + C my *f by /((1 - f a /F' ey *F by = 362/18, *903/((1-362/27,517*25, *0/((1-362/108,920*25,080 = ISC equation H 1-2 H 1-2 = f a /(0.6*1*F y + f bx /F bx + f by /F by = 362/(0.6*1*38, /25, /25,080 = , 3x3x1/4 Equal ngle legs are adequate. nchor bolts - Weight operating corroded condition governs Tensile loading per leg (2 bolts per leg R = 48*M/(N*BC - W/N = 48*18.2/(3*44-1,540.24/3 = lb f There is no net uplift (R is negative inch coarse threaded bolts are satisfactory. Check the leg to vessel fillet weld, Bednar 10.3, Weight operating corroded governs Note: continuous welding is assumed for all support leg fillet welds. 44/86

46 The following leg attachment weld analysis assumes the fillet weld is present on three sides (leg top closure plate is used. Z w = (2*b*d + d 2 /3 = (2*4.2426* /3 = in 2 J w = (b + 2*d 3 /12 - d 2 *(b + d 2 /(b + 2*d = ( *9.2 3 / *( /( *9.2 = in 3 E = d 2 /(b + 2*d = /( *9.2 = in Governing weld load f x = Cos(120*0 = 0 lb f Governing weld load f y = Sin(120*0 = 0 lb f f 1 = P 1 /L weld = / = lb f /in (V L direct shear f 2 = f y *L leg *0.5*b/J w = 0*26.8*0.5*4.2426/ = 0 lb f /in (V L torsion shear f 3 = f y /L weld = 0/ = 0 lb f /in (V c direct shear f 4 = f y *L leg *E/J w = 0*26.8*3.7381/ = 0 lb f /in (V c torsion shear f 5 = f x *L leg /Z w = 0*26.8/ = 0 lb f /in (M L bending f 6 = f x /L weld = 0/ = 0 lb f /in (Direct outward radial shear f = Sqr((f 1 + f (f 3 + f (f 5 + f 6 2 = Sqr(( ( ( = lb f /in (Resultant shear load Required leg to vessel fillet weld leg size (welded both sides + top t w = f / (0.707*0.55*S a = / (0.707*0.55*20,000 = in The 0.25 in leg to vessel attachment fillet weld size is adequate. Base plate thickness check, ISC /86

47 f p = P/(B*N = /(8*10 = 7 psi Required base plate thickness is the largest of the following: ( in t b = Sqr(0.5*P/S b = Sqr(0.5*520.04/24,000 = in t b = 0.5*(N - d*sqr(3*f p /S b = 0.5*(10-3*Sqr(3*7/24,000 = in The base plate thickness is adequate. Check the leg to vessel attachment stresses, WRC-107 (Weight operating corroded governs pplied Loads Radial load: P r = 0 lb f Circumferential moment: M c = 0 lb f -in Circumferential shear: V c = 0 lb f Longitudinal moment: M L = lb f -in Longitudinal shear: V L = lb f Torsion moment: M t = 0 lb f -in Internal pressure: P = 375 psi Mean shell radius: R m = in Local shell thickness: t = 0.5 in Shell yield stress: S y = 34,800 psi 46/86

48 Maximum stresses due to the applied loads at the leg edge (includes pressure R m /t =35.5 C 1 = , C 2 = in Local circumferential pressure stress = P*R i /t =13,125 psi Local longitudinal pressure stress = P*R i /2t =6,562 psi Maximum combined stress (P L +P b +Q = 13,209 psi llowable combined stress (P L +P b +Q = +-3*S = +-60,000 psi The maximum combined stress (P L +P b +Q is within allowable limits. Maximum local primary membrane stress (P L = 13,149 psi llowable local primary membrane (P L = +-1.5*S = +-30,000 psi The maximum local primary membrane stress (P L is within allowable limits. Stresses at the leg edge per WRC Bulletin 107 Figure value β u l B u B l C u C l D u D l 3C* C* C C * B* B Pressure stress* 13,125 13,125 13,125 13,125 13,125 13,125 13,125 13,125 Total circumferential stress 13,041 13,161 13,209 13,089 13,125 13,125 13,125 13,125 Primary membrane circumferential stress* 13,101 13,101 13,149 13,149 13,125 13,125 13,125 13,125 3C* C* C C * B* B Pressure stress* 6,562 6,562 6,562 6,562 6,562 6,562 6,562 6,562 Total longitudinal stress 6,483 6,603 6,641 6,521 6,562 6,562 6,562 6,562 Primary membrane longitudinal stress* 6,543 6,543 6,581 6,581 6,562 6,562 6,562 6,562 Shear from M t Circ shear from V c /86

49 Long shear from V L Total Shear stress Combined stress (P L +P b +Q 13,041 13,161 13,209 13,089 13,125 13,125 13,125 13,125 Note: * denotes primary stress. 48/86

50 3000# 1/2" HC (N1 SME Section VIII Division 1, 2007 Edition t w(lower = 0 in Leg 41 = in Note: round inside edges per UG-76(c Located on: 36" OD 5/8" Shell Liquid static head included: 0 psi Nozzle material specification: S-234 WPB (II-D p. 14, ln. 7 Nozzle longitudinal joint efficiency: 1 Nozzle description: 0.500" Class threaded Nozzle orientation: 0 Local vessel minimum thickness: 0.5 in Nozzle center line offset to datum line: 37 in End of nozzle to shell center: 20 in Nozzle inside diameter, new: 0.84 in Nozzle nominal wall thickness: in Nozzle corrosion allowance: 0 in Projection available outside vessel, Lpr: 2 in 49/86

51 Reinforcement Calculations for Internal Pressure The vessel wall thickness governs the MWP of this nozzle. UG-37 rea Calculation Summary (in 2 For P = F UG-45 Nozzle Wall Thickness Summary (in The nozzle passes UG-45 required available welds t req t min This nozzle is exempt from area calculations per UG-36(c(3(a UG-41 Weld Failure Path nalysis Summary The nozzle is exempt from weld strength calculations per UW-15(b(2 UW-16 Weld Sizing Summary Weld description Required weld throat size (in ctual weld throat size (in Status Nozzle to shell fillet (Leg weld size is adequate Calculations for internal pressure F Nozzle is impact test exempt to -155 F per UCS-66(b(3 (coincident ratio = Nozzle UCS-66 governing thk: in Nozzle rated MDMT: -155 F Limits of reinforcement per UG-40 Parallel to the vessel wall: Normal to the vessel wall outside: (R n + t n + t = in 2.5*(t n - C n + t e = in Nozzle required thickness per UG-27(c(1 t rn = P*R n /(S n *E - 0.6*P = *0.42/(17,100*1-0.6* = in Required thickness t r from UG-37(a t r = P*R o /(S*E + 0.4*P = *18/(20,000* * = in 50/86

52 This opening does not require reinforcement per UG-36(c(3(a UW-16(c Weld Check Fillet weld: t min = lesser of 0.75 or t n or t = in t c(min = lesser of 0.25 or 0.7*t min = in t c(actual = 0.7*Leg = 0.7* = in The fillet weld size is satisfactory. Weld strength calculations are not required for this detail which conforms to Fig. UW-16.1, sketch (a. SME B16.11 Coupling Wall Thickness Check Wall thickness req'd per SME B : t r1 = in (E =1 Wall thickness per UG-16(b: t r3 = in 51/86

53 vailable nozzle wall thickness new, t n = in The nozzle neck thickness is adequate. Reinforcement Calculations for MP The vessel wall thickness governs the MP of this nozzle. UG-37 rea Calculation Summary (in 2 For P = F UG-45 Nozzle Wall Thickness Summary (in The nozzle passes UG-45 required available welds t req t min This nozzle is exempt from area calculations per UG-36(c(3(a UG-41 Weld Failure Path nalysis Summary The nozzle is exempt from weld strength calculations per UW-15(b(2 UW-16 Weld Sizing Summary Weld description Required weld throat size (in ctual weld throat size (in Status Nozzle to shell fillet (Leg weld size is adequate Calculations for internal pressure F Limits of reinforcement per UG-40 Parallel to the vessel wall: Normal to the vessel wall outside: (R n + t n + t = in 2.5*(t n - C n + t e = in Nozzle required thickness per UG-27(c(1 t rn = P*R n /(S n *E - 0.6*P = *0.42/(17,100*1-0.6* = in Required thickness t r from UG-37(a t r = P*R o /(S*E + 0.4*P = *18/(20,000* * = in This opening does not require reinforcement per UG-36(c(3(a 52/86

54 UW-16(c Weld Check Fillet weld: t min = lesser of 0.75 or t n or t = in t c(min = lesser of 0.25 or 0.7*t min = in t c(actual = 0.7*Leg = 0.7* = in The fillet weld size is satisfactory. Weld strength calculations are not required for this detail which conforms to Fig. UW-16.1, sketch (a. SME B16.11 Coupling Wall Thickness Check Wall thickness req'd per SME B : t r1 = in (E =1 Wall thickness per UG-16(b: t r3 = in 53/86

55 vailable nozzle wall thickness new, t n = in The nozzle neck thickness is adequate. Reinforcement Calculations for External Pressure UG-37 rea Calculation Summary (in 2 For Pe = F UG-45 Nozzle Wall Thickness Summary (in The nozzle passes UG-45 required available welds t req t min This nozzle is exempt from area calculations per UG-36(c(3(a UG-41 Weld Failure Path nalysis Summary Weld strength calculations are not required for external pressure UW-16 Weld Sizing Summary Weld description Required weld throat size (in ctual weld throat size (in Status Nozzle to shell fillet (Leg weld size is adequate Calculations for external pressure F Limits of reinforcement per UG-40 Parallel to the vessel wall: Normal to the vessel wall outside: (R n + t n + t = in 2.5*(t n - C n + t e = in Nozzle required thickness per UG-28 t rn = in From UG-37(d(1 required thickness t r = 0.5 in This opening does not require reinforcement per UG-36(c(3(a UW-16(c Weld Check Fillet weld: t min = lesser of 0.75 or t n or t = in t c(min = lesser of 0.25 or 0.7*t min = in t c(actual = 0.7*Leg = 0.7* = in The fillet weld size is satisfactory. 54/86

56 Weld strength calculations are not required for this detail which conforms to Fig. UW-16.1, sketch (a. UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a: Wall thickness per UG-45(b(2: Wall thickness per UG-16(b: Standard wall pipe per UG-45(b(4: The greater of t r2 or t r3 : The lesser of t r4 or t r5 : t r1 = in t r2 = in t r3 = in t r4 = in t r5 = in t r6 = in Required per UG-45 is the larger of t r1 or t r6 = in vailable nozzle wall thickness new, t n = in The nozzle neck thickness is adequate. External Pressure, (Corroded & at 212 F UG-28(c L / D o = / = D o / t = / = From table G: = From table CS-2: B = 12,909 psi P a = 4*B / (3*(D o / t = 4* / (3*(1.125 / = psi Design thickness for external pressure P a = psi t a = t + Corrosion = = " 55/86

57 2" w/ 2" 300# RFWN (N3 SME Section VIII Division 1, 2007 Edition t w(lower = in Leg 41 = in Note: round inside edges per UG-76(c Located on: 36" OD 5/8" Shell Liquid static head included: 0 psi Nozzle material specification: S-106 B Smls pipe (II-D p. 14, ln. 5 Nozzle longitudinal joint efficiency: 1 Nozzle description: 2" Sch 80 (XS Flange description: 2 inch Class 300 WN 105 Bolt Material: S-193 B7 Bolt <= 2 1/2 (II-D p. 348, ln. 33 Flange rated MDMT: -55 F (UCS-66(b(1(b Liquid static head on flange: 0 psi SME B16.5 flange rating MWP: F SME B16.5 flange rating MP: F SME B16.5 flange hydro test: F Nozzle orientation: 180 Local vessel minimum thickness: 0.5 in Nozzle center line offset to datum line: 48 in End of nozzle to shell center: 27 in Nozzle inside diameter, new: in Nozzle nominal wall thickness: in Nozzle corrosion allowance: 0 in Projection available outside vessel, Lpr: 8.12 in Projection available outside vessel to flange face, Lf: 9 in 56/86

58 Reinforcement Calculations for Internal Pressure The vessel wall thickness governs the MWP of this nozzle. UG-37 rea Calculation Summary (in 2 For P = F UG-45 Nozzle Wall Thickness Summary (in The nozzle passes UG-45 required available welds t req t min This nozzle is exempt from area calculations per UG-36(c(3(a UG-41 Weld Failure Path nalysis Summary The nozzle is exempt from weld strength calculations per UW-15(b(2 UW-16 Weld Sizing Summary Weld description Required weld size (in ctual weld size (in Status Nozzle to shell fillet (Leg weld size is adequate Nozzle to shell groove (Lower weld size is adequate Calculations for internal pressure F Fig UCS-66.2 general note (1 applies. Nozzle is impact test exempt per UCS-66(d (NPS 4 or smaller pipe. Nozzle UCS-66 governing thk: in Nozzle rated MDMT: -155 F Limits of reinforcement per UG-40 Parallel to the vessel wall: Normal to the vessel wall outside: d = in 2.5*(t n - C n + t e = in Nozzle required thickness per UG-27(c(1 t rn = P*R n /(S n *E - 0.6*P = *0.9695/(17,100*1-0.6* = in Required thickness t r from UG-37(a t r = P*R o /(S*E + 0.4*P 57/86

59 = *18/(20,000* * = in This opening does not require reinforcement per UG-36(c(3(a UW-16(d Weld Check t min = lesser of 0.75 or t n or t = in t 1(min or t 2(min = lesser of 0.25 or 0.7*t min = in t 1(actual = 0.7*Leg = 0.7*0.218 = in The weld size t 1 is satisfactory. t 2(actual = in The weld size t 2 is satisfactory. t 1 + t 2 = >= 1.25*t min The combined weld sizes for t 1 and t 2 are satisfactory. UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a: t r1 = in (E =1 Wall thickness per UG-45(b(1: t r2 = in Wall thickness per UG-16(b: t r3 = in Standard wall pipe per UG-45(b(4: t r4 = in The greater of t r2 or t r3 : t r5 = in The lesser of t r4 or t r5 : t r6 = in 58/86

60 Required per UG-45 is the larger of t r1 or t r6 = in vailable nozzle wall thickness new, t n = 0.875*0.218 = in The nozzle neck thickness is adequate. Reinforcement Calculations for MP The vessel wall thickness governs the MP of this nozzle. UG-37 rea Calculation Summary (in 2 For P = F UG-45 Nozzle Wall Thickness Summary (in The nozzle passes UG-45 required available welds t req t min This nozzle is exempt from area calculations per UG-36(c(3(a UG-41 Weld Failure Path nalysis Summary The nozzle is exempt from weld strength calculations per UW-15(b(2 UW-16 Weld Sizing Summary Weld description Required weld size (in ctual weld size (in Status Nozzle to shell fillet (Leg weld size is adequate Nozzle to shell groove (Lower weld size is adequate Calculations for internal pressure F Limits of reinforcement per UG-40 Parallel to the vessel wall: Normal to the vessel wall outside: d = in 2.5*(t n - C n + t e = in Nozzle required thickness per UG-27(c(1 t rn = P*R n /(S n *E - 0.6*P = *0.9695/(17,100*1-0.6* = in Required thickness t r from UG-37(a t r = P*R o /(S*E + 0.4*P = *18/(20,000* * /86

61 = in This opening does not require reinforcement per UG-36(c(3(a UW-16(d Weld Check t min = lesser of 0.75 or t n or t = in t 1(min or t 2(min = lesser of 0.25 or 0.7*t min = in t 1(actual = 0.7*Leg = 0.7*0.218 = in The weld size t 1 is satisfactory. t 2(actual = in The weld size t 2 is satisfactory. t 1 + t 2 = >= 1.25*t min The combined weld sizes for t 1 and t 2 are satisfactory. UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a: t r1 = in (E =1 Wall thickness per UG-45(b(1: t r2 = in Wall thickness per UG-16(b: t r3 = in Standard wall pipe per UG-45(b(4: t r4 = in The greater of t r2 or t r3 : t r5 = in The lesser of t r4 or t r5 : t r6 = in 60/86

62 Required per UG-45 is the larger of t r1 or t r6 = in vailable nozzle wall thickness new, t n = 0.875*0.218 = in The nozzle neck thickness is adequate. Reinforcement Calculations for External Pressure UG-37 rea Calculation Summary (in 2 For Pe = F UG-45 Nozzle Wall Thickness Summary (in The nozzle passes UG-45 required available welds t req t min This nozzle is exempt from area calculations per UG-36(c(3(a UG-41 Weld Failure Path nalysis Summary Weld strength calculations are not required for external pressure UW-16 Weld Sizing Summary Weld description Required weld size (in ctual weld size (in Status Nozzle to shell fillet (Leg weld size is adequate Nozzle to shell groove (Lower weld size is adequate Calculations for external pressure F Limits of reinforcement per UG-40 Parallel to the vessel wall: Normal to the vessel wall outside: d = in 2.5*(t n - C n + t e = in Nozzle required thickness per UG-28 t rn = in From UG-37(d(1 required thickness t r = 0.5 in This opening does not require reinforcement per UG-36(c(3(a UW-16(d Weld Check t min = lesser of 0.75 or t n or t = in t 1(min or t 2(min = lesser of 0.25 or 0.7*t min = in 61/86

63 t 1(actual = 0.7*Leg = 0.7*0.218 = in The weld size t 1 is satisfactory. t 2(actual = in The weld size t 2 is satisfactory. t 1 + t 2 = >= 1.25*t min The combined weld sizes for t 1 and t 2 are satisfactory. UG-45 Nozzle Neck Thickness Check Wall thickness per UG-45(a: Wall thickness per UG-45(b(2: Wall thickness per UG-16(b: Standard wall pipe per UG-45(b(4: The greater of t r2 or t r3 : The lesser of t r4 or t r5 : t r1 = in t r2 = in t r3 = in t r4 = in t r5 = in t r6 = in Required per UG-45 is the larger of t r1 or t r6 = in vailable nozzle wall thickness new, t n = 0.875*0.218 = in The nozzle neck thickness is adequate. External Pressure, (Corroded & at 212 F UG-28(c L / D o = / = D o / t = / = From table G: = From table CS-2: B = 10,260 psi P a = 4*B / (3*(D o / t = 4* / (3*(2.375 / = psi Design thickness for external pressure P a = psi t a = t + Corrosion = = " 62/86

64 1 " with 1 " RFWN (N5 SME Section VIII Division 1, 2007 Edition t w(lower = 0 in Leg 41 = in Note: round inside edges per UG-76(c Located on: 36" OD 5/8" Shell Liquid static head included: 0 psi Nozzle material specification: S-106 B Smls pipe (II-D p. 14, ln. 5 Nozzle longitudinal joint efficiency: 1 Nozzle description: 1" Sch 80 (XS Flange description: 1 inch Class 300 WN 105 Bolt Material: S-193 B7 Bolt <= 2 1/2 (II-D p. 348, ln. 33 Flange rated MDMT: -55 F (UCS-66(b(1(b Liquid static head on flange: 0 psi SME B16.5 flange rating MWP: F SME B16.5 flange rating MP: F SME B16.5 flange hydro test: F Nozzle orientation: 0 Local vessel minimum thickness: 0.5 in Nozzle center line offset to datum line: 60 in End of nozzle to shell center: 22 in Nozzle inside diameter, new: in Nozzle nominal wall thickness: in Nozzle corrosion allowance: 0 in Projection available outside vessel, Lpr: 3.31 in Projection available outside vessel to flange face, Lf: 4 in 63/86