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24 in. OD × 720 psi Vertical Vessel

ASME Section VIII Division 1, 2023 Edition, CRN V2315.2134, Alberta registration, August 2024

This 24 in. OD vertical pressure vessel is designed for 720 psi at 130 °F with a minimum design metal temperature of -20 °F and a rated MDMT of -22.4 °F. The vessel has a 120 in. straight shell, 2:1 ellipsoidal heads, a skirt support, and multiple process, instrument, and coupling connections arranged on the shell and heads.

Reece Custom Manufacturing designed and registered this vessel under APEGA Permit to Practice 15926. The registered calculation file is 024_0720_0125_+130_-20_V_1 Rev. 3, and the hydrotest basis in the calculation package includes a vertical shop hydrotest at 1,080 psi and a UG-99(b) vertical field hydrotest at 936 psi plus static head.

CRNV2315.2134
CodeASME VIII-1, 2023 Edition
Design pressure720 psi
Design temperature130 °F
Design MDMT-20 °F
Rated MDMT-22.4 °F
MAWP720 psi at 130 °F
Shell specSA-516 70, 24 in. OD × 0.625 in.
Corrosion allowance0.125 in.
Joint efficiency1.00
Empty weight2,301 lb
Test weight4,238 lb
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About this example

This example is a compact vertical process vessel with a dense nozzle layout and a skirt support. The registered design combines a 24 in. diameter shell, two ellipsoidal heads, flanged process nozzles from 2 NPS to 6 NPS, threaded couplings, threadolets, and a seismic check to NBC 2020.

Design Basis and Code Compliance

The vessel is registered to ASME Section VIII Division 1, 2023 Edition for internal pressure service at 720 psi and 130 °F. The chamber summary reports a design MDMT of -20 °F, a rated MDMT of -22.4 °F, and no external pressure design case for the pressure boundary.

Loadings listed in the registered file include internal pressure, vessel and liquid weight, support loads, seismic, and hydrostatic test loading. Wind, snow, cyclic loading, impact loading, abnormal pressure, and thermal gradient loading are listed as not governing in the registered package.

The shell and heads are SA-516 Grade 70, and the MDMT path is based on UCS-66 with UCS-66.1 reduction applied to the main pressure parts. Several smaller nozzles and couplings are impact-test-exempt through the stress-ratio path noted in the registered file.

Required marking is RT4. The shell longitudinal seam is full radiography Type 1, and the circumferential seams are spot radiographed in line with the radiography summary reported in the calculation file.

Pressure and Thickness Summary

The main shell is entered as SA-516 Grade 70, 24 in. OD, 120 in. long, with 0.625 in. nominal thickness, 0.125 in. corrosion allowance, and joint efficiency of 1.00. The required design thickness reported for the cylinder is 0.5518 in. under internal pressure.

Both ellipsoidal heads are also SA-516 Grade 70 with 0.625 in. nominal thickness and 2 in. straight flanges. The required design thickness is reported at 0.5378 in. for the top head and 0.5388 in. for the bottom head.

The vessel chamber summary reports 720 psi MAWP hot and corroded at 130 °F. The overall rated MDMT is -22.4 °F, limited by the flange-rated low-temperature capability of the smallest Class 300 flanged nozzles.

The new empty weight is 2,301 lb, the operating weight is 3,036 lb, and the new vertical test weight is 4,238 lb. Vessel capacity is reported as 232 US gal.

Materials and Construction

The shell and both heads are SA-516 Grade 70. The support skirt is SA-53 electric-resistance-welded pipe, 20 in. ID × 24 in. long × 0.375 in. nominal thickness.

Main process nozzles are SA-106 Grade B seamless pipe with SA-105N weld neck flanges. The registered nozzle schedule includes 6 NPS Sch 160, 4 NPS XXS, 3 NPS Sch 160 or XXS, and 2 NPS Sch 160 nozzle necks, all with Class 300 flanges.

Small connections include SA-105 threaded couplings and SA-105 threadolets. The calculation package identifies several of these small openings as exempt from reinforcement calculations under the small-opening rules used in the registered file, while still checking minimum neck thickness.

Corrosion allowance on the primary pressure parts is 0.125 in. Head-to-shell seams and shell seams are listed in the radiography summary, and the vessel is marked RT4 in the registered design package.

Calculations Performed (Code Clause Index)
  • UG-16(b), for minimum wall thickness basis listed in the settings summary.
  • Appendix 1-4(c), for 2:1 ellipsoidal head internal pressure thickness calculations.
  • UG-27(c)(1) and Appendix 1 shell formulas, for cylindrical shell internal pressure thickness.
  • UG-37 and UG-40, for area replacement and reinforcement limits on larger nozzles.
  • UG-45, for minimum nozzle neck thickness checks.
  • UCS-66 and UCS-66.1, for carbon steel MDMT and stress-ratio reduction on the shell and heads.
  • UG-99(b) and UG-99(h), for hydrostatic test pressure and brittle-fracture temperature basis.
  • UW-11 and UG-116, for radiography basis and required marking.
  • NBC 2020 Section 4.1.8.18, for the seismic equipment check documented in the registered file.
Worked Examples (Selected Calculations)

Worked Example 1, Cylinder Thickness

Inputs: P = 720 psi; S = 20,000 psi at 130 °F; E = 1.00; outside diameter = 24 in.; corrosion allowance = 0.125 in.

t = (P · R) / (S · E - 0.4P)

The registered thickness summary reports a required cylinder thickness of 0.5518 in. for the shell under internal pressure. With a 0.625 in. nominal shell and 0.125 in. corrosion allowance in the design package, the selected shell thickness meets the registered pressure basis.

Worked Example 2, 2:1 Ellipsoidal Head Thickness

Inputs: P = 720 psi; D = 24 in.; S = 20,000 psi; E = 1.00; corrosion allowance = 0.125 in.

K = 1 / 6 [2 + (D / 2h)^2]
t = (P · D · K) / (2SE - 0.2P) + CA

The top head calculation pages report a required design thickness of 0.5378 in. and the bottom head pages report 0.5388 in. The selected 0.625 in. nominal head thickness provides the registered pressure thickness plus corrosion allowance.

Worked Example 3, Vessel MDMT Rating

Inputs: Design MDMT = -20 °F; shell and heads in SA-516 Grade 70; nozzle flange low-temperature ratings reported in the pressure summary notes.

Rated MDMT = max(component governing MDMT)

The shell and heads are rated colder than the design MDMT through the UCS-66 path shown in the calculation package. The chamber rated MDMT is -22.4 °F because the 2 NPS Class 300 flange rating governs the final chamber rating.

Worked Example 4, Hydrostatic Test Basis

Inputs: MAWP = 720 psi; shop hydrotest pressure entered by user = 1,080 psi; field test basis per UG-99(b) = 1.3 × design pressure.

P_test,field = 1.3 × 720 = 936 psi

The registered file reports a vertical shop hydrostatic test at 1,080 psi at 70 °F and a corroded vertical field hydrostatic test at 936 psi plus static head. The reported test summary shows all listed components within allowable test stress.

Why this case study is on the public site

This case study shows a compact high-pressure vertical vessel with a dense nozzle schedule, low-temperature evaluation, hydrotest checks, and seismic reporting for Alberta service. It is a useful public example for buyers and engineers looking for real registered vessel data such as code edition, CRN, pressure rating, material selection, nozzle arrangement, and test basis.

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Reece Custom Manufacturing, APEGA Permit to Practice 15926. Registered calculation reference: 024_0720_0125_+130_-20_V_1 Rev. 3. CRN V2315.2134. Registration date: August 13, 2024.

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]]> 36 in OD x 1350 PSI Vertical Stainless Vessel https://reececustom.com/36-in-od-x-1350-psi-vertical-stainless-vessel/ Fri, 15 May 2026 19:49:20 +0000 https://reececustom.com/?p=3600 36 in OD x 1350 PSI Vertical Stainless Vessel ASME Section VIII Division 1, 2023 Edition, CRN AA2082.2, Alberta registration, […]

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36 in OD x 1350 PSI Vertical Stainless Vessel

ASME Section VIII Division 1, 2023 Edition, CRN AA2082.2, Alberta registration, July 2024

This example is a 36 in outside diameter vertical stainless steel pressure vessel with SA-240 304 shell and heads, skirt support, and a set of Class 600 stainless flanged nozzles in the shell and top head. It is registered at 1350 psi and 130 F with a design MDMT of -20 F, and the austenitic stainless pressure boundary rates to -320 F per UHA-51(d)(1)(a), with the chamber rated MDMT limited back to the design MDMT setting in the calculation.

Reece Custom Manufacturing completed the registered design under APEGA Permit 15926 using ASME Section VIII Division 1, 2023 Edition. The calculation set records RT2 marking, a UG-99(b) vertical shop hydrotest basis at 1.3 times MAWP, and UHA-51(g) stress-ratio toughness checks on several nozzles, plus WRC 107 local-load evaluations on the shell, head nozzles, and lifting and tailing lugs.

CRNAA2082.2
CodeASME VIII-1, 2023
Design pressure1350 psi
Design temperature130 F
Design MDMT-20 F
Rated MDMT-20 F @ 1350 psi
MAWP1350 psi hot corroded
Shell specSA-240 304, 36 in OD x 1.5 in nominal
Corrosion allowance0 in (stainless)
Joint efficiency1.00
Empty weight6,674 lb new
Test weight10,119 lb new
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About this example

This vessel is a compact vertical stainless receiver with integral skirt and optional base ring, built entirely from SA-240 304 plate and stainless flanged nozzles. The registered calculation includes both the base configuration and several unregistered XXS nozzle options, which makes the page a useful public reference for stainless vessels that use UHA-51(d)(1)(a) carbon-content exemptions and UHA-51(g) stress-ratio paths instead of UCS-66.

Design Basis and Code Compliance

The design basis is ASME Section VIII Division 1, 2023 Edition in U.S. Customary units, with internal pressure as the governing load case. The pressure summary records MAWP of 1350 psi at 130 F, design MDMT of -20 F, rated MDMT of -20 F at 1350 psi, and a user-imposed MAWP limit of 1350 psi in the Set Mode dialog.

The shell and heads are SA-240 304 austenitic stainless with full radiography on the longitudinal shell seam and spot radiography on the circumferential seams, giving RT2 required marking under UG-116. The settings summary records a UG-99(b) shop hydrotest at 1.3 times MAWP, 90 percent of yield as the maximum test stress, UG-22 weight and wind loadings where supports are present, and no seismic or external-pressure design for this chamber.

  • Registration: CRN AA2082.2, dated July 31, 2024.
  • Permit reference: APEGA Permit 15926.
  • Main construction: 36 in OD shell with two 2:1 semi-ellipsoidal heads, skirt, optional base ring.
  • Marking basis: UG-116(e) RT2 radiography designation.
Pressure and Thickness Summary

The chamber MAWP is set equal to the design pressure, 1350 psi at 130 F, through the Maximize MDMT / No MAWP setting in the stainless material toughness dialog. The thickness summary shows design thickness of 1.1867 in for the 36 in OD shell and straight flanges under Appendix 1-1, and about 1.146 to 1.149 in for the 2:1 semi-ellipsoidal heads under Appendix 1-4(c), all without corrosion allowance.

The thickness tables also include combined-load checks with pressure, weight, and wind, which give required thickness around 0.650 in in tension and slightly less in compression, confirming that internal pressure still governs. The weight summary records new empty weight of 6674 lb, test and operating weight of 10,119 lb, and a geometric capacity of 411 US gal, excluding nozzles and attachments.

  • Main shell: 36 in OD, 1.5 in nominal, 1.1867 in required at design condition.
  • Heads: 36 in OD, 1.4375 in minimum after forming, about 1.15 in required at design condition.
  • Support: SA-240 304 skirt, 0.375 in nominal with wind-governed stress and thickness checks.
  • Chamber rating: 1350 psi MAWP hot corroded, rated MDMT -20 F per design limit.
Materials and Construction

The primary pressure boundary, including shell, heads, and skirt, is SA-240 304 stainless plate with no corrosion allowance. Nozzles are stainless as well, with SA-182 F304 long-weld-neck flanges for the 6 in, 4 in, and 3 in shell and head nozzles, and SA-312 TP304 pipe on the 2 in shell nozzle and the XXS option sets.

The nozzle schedule lists a 3 in long-weld-neck nozzle in the top head, one 6 in, one 4 in, and one 3 in long-weld-neck nozzle in the shell, and a 2 in Schedule 80 shell nozzle, all with Class 600 stainless flanges. The calculation file also carries several unregistered XXS nozzle options in 3 in, 4 in, and 6 in sizes, which are useful for design envelopes but do not appear on the registered CRN drawing.

  • Main pressure parts: SA-240 304 shell, heads, skirt, and optional base ring.
  • Nozzle forgings: SA-182 F304 Class 600 long-weld-neck flanges.
  • Pipe nozzles: SA-312 TP304 Schedule 80S and XXS pipe where listed.
  • Corrosion allowance: 0 in on all stainless pressure parts.
Calculations Performed (Code Clause Index)

The registered file includes cylindrical shell and straight-flange pressure checks under Appendix 1-1, two 2:1 semi-ellipsoidal head checks under Appendix 1-4(c), and stainless austenitic MDMT treatment under UHA-51(d)(1)(a) and UHA-51(g). Nozzle reinforcement is checked under UG-37 with UG-40 limits of reinforcement and UG-45 minimum neck thickness, and weld sizing under UW-16 with UG-76(c) inside-edge rounding.

Hydrotest calculations follow UG-99(b) with 1.3 times MAWP and 90 percent of yield as the stress cap, plus corroded vertical field-test checks at 2025 psi user pressure. Selected nozzles and lifting and tailing lugs are checked for local external loads using WRC 107 methods, and the combined primary plus bending plus secondary stresses are compared against Division 2 limits within the COMPRESS WRC module.

  • Appendix 1-1, shell and straight-flange pressure thickness and MAWP.
  • Appendix 1-4(c), 2:1 semi-ellipsoidal head pressure thickness and MAWP.
  • UHA-51(d)(1)(a) and UHA-51(g), stainless MDMT and impact-exemption stress-ratio path.
  • UG-37, UG-40, UG-45, UG-76(c), UW-16 for nozzle reinforcement and weld sizing.
  • UG-99(b) and UG-99(h) for hydrotest basis,, WRC 107 for nozzle and lug local-load checks.
Worked Examples (Selected Calculations)

1. Shell required thickness, Appendix 1-1

The 36 in OD SA-240 304 shell has a required thickness of 1.1867 in at 1354.18 psi effective shell pressure and 130 F, using the outside-radius form of the Appendix 1-1 cylindrical-shell equation and 0 in corrosion allowance.

t = P R_o / (S E + 0.40 P) + c

t = (1354.18 x 18) / (20000 x 1.00 + 0.40 x 1354.18) + 0

t = 1.1867 in

2. Head required thickness, Appendix 1-4(c)

The 36 in OD 2:1 semi-ellipsoidal heads have required thickness of about 1.146 to 1.149 in at the design condition, with a nominal formed thickness of 1.4375 in and no corrosion allowance. The head calculations use Appendix 1-4(c) with a K factor computed from the head geometry.

t = P D K / (2 S E - 0.2 P K) + c

For the registered head geometry, K is evaluated in the COMPRESS head module.

At 1354.18 psi and 130 F, the required corroded thickness is about 1.149 in.

3. Stainless MDMT exemption, UHA-51(d)(1)(a) and UHA-51(g)

For the shell and straight flanges, the stainless toughness check uses UHA-51(d)(1)(a) with carbon content not exceeding 0.10 percent, giving a rated MDMT of -320 F and no impact testing required at the design MDMT of -20 F. For selected nozzles, UHA-51(g) stress-ratio paths are used with coincident ratios in the 0.16 to 0.35 range.

t_r = P R_o / (S E + 0.40 P)

Stress ratio = (t_r E*) / (t_n - c)

Rated MDMT per UHA-51(d)(1)(a) = -320 F

Shell stress ratio example: 0.7911
Nozzle stress-ratio examples: 0.16 to 0.35

4. Shop hydrotest pressure, UG-99(b)

The vertical shop hydrotest is based on 1.3 times MAWP at 70 F, with a listed gauge pressure of 1755 psi at the top head. The shell and heads see slightly higher local test pressures once the static head is included, up to about 1759 psi at the bottom head and shell, all within the 27,000 psi allowable test stress for the stainless material.

P_test = 1.3 x MAWP x LSR

P_test = 1.3 x 1350 x 1.0

P_test = 1755 psi (gauge at the top head)

Why this case study is on the public site

This page adds a stainless vertical vessel example to the public library that uses the UHA toughness path instead of UCS-66. Buyers and engineers can see how a 36 in OD stainless vessel with skirt, optional base ring, Class 600 flanged nozzles, and lug checks is documented in a registered calculation, including UHA-51(d)(1)(a) exemptions, UHA-51(g) coincident ratios, and WRC 107 nozzle and lug load cases.

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APEGA Permit 15926. Calc file reference: 036_1350_0000_+130_-20_V1 Rev. 0.

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]]> 72 in OD x 1405 PSI Horizontal Pressure Vessel https://reececustom.com/72-in-od-x-1405-psi-horizontal-pressure-vessel/ Fri, 15 May 2026 19:47:57 +0000 https://reececustom.com/?p=3598 72 in OD x 1405 PSI Horizontal Pressure Vessel ASME Section VIII Division 1, 2023 Edition, CRN AA0903.2, Alberta registration, […]

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72 in OD x 1405 PSI Horizontal Pressure Vessel

ASME Section VIII Division 1, 2023 Edition, CRN AA0903.2, Alberta registration, March 2024

This example is a horizontal pressure vessel with a 72 in outside diameter shell, 2:1 semi-ellipsoidal heads, and a 24 in boot connection integrated into the pressure boundary. It is registered for 1405 psi at 158 F with a design MDMT of -20 F, and the calculated chamber rated MDMT is -24.9 F at the registered condition.

Reece Custom Manufacturing completed the registered design under APEGA Permit 15926 using ASME Section VIII Division 1, 2023 Edition. The calculation set records RT1 marking, a shop hydrotest basis of UG-99(b) at 1.3 times MAWP, and a horizontal vessel arrangement with saddles, multiple flanged process nozzles, and a booted side opening.

CRNAA0903.2
CodeASME VIII-1, 2023
Design pressure1405 psi
Design temperature158 F
Design MDMT-20 F
Rated MDMT-24.9 F
MAWP1405 psi
Shell specSA-516-70, 72 in OD x 2.75 in nominal
Corrosion allowance0.125 in
Joint efficiency1.00
Empty weight57,529 lb new
Test weight91,472 lb new
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About this example

This vessel is not a plain cylinder with standard nozzles only. The registered pressure boundary includes a 24 in boot shell with a repad, a 24 in 2:1 ellipsoidal boot head, a 20 in flanged head nozzle, several Class 600 flanged shell nozzles, and local-load checks on selected nozzles, which makes it a good public example of a more involved horizontal vessel layout.

Design Basis and Code Compliance

The registered design basis is ASME Section VIII Division 1, 2023 Edition, U.S. Customary units, with internal pressure governing the main chamber. The pressure summary lists 1405 psi MAWP at 158 F, design MDMT of -20 F, rated MDMT of -24.9 F, and no external-pressure design for the chamber.

The main shell and heads are SA-516-70 with full radiography on the shell Category A and B joints and RT1 required marking. The notes also record that the shop hydrotest is based on UG-99(b), the brittle-fracture provision of UG-99(h) is met at 70 F, and wind, seismic, support, operating-weight, and test-weight load cases were included where applicable.

  • Registration: CRN AA0903.2, dated March 25, 2024.
  • Permit reference: APEGA Permit 15926.
  • Main construction: 72 in OD shell, two 2:1 semi-ellipsoidal heads, horizontal saddles, 24 in booted side opening.
  • Marking basis: UG-116 with RT1 designation.
Pressure and Thickness Summary

The main chamber is registered exactly at the design pressure, 1405 psi at 158 F. For the primary pressure parts, the corroded required thicknesses shown in the calculation are 2.5875 in for the 72 in cylindrical shell and head straight flange under Appendix 1-1, and 2.4951 in for the 72 in 2:1 semi-ellipsoidal heads under Appendix 1-4(c).

The 24 in boot components rate above the vessel MAWP, so they do not govern the chamber pressure rating. The boot shell with repad is listed at 1444.21 psi MAWP, the boot straight flange at 2171.17 psi, and the 24 in boot head at 2075.84 psi.

  • Main shell: 72 in OD, 2.75 in nominal, 2.5875 in required at design condition.
  • Main heads: 72 in OD x 2.625 in minimum after forming, 2.4951 in required at design condition.
  • Boot shell opening: 24 in OD with 1.00 in nozzle wall and 2.75 in x 9.5 in reinforcing pad.
  • Chamber rating: 1405 psi MAWP hot corroded, rated MDMT -24.9 F.
Materials and Construction

The main shell, heads, and boot pressure parts are SA-516-70. Flanged nozzles include SA-105 forged components and SA-106 Grade B seamless pipe necks on several Class 600 weld-neck nozzles, with one SA-234 WPB long-radius elbow in the 3 in branch assembly.

The nozzle schedule lists a 20 in Class 600 head nozzle, two 8 in Class 600 shell nozzles, one 4 in Class 600 shell nozzle, one 3 in Class 600 shell nozzle, three 2 in Class 600 hillside shell nozzles, one 2 in Class 600 shell nozzle, one 2 in Class 600 boot-shell nozzle, and one 3 in Class 600 boot-head nozzle. The vessel weight summary records 4006 US gal new capacity, 57,529 lb empty new weight, 80,510 lb operating new weight, and 91,472 lb test new weight.

  • Main pressure parts: SA-516-70.
  • Forged nozzle bodies and flanges: SA-105 where listed.
  • Pipe nozzle necks: SA-106 Grade B seamless where listed.
  • Elbow in 3 in branch assembly: SA-234 WPB.
Calculations Performed (Code Clause Index)

The registered file includes internal-pressure thickness checks for cylindrical shells and straight flanges under Appendix 1-1 and formed 2:1 semi-ellipsoidal heads under Appendix 1-4(c). Opening reinforcement is checked under UG-37 with reinforcement limits under UG-40 and weld-failure-path review under UG-41 where applicable.

Nozzle minimum neck thickness is checked under UG-45, weld sizing is checked under UW-16, and local external nozzle load checks are included for selected nozzles using WRC Bulletin 107 in the registered calculation. MDMT and impact-test treatment follow UCS-66 and UG-84 for the carbon-steel pressure parts, and hydrotest checks follow UG-99(b) with brittle-fracture confirmation under UG-99(h).

  • Appendix 1-1, cylindrical shell and straight-flange pressure thickness.
  • Appendix 1-4(c), 2:1 semi-ellipsoidal head pressure thickness and MAWP.
  • UG-37, UG-40, UG-41, UG-45, UG-76(c), UW-16 for nozzle reinforcement and attachment details.
  • UCS-66 and UG-84 for MDMT and impact-test basis; UG-99(b) and UG-99(h) for shop hydrotest basis.
  • WRC Bulletin 107 local-load checks on selected nozzles in the registered file.
Worked Examples (Selected Calculations)

1. Main shell required thickness, Appendix 1-1

The 72 in OD shell is shown with a corroded required thickness of 2.5875 in at 1406.53 psi and 158 F, using outside-radius cylindrical-shell pressure calculation form with 0.125 in corrosion allowance.

t = P R / (S E - 0.40 P) + c

t = (1406.53 x 36) / (20000 x 1.00 - 0.40 x 1406.53) + 0.125

t = 2.5875 in

2. 72 in 2:1 semi-ellipsoidal head, Appendix 1-4(c)

The 72 in OD 2:1 semi-ellipsoidal heads are listed with corroded required thickness of 2.4951 in at the design condition. The registered file also shows the head factor K calculated at about 0.9951 in the corroded condition.

t = P D K / (2 S E - 0.2 P K) + c

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

For the registered head geometry, K = 0.9951

t = (1406.53 x 72 x 0.9951) / (2 x 20000 x 1.00 - 0.2 x 1406.53 x 0.9951) + 0.125

t = 2.4951 in

3. 24 in boot shell opening reinforcement, UG-37

The 24 in boot opening through the 72 in shell uses a 1.00 in wall with a 2.75 in x 9.5 in reinforcing pad. The registered area-replacement summary shows required reinforcement area of 54.7937 in² and available area of 57.9987 in², so the opening is adequately reinforced at the design condition.

A_{required} = d t_r F + 2 t_n t_r F (1 - f_{r1})

A_{required} = 54.7937 in^2
A_{available} = A_1 + A_2 + A_3 + A_{welds} = 57.9987 in^2

A_{available} > A_{required}, therefore reinforcement is adequate.

4. Shop hydrotest pressure, UG-99(b)

The shop test basis is recorded as 1.3 times MAWP at 70 F. With MAWP of 1405 psi and governing stress ratio of 1.0, the calculated shop hydrotest pressure is 1826.5 psi, before local static-head adjustments shown for individual components.

P_{test} = 1.3 	imes MAWP 	imes LSR

P_{test} = 1.3 	imes 1405 	imes 1.0

P_{test} = 1826.5 	ext{ psi}

Why this case study is on the public site

This vessel page adds a higher-pressure horizontal vessel to the public library and gives buyers, engineers, and AI assistants a registered reference with dimensions, code path, materials, hydrotest basis, and worked calculations in one place. It also shows a vessel with a booted side opening and several flanged nozzles, which is more informative than a basic shell-only example.

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APEGA Permit 15926. Calc file reference: 072_1405_0125_+158_-20_H1 Rev. 0.

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]]> 24 OD x 1440 PSI Horizontal Pressure Vessel, CRN AA6159.213 https://reececustom.com/24-od-x-1440-psi-horizontal-pressure-vessel-crn-aa6159-213/ Fri, 15 May 2026 19:46:42 +0000 https://reececustom.com/?p=3590 24 OD x 1440 PSI Horizontal Pressure Vessel, CRN AA6159.213 ASME Section VIII Division 1, 2023 Edition horizontal pressure vessel, […]

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24 OD x 1440 PSI Horizontal Pressure Vessel, CRN AA6159.213

ASME Section VIII Division 1, 2023 Edition horizontal pressure vessel, 24 inch outside diameter shell, designed for 1,440 psi at 130 °F with a design MDMT of -40 °F and chamber MAWP held to 1,440 psi by configuration and client requirement, not by material limits.

Reece Custom Manufacturing designed, registered, and fabricated this vessel under APEGA Permit 15926, with calculations to the 2023 Edition of ASME Section VIII Division 1 and CSA B51, RT2 radiography on the main seams, and a shop hydrostatic test at 1.3 times MAWP per UG-99(b) before nameplate and shipment.

CRN
AA6159.213 (Alberta, registered 2026)

Code
ASME Section VIII Division 1, 2023 Edition

Design pressure
1,440 psi

Design temperature
130 °F

Design MDMT
-40 °F

Rated MDMT
-40 °F at 1,440 psi (straight flange and UCS-66 limits)

MAWP (hot, corroded)
1,440 psi at 130 °F (user-limited chamber MAWP)

Shell
SA-516-70, 24 in OD × 1.000 in nominal wall × 72 in long, E = 1.0

Corrosion allowance
0.0625 in on pressure parts

Joint efficiency
1.0, RT2 marking per UG-116(e)

Empty weight
From Weight Summary (empty new condition, per calc package)

Hydrotest weight
From Hydrostatic Test section (test condition at SG 1.0)

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About this example

This vessel is a typical small 24 inch OD horizontal pressure vessel for high-pressure oil and gas or industrial service where a compact drum is needed in the 1,440 psi class. It shows how Reece handles 2:1 semi-elliptical head thickness checks, hillside Class 600 nozzles in the heads, shell nozzles with WRC 537 / API 660 nozzle load checks, and small-bore CL6000 outlets on the shell while keeping the chamber rating and MDMT aligned with Canadian registration practice.

Design Basis and Code Compliance

This vessel is designed to ASME Boiler and Pressure Vessel Code Section VIII Division 1, 2023 Edition, in U.S. customary units, with CSA B51 applied for Canadian Registration Number practice. Design conditions are 1,440 psi internal pressure, 130 °F design temperature, and -40 °F design MDMT, with a corrosion allowance of 0.0625 in applied to the shell, heads, and nozzles.

Item Value
Design pressure 1,440 psi internal
Design temperature 130 °F
Design MDMT -40 °F
Chamber MAWP (hot, corroded) 1,440 psi at 130 °F (user-limited MAWP)
Corrosion allowance 0.0625 in pressure parts
Radiography RT2 per UG-116(e)
Postweld heat treatment None per UG-116(f) and thickness limits

The UG-22 loading set includes internal pressure, the weight of the vessel and normal contents, supports such as saddles, wind reactions, seismic reactions, and the hydrostatic test pressure with coincident static head. Loads from internals, snow, cyclic and dynamic reactions, impact, temperature gradients, and abnormal pressures are not included, which matches the project scope and Engineering Notes in the calculation.

Toughness and MDMT are evaluated under UCS-66 and UCS-66.1 for SA-516-70 pressure parts, with Curve D used for shell and heads and bolt MDMTs set by Figure UCS-66 note (c) where applicable. Straight flange thickness and MDMT limits from UCS-66(b)(2) and UCS-66(b)(3) govern the rated -40 °F MDMT at 1,440 psi for the chamber, while CL6000 small-bore outlets qualify to much colder MDMTs on a component basis.

The shop hydrostatic test is defined per UG-99(b) at 1.3 times the chamber MAWP, with test liquid specific gravity of 1.00, maximum test stress limited to 90 percent of yield, and both nozzle intersection stresses and shell stresses verified to be within the allowable test stress in the Hydrostatic Test summary.

Pressure and Thickness Summary

The pressure summary table shows S.E. head #1, S.E. head #2, the straight flanges, the 24 in OD shell, saddles, and each nozzle with design pressure, design temperature, component MAWP, and MDMT. Chamber MAWP is held at 1,440 psi at 130 °F by the user MAWP cap, with several components such as the heads and CL6000 small-bore nozzles capable of higher MAWP or colder MDMT in isolation.

Component Design P (psi) Design T (°F) MAWP (psi) MDMT (°F)
S.E. head #1 1,440 130 1,571.94 -40.4
24 in OD shell 1,440 130 1,440 -40.4
S.E. head #2 1,440 130 1,440 -40.9
3 in CL 600 LWN hillside nozzle in head 1,440 130 ≈1,444 -55
4 in CL 600 LWN shell nozzle 1,440 130 ≈1,444 -55
2 in NPS XXS shell nozzle 1,440 130 1,441.72 -55
1½ in CL6000 TOL shell outlet 1,440 130 1,612.48 -155
3⁄4 in CL6000 outlets 1,440 130 1,612.48–1,612.91 -155

The thickness summary shows 1.000 in nominal wall thickness on the shell and straight flanges, with design thickness around 0.9026 in including 0.0625 in corrosion allowance and E = 1.0, so circumferential stress from internal pressure governs under UG-27. Heads have a formed minimum thickness of 0.9375 in after forming and meet MAWP requirements for 1,440 psi design with margin.

Hydrostatic test pressures are based on 1.3 times MAWP, so the governing shell and flanges see about 1,872 psi plus small static head, and the test summary confirms that all components have test stresses below 90 percent of yield. No field hydrotest condition is specified, and UG-99(h) brittle fracture provisions are satisfied because the 70 °F test temperature is warmer than the recommended minimum of -10 °F.

Materials and Construction

The main pressure boundary uses SA-516-70 plate for the 24 in OD shell and both 2:1 semi-elliptical heads, with longitudinal seams at joint efficiency 1.0 and corrosion allowance of 0.0625 in. Saddles and wear plates are carbon steel sized to carry operating, hydrotest, wind, and seismic loads at the manufacturer’s location without controlling the pressure design.

Component Material Size / rating Notes
Shell SA-516-70 24 in OD × 1.000 in nominal 72 in straight length, E = 1.0
Heads SA-516-70 24 in OD, 2:1 S.E. 0.9375 in min after forming
Shell nozzles Carbon steel flanges and pipe 4 in and 3 in CL 600 LWN Set-in nozzles, fillet welds per UW-16
Head nozzles Carbon steel flanges and pipe 3 in CL 600 LWN hillside Hillside 6.5 in in both heads
Small-bore outlets Carbon steel TOL and couplings CL6000 threaded outlets Instrument and utility connections
Saddles and wear plates Carbon steel Per saddle detail Supports horizontal vessel on foundation

The nozzle schedule in the calculation includes shell nozzles N-S-01 through N-S-08 and head nozzles N-H-01 and N-H-02, each with size, rating, projection, weld detail, and MAWP, along with an attached B16.9 elbow on one shell nozzle. Radiography is summarized as RT2, and no postweld heat treatment is required by thickness or service, so fabrication stays efficient while still meeting code marking requirements.

Calculations Performed (Code Clause Index)

The calculation package documents a full Div. 1 design for this vessel, including shell and head thickness checks, nozzle reinforcement, local-load checks, supports, and hydrotest. The code clause index below matches the clauses applied in the registered calculation.

Wall thickness and MAWP

  • UG-16(b) minimum wall thickness for shell and heads.
  • UG-27(c)(1) circumferential stress thickness for cylindrical shell.
  • Appendix 1-1 outside-diameter formula for shell MAWP.
  • UG-32 general head rules.
  • Appendix 1-4(c) 2:1 semi-elliptical head thickness and MAWP.

Nozzle reinforcement and local loads

  • UG-37 area replacement for set-in shell and head nozzles.
  • UG-40 limits of reinforcement, parallel and normal to the shell.
  • UG-41 weld failure path and exemptions for certain weld details.
  • UG-45 nozzle neck thickness checks.
  • UG-44 small connection external loads where applicable.
  • WRC 537 / API 660 local-load check on a 3 in Class 600 nozzle with combined pressure and external loads.
  • UW-15(b)(1) weld strength calculation exemption for specific details.
  • UW-16 weld sizing for fillet and butt welds at nozzle-to-shell junctions.

Toughness and MDMT

  • UCS-66 toughness curves and impact test exemptions for SA-516-70.
  • UCS-66.1 stress-ratio based MDMT reduction and coincident ratio reporting.
  • UCS-66(b)(2) MDMT limits for certain configurations.
  • UCS-66(b)(3) stress-ratio path for small-bore CL6000 outlets.
  • UCS-66(c)(1) LWN and flange MDMT assessment.
  • UCS-66(g) additional MDMT reduction for impact-tested flanges.
  • UCS-66(i) MDMT reductions for impact-tested nozzles.
  • Figure UCS-66 note (c) for bolt MDMT rating.

Hydrotest, marking, and interpretations

  • UG-99(b) shop hydrostatic test at 1.3 × MAWP with stress checks.
  • UG-99(h) brittle fracture considerations at test temperature.
  • UG-116(e) radiography marking RT2.
  • UG-116(f) postweld heat treatment marking.
  • Interpretations VIII-1-83-66, VIII-1-86-175, VIII-1-01-37, VIII-1-01-150 applied as set in the calculation settings.
Worked Examples (Selected Calculations)

These examples are extracted from the registered calculation. Each shows the inputs, governing code equation, substitution, and result for one part of the vessel design.

Shell wall thickness at 1,440 psi (Appendix 1-1 / UG-27(c)(1))

Inputs: Internal pressure P = 1,440 psi, outside radius Ro = 12 in, allowable stress S = 20,000 psi, joint efficiency E = 1.0, corrosion allowance = 0.0625 in.

t_req (pressure) = P · Ro / (S · E + 0.4 · P)

t_req (pressure) = 1,440 · 12 / (20,000 · 1.0 + 0.4 · 1,440)
                 = 17,280 / 20,576
                 ≈ 0.8399 in

t_design = t_req (pressure) + corrosion
         = 0.8399 + 0.0625
         ≈ 0.9024 in

t_nominal = 1.000 in > t_design ≈ 0.9024 in

The 24 in OD shell with 1.000 in nominal wall and E = 1.0 therefore satisfies UG-27(c)(1) for 1,440 psi internal pressure at 130 °F with the specified corrosion allowance.

2:1 S.E. head thickness and MAWP (Appendix 1-4(c))

Inputs: 2:1 semi-elliptical head, SA-516-70, 24 in OD, minimum thickness after forming t = 0.9375 in, design pressure 1,440 psi, S = 20,000 psi, E = 1.0, K factor from Appendix 1-4(c) per 2:1 geometry.

For a 2:1 semi-elliptical head (Appendix 1-4(c)):

t_req = (P · K · D_o) / (2 · S · E - 0.2 · P)

Rearranging for MAWP with given t:

MAWP = (2 · S · E · t) / (K · D_o + 0.2 · t)

Substituting values from the head calculation:

MAWP_head ≈ 1,571.94 psi > 1,440 psi design

The formed head thickness of 0.9375 in provides MAWP of about 1,572 psi at 130 °F, so the heads are not the governing component for the chamber MAWP of 1,440 psi.

3 in Class 600 shell nozzle reinforcement (UG-37, UG-40, UG-41, UG-45)

Inputs: One 3 in Class 600 LWN shell nozzle with set-in detail, shell radius Ro = 12 in, shell nominal thickness t = 1.000 in, design thickness t_shell = 0.9026 in, nozzle nominal thickness tn = 1.000 in, corrosion allowance C = 0.0625 in, weld detail per UW-16 fillet, reinforcement limits per UG-40.

From the nozzle reinforcement summary:

Required area per UG-37(c):
A_req = 2.0365 in²

Available areas from Fig. UG-37.1:
A1 = 0.3976 in²
A2 = 4.7170 in²
A4 (weld, etc.) = 0.1406 in²

Total available area:
A_avail = A1 + A2 + A4
        = 0.3976 + 4.7170 + 0.1406
        = 5.2552 in²

Check:
A_avail = 5.2552 in² ≥ A_req = 2.0365 in²  →  OK

The nozzle is exempt from weld strength calculations per UW-15(b)(1) for the selected detail, and the fillet weld throat sized per UW-16 meets the required weld size while staying inside the UG-40 reinforcement limits.

Nozzle neck thickness (UG-45): The calculation also checks the nozzle neck required thickness by combining ta from internal pressure and tb from external loads and reinforcement.

ta (UG-27 / UG-22) = 0.2548 in
tb = 0.2883 in

t_UG45 = max(ta, tb) = max(0.2548, 0.2883)
       = 0.2883 in

Available nozzle wall thickness (new):
tn = 1.16 in

tn = 1.16 in ≥ t_UG45 = 0.2883 in  →  OK

WRC 537 / API 660 nozzle local-load check (3 in Class 600)

Inputs: 3 in Class 600 nozzle, internal pressure P = 1,440 psi, mean shell radius Rm = 11.5313 in, local shell thickness T = 0.9375 in, design factor 3, and the applied loads from the calculation (Pr = -740 lbf, Mc = 9,000 lbf·in, Vc = 930 lbf, ML = 11,400 lbf·in, VL = 930 lbf, Mt = 14,520 lbf·in).

Geometric parameters:

γ = Rm / T
  = 11.5313 / 0.9375
  ≈ 12.3

β = 0.875 · r_o / Rm
  = 0.875 · 2.31 / 11.5313
  ≈ 0.1753

Pressure stress intensity factor (from Division 2 Part 4.5):
I = 1.0822

Local circumferential pressure stress:
σ_θ ≈ I · P · R_i / T
    ≈ 18,389 psi

Local longitudinal pressure stress:
σ_L ≈ I · P · R_i / (2 · T)
    ≈ 9,195 psi

Maximum combined stress including external loads:
(PL + Pb + Q) ≈ 21,584 psi

Allowable combined stress:
(PL + Pb + Q)_allow = 3 · S = 3 · 20,000 = 60,000 psi

Check:
21,584 psi ≤ 60,000 psi  →  OK

Maximum local primary membrane stress PL ≈ 19,347 psi
Allowable PL_allow = 1.5 · S = 30,000 psi

Check:
19,347 psi ≤ 30,000 psi  →  OK

The WRC 537 / API 660 evaluation confirms that the nozzle and shell junction can carry the specified external loads and pressure with stress intensities well within the Division 2-based allowable limits used for the local-load check.

Why this case study is on the public site

This 24 OD x 1,440 psi horizontal pressure vessel is a common configuration in Western Canada, and the registered calculation shows how Reece handles Div. 1 wall thickness checks, MDMT and UCS-66 toughness evaluation, nozzle reinforcement, and WRC 537 local-load checks within a single project. Buyers and engineers can see how a real CRN AA6159.213 project balances shell and head thickness, hillside nozzles, small-bore outlets, and hydrotest requirements at 1.3 times MAWP.

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Engineering sealed under APEGA Permit 15926. Reference calculation file 024_1440_00625_+130_-40_H1 Rev. 0, ASME Section VIII Division 1, 2023 Edition, CRN AA6159.213.

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]]> 20 inch horizontal receiver, 150 psi, CRN AA1678.2 https://reececustom.com/20-inch-horizontal-receiver-150-psi-crn-aa1678-2/ Fri, 15 May 2026 19:41:27 +0000 https://reececustom.com/?p=3586 ASME VIII-1, 2023 Edition 20 inch horizontal receiver, 150 psi, CRN AA1678.2 Registered in Alberta in June 2024 for 150 […]

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ASME VIII-1, 2023 Edition

20 inch horizontal receiver, 150 psi, CRN AA1678.2

Registered in Alberta in June 2024 for 150 psi at 250 °F, with design MDMT and rated MDMT both set at −49 °F.

Compact 20 inch OD horizontal receiver built as a general utility vessel with 2:1 semi-ellipsoidal heads, SA-333 Gr 6 shell, SA-516-70 heads, and five set-in nozzles on saddles.

CRNAA1678.2
Design pressure150 psi internal, 15 psi external
Design temperature250 °F
Hydrotest basisUG-99(b), 1.3 × MAWP

Specifications

Reece Custom Manufacturing Inc. designed this vessel under APEGA Permit to Practice 15926. The calculation file is 02001500125250-49H1 Rev. 0, and the chamber summary limits hot corroded MAWP to 150 psi at 250 °F.

CRN
AA1678.2
Code
ASME Section VIII, Division 1, 2023 Edition
Design pressure
150 psi internal
External pressure
15 psi
Design temperature
250 °F
Design MDMT
−49 °F
Rated MDMT
−49 °F
MAWP
150 psi at 250 °F
Shell
20 NPS SA-333 Gr 6 pipe, 75 in long
Corrosion allowance
0.125 in
Empty weight
842 lb new
Test weight
1,750 lb new
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About this example

This example is positioned as a generic 20 inch horizontal receiver for shop-built utility service. The calc models a single chamber with internal pressure, external pressure, saddles, nozzle loads, hydrotest, and material toughness checks, without internals such as trays or packed sections.

Case study details

Design Basis and Code Compliance

The vessel is designed in Design Mode to ASME Section VIII, Division 1, 2023 Edition, with minimum thickness per UG-16(b) of 0.0938 in. RT1 marking applies to the shell and head circumferential seams, shop hydrotest is set to UG-99(b) at 1.3 times MAWP, and UG-22 load cases include vessel weight, saddles, wind, seismic, and nozzle external loads.

Pressure and Thickness Summary

The 20 NPS SA-333 Gr 6 shell has a nominal wall of 0.375 in and a corroded design thickness of 0.2395 in governed by external pressure. Each 2:1 SE SA-516-70 head has required corroded thickness of 0.1987 in for internal pressure and 0.1753 in for external pressure, with 0.3125 in minimum after forming.

Materials and Construction

The shell is SA-333 Gr 6 welded seamless pipe, the heads are SA-516-70, and the flanged nozzles use A350 LF2 weld neck flanges with SA-193 B7 bolting. The vessel is mounted on two saddles with 55 in center-to-center spacing and uses a 0.125 in internal corrosion allowance on shell, heads, and nozzle necks.

Calculations Performed (Code Clause Index)
  • UG-16(b) minimum wall thickness.
  • Appendix 1-1 for cylindrical shell internal pressure.
  • UG-28 and CS-2 for cylindrical shell external pressure.
  • Appendix 1-4(c) for 2:1 semi-ellipsoidal heads.
  • UG-37, UG-40, UG-41, UG-45, UW-16, UG-76(c) for nozzle reinforcement, weld sizing, and nozzle details.
  • UG-99(b) and UG-99(h) for hydrotest pressure and brittle-fracture temperature.
  • UCS-66(b)(3), UCS-66(i), Figure UCS-66 note (c), and UCS-68(b) for MDMT and flange-bolt limits.

Worked examples

Example 1, shell external-pressure thickness

The shell external-pressure case governs. The calc solves UG-28 and CS-2 for 15 psi external pressure and arrives at a required corroded wall of 0.1145 in, then adds 0.125 in corrosion allowance for a design thickness of 0.2395 in.

t_required (external) = 0.1145 in

t_design = t_required + CA = 0.1145 + 0.125 = 0.2395 in

Example 2, shell internal-pressure thickness

Using Appendix 1-1 with outside-diameter form, the shell internal-pressure requirement at 150 psi and 250 °F is about 0.213 in corroded. Because 0.213 in is less than 0.2395 in, the external-pressure case remains controlling.

t_required (internal) ≈ 0.213 in

t_required (internal) < t_design (external) = 0.2395 in

Example 3, 2:1 SE head thickness

For the 20 in OD SA-516-70 heads, Appendix 1-4(c) gives a corroded internal-pressure thickness of 0.1987 in. The adopted minimum thickness after forming is 0.3125 in, so the formed head has margin over both internal and external pressure requirements.

t_required, head (internal) = 0.1987 in

t_min after forming = 0.3125 in

Example 4, 10 in nozzle reinforcement

The 10 NPS set-in nozzle with reinforcement pad passes UG-37 area replacement. The calc reports required reinforcement area of about 0.875 in² and available area of about 3.87 in², so the opening is adequately reinforced.

A_required ≈ 0.875 in²

A_available ≈ 3.87 in² > A_required

Why this case study is on the public site

This receiver is a clear example of a compact registered pressure vessel that still includes external-pressure checks, RT1 weld marking, full hydrotest basis, cold-temperature toughness review, nozzle reinforcement, and saddle support calculations. It is a useful public reference for buyers comparing small horizontal receivers by code edition, CRN, material set, design conditions, and test basis.

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Permit to Practice: 15926
Calc file reference: 02001500125250-49H1 Rev. 0

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]]> 8 NPS x 1,415 psi vertical filter vessel https://reececustom.com/8-nps-x-1415-psi-vertical-filter-vessel/ Fri, 15 May 2026 19:33:16 +0000 https://reececustom.com/?p=3577 8 NPS x 1,415 psi vertical filter vessel ASME VIII-1 (2023), CRN AA6166.213, Alberta, registered February 2026 This 8 NPS […]

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8 NPS x 1,415 psi vertical filter vessel

ASME VIII-1 (2023), CRN AA6166.213, Alberta, registered February 2026

This 8 NPS vertical filter vessel is designed for 1,415 psi at 150 °F with a quick-opening Class 600 LF2 closure at the top and a compact skirt support.

The chamber is registered to operate down to -49 °F MDMT, with several LF2 small-bore connections qualified colder by stress-ratio toughness rules.

Reece Custom Manufacturing designed and registered this vessel under APEGA Permit to Practice 15926 using ASME Section VIII Division 1, 2023 Edition, for Alberta CRN AA6166.213.

The 1,415 psi MAWP is a deliberate user cap in the design file, the hydrotest follows UG-99(b) with full vertical liquid head, and skirt and base-ring checks reference NBC 2020 wind at the manufacturer’s location.

CRN

AA6166.213 (Alberta)

Code

ASME VIII-1 (2023 Edition)

Design pressure

1,415 psi @ 150 °F

Design temperature

150 °F

Design MDMT

-49 °F

Rated MDMT

-49 °F @ 1,415 psi (chamber)

MAWP (hot, corroded)

1,415 psi @ 150 °F (user-limited)

Shell material

SA-333 Gr 6, 8 NPS Sch 80 pipe

Corrosion allowance

0.0625 in internal (pressure parts)

Longitudinal joint efficiency

E = 1.0 (seamless shell, spot RT circumferentials)

Empty weight

313 lb (new)

Hydrotest weight

418 lb (vertical, full of water)

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About this example

This unit is a small vertical filter vessel with an 8 NPS Sch 80 shell, LF2 threaded and flanged small connections, and a quick-opening 8 in Class 600 LF2 closure at the top supplied under its own CRN.

It is sized for high-pressure gas or liquid filtering service where a compact footprint, cold-weather rating, and rapid cartridge access matter more than internal volume.

The 12 to 13 US gal chamber volume and integral skirt make this a good template for wellsite and plant edge locations where structural steel is limited and utilities are simple.

Two 3 NPS XXS nozzle locations are designed for API 660 Class 600 external loads, giving flexibility for inlet and outlet or drain and header tie-ins without re-opening the registration.

Design Basis and Code Compliance

The design is based on ASME Section VIII Division 1, 2023 Edition, in U.S. Customary units, with minimum wall per UG-16(b) set to 0.0938 in plus corrosion allowance.

The vessel is designed for internal pressure only, no external pressure, with UG-22 loadings including internal pressure, vessel and contents weight, skirt reactions, wind, and test pressure with coincident static head.

The design case is 1,415 psi internal pressure at 150 °F, with the chamber MDMT set to -49 °F and the option enabled to limit rated MDMT to the design MDMT even where individual parts qualify lower.

The MAWP is slightly higher than design pressure for most components, but overall MAWP is limited to 1,415 psi by user setting in the calculation file so the registration matches the requested rating.

Radiography is set to RT2 marking under UG-116(e) with seamless cylindrical components and spot RT on circumferential welds per UW-11(a)(5)(b).

No nozzles require full radiography. B16.5 Class 600 flanges on the 3 NPS nozzles are UW-11(a)(4) exempt, and small threaded bosses follow UW-16 sketch details without weld strength checks.

No UG-20(f) exemption is taken. Toughness is established explicitly for all materials.

Pressure and Thickness Summary

The 8 NPS Sch 80 shell is SA-333 Gr 6 pipe, 8.625 in OD by 60 in long.

Nominal thickness is 0.500 in, minimum pipe tolerance thickness is 0.4375 in, and the required design thickness for internal pressure plus corrosion by Appendix 1-1 at 150 °F is 0.4085 in.

For the shell, the combined pressure, weight, and wind longitudinal stress check gives a required thickness around 0.189 in corroded, well below the pressure-governed 0.4085 in design thickness, and the computed MAWP at 150 °F is 1,538 psi before the user cap is applied.

The rated MDMT for the shell is -55 °F from UCS-66(i) and UCS-68(b), but the chamber MDMT is set at -49 °F to match the design setting.

The bottom closure is a modified ASME B16.9 pipe cap in SA-420 WPL6 with a short straight flange above it, both matched to the 8.625 in OD shell.

The cap itself has a required design thickness of 0.3887 in with MAWP 1,645 psi via Appendix 1-4(c), while the straight flange has a required thickness of 0.4085 in with MAWP 1,806 psi, so the flange governs both pressure and MDMT for that component.

A support skirt made from 8.625 in SA-333 Gr 6 pipe is 8.375 in tall with a nominal thickness of 0.322 in and joint efficiency 0.55.

Wind and weight combinations give required thicknesses less than 0.01 in for all load cases, so the skirt is governed by fabrication and anchorage rather than pressure-related stresses.

The vessel capacity is about 12 US gal new and 13 US gal corroded, excluding nozzles and attachments, and the operating weight with liquid is approximately 418 lb new.

The new empty lift weight is 313 lb with a center of gravity about 24.6 in above the bottom datum.

Materials and Construction

The main pressure boundary materials follow the UCS carbon steel path. The shell and the 3 NPS XXS nozzles are SA-333 Gr 6, and the bottom cap and straight flange are SA-420 WPL6.

All small threaded bosses, including 1 in, 2 in, 3/4 in, 1/2 in, and the head connection, are SA-350 LF2 Class 1, consistent with cold-service small-bore practice.

The quick-opening top closure is an 8 in Sch 80 Class 600 device in SA-350 LF2 CL1 with its own CRN 0H04712.213 provided by the closure vendor and referenced in the engineering notes as a supplied component.

Companion flanges on the 3 NPS nozzles are NPS 3 Class 600 weld neck SA-350 LF2 Cl.1, while the 6000-class threaded bosses are designed as plain bosses without separate flanges.

Corrosion allowance on all pressure parts is 0.0625 in on the internal surface, with no external corrosion allowance.

Longitudinal joints are seamless, circumferential seams on shell-to-head and shell-to-flange welds are spot radiographed per UW-11(a)(5)(b), and small-bore boss welds are sized to UW-16 fillet weld sketches with explicit throat checks.

Support components include the SA-333 Gr 6 skirt, a skirt opening in the skirt wall, and an optional base ring sized to transfer overturning and anchor forces under wind.

Calculations Performed (Code Clause Index)
  • Cylindrical shell internal pressure thickness, Appendix 1-1 outside-diameter form, with minimum thickness per UG-16(b).
  • Formed head design and MAWP for the pipe cap, Appendix 1-4(c) with K-factor based on geometry.
  • Straight flange on cap, Appendix 1-1 for the cylinder segment above the cap.
  • Material toughness and MDMT for shell, cap, flange, and larger nozzles, UCS-66(i) with TR from Fig. UCS-66.1 and UCS-68(b).
  • Material toughness and MDMT for low-utilization LF2 bosses, UCS-66(b)(3) stress-ratio path.
  • Nozzle wall thickness, UG-27(c)(1), UG-45, and UG-44 checks where applicable.
  • Reinforcement, UG-37 with limits of reinforcement per UG-40.
  • Weld failure path exempt per UW-15(b)(1) for applicable sketch details.
  • Weld sizing, UW-16.
  • External nozzle loads for the 3 NPS connections checked by WRC 537 with Division 2 Part 4.5 local stress evaluation.
  • Skirt and base ring checks under weight and wind.
  • Shop hydrotest per UG-99(b) and brittle-fracture provisions per UG-99(h).
  • Corroded field hydrotest at 2,160 psi with local primary membrane checks using Division 2 Part 4.5 basis.
Worked Examples (Selected Calculations)

Inputs: Example 1, shell thickness and MAWP at design conditions.

t = (P · Ro) / (S · E + 0.40 · P) + Corrosion
  = (1,417.17 · 4.3125) / (17,100 · 1.00 + 0.40 · 1,417.17) + 0.0625
  = 0.4085 in
P = (S · E · t) / (Ro - 0.40 · t) - Ps
  = (17,100 · 1.00 · (0.5 · 0.875 - 0.0625)) /
    (4.3125 - 0.40 · (0.5 · 0.875 - 0.0625)) - 2.17
  = 1,538.37 psi

The shell qualifies to -55 °F by the UCS-66(i) and UCS-68(b) path, which is below the chamber design MDMT of -49 °F.

Inputs: Example 2, bottom cap thickness by Appendix 1-4(c).

t = (P · Do · K) / (2 · S · E + 2 · P · (K - 0.1)) + Corrosion
  = (1,417.29 · 8.625 · 0.9790) /
    (2 · 17,100 · 1 + 2 · 1,417.29 · (0.9790 - 0.1)) + 0.0625
  = 0.3887 in
P = (2 · S · E · t) / (K · Do - 2 · t · (K - 0.1)) - Ps
  = 1,645.18 psi

The straight flange above the cap requires 0.4085 in and therefore governs the bottom-end component rating.

Inputs: Example 3, 3 NPS XXS nozzle reinforcement and local loads.

UG-37 area replacement at 1,416.85 psi
A required = 0.8647 in²
A available = 1.09 in²
WRC 537 local stress check
PL + Pb + Q = 43,021 psi ≤ 51,300 psi
PL = 25,087 psi ≤ 25,650 psi

The nozzle is adequately reinforced and remains within the local stress allowables for the applied Class 600 load set.

Inputs: Example 4, shop hydrotest pressure.

Ptest = 1.3 · MAWP · LSR
      = 1.3 · 1,415 · 1
      = 1,839.5 psi

Including static head, local shop hydrotest pressures are about 1,842 psi, and the chamber minimum recommended test temperature is about -19 °F, which is well below the 70 °F test temperature stated in the file.

Why this case study is on the public site

This vertical filter vessel shows how Reece Custom Manufacturing registers compact, high-pressure filter shells that use standard 8 in Sch 80 piping, LF2 nozzles, and a quick-opening closure while still meeting 2023 Edition VIII-1 rules for pressure, local loads, and cold-weather toughness.

The file also shows a practical Division 1 pattern that combines UCS-66(i), UCS-66(b)(3), UCS-68(b), and Division 2 Part 4.5 local stress checks inside one registered package.

Start a similar filter vessel design
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Permit to Practice: APEGA 15926

Calc file reference: 008_1415_00625_+150_-49_V1 Rev.0

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]]> 4″ NPS x 1290 PSI Stainless Steel Bridle | CRN AA3841.2 | Reece Custom Manufacturing https://reececustom.com/4-nps-x-1290-psi-stainless-steel-bridle/ Fri, 08 May 2026 21:04:49 +0000 https://reececustom.com/?p=3558 4″ NPS x 1290 PSI Stainless Steel Bridle ASME Section VIII Div. 1, 2023 Edition  |  CRN AA3841.2  |  Registered […]

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4″ NPS x 1290 PSI Stainless Steel Bridle

ASME Section VIII Div. 1, 2023 Edition  |  CRN AA3841.2  |  Registered in Alberta, March 2025

This is a small-diameter stainless steel bridle assembly built and registered for high-pressure level-gauge service in Alberta. The shell is 4.5 inch outside diameter SA-312 TP304 welded and seamless pipe, the top closure is a Class 600 weld-neck flange and blind, the bottom is a B16.9 SCH 80S pipe cap, and a B16.9 4×3 reducing tee is welded into the lower shell to carry a Class 600 process tap. A 1/2 inch threaded outlet on the bottom cap and a 2 inch SCH 160 weldolet on the shell complete the connection set. The assembly is rated for 1,290 psi at 150 F with a -20 F design MDMT and a -20 F rated MDMT at full pressure (limited by the design temperature, not the material).

Reece Custom Manufacturing designed the assembly under APEGA Permit 15926 and registered the calculation file as Canadian Registration Number AA3841.2 on March 14, 2025. Shop hydrostatic test is performed at 1.3 x MAWP per UG-99(b); a vertical field test option is registered at the same gauge pressure. Both options were checked against UG-99(h) brittle-fracture provisions.

CRN
AA3841.2
Code
ASME VIII Div 1, 2023
Design Pressure
1,290 psi
Design Temp
150 °F
Design MDMT
-20 °F
Rated MDMT
-20 °F @ 1,290 psi
MAWP (limited)
1,290 psi
Shell
NPS 4 Sch 80S TP304
Corrosion Allowance
0 in
Joint Efficiency
1.00 throughout
Empty Weight
197 lb
Operating / Test Weight
222 lb
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About this example

A bridle is a small instrumentation tower mounted alongside a process vessel to host level transmitters, sight glasses, and high/low level switches. It is treated as a pressure vessel under ASME Section VIII because it sees the same internal pressure as the parent vessel and is connected to it through a process tap. This unit is a 4 inch NPS bridle in 304 stainless, rated for 1,290 psi sour or sweet service, with a Class 600 top flange that lets the operator unbolt the cover for internals access without breaking the process tap.

Calculation Package and Code Compliance

The five sections below mirror the registered calculation package for CRN AA3841.2. Numbers, code clauses, and equations are reproduced from the as-built design record. Personal identifiers, sealing-engineer credentials, and design-software license details have been removed from the public version.

1. Design Basis and Code Compliance

Design conditions and code edition

Parameter Value
Code of construction ASME Boiler and Pressure Vessel Code, Section VIII Division 1, 2023 Edition
Jurisdiction Alberta, Canada (CRN AA3841.2). First-of-class registration, file 25-050
Design pressure (internal) 1,290 psi
Design temperature 150 °F
Design MDMT -20 °F
Rated MDMT at full design pressure -20 °F (limited to design MDMT; flange components govern at -55 °F bolt-limited, stainless components rate to -320 °F)
MAWP (user-limited) 1,290 psi (governed by Class 600 flanges at 1,318-1,320 psi rating)
Corrosion allowance 0 in (austenitic stainless steel, no corrosion allowance specified)
Joint efficiencies E = 1.00 throughout, Full UW-11(a) Type 1 radiography on circumferential seams; longitudinal seams seamless
Service Liquid level gauge bridle, vertical orientation, Alberta installation
Engineering certification APEGA Permit 15926, sealed March 14, 2025 by Reece in-house engineering

UG-22 loadings considered

UG-22 of Section VIII Division 1 requires the designer to consider every loading that can act on the vessel. For this bridle the following were evaluated and are recorded in the calculation file:

  • Internal design pressure of 1,290 psi at 150 °F.
  • Static head of test liquid during shop and field hydrotest (vertical orientation, water at 70 °F).
  • Self-weight of the bridle and contents in the operating and test conditions.
  • Wind: not applicable, the bridle is supported by mounting brackets to the parent vessel and is not free-standing.
  • Seismic: no skirt, legs, or lug supports, so a seismic analysis was not required at the bridle level.
  • Reactions from attached piping and instrumentation: covered by WRC 537 nozzle local-load checks at the 2 inch shell tap (see Accordion 4).
  • Cyclic loading: not a fatigue-screened service.

Material toughness basis

The shell, pipe cap, straight flange, both nozzle necks, and the integrated tee are SA-312 TP304, SA-403 304, or SA-182 F304 austenitic stainless steel. All of these clear the impact-test exemption under UHA-51(d)(1)(a) because the carbon content does not exceed 0.10 percent, which gives a -320 °F rated MDMT for those components. The 1/2 inch threaded outlet on the head clears UHA-51(g) by stress-ratio at 0.2016, also rated to -320 °F. The B7 bolts on the Class 600 flanges are rated to -55 °F per Figure UCS-66 note (c). The reported -20 °F rated MDMT for the assembly is therefore limited by the design MDMT, not by any material on the unit.

Hydrostatic test basis

Shop hydrotest is the standard UG-99(b) case at 1.3 x MAWP corrected for stress ratio. The Shell 4 inch SCH 80S governs the stress ratio at 0.4804, but because the user-limited MAWP of 1,290 psi is well below the component MAWPs, the stress-ratio multiplier defaults to 1.0 and the test pressure is simply 1.3 x 1,290 = 1,677 psi at the gauge. A vertical field test at the same gauge pressure is also calculated and registered as an option. Test temperature of 70 °F clears UG-99(h) brittle-fracture floor by a wide margin because all pressure-retaining materials are exempt down to -320 °F.

Source: registered calculation package 004_1290_0000_+150_-20_V1 Rev. 0, pages 4 to 14.

2. Pressure and Thickness Summary

Each pressure-retaining component was sized for the governing condition per the relevant ASME clause. The pipe-based components have substantially more pressure capacity than the user-set design pressure, so the assembly MAWP is limited to 1,290 psi by the Class 600 flanges. With zero corrosion allowance, UG-16(b) minimum wall of 1/16 in (0.0938 in) is satisfied by all components.

Pressure summary by component

Component Material Design thickness t (in) MAWP (psi) Rated MDMT (°F) Governing clause
4″ Top Flange (NPS 4 Class 600 WN) SA-182 F304 B16.5 std 1,320 -55 (bolts) ASME B16.5
Top Blind (NPS 4 Class 600) SA-182 F304 B16.5 std 1,320 -55 (bolts) ASME B16.5
Shell (NPS 4 Sch 80S, 44.5″ long) SA-312 TP304 0.1417 2,764.36 -320 Appendix 1-1
B16.9 SCH 80S 4×3 Tee (N-S-02) SA-403 304 — 2,764.06 -320 B16.9 / UG-37
Tee 3″ branch flange (NPS 3 Class 600 WN) SA-182 F304 B16.5 std 1,318.02 -55 (bolts) ASME B16.5
Straight flange on bottom pipe cap SA-403 304 0.1417 3,184.36 -320 Appendix 1-1
B16.9 Bottom Pipe Cap SA-403 304 0.1374 2,969.48 -320 Appendix 1-4(c)
N-H-01: 1/2″ Class 3000 TOL on cap SA-182 F304 0.0282 tr 3,090.30 -320 UG-37, UG-41, UG-45
N-S-01: 2″ SCH 160 WOL on shell SA-182 F304 0.1417 tr 1,318.33 -320 nozzle / -55 flange UG-37, UG-41, UG-45 / B16.5

The flanged connections (top flange, tee branch flange, and 2 inch shell flange) all rate at 1,318 to 1,320 psi at 150 °F under ASME B16.5. The user has chosen 1,290 psi as the design pressure to leave a small margin and to round to a typical class-rating-compatible spec. The pipe-and-cap components carry more than twice the design pressure in their wall calculation.

UG-16(b) governing minimum thickness

For pipe-based components with zero corrosion allowance, UG-16(b) requires a minimum wall of 1/16 in (0.0938 in). The shell, cap straight flange, and pipe cap all clear this floor on their pipe-tolerance-corrected wall (nominal x 0.875). The pressure equation governs design thickness on these components.

Hydrotest summary (vertical field test, gauge = 1,935 psi)

Local test pressure includes static liquid head at the component elevation. Allowable test stress = 0.9 Sy for stainless components per UG-99 commentary. Stress excessive flag is “No” for all components.

Component Local test pressure (psi) Test liquid static head (psi) Stress during test (psi) Allowable test stress (psi) Stress excessive?
4″ Top Flange 1,935.15 0.15 NI NI NI
Shell 4″ SCH 80S 1,936.76 1.76 13,787 27,000 No
B16.9 SCH 80S 4×3 Tee (N-S-02) 1,937.06 2.06 13,789 27,000 No
Straight flange on bottom pipe cap 1,937.10 2.10 13,790 27,000 No
B16.9 Bottom Pipe Cap 1,937.14 2.14 13,790 27,000 No
1/2″ 3M TOL, head (N-H-01) 1,937.18 2.18 18,887 40,500 No
2″ SCH 160 WOL, shell (N-S-01) 1,936.70 1.70 19,049 40,500 No

NI = not investigated (B16.5 flange components are checked by rating, not by test stress). Test gauge pressure at 70 °F = 1.3 x MAWP x LSR = 1.3 x 1,290 x 1 = 1,677 psi for shop test; vertical field test gauge of 1,935 psi shown above. Brittle-fracture provision UG-99(h) satisfied because all stainless components are exempt to -320 °F.

3. Materials and Construction

Material schedule

Component Material specification ASME II-D reference Notes
Shell SA-312 TP304 welded and seamless pipe II-D Table 1A, p. 92, line 25 NPS 4 Sch 80S (XS), 4.5 in OD x 0.337 in nominal wall, 44.5 in long
B16.9 4×3 Reducing Tee (N-S-02) SA-403 304 II-D Table 1A, p. 92, line 40 ASME B16.9 SCH 80S, branch outlet flanged with NPS 3 Class 600 WN
B16.9 Bottom Pipe Cap SA-403 304 II-D Table 1A, p. 92, line 40 ASME B16.9 SCH 80S, modified, with integral straight flange Lsf = 1.2486 in
4″ Top Flange SA-182 F304 II-D Table 1A, p. 92, line 4 NPS 4 Class 600 WN, B16.5-2020, bore 3.826 in, supplied with blind and SNG
4″ Top Blind SA-182 F304 II-D Table 1A, p. 92, line 4 NPS 4 Class 600, B16.5-2020
3″ Tee branch flange SA-182 F304 II-D Table 1A, p. 92, line 4 NPS 3 Class 600 WN, B16.5-2020
2″ Shell flange SA-182 F304 II-D Table 1A, p. 92, line 4 NPS 2 Class 600 WN, B16.5-2020, bore 1.687 in
1/2″ Threaded Outlet (N-H-01) SA-182 F304 II-D Table 1A, p. 92, line 4 NPS 1/2 Class 3000 threaded boss, 0.84 in ID, 0.14 in wall
2″ Weldolet (N-S-01) SA-182 F304 II-D Table 1A, p. 92, line 4 2.375 in OD x 0.344 in wall x 1.69 in long, manufacturer standard
Flange bolting SA-193 B7 Bolt ≤ 2 1/2 II-D Table 3, p. 418, line 32 Standard B16.5 bolting, governs the rated MDMT of the flange joints

Nozzle schedule

Tag Size / Class Location Type Welds Orientation / offset
Top flange NPS 4 Class 600 WN Top of shell Weld-neck flange with blind, gasket, studs, nuts Butt weld to shell, Full UW-11(a) Type 1 Top circumferential
N-H-01 NPS 1/2 Class 3000 Bottom pipe cap (head) Threaded outlet boss, set on the cap Inner fillet Leg41 = 0.25 in 0°, end of nozzle to datum -3.4006 in
N-S-01 NPS 2 Class 600 (weldolet + WN flange) Shell SCH 160 weldolet on shell, NPS 2 Class 600 WN flange on weldolet Inner fillet Leg41 = 0.375 in plus full pen on weldolet 0°, nozzle centerline 10.74 in offset to datum
N-S-02 B16.9 4×3 reducing tee Lower shell, integral Integrated branch tee with NPS 3 Class 600 WN flange on branch Tee-to-shell butt welds, Full UW-11(a) Type 1 Branch oriented for process tap

All nozzle inside edges rounded per UG-76(c). All nozzle weld throats sized per UW-16 and verified by UG-41 weld failure path analysis. The 2 inch weldolet additionally checked for local-load capability against API 660 nozzle loads using WRC 537 (see Accordion 4).

Radiography summary

Joint Category Type Joint efficiency RT
Shell longitudinal seam A Seamless pipe 1.00 None (seamless)
Top flange to shell circumferential B Type 1 butt weld 1.00 Full UW-11(a)
Shell to tee circumferential B Type 1 butt weld 1.00 Full UW-11(a)
Tee to bottom pipe cap circumferential B Type 1 butt weld 1.00 Full UW-11(a)
Pipe-cap head-to-shell seam (B16.9 cap) B Type 1 butt weld 1.00 Full UW-11(a)
Nozzle attachment fillets — Per UW-16 / Fig. UW-16.1 sketch (a) n/a None

Marking includes the RT1 designator under UW-11(a)(5) because all Category A and B butt joints receive full radiography.

Dimensional summary

  • Shell: 4.5 in OD x 0.337 in nominal wall x 44.5 in long.
  • Pipe cap: 2.5 in overall length E, 1.2486 in straight flange Lsf.
  • Top flange: NPS 4 Class 600 WN, 3.826 in bore.
  • 2 inch weldolet projection: 1.3511 in available outside vessel; flange face at 4.4811 in projection.
  • Empty weight: 197 lb. Operating weight: 222 lb. Test weight: 222 lb. Capacity 3 US gal. Surface area 10 ft².
  • Liquid level reference: 57 in from datum.

4. Calculations Performed (Code Clause Index)

The registered calculation file performs the following code checks. Each one is a discrete pass/fail item in the design record and is reproducible from the inputs in Section 1.

Pressure-retaining wall thickness

  • UG-27(c)(1) circumferential stress for cylindrical shells. Shown as the Appendix 1-1 outside-diameter form for radii Ro greater than 0.5 R.
  • Appendix 1-1 alternative thickness equations on the outside diameter basis. Used for the shell, the pipe-cap straight flange, and the cylindrical body of the B16.9 cap.
  • Appendix 1-4(c) for the B16.9 pipe cap dish, with the K factor calculated from inside diameter and dish height.
  • UG-32 formed-head requirements (referenced for the cap geometry check).
  • UG-16(b) minimum wall thickness, 1/16 in plus corrosion allowance, applied to all pressure-retaining components. CA = 0 for stainless.
  • UG-23 allowable stress lookup at design temperature for each material grade.
  • UG-80(a) out-of-roundness tolerance check on the shell (1 percent of D).
  • UG-81(a) out-of-roundness for the pipe-cap dish (1.25 percent outside / 0.625 percent inside).

Nozzle and opening reinforcement

  • UG-37 area-replacement reinforcement check for N-H-01 (1/2 inch TOL on cap) and N-S-01 (2 inch weldolet on shell). Each nozzle reports Arequired, Aavailable, A1, A2, A3, A5, Awelds.
  • UG-40 limits of reinforcement parallel (LR) and normal (LH) to the vessel surface.
  • UG-41 weld failure path analysis. The 2 inch weldolet is exempt from weld strength calculations per UW-15(b)(1) because the joint conforms to Fig. UW-16.1 sketch (a). The 1/2 inch TOL is also exempt under the same provision.
  • UG-45 minimum nozzle neck thickness check for each connection.
  • UG-76(c) requirement to round inside edges of openings.
  • WRC 537 external-loads check on the 2 inch shell weldolet (N-S-01) using API 660 nozzle load envelope. Four load cases checked: operating, hot shut-down, Pr reversed, and Pr reversed at hot shut-down. Maximum combined stress 37,871 psi against an allowable of 60,000 psi; maximum local primary stress 19,950 psi against 30,000 psi. No overstress.

Welds and joint design

  • UW-11(a) Type 1 full radiography on all Category A and B circumferential butt joints, qualifying the assembly for the RT1 marking.
  • UW-15(b)(1) nozzle weld strength exemption for fillet welds conforming to Fig. UW-16.1 sketch (a).
  • UW-16 weld sizing for nozzle attachment fillets. 1/2 inch TOL Leg41 = 0.25 in (throat 0.175 in vs. 0.0656 in required); 2 inch weldolet Leg41 = 0.375 in (throat 0.2625 in vs. 0.0938 in required).
  • UCS-66.3(a) tapered-butt-weld transition checks where dissimilar wall thicknesses meet (referenced in the design record for any pipe-to-fitting wall mismatch).

Toughness and brittle fracture

  • UHA-51(d)(1)(a) impact-test exemption for austenitic stainless steels with carbon content not exceeding 0.10 percent. Applies to the shell, pipe cap, straight flange, B16.9 tee, top flange, blind, branch flange, and the 2 inch weldolet shell flange. Rated MDMT for these components is -320 °F.
  • UHA-51(g) stress-ratio path used for the 1/2 inch TOL: coincident ratio 0.2016, rated MDMT -320 °F.
  • Figure UCS-66 note (c) for the SA-193 B7 bolts on the Class 600 flanges. Rated MDMT -55 °F.
  • Assembly rated MDMT is reported as -20 °F because the user-specified design MDMT (-20 °F) is the warmer of the design and component limits, and the rated MDMT cannot be colder than the design MDMT.

Hydrostatic test

  • UG-99(b) shop hydrostatic test at 1.3 x MAWP. Lowest stress ratio across components is 0.4804 (Shell 4 inch SCH 80S), but because the user-limited MAWP is well below the component MAWPs, the LSR multiplier defaults to 1.0 in the test-pressure calculation.
  • UG-99(h) brittle-fracture provision: shop test at 70 °F is well above the -320 °F floor for all stainless components.
  • Vertical field test option calculated at the same gauge pressure (1,935 psi local) for in-service retest, all components clear with stress less than allowable.

Marking and registration

  • UG-116 nameplate marking content. RT1 designator applied because all Category A and B joints are full radiography.
  • Canadian Registration: CRN AA3841.2, jurisdiction Alberta. Calculation file 25-050.
Deficiencies: none. Every clause checked passes with margin. The pressure-limiting items are the Class 600 flanges (1,318 to 1,320 psi rating at 150 °F), the toughness-limiting items are the SA-193 B7 bolts at -55 °F, and the assembly is operating well within both envelopes at 1,290 psi and -20 °F design MDMT.

5. Worked Examples (Selected Calculations)

The four examples below are pulled from the registered calculation package and show the actual numbers used to register CRN AA3841.2. Each one shows the input, the equation, the substitution, and the result.

Example 1. Shell wall thickness and MAWP, Appendix 1-1

NPS 4 Sch 80S (XS) SA-312 TP304 welded and seamless pipe, 4.5 in OD, 0.337 in nominal wall, pipe tolerance factor 0.875, 1.00 joint efficiency, 0 corrosion allowance.

Inputs: P + Ps = 1,291.76 psi (design plus 1.76 psi static head), Ro = 2.25 in, S = 20,000 psi (SA-312 TP304 at 150 °F), E = 1.00, c = 0.

Required thickness:

t = (P x Ro) / (S x E + 0.40 x P) + Corrosion
t = (1,291.76 x 2.25) / (20,000 x 1.00 + 0.40 x 1,291.76) + 0
t = 0.1417 in

UG-16(b) check: 1/16 + c = 0.0938 + 0 = 0.0938 in. Pressure equation governs.

MAWP at 150 °F (using nominal wall x mill tolerance 0.875):

P = (S x E x t) / (Ro - 0.40 x t) - Ps
P = (20,000 x 1.00 x (0.337 x 0.875)) / (2.25 - 0.40 x (0.337 x 0.875)) - 1.76
P = 2,764.36 psi

The shell carries about 2.14 times the user-set design pressure. UHA-51(d)(1)(a) stress ratio = (0.1417 x 1) / (0.2949 – 0) = 0.4804. Because TP304 carbon content does not exceed 0.10 percent, the shell is exempt from impact testing and the rated MDMT is -320 °F.

Example 2. B16.9 Bottom Pipe Cap, Appendix 1-4(c)

SA-403 304, NPS 4 SCH 80S B16.9 cap modified, dish height h = 0.9565 in, inside diameter D = 3.826 in, outside diameter Do = 4.5 in.

Geometry factor K (corroded condition, c = 0):

K = (1/6) x [2 + (D / (2 x h))^2]
K = (1/6) x [2 + (3.826 / (2 x 0.9565))^2]
K = 1.0

Required thickness, corroded at 150 °F:

t = (P x Do x K) / (2 x S x E + 2 x P x (K - 0.1)) + Corrosion
t = (1,292.14 x 4.5 x 1) / (2 x 20,000 x 1 + 2 x 1,292.14 x (1 - 0.1)) + 0
t = 0.1374 in

MAWP, corroded at 150 °F:

P = (2 x S x E x t) / (K x Do - 2 x t x (K - 0.1)) - Ps
P = (2 x 20,000 x 1 x (0.875 x 0.337)) / (1 x 4.5 - 2 x (0.875 x 0.337) x (1 - 0.1)) - 2.14
P = 2,969.48 psi

The straight flange on the cap controls the cap MDMT, and clears UHA-51(d)(1)(a) at -320 °F.

Example 3. 2″ SCH 160 Weldolet on Shell, UG-37 area replacement

SA-182 F304 manufacturer-standard weldolet, 2.375 in OD, 0.344 in wall, 1.687 in inside diameter, 1.69 in long, set on the shell with a 0.375 in inner fillet (Leg41). Local vessel minimum thickness = 0.2949 in.

Required nozzle wall (UG-27):

trn = (P x Rn) / (Sn x E - 0.6 x P)
trn = (1,291.7 x 0.8435) / (20,000 x 1 - 0.6 x 1,291.7)
trn = 0.0567 in

Required shell wall (Appendix 1-1):

tr = (P x Ro) / (S x E + 0.40 x P)
tr = (1,291.7 x 2.25) / (20,000 x 1 + 0.40 x 1,291.7)
tr = 0.1417 in

Limits of reinforcement (UG-40):

LR (parallel) = max [d, Rn + (tn - Cn) + (t - C)]
              = max [1.687, 0.8435 + 0.344 + 0.2949]
              = 1.687 in

LH (normal)   = min [2.5 x (t - C), 2.5 x (tn - Cn) + te]
              = min [2.5 x 0.2949, 2.5 x 0.344 + 0]
              = 0.7373 in

Area required (UG-37(c)):

A = d x tr x F + 2 x tn x tr x F x (1 - fr1)
A = 1.687 x 0.1417 x 1 + 2 x 0.344 x 0.1417 x 1 x (1 - 1)
A = 0.239 in^2

Area available:

A1 (excess shell) A2 (excess nozzle) A41 (welds) Aavailable
0.2585 in² 0.4236 in² 0.1406 in² 0.8227 in²

Aavailable (0.8227 in²) is greater than Arequired (0.239 in²), so the opening is adequately reinforced with a margin of 3.4x.

UG-45 minimum nozzle neck check:

ta (App 1-1)  = 0.0748 in
ta (UG-22)    = 0.1273 in
ta = max[ta(App 1-1), ta(UG-22)] = 0.1273 in
tb (App 1-1)  = 0.1417 in
tb1 = max[tb, tb_UG16] = 0.1417 in
tb  = min[tb3 (std wall - mill tol), tb1] = 0.1348 in
tUG-45 = max[ta, tb] = 0.1348 in
Available wall tn = 0.344 in. Passes with 2.55x margin.

UHA-51(d)(1)(a) toughness: stress ratio (0.1417 x 1) / (0.2949 – 0) = 0.4804, carbon content not exceeding 0.10 percent, so rated MDMT = -320 °F.

Example 4. 1/2″ Class 3000 TOL on Bottom Cap, UHA-51(g) stress-ratio path

SA-182 F304 threaded outlet boss on the bottom pipe cap, 0.84 in inside diameter, 0.14 in nominal wall, no corrosion allowance. Local vessel minimum thickness = 0.2949 in. Inner fillet Leg41 = 0.25 in.

Required nozzle wall:

tr = (P x R) / (S x E - 0.6 x P)
tr = (1,292.17 x 0.42) / (20,000 x 1 - 0.6 x 1,292.17)
tr = 0.0282 in

UHA-51(g) stress ratio:

Stress ratio = (tr x E*) / (tn - c)
             = (0.0282 x 1) / (0.14 - 0)
             = 0.2016

The coincident ratio of 0.2016 is below the threshold for impact-test exemption under UHA-51(g), so the threaded outlet is exempt from impact testing at the design MDMT of -20 °F with a rated MDMT of -320 °F. Material is austenitic stainless and the carbon content does not exceed 0.10 percent, which is the parallel exemption under UHA-51(d)(1)(a).

Other components, summary

Component Design thickness t (in) MAWP (psi) Stress ratio Rated MDMT (°F) Toughness path
Shell 4″ SCH 80S 0.1417 2,764.36 0.4804 -320 UHA-51(d)(1)(a)
Straight flange on bottom cap 0.1417 3,184.36 0.4205 -320 UHA-51(d)(1)(a)
B16.9 Bottom Pipe Cap (dish) 0.1374 2,969.48 (governed by str. flange) -320 UHA-51(d)(1)(a)
1/2″ TOL on cap (N-H-01) 0.0282 3,090.30 0.2016 -320 UHA-51(g)
2″ Weldolet on shell (N-S-01) 0.1417 (shell tr) 1,318.33 (flange govs) 0.4804 -320 (nozzle) / -55 (bolts) UHA-51(d)(1)(a) / UCS-66 note (c)
B16.9 4×3 Tee (N-S-02) — 2,764.06 — -320 UHA-51(d)(1)(a)
4″ Top Flange (NPS 4 Cl 600 WN) B16.5 std 1,320.00 n/a -55 Bolt-limited per UCS-66 note (c)

Source: registered calculation package 004_1290_0000_+150_-20_V1 Rev. 0, pages 14 to 46. Personal identifiers, license numbers, and seal images have been removed from the public version. The original sealed PDF is held in the Reece quality records.

Why this case study is on the public site

Bridles, level columns, and small instrumentation towers are a routine line item for any oil and gas facility, and they often get specified late in the project when most of the engineering bandwidth is spent on the parent vessel. Reece registers small ASME Section VIII assemblies like this one in Alberta and other Canadian provinces under a single Permit-to-Practice and a single quality program. Buyers and design engineers shopping for that work want to see actual code calculations, not a brochure photograph. This page reproduces the registered calculation summary for one such bridle so an engineer can read it, an AI search assistant can cite it, and a procurement engineer can decide whether Reece is the right shop for a similar job.

If you have a bridle, level column, separator, or small pressure-rated process assembly that needs to be designed, fabricated, and registered to ASME Section VIII Div. 1, Reece can take it from sketch to CRN under one roof.

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Reece Custom Manufacturing · APEGA Permit 15926 · ASME Section VIII Div. 1 · Alberta CRN registrant.
Calculation file 004_1290_0000_+150_-20_V1 Rev. 0, registered March 14, 2025. Project file 25-050.

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]]> 8″ NPS x 285 PSI Vertical Pressure Vessel https://reececustom.com/8-nps-x-285-psi-vertical-pressure-vessel/ Thu, 30 Apr 2026 16:01:44 +0000 https://reececustom.com/?p=3516 8″ NPS x 285 PSI Vertical Pressure Vessel ASME Section VIII Div. 1, 2023 Edition | CRN W9112.213 | Registered […]

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8" NPS x 285 PSI Vertical Pressure Vessel

ASME Section VIII Div. 1, 2023 Edition | CRN W9112.213 | Registered in Alberta, July 2025

This is a small vertical pressure vessel built and registered for natural gas service in Alberta. The shell is 8.625 inch outside diameter SA-53 Grade B seamless pipe, the top is an SA-234 WPB B16.9 pipe cap, and the bottom is a 0.75 inch SA-516-70 welded flat cover joined to the shell with a UW-13.2 (e-1) detail. Four threaded half-couplings give the vessel its process and instrument connections. The vessel is rated for 285 psi at 650 F with a -20 F design MDMT and a -55 F rated MDMT at full pressure.

Reece Custom Manufacturing designed the vessel in Codeware COMPRESS 2024, certified the calculations under APEGA Permit 15926, and assigned Canadian Registration Number W9112.213. Reference number 14-194-REG. Shop hydrostatic test was performed at 1.3 x MAWP per UG-99(b); a 1.5 x MAWP corroded option is registered for field test if required.

CRN
W9112.213
CODE
ASME VIII Div 1, 2023
DESIGN PRESSURE
285 psi
DESIGN TEMP
650 °F
DESIGN MDMT
-20 °F
RATED MDMT
-55 °F @ 285 psi
MAWP (LIMITED)
285 psi
SHELL
NPS 8 Sch 40 SA-53B
CORROSION ALLOWANCE
0.125″ inner
JOINT EFFICIENCY
0.85 shell, 1.00 cover
EMPTY WEIGHT
158 lb new / 103 lb corr.
TEST WEIGHT
258 lb

Calculation Package and Code Compliance

The five sections below mirror the registered calculation package for CRN W9112.213. Numbers, code clauses, and equations are reproduced from the as-built design record. Personal identifiers, sealing-engineer credentials, and software license details have been removed from the public version.

Design conditions and code edition

ParameterValue
Code of constructionASME Boiler and Pressure Vessel Code, Section VIII Division 1, 2023 Edition
JurisdictionAlberta, Canada (CRN W9112.213). Reference 14-194-REG
Design pressure (internal)285 psi
Design temperature650 °F
Design MDMT-20 °F
Rated MDMT at full design pressure-55 °F
MAWP (component-limited by welded cover)285 psi
Corrosion allowance0.125 in inner surface, 0 in outer surface
Joint efficienciesE = 0.85 for shell longitudinal seams (seamless pipe, no RT) per UW-11(c) and Type 1; E = 1.00 for welded cover
ServiceSweet natural gas, vertical orientation, Alberta installation
Design softwareCodeware COMPRESS 2024 (Build 8400)
Engineering certificationAPEGA Permit 15926, sealed July 8, 2025 by Reece in-house engineering

UG-22 loadings considered

UG-22 of Section VIII Division 1 requires the designer to consider every loading that can act on the vessel. For this vessel the following were evaluated and are recorded in the calculation file:

  • Internal design pressure of 285 psi at 650 °F.
  • Static head of test liquid during shop hydrotest (vertical orientation, water at 70 °F).
  • Self-weight of vessel and contents in the new and corroded conditions.
  • Wind: not applicable, vessel is supported by external piping and is not free-standing.
  • Seismic: vessel has no skirt, legs, or lug supports, so seismic calculations were not required (NBC 2020 considered for manufacturer location only).
  • Reactions from attached piping: covered by the attaching pipe spec rather than vessel design.
  • Cyclic loading: not a fatigue-screened service.

Material toughness basis

All pressure-retaining materials were screened for low-temperature toughness using UCS-66, with reductions per UCS-66.1. The shell, top cap, straight flange, and all four nozzles fall within the impact-test exemption. The welded cover plate, governed by UCS-66 Curve D, also clears the exemption check. The result is a -55 °F rated MDMT at full design pressure of 285 psi without any impact testing.

Hydrostatic test basis

Two test conditions are registered. The shop test is the standard UG-99(b) case at 1.3 x MAWP corrected for stress ratio. A field corroded test at 1.5 x MAWP is also calculated and registered as an option for in-service retest. Test temperature of 70 °F is above the brittle-fracture floor required by UG-99(h).

Source: registered calculation package 008_0285_0125_+650_-20_V_1 Rev. 1, pages 4 to 5 and 12 to 13.

Each pressure-retaining component was sized for the governing condition per the relevant ASME clause. The shell, top cap straight flange, and three of four nozzles end up governed by UG-16 minimum thickness, not by the pressure equation. The welded bottom cover is the pressure-limiting component at 285 psi MAWP.

Pressure summary by component

ComponentMaterialDesign thickness t (in)MAWP (psi)Rated MDMT (°F)Governing clause
Shell (pipe, NPS 8 Sch 40)SA-53 Gr B Smls0.209536.11-55Appendix 1-1
Top: B16.9 pipe capSA-234 WPB0.205568.10-55Appendix 1-4(c)
Top: cap straight flangeSA-234 WPB0.209676.33-55Appendix 1-1
Bottom: welded flat coverSA-516-700.7072328.47-55UG-34(c)(2), Sketch (h)
N-H-01: 2″ Class 3000 cplg, head, set-through, double filletSA-105 (norm.)0.0171 tr543.73-155UG-37, UG-41, UG-44
N-S-01: 2″ Class 6000 cplg, shell, set-on, single filletSA-105 (norm.)0.0172 tr375.00-155UG-37, UG-41, UG-44
N-S-02: 1″ Class 6000 cplg, shell, passes Cat A jointSA-105 (norm.)0.0095 tr375.00-155UG-37, UG-41, UG-44
N-S-03: 3/4″ Class 6000 cplg, shell, set-on, single filletSA-105 (norm.)0.0093 tr375.00-155UG-37, UG-41, UG-44

The vessel MAWP is limited to 285 psi by the welded cover, even though the shell and cap have substantially more pressure capacity. This is a deliberate choice on small vessels because increasing the cover plate thickness adds cost and welding for no benefit, the cover already meets the 285 psi service requirement.

UG-16(b) governing minimum thickness

For pipe-based components, UG-16(b) requires a minimum wall of 1/16 in plus corrosion allowance. With 0.125 in inner CA, that comes to 0.0938 + 0.125 = 0.2188 in. The shell, cap, and straight flange all clear this floor and the pressure equation drives a thinner number, so UG-16 is the governing condition for those parts.

Hydrotest summary (shop test, UG-99(b))

ComponentLocal test pressure (psi)Stress during test (psi)Allowable test stress (psi)Stress excessive?
B16.9 pipe cap top (governs UG-99(b) ratio)370.675,43331,500No
Straight flange on cap370.674,77731,500No
Shell372.555,46131,500No
Welded cover bottom372.5513,92251,300No
1″ cplg N-S-02372.145,27047,250No
2″ cplg N-H-01 (head)370.534,72347,250No
2″ cplg N-S-01 (shell)372.385,27347,250No
3/4″ cplg N-S-03371.925,26747,250No

Test gauge pressure at 70 °F = 1.3 x MAWP x LSR = 1.3 x 285 x 1 = 370.5 psi. Field test condition not investigated. Brittle-fracture provision UG-99(h) satisfied because test temperature of 70 °F is above the -25 °F minimum recommended temperature.

Material schedule

ComponentMaterial specificationASME II-D referenceNotes
ShellSA-53 Grade B, seamless pipeII-D Table 1A, p. 16, line 15NPS 8 Sch 40 (Std), 8.625 in OD x 0.322 in nominal wall
Top capSA-234 WPBII-D Table 1A, p. 16, line 18ASME B16.9 pipe cap, modified, 0.322 in nominal wall
Welded bottom coverSA-516 Grade 70II-D Table 1A, p. 20, line 45Plate, 0.75 in thick, normalized, fine grain practice
Threaded half-couplings (all four)SA-105 (normalized)II-D Table 1A, p. 20, line 31Class 3000 (head) and Class 6000 (shell)

Nozzle schedule

TagSize / ClassLocationTypeWeldsOrientation / offset
N-H-01NPS 2 Class 3000Head (top cap)Threaded half-coupling, set throughInner and outer fillet (double fillet)Centered on cap
N-S-01NPS 2 Class 6000ShellThreaded half-coupling, set onOuter fillet only (single fillet)0°, 36 in offset to datum
N-S-02NPS 1 Class 6000ShellThreaded half-coupling, set on, passes through Category A jointOuter fillet (single fillet) plus joint reinforcement180°, 5 in offset to datum
N-S-03NPS 3/4 Class 6000ShellThreaded half-coupling, set onOuter fillet only (single fillet)180°, 18 in offset to datum

All nozzle inside edges rounded per UG-76(c). All nozzle weld throats sized per UW-16 and verified by UG-41 weld failure path analysis.

Radiography summary

JointCategoryTypeJoint efficiencyRT
Shell longitudinal seamASeamless pipe, Type 10.85None per UW-11(c)
Top: cap to shell circumferentialBType 1 butt with one-side weld0.85None per UW-11(c)
Bottom: welded cover to shellCFigure UW-13.2 sketch (e-1) corner joint1.00None required
All nozzle longitudinal seamsASeamless half-coupling forgingn/aNone

Dimensional summary

  • Overall length: shell 52 in plus B16.9 cap straight flange of 1.723 in plus cap dish, plus welded cover thickness of 0.75 in.
  • Outside diameter at shell: 8.625 in (NPS 8 Sch 40 Std).
  • Welded cover outside diameter: 10.875 in (cover overhangs the shell to provide the UG-34 weld land).
  • Cover weld bevel depth: 0.572 in (clears the UW-13.2 minimum of 0.519 in).
  • Empty weight new: 158 lb. Empty weight corroded: 103 lb. Test weight (water filled): 258 lb.

The registered calculation file performs the following code checks. Each one is a discrete pass/fail item in the design record and is reproducible from the inputs in Section 1.

Pressure-retaining wall thickness

  • UG-27(c)(1) circumferential stress for cylindrical shells. Shown as the Appendix 1-1 outside-diameter form for radii Ro greater than 0.5 R.
  • Appendix 1-1 alternative thickness equations on the outside diameter basis. Used for the shell and the cap straight flange.
  • Appendix 1-4(c) for the B16.9 pipe cap dish, with the K factor calculated from inside diameter and dish height in both new and corroded conditions.
  • UG-32 formed-head requirements (referenced for the cap geometry check).
  • UG-34(c)(2) with Sketch (h) for the welded flat cover, using factor C = 0.33 from Figure UG-34.
  • UG-34(d) dimensional checks: shell wall ts greater than or equal to 1.25 tr.
  • UG-16(b) minimum wall thickness, 1/16 in plus corrosion allowance, applied to all pressure-retaining components.

Nozzle and opening reinforcement

  • UG-37 area-replacement reinforcement check for each of N-H-01, N-S-01, N-S-02, N-S-03. Each nozzle reports Arequired, Aavailable, A1, A2, A3, A5, Awelds.
  • UG-40 limits of reinforcement parallel and normal to the vessel surface.
  • UG-41 weld failure path analysis. Three paths checked per nozzle: weld load W, path 1-1 strength, path 2-2 strength.
  • UG-44 external loads on small connections, all four nozzles cleared by inspection.
  • UG-45 minimum nozzle neck thickness check for each connection.
  • UG-76(c) requirement to round inside edges of openings.

Welds and joint design

  • UW-11(c) radiography exemption for Type 1 butt joints in lethal/severe service categories not invoked here.
  • UW-13.2 sketch (e-1) detail for the welded flat cover to shell joint, including bevel depth and outer fillet leg.
  • UW-16 weld sizing for nozzle attachment fillets. All four nozzle fillets sized at Leg41 = 0.2188 in throat.

Toughness and brittle fracture

  • UCS-66 base MDMT screening from Curves A through D for each material.
  • UCS-66.1 reduction in MDMT based on stress ratio trE* / (tn – c).
  • UCS-66(b)(3) stress-ratio path used for the threaded couplings to drop their rated MDMT to -155 °F at the design pressure.
  • UCS-68(c) cold-bending exemption check (not triggered here, no cold-formed parts).

Hydrostatic test

  • UG-99(b) shop hydrostatic test at 1.3 x MAWP, corrected by the lowest stress ratio of the components. The B16.9 pipe cap governs the stress ratio at 1.0000 (all others 1.0638 to 1.1236).
  • UG-99(h) brittle-fracture provision: minimum test temperature of -25 °F. Shop test at 70 °F passes by 95 °F margin.
  • UG-99(l) note for custom flange assemblies (not applicable, no flanges on this vessel).
  • Field corroded test option calculated at 428 psi (1.5 x MAWP basis), all components clear with stress less than allowable test stress.

Marking and registration

  • UG-116 nameplate marking content.
  • Canadian Registration: CRN W9112.213, jurisdiction Alberta. Reference 14-194-REG.
Deficiencies: none. Every clause checked passes with margin. The pressure-limiting item is the welded bottom cover (328.47 psi MAWP), and the toughness-limiting item is the welded cover at -55 °F rated MDMT.

The four examples below are pulled from the registered calculation package and show the actual numbers used to register CRN W9112.213. Each one shows the input, the equation, the substitution, and the result.

Example 1. Shell wall thickness and MAWP, Appendix 1-1

NPS 8 Sch 40 SA-53 Grade B seamless pipe, 8.625 in OD, 0.322 in nominal wall, 0.85 joint efficiency, 0.125 in inner corrosion allowance.

Inputs: P = 285 psi, Ro = 4.3125 in, S = 17,100 psi (SA-53B at 650 °F), E = 0.85, c = 0.125 in.

Required thickness:

t = (P x Ro) / (S x E + 0.40 x P) + Corrosion t = (285 x 4.3125) / (17,100 x 0.85 + 0.40 x 285) + 0.125 t = 0.0839 + 0.125 = 0.209 in

UG-16(b) check: 1/16 + c = 0.0938 + 0.125 = 0.2188 in. Governs over the pressure equation.

MAWP at 650 °F (corroded, with mill tolerance 0.875):

P = (S x E x t) / (Ro – 0.40 x t) – Ps P = (17,100 x 0.85 x (0.322 x 0.875 – 0.125)) / (4.3125 – 0.40 x (0.322 x 0.875 – 0.125)) – 0 P = 536.11 psi

The shell carries about 1.88 times the design pressure in the corroded condition. UCS-66 stress ratio = (0.0839 x 0.85) / (0.2818 – 0.125) = 0.455, which gives a 68.9 °F reduction from the Curve B exemption temperature of -20 °F, so the rated MDMT is -55 °F (limited by the -55 floor).

Example 2. B16.9 pipe cap, Appendix 1-4(c)

SA-234 WPB, NPS 8 Sch 40 cap modified, dish height h = 1.9953 in (new) or 2.1203 in (corroded), inside diameter D = 7.981 in (new) or 8.231 in (corroded).

Geometry factor K (corroded):

K = (1/6) x [2 + (D / (2 x h))^2] K = (1/6) x [2 + (8.231 / (2 x 2.1203))^2] K = 0.9613

Required thickness, corroded at 650 °F:

t = (P x Do x K) / (2 x S x E + 2 x P x (K – 0.1)) + Corrosion t = (285 x 8.625 x 0.961276) / (2 x 17,100 x 0.85 + 2 x 285 x (0.961276 – 0.1)) + 0.125 t = 0.2049 in

MAWP, corroded at 650 °F:

P = (2 x S x E x t) / (K x Do – 2 x t x (K – 0.1)) – Ps P = (2 x 17,100 x 0.85 x (0.875 x 0.322 – 0.125)) / (0.961276 x 8.625 – 2 x (0.875 x 0.322 – 0.125) x (0.961276 – 0.1)) P = 568.10 psi

The cap is governed by UG-16 minimum thickness (0.2188 in), not by the pressure equation, so the wall used in fabrication is the standard cap thickness of 0.322 in.

Example 3. Welded flat cover, UG-34(c)(2) Sketch (h) with UW-13.2 (e-1) weld

SA-516 Grade 70 plate, 0.75 in nominal thickness, normalized and fine-grain practice, attached to NPS 8 shell with the corner-joint detail of Figure UW-13.2 sketch (e-1).

Inputs: d = 8.231 in (corroded ID), C = 0.33 from Figure UG-34 sketch (h), S = 18,800 psi, E = 1.00, P = 285 psi.

Required thickness:

t = d x sqrt(C x P / (S x E)) + Corrosion t = 8.231 x sqrt(0.33 x 285 / (18,800 x 1)) + 0.125 t = 0.7072 in

MAWP at 650 °F:

MAWP = (S x E / C) x (t / d)^2 – Ps MAWP = (18,800 x 1 / 0.33) x (0.625 / 8.231)^2 – 0 MAWP = 328.47 psi

UW-13.2 weld sizing:

a >= 2 x ts + Ci,shell + Co,shell / 0.7 a >= 2 x 0.197 + 0.125 + 0 / 0.7 a >= 0.519 in. Bevel depth provided = 0.572 in. OK.

UG-34(d) check: ts = 0.197 in ≥ 1.25 x tr = 1.25 x 0.0714 = 0.0892 in. OK. UCS-66 Curve D gives a 0.8156 stress ratio and 18.4 °F reduction, so the cover is exempt from impact testing at the -20 °F design MDMT, with a -55 °F rated MDMT at full pressure.

Example 4. Nozzle reinforcement, N-S-03 (3/4 inch Class 6000 coupling)

SA-105 normalized threaded half-coupling, 1.05 in inside diameter, 0.35 in nominal wall, 0.125 in corrosion allowance, set on the shell with a single 0.3125 in inner fillet (Leg41).

UG-37 area replacement, P = 285 psi at 650 °F:

ArequiredAavailableA1AweldsResult
0.0928 in²0.1781 in²0.0804 in²0.0977 in²Adequately reinforced

UG-44 minimum nozzle neck: treq = 0.285 in, tmin = 0.35 in. Passes.

UG-41 weld failure path:

Weld load W (lbf)W1-1 (lbf)Path 1-1 strength (lbf)W2-2 (lbf)Path 2-2 strength (lbf)
688.551,670.6713,913.492,877.257,197.81

All paths are stronger than the applied weld loads.

UCS-66 toughness:

tr = (P x R) / (S x E – 0.6 x P) = (285 x 0.65) / (20,000 x 1 – 0.6 x 285) = 0.0093 in Stress ratio = (tr x E*) / (tn – c) = (0.0093 x 1) / (0.35 – 0.125) = 0.0415 Stress ratio ≤ 0.35, so MDMT per UCS-66(b)(3) = -155 °F.

The coupling is exempt from impact testing at the -20 °F design MDMT with a -155 °F rated MDMT at full pressure.

Other nozzles, summary

NozzleAreq / Aavail (in²)UG-44 treq / tmin (in)UCS-66 stress ratioRated MDMT (°F)
N-H-01 (2″ 3M, head, set-through, double fillet)0.179 / 0.3490.214 / 0.2180.0545-155
N-S-01 (2″ 6M, shell, set-on, single fillet)0.179 / 0.3490.214 / 0.2180.0276-155
N-S-02 (1″ 6M, shell, passes Cat A joint)0.117 / 0.2180.114 / 0.1790.0203-155
N-S-03 (3/4″ 6M, shell, set-on, single fillet)0.0928 / 0.17810.285 / 0.3500.0415-155

Source: registered calculation package 008_0285_0125_+650_-20_V_1 Rev. 1, pages 14 to 30. Personal identifiers, license numbers, and seal images have been removed from the public version. The original sealed PDF is held in the Reece quality records.

Why this case study is on the public site

Most of the small ASME pressure vessels Reece registers in Alberta and other Canadian provinces look like this one in scope: 50 to 200 lb empty, registered under a CRN, sealed by a Permit-to-Practice firm, and built from pipe-and-cap or pipe-and-cover construction. Buyers and design engineers shopping for that work want to see actual code calculations, not a brochure photograph. This page reproduces the registered calculation summary for one such vessel so an engineer can read it, an AI search assistant can cite it, and a procurement engineer can decide whether Reece is the right shop for a similar job.

If you have a pressure vessel, separator, or pressure-rated process equipment that needs to be designed, fabricated, and registered to ASME Section VIII Div. 1, Reece can take it from sketch to CRN under one roof.

Request a Quote on Similar Vessel

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]]> Mobile Test Separator https://reececustom.com/mobile-test-separator/ Mon, 06 Dec 2021 17:15:26 +0000 https://reececustom.com/?p=2793 PURPOSE DRIVEN EQUIPMENT At Reece we take pride in going the extra mile to understand our customers needs. Every piece […]

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PURPOSE DRIVEN EQUIPMENT

At Reece we take pride in going the extra mile to understand our customers needs. Every piece of equipment is custom crafted to spec with careful attention to detail.

This 48” D x 12’ L Mobile Test Separator complete with custom trailer was designed for our client right here in our Redcliff, AB shop. After careful consideration we developed a solution that was convenient, economical and delivered on time.

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]]> Reece Custom Manufacturing Featured by Apex Alberta https://reececustom.com/reece-custom-manufacturing-featured-by-apex-alberta/ Wed, 08 Sep 2021 19:28:24 +0000 https://reececustom.com/?p=2727 The post Reece Custom Manufacturing Featured by Apex Alberta appeared first on Reece Custom Manufacturing.

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