Attachment_D-1_-_Drawings_Total.pdf

Facilities The facilities will include Stanton Energy Center Combined Cycle Unit B, Unit 1 and Unit 2. All three facilities are located at 5100 South Alfaya Trail, Orlando, Florida, 32831.

This shall also include other natural gas system facilities as may be requested in the future via Amendment to contract or Time & Material rates.

The following are related to the Stanton Energy Center Combined Cycle Unit B:

Cathodic Protection Details

Drawing Number Sheet Revision

CP 101 1 of 1 AB CP 102 1 of 2 AB CP 102 2 of 2 AB CP 103 1 of 1 AB CP 104 1 of 1 AB CP 105 1 of 1 AB

Condensate Drain Tank

28376 1 of 1 0

Inlet Separator

Calculations R0 45 Pages Document Data Book 148 Pages Inlet Coalescing Filter Data Sheet 3 Pages B113053 1 Page 0 4560 D-113051-AB502076 1 Page 0 Series Peach Gemini Pura-SEP 405 2 Pages Specification Data Sheet 4 Pages

Instrument Gas Regulator

Instrument Regulator Diagram 1 Page

Manual Ball Valves

00S1814A 1 of 1 A 00S17255A 1 of 1 C 00S2032A 1 of 1 B 00S1621A 1 of 1 D 00S1725A 1 of 1 C

Drawing Number Sheet Revision

Outlet Separator

75H-13-336-24-740-WP SHELL CC 37 Pages 75H-13-336-24-740-WP SUMP CC 9 Pages Documentation Data Book 130 Pages 4151 D-112865 1 Page 1 B112945 1 Page 0 4149 D-112843 1 Page 2 Series 75 H&V 2 Pages Specification Data Sheet 4 Pages

Piping Design

SOCO-13908-001 1 of 2 1 SOCO-13908-002 2 of 2 1 SOCO-13908-003 1 of 1 1 SOCO-13908-004 1 of 1 1 SOCO-13908-005 1 of 1 1 SOCO-13908-006 1 of 1 1 SOCO-13908-500 1 of 1 1 SOCO-13908-500-1 1 of 1 1 SOCO-13908-500-2 1 of 1 1 SOCO-13908-500-3 1 of 1 1 SOCO-13908-1000 1 of 1 1 SOCO-13908-1001 1 of 1 1 SOCO-13908-200 1 of 1 2 SOCO-13908-400 1 of 1 1 SOCO-13908-400-1 1 of 1 1 SOCO-13908-400-2 1 of 1 1 SOCO-13908-400-3 1 of 1 2 SOCO-13908-401 1 of 1 2 SOCO-13908-401-1 1 of 1 1 SOCO-13908-401-2 1 of 1 1 SOCO-13908-700 1 of 1 1

Regulator Valves

GG03331-81 1 of 1 A GG03331-83 1 of 1 A

Drawing Number Sheet Revision

Station Grounding Details

SOCO-13908-200 1 of 1 A SOCO-13908-201 1 of 1 2 SOCO-13908-201-1 1 of 1 0 SOCO-13908-201-2 1 of 1 0

I N

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PERRY EQUIPMENT CORPORATION

AN ISO 9001 COMPANY

ENGINEERED FILTRATION TECHNOLOGIES

PEACH ®

GEMINI PURA-SEP ®

Horizontal Type Series PGCPH

The access to the elements is through a full end opening PECO Quick Opening Closure, located at the inlet end of the vessel.

These horizontal vessels are of a double horizontal barrel design, each with two compartments. The upper barrel provides the filtration-coalescer-separation of the solids and liquids, while the lower barrel collects the liquid. Some of the solids will drain into the lower barrel below the first stage, but most of the solids collect on the elements and on the bottom of the first stage upper barrel.

The wet, dirty gas to be cleaned enters the vessel through the inlet nozzle and encounters the pipe risers.

Here the free liquids fall to the bottom and flow into the first stage sump. Large droplets strike the pipe risers by inertial impaction and then coalesce on the pipe risers and make their way to the bottom of the first stage and into the sump for removal. This removes droplets greater than 100 micron in size.

The gas with solid particulate and liquid droplets then must travel from the outside of the element to the core in order to move into the second stage of the vessel. Here most particulate is removed and the liquid droplets greater that 0.5 to 1.0 micron are removed by direct interception and coalescing.

The gas then travels into the second stage in the core of the element. The liquid is drained through the element. The remaining aerosols see another stage of coalescing as the gas travels from the inside of the element to the outside. This coalesces droplets as small as 0.3 micron.

From here the secret to the operation of the vessel is to keep this liquid from re-entraing in the gas and to allow the clean gas to flow out the outlet nozzle. There are several devices in the second stage that make this possible. The first device is the louvered impingement baffle or LIB. This stainless steel baffle allows the gas to flow from the gas element while the liquid droplets settle to the bottom of the second stage into the second stage sump. It is critical to achieving the performance required while in a horizontal configuration.

The large droplets of coalesced liquid impact the LIB while the gas is released and travels out the back end of the vessel.

A stilling screen installed in the bottom of the second stage prevents the gas from re-entraining the liquid that collects in the bottom of the second stage as it flows into the sump. Finally, the outlet nozzle, which is placed in the top of the second stage, projects into the vessel. This prevents liquid, which may creep along the vessel wall, from going out the outlet pipe.

PRINCIPAL OF OPERATION

The PEACH® Gemini Pura-Sep® is two-stage filter-coalescer used for removing solids and liquids from a natural gas stream. The uniqueness of this design is that one replaceable element acts as both the primary an secondary stage, with a element support plate separating the two stages. This provides dual stage coalescing. This portion of the element is inside a Louvered Impingement Baffle (LIB). This LIB is a stainless steel louvered cylinder placed in the second stage of the vessel. However, if it becomes plugged, it is easily removed from the primary stage of the vessel. It can then be cleaned and/or replaced.

Administrator Information Only

OPERATING INSTRUCTIONS

CHANGING THE ELEMENTS

1. The elements must become completely saturated before they will begin stripping liquids. This may take 24 hours or longer, depending on the amount of free liquid in the gas stream.

2. Under no circumstances the vessel to be back-flowed. Back-flowing will damage the internals.

3. If a unit has been flowing at a capacity far lower than the design capacity, it is recommended to take the vessel offline and clean it before increasing to maximum capacity.

4. Do not clean the unit with steam injected directly onto the elements.

5. If the solids removed from the gas cause combustion with air, it is recommended to flood the vessel offline and clean it before increasing to maximum capacity.

6. If the unit has been operating for any length of time, it is recommended to open the drain in the primary and secondary stage to remove any condensate that may have collected there.

1. Blow down the vessel and prepare the vessel to be opened following the COMPANY procedures. Once the operator is assured that the pressure in the vessel is 0 psig, then go to step 2.

2. Open the closure following the Manufacturer’s instructions. It is critical that the procedures for the closure be followed, in order to assure safe and efficient operation. For a PECO closure, the instructions are found in the PECO Quick Opening Closure Operating Instructions, PECO Quick Opening Closure Operating Instructions (6” to 8”) or PECO Safelock Operating Instructions.

3. Remove the inlet support grid. This is done by removing the clevis pins, which attach the inlet support grid to the vessel wall. In larger vessels, the inlet support grid may be more than one piece to make removal easier. In these vessels the pieces of the support grid are held together using bolts and fixed nuts. Therefore, bolts should be removed after the clevis pins are removed. The inlet support grid is then removed from the vessel.

4. Remove the elements by pulling the element straight outward. You will note that the inlet end cap of the element is colored and the outlet end cap is white.

5. Clean the interior of the vessel, as required, by removing solids and liquids that have collected.

6. Install the clean elements, being sure that the chevron seal located on the element seal ring which is placed near the center of the element is properly placed. The larger OD of the chevron seal should be on the inlet side of the element.

A. As noted above the second stage end of the element has a white end cap. This end cap is inserted first through the riser pipe and into the second stage.

B. The chevron seal must seat inside the riser pipe to obtain a seal on the element and not allow a bypass around the element. The bayonets on the end caps are also of a different size to help assure that the element is placed properly.

7. After all of the elements are installed, replace the inlet support grid. This is done by placing it in the vessel in such a manner that the bayonets on the inlet end caps (these are the colored ones) go through the appropriate hole in the support grid.

8. The grid is then secured to the vessel by replacing the clevis pins once the support clips attached to the vessel have been brought through the appropriate hole in the inlet support grid. In larger vessels the bolts connecting the sections must also be replaced and tightened.

9. Once everything is completed, the elements change out is complete and the closure may be closed. Remember all of the end caps that are seen through the inlet support grid should be the same length and should be colored.

10. Again the closure manufacturer’s operating instructions must be followed in cleaning, inspecting, and closing the closure.

11. Care must be taken during the re-pressuring of the vessel so that gas does not flow through the vessel from outlet to inlet, thus resulting in a back flow condition. This can damage the internals of the vessel

IF ANY DIFFICULTIES ARE EXPERIENCED WITH THE UNIT, PLEASE CONTACT PECO OR YOUR REPRESENTATIVE

1. Please follow all COMPANY/CONTRACTOR PROCEDURES and SAFETY RULES while installing the vessel.

2. Review the vessel drawings and locate all of the connection’s elevations and orientations.

3. For horizontal vessels, the liquid level control equipment will be installed on both the primary and secondary sections of the lower barrel.

4. A direct reading differential pressure gauge should be installed across the element support plate. This is necessary

To know when to change out the elements. The inlet section (primary stage) is the high pressure side, and the outlet section (secondary stage) is the low pressure side. Pressure drop is the only immediate indication that the element require changing.

5. Connect the upstream piping to the vessel inlet and the downstream piping to the outlet.

6. Connect all of the piping in the inlet and outlet sections independently. Do not interconnect the drain piping without using a check valve. Do not manifold the control equipment between the first and second stage as this will cause a bypass of the internals.

7. Once the piping is completed, the vessel is ready to be checked out for any leaks.

8. Following the COMPANY procedures, slowly purge the vessel of all air, then check for leaks.

9. The vessel is ready to be pressurized and placed on stream.

INSTALLATION OF THE VESSEL

PERRY EQUIPMENT CORPORATION

118 Washington Street

Wolters Industrial Park

Mineral Wells, TX 76067

800-877-7326

COMPRESS Pressure Vessel Design Calculations

PECO PROJECT MW-502076 UPPER BARRELL CALCULATIONS

Customer: SOUTHERN COMPANY

Purchase Order No.: 5012242-0000

Vessel Model No.: PGCPH-7-373-22-1480

Peco Item No.: 4560

Project Coordinator: CHARLES MAYS

Date: Wednesday, January 07, 2009

2/6/2009PGCPH-7-373-22-1480 SHELL

CERTIFIED FINAL

Table Of Contents

1. Revision History

2. 22" I.D. SHELL

3. 2:1 ELLIPTICAL HEAD

4. INLET (IN)

5. OUTLET (OUT)

6. SHELL DOWNCOMER (DCMR)

7. SADDLE SUPPORTS

2/6/2009PGCPH-7-373-22-1480 SHELL

Revision History

No. Date Operator Notes

0 1/ 7/2009 CHARLES MAYS FIRST ISSUE

22" I.D. SHELL

ASME Section VIII Division 1, 2007 Edition

Material is impact test exempt per UG-20(f) UCS-66 governing thickness = 1 in

Internal design pressure: P = 1,480 psi @ 100 °F

Static liquid head:

Design thickness, (at 100 °F) UG-27(c)(1)

Maximum allowable working pressure, (at 100 °F) UG-27(c)(1)

Maximum allowable pressure, (at 70 °F) UG-27(c)(1)

% Extreme fiber elongation - UCS-79(d)

Component: Cylinder Material specification: SA-516 70 (II-D p. 18, ln. 22)

Pth =1.19 psi (SG = 1, Hs = 33", Horizontal test head)

Corrosion allowance Inner C = 0.0625" Outer C = 0"

Design MDMT = -20 °F No impact test performed Rated MDMT = -20 °F Material is not normalized

Material is not produced to Fine Grain Practice PWHT is not performed

Radiography: Longitudinal joint - Full UW-11(a) Type 1 Left circumferential joint - Full UW-11(a) Type 1 Right circumferential joint - Full UW-11(a) Type 1

Estimated weight New = 1,963.1 lb corr = 1,845.4 lb

Capacity New = 157.98 US gal corr = 159.78 US gal

ID = 22"

Length Lc = 96" t = 1" t = P*R / (S*E - 0.60*P) + Corrosion = 1,480*11.0625 / (20,000*1.00 - 0.60*1,480) + 0.0625 = 0.9192"

P = S*E*t / (R + 0.60*t) - Ps = 20,000*1.00*0.9375 / (11.0625 + 0.60*0.9375) - 0 = 1,612.9 psi

P = S*E*t / (R + 0.60*t) = 20,000*1.00*1 / (11 + 0.60*1) = 1,724.14 psi

EFE = (50*t / Rf)*(1 - Rf / Ro)

= (50*1 / 11.5)*(1 - 11.5 / ∞)

= 4.3478%

The extreme fiber elongation does not exceed 5%.

Allowable Compressive Stress, Hot and Corroded- ScHC, (table CS-2)

A = 0.125 / (Ro / t)

= 0.125 / (12 / 0.9375)

= 0.009766

B = 17,365 psi

S = 20,000 / 1.00 = 20,000 psi

ScHC = min(B, S) = 17,365 psi

Allowable Compressive Stress, Hot and New- ScHN, (table CS-2)

= 0.125 / (12 / 1)

= 0.010417

B = 17,381 psi

ScHN = min(B, S) = 17,381 psi

Allowable Compressive Stress, Cold and New- ScCN, (table CS-2)

= 0.125 / (12 / 1)

= 0.010417

B = 17,381 psi

ScCN = min(B, S) = 17,381 psi

Allowable Compressive Stress, Cold and Corroded- ScCC, (table CS-2)

= 0.125 / (12 / 0.9375)

= 0.009766

B = 17,365 psi

ScCC = min(B, S) = 17,365 psi

Allowable Compressive Stress, Vacuum and Corroded- ScVC, (table CS-2)

= 0.125 / (12 / 0.9375)

= 0.009766

B = 17,365 psi

S = 20,000 / 1.00 = 20,000 psi

ScVC = min(B, S) = 17,365 psi

2:1 ELLIPTICAL HEAD

ASME Section VIII, Division 1, 2007 Edition

Straight Flange governs MDMT

Internal design pressure: P = 1,480 psi @ 100 °F

Static liquid head:

Ps= 0 psi (SG=1, Hs=0" Operating head)

Pth= 1.1912 psi (SG=1, Hs=33" Horizontal test head)

* includes straight flange

* includes straight flange if applicable

Results Summary

Design thickness for internal pressure, (Corroded at 100 °F) Appendix 1-4(c)

Component: Ellipsoidal Head

Material Specification: SA-516 70 (II-D p.18, ln. 22)

Corrosion allowance: Inner C = 0.0625" Outer C = 0"

Design MDMT = -20°F No impact test performed

Rated MDMT = -20°F Material is not normalized

Material is not produced to fine grain practice

PWHT is not performed

Do not Optimize MDMT / Find MAWP

Radiography: Category A joints - Seamless No RT

Head to shell seam - Full UW-11(a) Type 1

Estimated weight*: new = 205 lb corr = 192.6 lb

Capacity*: new = 9.3 US gal corr = 9.5 US gal

Inner diameter = 22" Minimum head thickness = 0.937" Head ratio D/2h = 2 (new) Head ratio D/2h = 1.9888 (corroded) Straight flange length Lsf = 2"

Nominal straight flange thickness tsf = 1"

Insulation thk*: 0" density: 0 lb/ft3 weight: 0 lb

Insulation support ring spacing: 0" individual weight: 0 lb total weight: 0 lb

The governing condition is internal pressure.

Minimum thickness per UG-16 = 0.0625" + 0.0625" = 0.125" Design thickness due to internal pressure (t) = 0.8811" Maximum allowable working pressure (MAWP) = 1,580.33 psi Maximum allowable pressure (MAP) = 1,689.25 psi

K (Corroded)

K = (1/6)*[2 + (D / (2*h))2]

= (1/6)*[2 + (22.125 / (2*5.5625))2] = 0.99253

K (New)

K = (1/6)*[2 + (D / (2*h))2]

= (1/6)*[2 + (22 / (2*5.5))2] = 1

The head internal pressure design thickness is 0.8811".

Maximum allowable working pressure, (Corroded at 100 °F) Appendix 1-4(c)

The maximum allowable working pressure (MAWP) is 1,580.33 psi.

Maximum allowable pressure, (New at 70 °F) Appendix 1-4(c)

The maximum allowable pressure (MAP) is 1,689.25 psi.

The extreme fiber elongation exceeds 5 percent and the thickness exceeds 5/8 inch;. Heat treatment per UCS-56 is required if fabricated by cold forming.

t = P*D*K / (2*S*E - 0.2*P) + Corrosion = 1,480*22.125*0.99253 / (2*20,000*1 - 0.2*1,480) + 0.0625 = 0.8811"

P = 2*S*E*t / (K*D + 0.2*t) - Ps = 2*20,000*1*0.8745 / (0.99253*22.125 +0.2*0.8745) - 0 = 1,580.33 psi

P = 2*S*E*t / (K*D + 0.2*t) - Ps = 2*20,000*1*0.937 / (1*22 +0.2*0.937) - 0 = 1,689.25 psi

EFE = (75*t / Rf)*(1 - Rf / Ro)

= (75*1 / 4.24)*(1 - 4.24 / ∞)

= 17.6887%

INLET (IN)

Note: round inside edges per UG-76(c) tw(lower) = 1 in

Leg41 = 0.375 in tw(upper) = 1 in

Leg42 = 0.5625 in

Dp = 13.625 in te = 1 in

Located on: 22" I.D. SHELL

Liquid static head included: 0 psi

Nozzle material specification: SA-106 C Smls pipe (II-D p. 18, ln. 28)

Nozzle longitudinal joint efficiency: 1

Nozzle description: 8" Sch 80 (XS)

Pad material specification: SA-516 70 (II-D p. 18, ln. 22)

Pad diameter: 13.625 in

Flange description: 8 inch Class 600 WN A105

Bolt Material: SA-193 B7 Bolt <= 2 1/2 (II-D p. 348, ln. 33)

Flange rated MDMT: -20°F

(UCS-66(b)(1)(b))

Liquid static head on flange: 0 psi

ASME B16.5 flange rating MAWP: 1480 psi @ 100°F

ASME B16.5 flange rating MAP: 1480 psi @ 70°F

ASME B16.5 flange hydro test: 2225 psi @ 70°F

Nozzle orientation: 0°

Local vessel minimum thickness: 1 in

Nozzle center line offset to datum line: 54 in

End of nozzle to shell center: 22 in

Nozzle inside diameter, new: 7.625 in

Nozzle nominal wall thickness: 0.5 in

Nozzle corrosion allowance: 0.0625 in

Projection available outside vessel, Lpr: 7.56 in

Projection available outside vessel to flange face, Lf: 10 in

Pad is split: no

Reinforcement Calculations for Internal Pressure

The attached ASME B16.5 flange limits the nozzle MAWP.

Calculations for internal pressure 1480 psi @ 100 °F

Fig UCS-66.2 general note (1) applies.

Nozzle impact test exemption temperature from Fig UCS-66 Curve B = -13 °F Fig UCS-66.1 MDMT reduction = 20 °F, (coincident ratio = 0.8002).

Pad is impact test exempt per UG-20(f).

Limits of reinforcement per UG-40

Nozzle required thickness per UG-27(c)(1)

Required thickness tr from UG-37(a)

UG-37 Area Calculation Summary (in2)

For P = 1480 psi @ 100 °F The opening is adequately reinforced

UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45

A required A available A1 A2 A3 A5

A welds treq tmin

6.6391 6.6589 0.6265 0.5754 -- 5 0.457 0.3626 0.4375

UG-41 Weld Failure Path Analysis Summary (lbf)

All failure paths are stronger than the applicable weld loads

Weld load

W

Weld load

W1-1 Path 1-1 strength

Weld load

W2-2 Path 2-2 strength

Weld load

W3-3 Path 3-3 strength

121,667 120,648 196,752.06 30,726.25 438,281.63 137,054.25 305,959.22

UW-16 Weld Sizing Summary

Weld description Required weld size (in) Actual weld size (in) Status

Nozzle to pad fillet (Leg41) 0.25 0.2625 weld size is adequate

Pad to shell fillet (Leg42) 0.375 0.3938 weld size is adequate

Nozzle to pad groove (Upper) 0.3063 1 weld size is adequate

Nozzle UCS-66 governing thk: 0.4375 in

Nozzle rated MDMT: -33 °F

Pad UCS-66 governing thickness: 1 in

Pad rated MDMT: -20 °F

Parallel to the vessel wall: d = 7.75 in

Normal to the vessel wall outside: 2.5*(tn - Cn) + te = 2.0938 in trn = P*Rn/(Sn*E - 0.6*P)

= 1,480.001*3.875/(20,000*1 - 0.6*1,480.001)

= 0.3001 in tr = P*R/(S*E - 0.6*P)

= 1,480.001*11.0625/(20,000*1 - 0.6*1,480.001)

Area required per UG-37(c)

Allowable stresses: Sn = 20,000, Sv = 20,000, Sp = 20,000 psi fr1 = lesser of 1 or Sn/Sv = 1 fr2 = lesser of 1 or Sn/Sv = 1 fr3 = lesser of fr2 or Sp/Sv = 1 fr4 = lesser of 1 or Sp/Sv = 1

Area available from FIG. UG-37.1

A1 = larger of the following= 0.6265 in

A2 = smaller of the following= 0.5754 in

As Area >= A the reinforcement is adequate.

UW-16(c)(2) Weld Check

= 0.8567 in

A = d*tr*F + 2*tn*tr*F*(1 - fr1)

= 7.75*0.8567*1 + 2*0.4375*0.8567*1*(1 - 1)

= 6.6391 in2

= d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1)

= 7.75*(1*0.9375 - 1*0.8567) - 2*0.4375*(1*0.9375 - 1*0.8567)*(1 - 1)

= 0.6265 in2

= 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1)

= 2*(0.9375 + 0.4375)*(1*0.9375 - 1*0.8567) - 2*0.4375*(1*0.9375 - 1*0.8567)*(1 - 1)

= 0.2223 in2

= 5*(tn - trn)*fr2*t

= 5*(0.4375 - 0.3001)*1*0.9375

= 0.6441 in2

= 2*(tn - trn)*(2.5*tn + te)*fr2

= 2*(0.4375 - 0.3001)*(2.5*0.4375 + 1)*1

= 0.5754 in2

A41 = Leg2*fr3

= 0.3752*1

= 0.1406 in2

A42 = Leg2*fr4

= 0.56252*1

= 0.3164 in2

A5 = (Dp - d - 2*tn)*te*fr4

= (13.625 - 7.75 - 2*0.4375)*1*1

= 5 in2

Area = A1 + A2 + A41 + A42 + A5

= 0.6265 + 0.5754 + 0.1406 + 0.3164 + 5

= 6.6589 in2

Inner fillet: tmin = lesser of 0.75 or tn or te = 0.4375 in

UG-45 Nozzle Neck Thickness Check

Required per UG-45 is the larger of tr1 or tr6 = 0.3626 in

Available nozzle wall thickness new, tn = 0.875*0.5 = 0.4375 in

The nozzle neck thickness is adequate.

Allowable stresses in joints UG-45(c) and UW-15(c)

Strength of welded joints:

(1) Inner fillet weld in shear

(π/2)*Nozzle OD*Leg*Si = (π/2)*8.625*0.375*9,800 = 49,789.34 lbf

(2) Outer fillet weld in shear

(π/2)*Pad OD*Leg*So = (π/2)*13.625*0.5625*9,800 = 117,979.08 lbf

(3) Nozzle wall in shear

(π/2)*Mean nozzle dia*tn*Sn = (π/2)*8.1875*0.4375*14,000 = 78,772.98 lbf

(4) Groove weld in tension

(π/2)*Nozzle OD*tw*Sg = (π/2)*8.625*0.9375*14,800 = 187,980.14 lbf

(6) Upper groove weld in tension

(π/2)*Nozzle OD*tw*Sg = (π/2)*8.625*1*14,800 = 200,512.16 lbf

Loading on welds per UG-41(b)(1) tc(min) = lesser of 0.25 or 0.7*tmin = 0.25 in tc(actual) = 0.7*Leg = 0.7*0.375 = 0.2625 in

Outer fillet: tmin = lesser of 0.75 or te or t = 0.75 in tw(min) = 0.5*tmin = 0.375 in tw(actual) = 0.7*Leg = 0.7*0.5625 = 0.3938 in

Wall thickness per UG-45(a): tr1 = 0.3626 in (E =1)

Wall thickness per UG-45(b)(1): tr2 = 0.9192 in

Wall thickness per UG-16(b): tr3 = 0.125 in

Standard wall pipe per UG-45(b)(4): tr4 = 0.3443 in

The greater of tr2 or tr3: tr5 = 0.9192 in

The lesser of tr4 or tr5: tr6 = 0.3443 in

Groove weld in tension: 0.74*20,000 = 14,800 psi

Nozzle wall in shear: 0.7*20,000 = 14,000 psi

Inner fillet weld in shear: 0.49*20,000 = 9,800 psi

Outer fillet weld in shear: 0.49*20,000 = 9,800 psi

Upper groove weld in tension: 0.74*20,000 = 14,800 psi

W = (A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv

= (6.6391 - 0.6265 + 2*0.4375*1*(1*0.9375 - 1*0.8567))*20,000

= 121,667 lbf

W1-1 = (A2 + A5 + A41 + A42)*Sv

= (0.5754 + 5 + 0.1406 + 0.3164)*20,000

= 120,648 lbf

Load for path 1-1 lesser of W or W1-1 = 120648 lbf

Path 1-1 through (2) & (3) = 117,979.1 + 78,772.98 = 196,752.06 lbf

Path 1-1 is stronger than W1-1 so it is acceptable per UG-41(b)(1).

Load for path 2-2 lesser of W or W2-2 = 30726.25 lbf

Path 2-2 through (1), (4), (6) = 49,789.34 + 187,980.1 + 200,512.2 = 438,281.63 lbf

Path 2-2 is stronger than W2-2 so it is acceptable per UG-41(b)(1).

Load for path 3-3 lesser of W or W3-3 = 121667 lbf

Path 3-3 through (2), (4) = 117,979.1 + 187,980.1 = 305,959.22 lbf

Path 3-3 is stronger than W so it is acceptable per UG-41(b)(2).

W2-2 = (A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv

= (0.5754 + 0 + 0.1406 + 0 + 2*0.4375*0.9375*1)*20,000

= 30,726.25 lbf

W3-3 = (A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv

= (0.5754 + 0 + 5 + 0.1406 + 0.3164 + 0 + 2*0.4375*0.9375*1)*20,000

= 137,054.3 lbf

Reinforcement Calculations for MAP

The attached ASME B16.5 flange limits the nozzle MAP.

Calculations for internal pressure 1480 psi @ 70 °F

Allowable stresses: Sn = 20,000, Sv = 20,000, Sp = 20,000 psi

For P = 1480 psi @ 70 °F

UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45

A required A available A1 A2 A3 A5

A welds treq tmin

6.4951 7.5085 1.1299 0.9216 -- 5 0.457 0.2952 0.4375

W

Weld load

W1-1 Path 1-1 strength

Weld load

W2-2 Path 2-2 strength

Weld load

W3-3 Path 3-3 strength

110,268.16 127,572 207,318.13 41,244 450,813.66 147,572 318,491.25

UW-16 Weld Sizing Summary

Weld description Required weld size (in) Actual weld size (in) Status

Nozzle to pad fillet (Leg41) 0.25 0.2625 weld size is adequate

Pad to shell fillet (Leg42) 0.375 0.3938 weld size is adequate

Nozzle to pad groove (Upper) 0.35 1 weld size is adequate

Parallel to the vessel wall: d = 7.625 in

Normal to the vessel wall outside: 2.5*(tn - Cn) + te = 2.25 in trn = P*Rn/(Sn*E - 0.6*P)

= 1,480.001*3.8125/(20,000*1 - 0.6*1,480.001)

= 0.2952 in tr = P*R/(S*E - 0.6*P)

= 1,480.001*11/(20,000*1 - 0.6*1,480.001)

= 0.8518 in

A1 = larger of the following= 1.1299 in

A2 = smaller of the following= 0.9216 in

= 7.625*0.8518*1 + 2*0.5*0.8518*1*(1 - 1)

= 6.4951 in2

= d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1)

= 7.625*(1*1 - 1*0.8518) - 2*0.5*(1*1 - 1*0.8518)*(1 - 1)

= 1.1299 in2

= 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1)

= 2*(1 + 0.5)*(1*1 - 1*0.8518) - 2*0.5*(1*1 - 1*0.8518)*(1 - 1)

= 0.4445 in2

= 5*(tn - trn)*fr2*t

= 5*(0.5 - 0.2952)*1*1

= 1.024 in2

= 2*(tn - trn)*(2.5*tn + te)*fr2

= 2*(0.5 - 0.2952)*(2.5*0.5 + 1)*1

= 0.9216 in2

A41 = Leg2*fr3

= 0.3752*1

= 0.1406 in2

A42 = Leg2*fr4

= 0.56252*1

= 0.3164 in2

A5 = (Dp - d - 2*tn)*te*fr4

= (13.625 - 7.625 - 2*0.5)*1*1

= 5 in2

Area = A1 + A2 + A41 + A42 + A5

= 1.1299 + 0.9216 + 0.1406 + 0.3164 + 5

= 7.5085 in2

Inner fillet: tmin = lesser of 0.75 or tn or te = 0.5 in tc(min) = lesser of 0.25 or 0.7*tmin = 0.25 in tc(actual) = 0.7*Leg = 0.7*0.375 = 0.2625 in

Outer fillet: tmin = lesser of 0.75 or te or t = 0.75 in tw(min) = 0.5*tmin = 0.375 in tw(actual) = 0.7*Leg = 0.7*0.5625 = 0.3938 in

Required per UG-45 is the larger of tr1 or tr6 = 0.2952 in

Available nozzle wall thickness new, tn = 0.875*0.5 = 0.4375 in

(π/2)*Nozzle OD*Leg*Si = (π/2)*8.625*0.375*9,800 = 49,789.34 lbf

(π/2)*Pad OD*Leg*So = (π/2)*13.625*0.5625*9,800 = 117,979.08 lbf

(π/2)*Mean nozzle dia*tn*Sn = (π/2)*8.125*0.5*14,000 = 89,339.05 lbf

Load for path 1-1 lesser of W or W1-1 = 110268.2 lbf

Wall thickness per UG-45(a): tr1 = 0.2952 in (E =1)

Wall thickness per UG-45(b)(1): tr2 = 0.8518 in

Wall thickness per UG-16(b): tr3 = 0.0625 in

Standard wall pipe per UG-45(b)(4): tr4 = 0.2818 in

The greater of tr2 or tr3: tr5 = 0.8518 in

The lesser of tr4 or tr5: tr6 = 0.2818 in

Groove weld in tension: 0.74*20,000 = 14,800 psi

Nozzle wall in shear: 0.7*20,000 = 14,000 psi

Inner fillet weld in shear: 0.49*20,000 = 9,800 psi

Outer fillet weld in shear: 0.49*20,000 = 9,800 psi

Upper groove weld in tension: 0.74*20,000 = 14,800 psi

W = (A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv

= (6.4951 - 1.1299 + 2*0.5*1*(1*1 - 1*0.8518))*20,000

= 110,268.2 lbf

W1-1 = (A2 + A5 + A41 + A42)*Sv

= (0.9216 + 5 + 0.1406 + 0.3164)*20,000

= 127,572 lbf

W2-2 = (A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv

= (0.9216 + 0 + 0.1406 + 0 + 2*0.5*1*1)*20,000

= 41,244 lbf

W3-3 = (A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv

= (0.9216 + 0 + 5 + 0.1406 + 0.3164 + 0 + 2*0.5*1*1)*20,000

= 147,572 lbf

Path 1-1 through (2) & (3) = 117,979.1 + 89,339.05 = 207,318.13 lbf

Path 1-1 is stronger than W so it is acceptable per UG-41(b)(2).

Load for path 2-2 lesser of W or W2-2 = 41244 lbf

Path 2-2 through (1), (4), (6) = 49,789.34 + 200,512.2 + 200,512.2 = 450,813.66 lbf

Path 2-2 is stronger than W2-2 so it is acceptable per UG-41(b)(1).

Load for path 3-3 lesser of W or W3-3 = 110268.2 lbf

Path 3-3 through (2), (4) = 117,979.1 + 200,512.2 = 318,491.25 lbf

OUTLET (OUT)

Leg43 = 0 in hnew = 2 in

Located on: 22" I.D. SHELL

Liquid static head included: 0 psi

Nozzle material specification: SA-105 (II-D p. 18, ln. 8)

Nozzle longitudinal joint efficiency: 1

Flange description: 8 inch Class 600 LWN A105

Bolt Material: SA-193 B7 Bolt <= 2 1/2 (II-D p. 348, ln. 33)

Flange rated MDMT: -20°F

(UCS-66(b)(1)(b))

Liquid static head on flange: 0 psi

ASME B16.5 flange rating MAWP: 1480 psi @ 100°F

ASME B16.5 flange rating MAP: 1480 psi @ 70°F

ASME B16.5 flange hydro test: 2225 psi @ 70°F

Nozzle orientation: 0°

Local vessel minimum thickness: 1 in

Nozzle center line offset to datum line: 10 in

End of nozzle to shell center: 22 in

Nozzle inside diameter, new: 8 in

Nozzle nominal wall thickness: 1.375 in

Nozzle corrosion allowance: 0.0625 in

Projection available outside vessel, Lpr: 7.56 in

Internal projection, hnew: 2 in

Projection available outside vessel to flange face, Lf: 10 in

Calculations for internal pressure 1480 psi @ 100 °F

Nozzle is impact test exempt per UG-20(f).

Allowable stresses: Sn = 20,000, Sv = 20,000 psi

For P = 1480 psi @ 100 °F

UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45

A required A available A1 A2 A3 A5

A welds treq tmin

6.9604 10.3189 0.6568 4.6777 4.8438 -- 0.1406 0.3819 1.375

UG-41 Weld Failure Path Analysis Summary

The nozzle is exempt from weld strength calculations per UW-15(b)(1)

UW-16 Weld Sizing Summary

Weld description Required weld throat size (in) Actual weld throat size (in) Status

Nozzle to shell fillet (Leg41) 0.25 0.2625 weld size is adequate

Nozzle UCS-66 governing thk: 1 in

Nozzle rated MDMT: -20 °F

Parallel to the vessel wall: d = 8.125 in

Normal to the vessel wall outside: 2.5*(t - C) = 2.3438 in

Normal to the vessel wall inside: 2.5*(t - C) = 2.3438 in trn = P*Rn/(Sn*E - 0.6*P)

= 1,480.001*4.0625/(20,000*1 - 0.6*1,480.001)

= 0.3146 in tr = P*R/(S*E - 0.6*P)

= 1,480.001*11.0625/(20,000*1 - 0.6*1,480.001)

= 0.8567 in

A = d*tr*F + 2*tn*tr*F*(1 - fr1)

= 8.125*0.8567*1 + 2*1.3125*0.8567*1*(1 - 1)

= 6.9604 in2

A1 = larger of the following= 0.6568 in

A2 = smaller of the following= 4.6777 in

A3 = smaller of the following= 4.8438 in

UW-16(c) Weld Check

Fillet weld: tmin = lesser of 0.75 or tn or t = 0.75 in

The fillet weld size is satisfactory.

Weld strength calculations are not required for this detail which conforms to Fig. UW-16.1, sketch (c-e).

= d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1)

= 8.125*(1*0.9375 - 1*0.8567) - 2*1.3125*(1*0.9375 - 1*0.8567)*(1 - 1)

= 0.6568 in2

= 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1)

= 2*(0.9375 + 1.3125)*(1*0.9375 - 1*0.8567) - 2*1.3125*(1*0.9375 - 1*0.8567)*(1 - 1)

= 0.3638 in2

= 5*(tn - trn)*fr2*t

= 5*(1.3125 - 0.3146)*1*0.9375

= 4.6777 in2

= 5*(tn - trn)*fr2*tn

= 5*(1.3125 - 0.3146)*1*1.3125

= 6.5487 in2

= 5*t*ti*fr2

= 5*0.9375*1.25*1

= 5.8594 in2

= 5*ti*ti*fr2

= 5*1.25*1.25*1

= 7.8125 in2

= 2*h*ti*fr2

= 2*1.9375*1.25*1

= 4.8438 in2

A41 = Leg2*fr2

= 0.3752*1

= 0.1406 in2

Area = A1 + A2 + A3 + A41

= 0.6568 + 4.6777 + 4.8438 + 0.1406

= 10.3189 in2

Required per UG-45 is the larger of tr1 or tr6 = 0.3819 in

Available nozzle wall thickness new, tn = 1.375 in

Wall thickness per UG-45(a): tr1 = 0.3771 in (E =1)

Wall thickness per UG-45(b)(1): tr2 = 0.9192 in

Wall thickness per UG-16(b): tr3 = 0.125 in

Standard wall pipe per UG-45(b)(4): tr4 = 0.3819 in

The greater of tr2 or tr3: tr5 = 0.9192 in

The lesser of tr4 or tr5: tr6 = 0.3819 in

The attached ASME B16.5 flange limits the nozzle MAP.

Calculations for internal pressure 1480 psi @ 70 °F

Allowable stresses: Sn = 20,000, Sv = 20,000 psi

A1 = larger of the following= 1.1854 in

For P = 1480 psi @ 70 °F

UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45

A required A available A1 A2 A3 A5

A welds treq tmin

6.8146 12.152 1.1854 5.326 5.5 -- 0.1406 0.3194 1.375

UG-41 Weld Failure Path Analysis Summary

The nozzle is exempt from weld strength calculations per UW-15(b)(1)

UW-16 Weld Sizing Summary

Weld description Required weld throat size (in) Actual weld throat size (in) Status

Nozzle to shell fillet (Leg41) 0.25 0.2625 weld size is adequate

Parallel to the vessel wall: d = 8 in

Normal to the vessel wall outside: 2.5*(t - C) = 2.5 in

Normal to the vessel wall inside: 2.5*(t - C) = 2.5 in trn = P*Rn/(Sn*E - 0.6*P)

= 1,480.001*4/(20,000*1 - 0.6*1,480.001)

= 0.3098 in tr = P*R/(S*E - 0.6*P)

= 1,480.001*11/(20,000*1 - 0.6*1,480.001)

= 0.8518 in

A = d*tr*F + 2*tn*tr*F*(1 - fr1)

= 8*0.8518*1 + 2*1.375*0.8518*1*(1 - 1)

= 6.8146 in2

A2 = smaller of the following= 5.326 in

A3 = smaller of the following= 5.5 in

Fillet weld: tmin = lesser of 0.75 or tn or t = 0.75 in

Weld strength calculations are not required for this detail which conforms to Fig. UW-16.1, sketch (c-e).

= d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1)

= 8*(1*1 - 1*0.8518) - 2*1.375*(1*1 - 1*0.8518)*(1 - 1)

= 1.1854 in2

= 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1)

= 2*(1 + 1.375)*(1*1 - 1*0.8518) - 2*1.375*(1*1 - 1*0.8518)*(1 - 1)

= 0.7039 in2

= 5*(tn - trn)*fr2*t

= 5*(1.375 - 0.3098)*1*1

= 5.326 in2

= 5*(tn - trn)*fr2*tn

= 5*(1.375 - 0.3098)*1*1.375

= 7.3232 in2

= 5*t*ti*fr2

= 5*1*1.375*1

= 6.875 in2

= 5*ti*ti*fr2

= 5*1.375*1.375*1

= 9.4531 in2

= 2*h*ti*fr2

= 2*2*1.375*1

= 5.5 in2

A41 = Leg2*fr2

= 0.3752*1

= 0.1406 in2

Area = A1 + A2 + A3 + A41

= 1.1854 + 5.326 + 5.5 + 0.1406

= 12.152 in2

Wall thickness per UG-45(a): tr1 = 0.3098 in (E =1)

Wall thickness per UG-45(b)(1): tr2 = 0.8518 in

Wall thickness per UG-16(b): tr3 = 0.0625 in

Required per UG-45 is the larger of tr1 or tr6 = 0.3194 in

Available nozzle wall thickness new, tn = 1.375 in

Standard wall pipe per UG-45(b)(4): tr4 = 0.3194 in

The greater of tr2 or tr3: tr5 = 0.8518 in

The lesser of tr4 or tr5: tr6 = 0.3194 in

SHELL DOWNCOMER (DCMR)

tw(upper) = 0.375 in

Leg42 = 0.375 in

Dp = 7.5 in te = 0.375 in

Located on: 22" I.D. SHELL

Liquid static head included: 0 psi

Nozzle material specification: SA-106 B Smls pipe (II-D p. 14, ln. 5)

Nozzle longitudinal joint efficiency: 1

Nozzle description: 3" XX Heavy

Pad material specification: SA-516 70 (II-D p. 18, ln. 22)

Pad diameter: 7.5 in

Nozzle orientation: 180°

Local vessel minimum thickness: 1 in

Nozzle center line offset to datum line: 85 in

End of nozzle to shell center: 18 in

Nozzle inside diameter, new: 2.3 in

Nozzle nominal wall thickness: 0.6 in

Nozzle corrosion allowance: 0.0625 in

Projection available outside vessel, Lpr: 6 in

Pad is split: no

Available reinforcement per UG-37 governs the MAWP of this nozzle.

Calculations for internal pressure 1506.51 psi @ 100 °F

Nozzle is impact test exempt to -155 °F per UCS-66(b)(3) (coincident ratio = 0.23933).

Pad impact test exemption temperature from Fig UCS-66 Curve B = -20 °F Fig UCS-66.1 MDMT reduction = 8.6 °F, (coincident ratio = 0.91377).

For P = 1506.51 psi @ 100 °F

UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45

A required A available A1 A2 A3 A5

A welds treq tmin

2.2524 2.2525 0.181 1.2482 -- 0.7031 0.1202 0.2515 0.525

W

Weld load

W1-1 Path 1-1 strength

Weld load

W2-2 Path 2-2 strength

Weld load

W3-3 Path 3-3 strength

42,618.78 41,430.5 73,235.02 44,601.6 124,069.27 58,664.1 119,576.88

UW-16 Weld Sizing Summary

Weld description Required weld size (in) Actual weld size (in) Status

Nozzle to pad fillet (Leg41) 0.25 0.2625 weld size is adequate

Pad to shell fillet (Leg42) 0.1875 0.2625 weld size is adequate

Nozzle to pad groove (Upper) 0.2625 0.375 weld size is adequate

Nozzle UCS-66 governing thk: 0.525 in

Nozzle rated MDMT: -155 °F

Pad UCS-66 governing thickness: 0.375 in

Pad rated MDMT: -28.6 °F

Parallel to the vessel wall: (Rn + tn + t )= 2.6875 in

Normal to the vessel wall outside: 2.5*(tn - Cn) + te = 1.7188 in trn = P*Rn/(Sn*E - 0.6*P)

= 1,506.513*1.2125/(17,100*1 - 0.6*1,506.513)

= 0.1128 in tr = P*R/(S*E - 0.6*P)

= 1,506.513*11.0625/(20,000*1 - 0.6*1,506.513)

Allowable stresses: Sn = 17,100, Sv = 20,000, Sp = 20,000 psi fr1 = lesser of 1 or Sn/Sv = 0.855 fr2 = lesser of 1 or Sn/Sv = 0.855 fr3 = lesser of fr2 or Sp/Sv = 0.855

A1 = larger of the following= 0.181 in

A2 = smaller of the following= 1.2482 in

(Part of the weld is outside of the limits)

= 0.8727 in

= 2.425*0.8727*1 + 2*0.5375*0.8727*1*(1 - 0.855)

= 2.2524 in2

= d*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1)

= 2.425*(1*0.9375 - 1*0.8727) - 2*0.5375*(1*0.9375 - 1*0.8727)*(1 - 0.855)

= 0.147 in2

= 2*(t + tn)*(E1*t - F*tr) - 2*tn*(E1*t - F*tr)*(1 - fr1)

= 2*(0.9375 + 0.5375)*(1*0.9375 - 1*0.8727) - 2*0.5375*(1*0.9375 - 1*0.8727)*(1 - 0.855)

= 0.181 in2

= 5*(tn - trn)*fr2*t

= 5*(0.5375 - 0.1128)*0.855*0.9375

= 1.7021 in2

= 2*(tn - trn)*(2.5*tn + te)*fr2

= 2*(0.5375 - 0.1128)*(2.5*0.5375 + 0.375)*0.855

= 1.2482 in2

A41 = Leg2*fr3

= 0.3752*0.855

= 0.1202 in2

A42 = Leg2*fr4

= 02*1

= 0 in2

A5 = (Dp - d - 2*tn)*te*fr4

= (5.375 - 2.425 - 2*0.5375)*0.375*1

= 0.7031 in2

Area = A1 + A2 + A41 + A42 + A5

= 0.181 + 1.2482 + 0.1202 + 0 + 0.7031

= 2.2525 in2

Required per UG-45 is the larger of tr1 or tr6 = 0.2515 in

Available nozzle wall thickness new, tn = 0.875*0.6 = 0.525 in

(π/2)*Nozzle OD*Leg*Si = (π/2)*3.5*0.375*8,379 = 17,274.74 lbf

(π/2)*Pad OD*Leg*So = (π/2)*7.5*0.375*9,800 = 43,295.07 lbf

(π/2)*Mean nozzle dia*tn*Sn = (π/2)*2.9625*0.5375*11,970 = 29,939.94 lbf

(π/2)*Nozzle OD*tw*Sg = (π/2)*3.5*0.9375*14,800 = 76,281.8 lbf

(π/2)*Nozzle OD*tw*Sg = (π/2)*3.5*0.375*14,800 = 30,512.72 lbf

Inner fillet: tmin = lesser of 0.75 or tn or te = 0.375 in tc(actual) = 0.7*Leg = 0.7*0.375 = 0.2625 in

Outer fillet: tmin = lesser of 0.75 or te or t = 0.375 in tw(min) = 0.5*tmin = 0.1875 in tw(actual) = 0.7*Leg = 0.7*0.375 = 0.2625 in

Wall thickness per UG-45(a): tr1 = 0.1753 in (E =1)

Wall thickness per UG-45(b)(1): tr2 = 0.9352 in

Wall thickness per UG-16(b): tr3 = 0.125 in

Standard wall pipe per UG-45(b)(4): tr4 = 0.2515 in

The greater of tr2 or tr3: tr5 = 0.9352 in

The lesser of tr4 or tr5: tr6 = 0.2515 in

Groove weld in tension: 0.74*20,000 = 14,800 psi

Nozzle wall in shear: 0.7*17,100 = 11,970 psi

Inner fillet weld in shear: 0.49*17,100 = 8,379 psi

Outer fillet weld in shear: 0.49*20,000 = 9,800 psi

Upper groove weld in tension: 0.74*20,000 = 14,800 psi

W = (A - A1 + 2*tn*fr1*(E1*t - F*tr))*Sv

= (2.2524 - 0.181 + 2*0.5375*0.855*(1*0.9375 - 1*0.8727))*20,000

= 42,618.78 lbf

W1-1 = (A2 + A5 + A41 + A42)*Sv

= (1.2482 + 0.7031 + 0.1202 + 0)*20,000

Load for path 1-1 lesser of W or W1-1 = 41430.5 lbf

Path 1-1 through (2) & (3) = 43,295.07 + 29,939.94 = 73,235.02 lbf

Path 1-1 is stronger than W1-1 so it is acceptable per UG-41(b)(1).

Load for path 2-2 lesser of W or W2-2 = 42618.78 lbf

Path 2-2 through (1), (4), (6) = 17,274.74 + 76,281.8 + 30,512.72 = 124,069.27 lbf

Path 2-2 is stronger than W so it is acceptable per UG-41(b)(2).

Load for path 3-3 lesser of W or W3-3 = 42618.78 lbf

Path 3-3 through (2), (4) = 43,295.07 + 76,281.8 = 119,576.88 lbf

= 41,430.5 lbf

W2-2 = (A2 + A3 + A41 + A43 + 2*tn*t*fr1)*Sv

= (1.2482 + 0 + 0.1202 + 0 + 2*0.5375*0.9375*0.855)*20,000

= 44,601.6 lbf

W3-3 = (A2 + A3 + A5 + A41 + A42 + A43 + 2*tn*t*fr1)*Sv

= (1.2482 + 0 + 0.7031 + 0.1202 + 0 + 0 + 2*0.5375*0.9375*0.855)*20,000

= 58,664.1 lbf

The vessel wall thickness governs the MAP of this nozzle.

Calculations for internal pressure 1724.14 psi @ 70 °F

This opening does not require reinforcement per UG-36(c)(3)(a)

For P = 1724.14 psi @ 70 °F

UG-45 Nozzle Wall Thickness Summary (in) The nozzle passes UG-45

A required A available A1 A2 A3 A5

A welds treq tmin

This nozzle is exempt from area calculations per UG-36(c)(3)(a) 0.189 0.525

UG-41 Weld Failure Path Analysis 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) Actual weld size (in) Status

Nozzle to pad fillet (Leg41) 0.25 0.2625 weld size is adequate

Pad to shell fillet (Leg42) 0.1875 0.2625 weld size is adequate

Nozzle to pad groove (Upper) 0.2625 0.375 weld size is adequate

Parallel to the vessel wall: (Rn + tn + t )= 2.75 in

Normal to the vessel wall outside: 2.5*(tn - Cn) + te = 1.875 in trn = P*Rn/(Sn*E - 0.6*P)

= 1,724.141*1.15/(17,100*1 - 0.6*1,724.141)

= 0.1234 in tr = P*R/(S*E - 0.6*P)

= 1,724.141*11/(20,000*1 - 0.6*1,724.141)

= 1 in

Inner fillet: tmin = lesser of 0.75 or tn or te = 0.375 in tc(min) = lesser of 0.25 or 0.7*tmin = 0.25 in tc(actual) = 0.7*Leg = 0.7*0.375 = 0.2625 in

Outer fillet: tmin = lesser of 0.75 or te or t = 0.375 in tw(min) = 0.5*tmin = 0.1875 in

Required per UG-45 is the larger of tr1 or tr6 = 0.189 in tw(actual) = 0.7*Leg = 0.7*0.375 = 0.2625 in

Wall thickness per UG-45(a): tr1 = 0.1234 in (E =1)

Wall thickness per UG-45(b)(1): tr2 = 1 in

Wall thickness per UG-16(b): tr3 = 0.0625 in

Standard wall pipe per UG-45(b)(4): tr4 = 0.189 in

The greater of tr2 or tr3: tr5 = 1 in

The lesser of tr4 or tr5: tr6 = 0.189 in

SADDLE SUPPORTS

Notes:

(1) Saddle calculations are based on the method presented in "Stresses in Large Cylindrical Pressure Vessels on Two Saddle Supports" by L.P. Zick.

Saddle material: SA-516-70

Saddle construction is: Web at edge of rib

Saddle allowable stress: Ss = 20,000 psi

Saddle yield stress: Sy = 38,000 psi

Saddle distance to datum: 5 in

Tangent to tangent length: L = 104 in

Saddle separation: Ls = 86 in

Vessel radius: R = 12 in

Tangent distance left: Al = 11 in

Tangent distance right: Ar = 7 in

Saddle height: Hs = 53 in

Saddle contact angle: θ = 120 °

Web plate thickness: ts = 0.375 in

Base plate length: E = 22 in

Base plate width: F = 8 in

Base plate thickness: tb = 0.75 in

Number of stiffener ribs: n = 2

Largest stiffener rib spacing: di = 20.4096 in

Stiffener rib thickness: tw = 0.375 in

Saddle width: B = 6 in

Anchor bolt size & type: 0.75 inch series 8 threaded

Anchor bolt material: SUPPLIED BY CUSTOMER

Anchor bolt allowable shear: 15,000 psi

Anchor bolt corrosion allowance: 0 in

Anchor bolts per saddle: 2

Base coefficient of friction: µ = 0.45

Weight on left saddle: operating corr = 2,925 lb, test new = 3,817 lb

Weight on right saddle: operating corr = 2,084 lb, test new = 2,901 lb

Weight of saddle pair = 376 lb

Load Case 1: Weight ,Operating

Longitudinal stress between saddles (Weight ,Operating, left saddle loading and geometry govern)

S1 = +- 3*K1*Q*(L/12) / (π*R 2*t)

= 3*0.5182*2,925*(104/12) / (π*11.53132*0.9375)

= 101 psi

Sp = P*R/(2*t)

= 1,480*11.0625/(2*0.9375) = 8,732 psi

Maximum tensile stress S1t = S1 + Sp = 8,833 psi

Maximum compressive stress (shut down) S1c = S1 = 101 psi

Tensile stress is acceptable (<=1*S*E = 20,000 psi) Compressive stress is acceptable (<=1*Sc = 17,365 psi)

Longitudinal stress at the left saddle (Weight ,Operating)

Le = 2*(Left head depth)/3 + L + 2*(Right head depth)/3

= 2*6.437/3 + 104 + 2*6.437/3 = 112.5827 in w = Wt/Le = 5,009/112.5827 = 44.49 lb/in

Bending moment at the left saddle:

Mq = w*(2*H*Al/3 + Al 2/2 - (R2 - H2)/4)

= 44.49*(2*6.437*11/3 + 112/2 - (122 - 6.4372)/4)

= 3,651.1 lb-in

S2 = +- Mq*K1'/ (π*R

= 3,651.1*9.3799/ (π*11.53132*0.9375)

= 87 psi

Sp = P*R/(2*t)

= 1,480*11.0625/(2*0.9375) = 8,732 psi

Load Vessel condition

Bending + pressure between saddles

(psi)

Bending + pressure at the saddle (psi)

S1 allow

S1

S2

S2

Weight Operating 8,833 20,000 101 17,365 8,819 20,000 87 17,365

Weight Test 12,340 34,200 124 17,365 12,327 34,200 111 17,365

Load Vessel condition

Tangential shear (psi)

Circumferential stress (psi)

Stress over saddle (psi)

Splitting (psi)

S3 allow S4

(horns)

S5 allow S6 allow

Weight Operating 243 16,000 -300 30,000 423 19,000 397 13,333

Weight Test 296 27,360 -348 34,200 502 34,200 518 34,200

Maximum tensile stress S2t = S2 + Sp = 8,819 psi

Maximum compressive stress (shut down) S2c = S2 = 87 psi

Tensile stress is acceptable (<=1*S = 20,000 psi)

Tangential shear stress in the shell (left saddle, Weight ,Operating)

Qshear = Q - w*(a + 2*H/3)

= 2,925 - 44.49*(11 + 2*6.437/3) = 2,244.66 lbf

S3 = K2.2*Qshear/(R*t)

= 1.1707*2,244.66/(11.5313*0.9375) = 243 psi

Tangential shear stress is acceptable (<= 0.8*S = 16,000 psi)

Circumferential stress at the left saddle horns (Weight ,Operating)

S4 = -Q/(4*t*(b+1.56*Sqr(Ro*t))) - 3*K3*Q/(2*t 2)

= -2,925/(4*0.9375*(6+1.56*Sqr(12*0.9375))) - 3*0.0462*2,925/(2*0.93752)

= -300 psi

Circumferential stress at saddle horns is acceptable (<=1.5*Sa = 30,000 psi)

Ring compression in shell over left saddle (Weight ,Operating)

S5 = K5*Q/((t)*(ts + 1.56*Sqr(Ro*tc)))

= 0.7603*2,925/((0.9375)*(0.375 + 1.56*Sqr(12*0.9375))) = 423 psi

Ring compression in shell is acceptable (<= 0.5*Sy = 19,000 psi)

Saddle splitting load (left, Weight ,Operating)

Area resisting splitting force = Web area + wear plate area

Ae = Heff*ts + tp*Wp

= 4*0.375 + 0*0

= 1.5 in2

S6 = K8*Q / Ae

= 0.2035*2,925 / 1.5 = 397 psi

Stress in saddle is acceptable (<= (2/3)*Ss = 13,333 psi)

Load Case 2: Weight ,Test

Longitudinal stress between saddles (Weight ,Test, left saddle loading and geometry govern)

S1 = +- 3*K1*Q*(L/12) / (π*R

= 3*0.5182*3,817*(104/12) / (π*11.52*1)

= 124 psi

Sp = P*R/(2*t)

= 2,221.19*11/(2*1) = 12,217 psi

Maximum tensile stress S1t = S1 + Sp = 12,340 psi

Maximum compressive stress (shut down) S1c = S1 = 124 psi

Tensile stress is acceptable (<= 0.9*Sy = 34,200 psi)

Longitudinal stress at the left saddle (Weight ,Test)

Le = 2*(Left head depth)/3 + L + 2*(Right head depth)/3

= 2*6.437/3 + 104 + 2*6.437/3 = 112.5827 in w = Wt/Le = 6,718/112.5827 = 59.67 lb/in

Bending moment at the left saddle:

Mq = w*(2*H*Al/3 + Al 2/2 - (R2 - H2)/4)

= 59.67*(2*6.437*11/3 + 112/2 - (122 - 6.4372)/4)

= 4,896.9 lb-in

S2 = +- Mq*K1'/ (π*R

= 4,896.9*9.3799/ (π*11.52*1)

= 111 psi

Sp = P*R/(2*t)

= 2,221.19*11/(2*1) = 12,217 psi

Maximum tensile stress S2t = S2 + Sp = 12,327 psi

Maximum compressive stress (shut down) S2c = S2 = 111 psi

Tensile stress is acceptable (<= 0.9*Sy = 34,200 psi)

Tangential shear stress in the shell (left saddle, Weight ,Test)

Qshear = Q - w*(a + 2*H/3)

= 3,817 - 59.67*(11 + 2*6.437/3) = 2,904.54 lbf

S3 = K2.2*Qshear/(R*t)

= 1.1707*2,904.54/(11.5*1) = 296 psi

Tangential shear stress is acceptable (<= 0.8*(0.9*Sy) = 27,360 psi)

Circumferential stress at the left saddle horns (Weight ,Test)

S4 = -Q/(4*t*(b+1.56*Sqr(Ro*t))) - 3*K3*Q/(2*t

= -3,817/(4*1*(6+1.56*Sqr(12*1))) - 3*0.0462*3,817/(2*12)

= -348 psi

Circumferential stress at saddle horns is acceptable (<= 0.9*Sy = 34,200 psi)

Ring compression in shell over left saddle (Weight ,Test)

S5 = K5*Q/((t)*(ts + 1.56*Sqr(Ro*tc)))

= 0.7603*3,817/((1)*(0.375 + 1.56*Sqr(12*1))) = 502 psi

Ring compression in shell is acceptable (<= 0.9*Sy = 34,200 psi)

Saddle splitting load (left, Weight ,Test)

Area resisting splitting force = Web area + wear plate area

Ae = Heff*ts + tp*Wp

= 4*0.375 + 0*0

= 1.5 in2

S6 = K8*Q / Ae

= 0.2035*3,817 / 1.5 = 518 psi

Stress in saddle is acceptable (<= 0.9*Sy = 34,200 psi)

Shear stress in anchor bolting, one end slotted

Maximum seismic or wind base shear = 0 lbf

Thermal expansion base shear = W*µ = 3,113 * 0.45= 1,400.85 lbf

Corroded root area for a 0.75 inch series 8 threaded bolt = 0.302 in2 ( 2 per saddle )

Bolt shear stress = 1,400.85/(0.302*2) = 2,319 psi

Anchor bolt stress is acceptable (<= 15,000 psi)

Web plate buckling check (Escoe pg 251)

Allowable compressive stress Sc is the lesser of 20,000 or 11,326 psi: (11,326)

Sc = Ki*π2*E/(12*(1 - 0.32)*(di/tw)

= 1.28*π2*29E+06/(12*(1 - 0.32)*(20.4096/0.375)2)

= 11,326 psi

Allowable compressive load on the saddle be = di*ts/(di*ts + 2*tw*(b - 1))

= 20.4096*0.375/(20.4096*0.375 + 2*0.375*(6 - 1)) = 0.6712

Fb = n*(As + 2*be*tw)*Sc

= 2*(2.1094 + 2*0.6712*0.375)*11,326 = 59,184.13 lbf

Saddle loading of 4,005 lbf is <= Fb; satisfactory.

Primary bending + axial stress in the saddle due to end loads (assumes one saddle slotted) σb = V * (Hs - xo)* y / I + Q / A

= 0 * (53 - 9.9239)* 4.0817 / 27.22 + 2,925 / 12.013 = 243 psi

The primary bending + axial stress in the saddle <= 20,000 psi; satisfactory.

Secondary bending + axial stress in the saddle due to end loads (includes thermal expansion, assumes one saddle slotted) σb = V * (Hs - xo)* y / I + Q / A

= 1,400.85 * (53 - 9.9239)* 4.0817 / 27.22 + 2,925 / 12.013 = 9,291 psi

The secondary bending + axial stress in the saddle < 2*Sy= 76,000 psi; satisfactory.

Saddle base plate thickness check (Roark sixth edition, Table 26, case 7a) where a = 20.4096, b = 7.625 in tb = (β1*q*b 2/(1.5*Sa))

0.5

= (2.2411*23*7.6252/(1.5*20,000))0.5

= 0.3144 in

The base plate thickness of 0.75 in is adequate.

Foundation bearing check

Sf = Qmax / (F*E)

= 4,005 / (8*22) = 23 psi

Concrete bearing stress < 1,658 psi ; satisfactory.

Wolters Industrial Park

PECO PROJECT MW-502076 SUMP CALCULATIONS

Vessel Model No.: PGCPH-7-373-22-1480

Peco Item No.: 4560

Project Coordinator: CHARLES MAYS

Date: Wednesday, January 07, 2009

1/8/2009PGCPH-7-373-22-1480 SUMP

2. 8" NOM SUMP

3. SUMP DOWNCOMER (DMCR)

0 1/ 7/2009 CHARLES MAYS FIRST ISSUE

8" NOM SUMP

Material is impact test exempt per UG-20(f) UCS-66 governing thickness = 0.4375 in

Internal design pressure: P = 1,480 psi @ 100 °F

Static liquid head:

Design thickness, (at 100 °F) Appendix 1-1

Maximum allowable working pressure, (at 100 °F) Appendix 1-1

Maximum allowable pressure, (at 70 °F) Appendix 1-1

Material specification: SA-106 B Smls pipe (II-D p. 14, ln. 5) Pipe NPS and Schedule: 8" Sch 80 (XS)

Pth =0.57 psi (SG = 1, Hs = 15.8125", Horizontal test head)

Corrosion allowance Inner C = 0.0625" Outer C = 0"

Design MDMT = -20 °F No impact test performed Rated MDMT = -20 °F Material is not normalized

Material is not produced to Fine Grain Practice PWHT is not performed

Radiography: Longitudinal joint - Seamless No RT Left circumferential joint - Full UW-11(a) Type 1 Right circumferential joint - Full UW-11(a) Type 1

Estimated weight New = 346.7 lb corr = 305.7 lb

Capacity New = 18.98 US gal corr = 19.6 US gal

OD = 8.625"

Length Lc = 96" t = 0.5" t = P*Ro / (S*E + 0.40*P) + Corrosion

= 1,480*4.3125 / (17,100*1.00 + 0.40*1,480) + 0.0625 = 0.4233"

P = S*E*t / (Ro - 0.40*t) - Ps = 17,100*1.00*0.375 / (4.3125 - 0.40*0.375) - 0 = 1,540.54 psi

P = S*E*t / (Ro - 0.40*t)

= 17,100*1.00*0.4375 / (4.3125 - 0.40*0.4375) = 1,808.16 psi

SUMP DOWNCOMER (DMCR)

tw(lower) = 0.5 in

Located on: 8" NOM SUMP

Liquid static head included: 0 psi

Nozzle material specification: SA-106 B Smls pipe (II-D p. 14, ln. 5)

Nozzle longitudinal joint efficiency: 1

Nozzle description: 3" XX Heavy

Nozzle orientation: 0°

Local vessel minimum thickness: 0.4375 in

Nozzle center line offset to datum line: 90.5 in

End of nozzle to shell center: 12 in

Nozzle inside diameter, new: 2.3 in

Nozzle nominal wall thickness: 0.6 in

Nozzle corrosion allowance: 0.0625 in

Projection available outside vessel, Lpr: 7.6875 in

The vessel wall thickness governs the MAWP of this nozzle.

Calculations for internal pressure 1540.52 psi @ 100 °F

Nozzle is impact test exempt per UG-20(f).

Fillet weld: tmin = lesser of 0.75 or tn or t = 0.375 in

For P = 1540.52 psi @ 100 °F

Thickness Summary (in) The nozzle passes UG-45

A required A available A1 A2 A3 A5

A welds treq tmin

This nozzle is exempt from area calculations per UG-36(c)(3)(a) 0.2515 0.525

UG-41 Weld Failure Path Analysis 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) Actual weld throat size (in) Status

Nozzle to shell fillet (Leg41) 0.25 0.2625 weld size is adequate

Nozzle UCS-66 governing thk: 0.4375 in

Nozzle rated MDMT: -20 °F

Parallel to the vessel wall: d = 2.425 in

Normal to the vessel wall outside: 2.5*(t - C) = 0.9375 in trn = P*Rn/(Sn*E - 0.6*P)

= 1,540.517*1.2125/(17,100*1 - 0.6*1,540.517)

= 0.1155 in tr = P*Ro/(S*E + 0.4*P)

= 1,540.517*4.3125/(17,100*1 + 0.4*1,540.517)

= 0.375 in

Weld strength calculations are not required for this detail which conforms to Fig. UW-16.1, sketch (c-e).

Wall thickness per UG-45(a): tr1 = 0.178 in (E =1)

Wall thickness per UG-45(b)(1): tr2 = 0.4375 in

Wall thickness per UG-16(b): tr3 = 0.125 in

Standard wall pipe per UG-45(b)(4): tr4 = 0.2515 in

The greater of tr2 or tr3: tr5 = 0.4375 in

The lesser of tr4 or tr5: tr6 = 0.2515 in

Calculations for internal pressure 1808.13 psi @ 70 °F

Fillet weld: tmin = lesser of…