asme

PDHonline Course M398 (3 PDH) ASME Section I & Section VIII Fundamentals Instructor: Jurandir Primo, PE 2012 PDH Online | PDH Center 5272 Meadow Estates Drive Fairfax, VA 22030-6658 Phone & Fax: 703-988-0088 www.PDHonline.org www.PDHcenter.com An Approved Continuing Education Provider www.PDHcenter.com PDH Course M398 www.PDHonline.org 1.0 - INTRODUCTION: The ASME Code design criteria consist of basic rules specifying the design method, design loads, allowable stress, acceptable materials, fabrication, testing, certification and inspection requirements. The design method known as "design by rule" uses design pressure, allowable stress and a design formula compatible with the geometry to calculate the minimum required thickness of pressurized tanks, vessels and pipes. The ASME - American Society of Mechanical Engineers - International Boiler and Pressure Vessel Code is made of 12 sections and contains over 15 divisions and subsections. 1.1 - Code Sections I. Power Boilers II. Materials III. Rules for Construction of Nuclear Facility Components IV. Heating Boilers V. Nondestructive Examination VI. Recommended Rules for the Care and Operation of Heating Boilers VII. Recommended Guidelines for the Care of Power Boilers VIII. Pressure Vessels IX. Welding and Brazing Qualifications X. Fiber-Reinforced Plastic Pressure Vessels XI. Rules for In-service Inspection of Nuclear Power Plant Components XII. Rules for Construction and Continued Service of Transport Tanks SECTION I. Power Boilers This Section provides requirements for all methods of construction of power, electric, and miniature boilers; high temperature water boilers used in stationary service; and power boilers used in locomotive, portable, and traction service. SECTION II. Materials • • • • Part A - Ferrous Material Specifications Part B - Nonferrous Material Specifications Part C - Specifications for Welding Rods, Electrodes, and Filler Metals Part D - Properties SECTION III. Rules for Construction of Nuclear Facility Components • Subsection NCA - General Requirements for Divisions 1 and 2 DIVISION 1 • • • • • • • Subsection NB- Class 1 Components Subsection NC- Class 2 Components Subsection ND- Class 3 Components Subsection NE- Class MC Components Subsection NF - Supports Subsection NG - Core Support Structures Subsection NH - Class 1 Components in Elevated Temperature Service Page 2 of 53 © Jurandir Primo www.PDHcenter.com PDH Course M398 www.PDHonline.org DIVISION 2 • Code for Concrete Containments DIVISION 3 • Containments for Transportation and Storage SECTION IV. Heating Boilers Requirements for design, fabrication, installation and inspection of steam generating boilers, and hot water boilers intended for low pressure service that are directly fired by oil, gas, electricity, or coal. It contains appendices which cover approval of new material, methods of checking safety valve, safety relief valve capacity, definitions relating to boiler design and welding and quality control systems. SECTION V. Nondestructive Examination Requirements and methods for nondestructive examination which are referenced and required by other code Sections. It also includes manufacturer's examination responsibilities, duties of authorized inspectors and requirements for qualification of personnel, inspection and examination. SECTION VI. Recommended Rules for the Care and Operation of Heating Boilers It defines general descriptions, terminology and guidelines applicable to steel and cast iron boilers limited to the operating ranges of Section IV Heating Boilers. It includes guidelines for associated controls and automatic fuel burning equipment. SECTION VII. Recommended Guidelines for the Care of Power Boilers Guidelines to promote safety in the use of stationary, portable, and traction type heating boilers. The section provides guidelines to assist operators of power boilers in maintaining their plants as safely as possible. Contains fuels for routine operation; Operating and maintaining boiler appliances; Inspection and prevention of boiler failure; Design of installation; Operation of boiler auxiliaries; Control of internal chemical conditions SECTION VIII. Pressure Vessels Division 1 - Provides requirements applicable to the design, fabrication, inspection, testing, and certification of pressure vessels operating at either internal or external pressures exceeding 15 psig. Division 2 - Alternative rules, provides requirements to the design, fabrication, inspection, testing, and certification of pressure vessels operating at either internal or external pressures exceeding 15 psig. Division 3 - Alternative rules for Construction of High Pressure Vessels, provides requirements applicable to the design, fabrication, inspection, testing, and certification of pressure vessels operating at either internal or external pressures generally above 10,000 psi. SECTION IX. Welding and Brazing Qualifications Rules relating to the qualification of welding and brazing procedures as required by other Code Sections for component manufacture. Covers rules are related to the qualification and re-qualification of welders and welding and brazing operators in order that they may perform welding or brazing as required by other Code Sections in the manufacture of components. © Jurandir Primo Page 3 of 53 www.PDHcenter.com PDH Course M398 www.PDHonline.org SECTION X. Fiber-Reinforced Plastic Pressure Vessels Requirements for construction of FRP (Fiber-Reinforced Plastic) pressure vessels in conformance with a manufacturer's design report. It includes production, processing, fabrication, inspection and testing methods required. SECTION XI. Rules for In-service Inspection of Nuclear Power Plant Components Requirements for the examination, in-service testing and inspection, and repair and replacement of components and systems in light-water cooled and liquid-metal cooled nuclear power plants. SECTION XII. Rules for Construction and Continued Service of Transport Tanks Requirements for construction and continued service of pressure vessels for the transportation of dangerous goods via highway, rail, air or water at pressures from full vacuum to 3,000 psig and volumes greater than 120 gallons. 1.2 - The ASME B31 Code ASME B31 was earlier known as ANSI B31. The B31 Code for Pressure Piping, covers Power Piping, Fuel Gas Piping, Process Piping, Pipeline Transportation Systems for Liquid Hydrocarbons and Other Liquids, Refrigeration Piping and Heat Transfer Components and Building Services Piping. Piping consists of pipe, flanges, bolting, gaskets, valves, relief devices, fittings and the pressure containing parts of other piping components. It also includes hangers and supports, and other equipment items necessary to prevent overstressing the pressure containing parts. It does not include support structures such as frames of buildings, buildings stanchions or foundations. B31.1 - 2001 - Power Piping Required piping for industrial plants and marine applications. This code prescribes requirements for the design, materials, fabrication, erection, test, and inspection of power and auxiliary service piping systems for electric generation stations, industrial institutional plants, central and district heating plants. The code covers boiler external piping for power boilers and high temperature, high pressure water boilers in which steam or vapor is generated at a pressure of more than 15 PSIG; and high temperature water is generated at pressures exceeding 160 PSIG and/or temperatures exceeding 250 degrees F. B31.2 - 1968 - Fuel Gas Piping This has been withdrawn as a National Standard and replaced by ANSI/NFPA Z223.1, but B31.2 is still available from ASME and is a good reference for the design of gas piping systems (from the meter to the appliance). B31.3 - 2002 - Process Piping Code rules for design of chemical, petroleum plants, refineries, hydrocarbons, water and steam. This Code contains rules for piping typically found in petroleum refineries; chemical, pharmaceutical, textile, paper, semiconductor, and cryogenic plants; and related processing plants and terminals. It prescribes requirements for materials and components, design, fabrication, assembly, erection, examination, inspection, and testing of piping. Also included is piping which interconnects pieces or stages within a packaged equipment assembly. © Jurandir Primo Page 4 of 53 www.PDHcenter.com PDH Course M398 www.PDHonline.org B31.4 - 2002 - Pipeline Transportation Systems for Liquid Hydrocarbons and Other Liquids This Code prescribes requirements for the design, materials, construction, assembly, inspection, and testing of piping transporting liquids such as crude oil, condensate, natural gasoline, natural gas liquids, liquefied petroleum gas, carbon dioxide, liquid alcohol, liquid anhydrous ammonia and liquid petroleum products between producers' lease facilities, tank farms, natural gas processing plants, refineries, stations, ammonia plants, terminals (marine, rail and truck) and other delivery and receiving points. The requirements for offshore pipelines are found in Chapter IX. Also included within the scope of this Code are: • Primary and associated auxiliary liquid petroleum and liquid anhydrous ammonia piping at pipeline terminals (marine, rail and truck), tank farms, pump stations, pressure reducing stations and metering stations, including scraper traps, strainers, and proper loops; • Storage and working tanks including pipe-type storage fabricated from pipe and fittings, and piping interconnecting these facilities; • Liquid petroleum and liquid anhydrous ammonia piping located on property which has been set aside for such piping within petroleum refinery, natural gasoline, gas processing, ammonia, and bulk plants; • Those aspects of operation and maintenance of liquid pipeline systems relating to the safety and protection of the general public, operating company personnel, environment, property and the piping systems. B31.5 - 2001 - Refrigeration Piping and Heat Transfer Components This Code prescribes requirements for the materials, design, fabrication, assembly, erection, test, and inspection of refrigerant, heat transfer components, and secondary coolant piping for temperatures as low as -320 °F (-196 °C), whether erected on the premises or factory assembled, except as specifically excluded in the following paragraphs. Users are advised that other piping Code Sections may provide requirements for refrigeration piping in their respective jurisdictions. This Code shall not apply to: • Any self- contained or unit systems subject to the requirements of Underwriters Laboratories or other nationally recognized testing laboratory: • Water piping and piping designed for external or internal gage pressure not exceeding 15 psi (105 kPa) regardless of size; or • Pressure vessels, compressors, or pumps, but does include all connecting refrigerant and secondary coolant piping starting at the first joint adjacent to such apparatus. B31.8 - 2003 - Gas Transmission and Distribution Piping Systems This Code covers the design, fabrication, installation, inspection, and testing of pipeline facilities used for the transportation of gas. This Code also covers safety aspects of the operation and maintenance of those facilities. B31.8S-2001 - 2002 - Managing System Integrity of Gas Pipelines This Standard applies to on-shore pipeline systems constructed with ferrous materials and that transport gas. Pipeline system means all parts of physical facilities through which gas is transported, including pipe, valves, appurtenances attached to pipe, compressor units, metering stations, regulator stations, delivery stations, holders and fabricated assemblies. © Jurandir Primo Page 5 of 53 11 . which means that the Pressure Vessel fully complies with the ASME Code rules for construction of Pressure Vessels. All welders must be certified. B31G . and temperatures covered in B31. construction. Gas Transmission and Distribution Piping Systems. and multi-unit residences.4 – Imperial and Metric Values: Professionals and students should be well versed in conversion practice.3 . which does not require the range of sizes. Manufacturers have an Authorized Inspector. The National Board of Boiler & Pressure Vessel Inspectors uses the “NB” Symbol as well the “R” Symbol to repair or to alter any previous Stamped Pressure Vessel. ASME B31. commercial and public buildings. institutional. overlap and excessive reinforcement. © Jurandir Primo Page 6 of 53 .1991 . B31. "S". "PP" and "H" Stamps covers the fabrication and alteration of high pressure boilers.Slurry Transportation Piping Systems Rule for design.www. and 4 are based on material included in ASME Guide for Gas Transmission and Distribution Piping Systems.2002 .1996 . Liquid Transportation Systems for Hydrocarbons. tested and approved by the ASME Authorized Inspector. materials. This code covers piping systems that transport aqueous slurries of no hazardous materials. inspection.ASME Certification and Inspection Procedures: The symbols "A". 1. "U". and ASME B31.1. and Alcohols. The processes and approaches within this Standard are applicable to the entire pipeline system.5 times working pressure and observed for leaks.8. 1983 Edition. Parts 2. Liquid Petroleum Gas.Manual for Determining Remaining Strength of Corroded Pipelines The scope of this Manual includes all pipelines within the scope of the pipeline codes that are part of ASME B31 Code for Pressure Piping. inspection and security requirements of slurry piping systems.11. The quality of weld is then checked for lack of weld penetration. unfired pressure vessels. B31.4. it is checked. 3. This Code prescribes requirements for the design. Slurry Transportation Piping Systems. examination and testing of piping systems for building services. It includes piping systems in the building or within the property limits. power piping and heating boilers.org The principles and processes are applicable to all pipeline systems. pressures.9 .Building Services Piping This Code Section has rules for the piping in industrial. ASME B31. At the final inspection the units are hydrostatically tested at 1. This Standard is specifically designed to provide the operator (as defined in section 13) with the information necessary to develop and implement an effective integrity management program utilizing proven industry practices and processes.PDHonline. such as coal. Many US customary unit values presented in the ASME codes do not convert directly into metric values in the ASME editions. who review all the procedures and all the documentation and sign the Data Report Form before to procedure to Stamp the name plate with the “U” or “UM” symbols. Once any ASME Stamped Pressure Vessel is manufactured.com PDH Course M398 www. slag inclusion. Anhydrous Ammonia.PDHcenter. mineral ores and other solids between a slurry processing plant and the receiving plant. who is the judge of code acceptability. installation. 1. fabrication. All material used in manufacture must be documented. Maximum Allowable Stress Value for Common Steels Material Spec.203 Grade A Grade B Grade C High Alloy Steel Plates SA .000 psi tensile strength material will become 20.800 18.300 21. When the vessel design is required fully radiographed longitudinal butt-welded joint.200 12.300 11.300 10.700 20.500 16.org 2.000 16. © Jurandir Primo Page 7 of 53 . Division 2 governs the design by Analysis and incorporates a lower safety factor of 3.300 17.700 18. 2.300 15.5 in.000 16.PDHonline.300 20.0.000 16.500 11. When the vessel design is required non radiographed longitudinal butt-welded joints the vessel will have a joint efficiency factor (E) of 0. is less stringent from the standpoint of certain design details and inspection procedures.240 Division 1 governs the design by Rules.PDHcenter.7.www. drums and headers using the Maximum Allowable Working Pressure (MAWP). requires longitudinal and circumferential butt joints to be examined by full radiograph..700 17. as well as Section VIII.300 16.700 23. Nbr Grade Grade Grade Grade Grade 55 60 65 70 DIVISION 1 DIVISION 2 -20°F to -20°F to 650°F 650°F 13. that these formulae may be also used for calculating wall thickness of tubes and pipes under internal pressure.900 21.700 SA . However. Thus. the maximum allowable stress value for a 60.000 psi tensile strength material is used. resulting in an increase of 43% in the thickness of the plates.000 psi.700 23.700 Grade Grade Grade Grade Grade Grade Grade Grade A B D E 304 304L 316 316L 16. 2. This factor corresponds to a safety factor (or material quality factor) of 3.516 Carbon Steel Plates and Sheets SA .36 SA . tubes. the Maximum Allowable Stress Value is 15.0 – SECTION I & SECTION VIII – Fundamentals: The formulae in ASME Section I and Section VIII are used to determine the minimum required thickness and design pressure of piping.000 16. Paragraph UG-31 states.2 – Pressure Vessels Maximum Allowable Stress Values The maximum allowable stress values to be used in the calculation of the vessel’s wall thickness are given in the ASME Code for many different materials.500 23. if a 60.800 12. These stress values are a function of temperature.200 15.1 – Design: The ASME Boiler Code Section I. and thus incorporates a higher safety factor of 4.300 21. which corresponds to a safety factor of 0.300 17. the cylindrical shell will have a joint efficiency factor (E) of 1.com PDH Course M398 www.000 20.5 in the parent metal.500 13.300 12.000 psi.285 SA . For example. high temperature water boilers used in stationary service.800 psi – allowable stress – Div. and other pressure parts connected directly to the boiler without intervening valves are considered as part of the scope of Section 1. 3.75 in O.www. Solution: For tubing up to and including 5 in O..04 for expanded tubes. manufacturers will choose Division 1 for low-pressure vessels and Division 2 for highpressure vessels. A. Normally.D. M. 0 = for strength welded tubes) S = Maximum Allowable Stress According to ASME Section II. Table 1A: SA-192 = 11.org Many companies require that all their pressure vessels be constructed in accordance with Division 2 because of the more exacting standards.0 – ASME SECTION I Power Boilers – Types. portable. Note: Before starting calculations check the correct stress table in ASME Section II. The Maximum Allowable Working Pressure (MAWP) is 580 psi gauge.. strength welded (e = 0) into place in a boiler. To calculate the minimum required thickness. The maximum allowable stress values at normal temperature range for the steel plates most commonly used in the fabrication of pressure vessels are given in Table above. electric.PDHonline. The tube has an average wall temperature of 650°F. The rules are applicable to boilers in which steam is generated at pressures exceeding 15 psig. and power boilers used in locomotive. S and E symbol stamps. 1.2. according to paragraph PG-27. 3. and miniature boilers.Boiler Tube: Calculate the minimum required wall thickness of a water tube boiler 2.1 – SECTION I – Boiler Tubes up to and including 5 inches O.1. and traction service.com PDH Course M398 www. and high temperature water boilers for operation at pressures exceeding 160 psig and/or temperatures exceeding 250 °F. Design. Rules allow the use of the V. Fabrication. This code covers power boiler superheaters. © Jurandir Primo Page 8 of 53 .D.D. PP. (125 mm): 4. use equation 1.1 above. Inspection & Repair Provides requirements for construction of power. economizers. Table 1A Example 1 . use equation below: b) To calculate the Maximum Allowable Working Pressure (MAWP): Where: t = Minimum Design Wall Thickness (in) P = Design Pressure (psi) D = Tube Outside Diameter (in) e = Thickness Factor (0.PDHcenter. Others find that they can purchase less expensive vessels by allowing manufacturers the choice of either Division 1 or Division 2. Material is carbon steel SA-192. alloy steel. paragraph PG-27. 0.0625 in. or headers may be given with either the inside I or outside (D) measurement. so should be used 1/8 in (3. Using the outside diameter: b) Using the inside radius: Where: t = Minimum Design Wall Thickness (in) P = Design Pressure (psi) D = Tube Outside Diameter (in) R = Tube Radius (in) E = Tube Welding Factor (1. (10 inches nominal) plain end. the material is SA-335 – P1. The piping is 10. Table 1A Example 2 – Steam Piping: Calculate the required minimum thickness of a seamless steam piping which carries steam at a pressure of 900 psi gauge and a temperature of 700°F.5%.0 for seamless pipe.125 in. 0.75 x 580 2 (11. 0.75) + 0 t = 0.800) + 580 + 0.75 in] e = 0 (strength welded) S = [11..org P = [580 psi] D = [2.D.2. Note: Where the manufacturing process produces only standard plate thickness. 4. Allow a manufacturer’s tolerance allowance of 12.77 in O. commonly used. drums. and Headers: The following formulae are found in ASME Section I. The information for piping. 3.800 psi] at [650°F]) t= 2.079 in. Drums.2 – SECTION I – Piping.4 for 900°F & lower.PDHonline.www.85 = for welded pipe) y = Wall Thickness Welding Factor (0.005 (2.7 for 950°F & up) C = Corrosion Allowance (0 for no corrosion. maximum) S = Maximum Allowable Stress According to ASME Section II.2 mm) minimum.PDHcenter.2.com PDH Course M398 www. © Jurandir Primo Page 9 of 53 . 0. 70 in.75 – (2 x 0.0) + 2(0.34 in.1.4 (austenitic steel at 850°F) Use equation 2. Therefore. Table 1A: SA-335 – P1 = 13.800 psi – allowable stress – Div.46 = 12. on the tube sheet and 19.0 (seamless pipe as per PG-9.68 in on the drum.125 = 0. SA-209-T1 at 850°F) E = 1.34 × 1. 12 in.4) (0.1.) with a wall thickness of 0.368 P = 973 psi Example 4 – Welded Tube Boiler Drum: A welded water tube boiler drum of SA-515-60 material is fabricated to an inside radius of 18. The outside pipe diameter is 12. (nominal diam.100 psi (Section II.0. The operating temperature is 850°F.PDHcenter.200 x 0.46 – 0) = 12. Div.4 (Ferritic steel less than 900°F) t= 900 x 10.38 in. D = 12. The plate thickness of the tube sheet and drum are 2.77 in] C=0 S = [13. Table 1A.1) y = 0.PDHonline..75 in (outside diameter) t = 0.46 in.2: P= 2SE (t – C) = D – (2y) (t – C) P = 2 (13. respectively.75 in.75 – 0.800)(1. Use equation 2.34 in. including a manufacturer’s allowance of 12. Example 3 – Maximum Allowable Working Pressure (MAWP): Calculate the Maximum Allowable Working Pressure (MAWP) for a seamless steel pipe of material SA209-T1.org Note: Before starting calculations check the material stress table in ASME Section II.1: P = [900 psi] D = [10.com PDH Course M398 www. The pipe is plain ended. + 0 = 2(13. © Jurandir Primo Page 10 of 53 .46 in C = 0 (3 to 4 inches nominal and larger) S = 13.800] – (SA-335 – P1 alloy steel at 700°F) E = 1.0 y = 0.4)(900) t = 0. .100) (1.49 in.5%.46 – 0) P = 26. and 1.77……….0) x (0.www. Determine the Maximum Allowable Working Pressure (MAWP) based on: Welded Water Tube Boiler Drum: DRUM & TUBESHEET Note: This is a common example of a water tube drum fabricated from two plates of different thickness.34 in C = 0 (3 to 4 inches nominal and larger) R = 18.56 < 2 x 0.49 – 0) Drum – P = 15. b) The tube sheet – consider the drum to have penetrations for boiler tubes.000 x 1. = R + (1 – y (t – C) . = R + (1 – y (t – C) SE (t – C)….086 psi (b) Tube Sheet.4 (Ferritic steel less than 900°F) Drum – P = (15. therefore = 0. Div.000 psi (Section II.56 (circumferential stress = 30% and longitudinal stress = 56%.70 in y = 0. Use equation 2.1.0) (1.49 in C=0 R = 19. = 19. and the ligament efficiencies are 56% horizontal and 30% circumferential.68 in y = 0.com PDH Course M398 www.000) (1. SA-515-60 at 500°F) E = 1. Use equation 2.4 (Ferritic steel less than 900°F) © Jurandir Primo Page 11 of 53 SE (t – C)…. This example has two parts: a) The drum – consider the drum to be plain with no penetrations.49 – 0).PDHonline.PDHcenter.30) t = 2.org The longitudinal joint efficiency is 100%.68 + 0.894 Drum – P = 1.www..49 19.000 psi E = 0.4) (1.68 + (1 – 0. (a) Drum. Thicker material is required where the boiler tubes enter the drum than is required for a plain drum.0 t = 1. Table 1A.4 (inside radius R): Drum – P = Where: S = 15.4 (inside radius R): Tube Sheet – P = Where: S = 15. The operating temperature is not to exceed 500°F. 404 Tube Sheet – P = 1.25SE 4.70 + (1 – 0.385SE: b) Longitudinal Stress (circumferential welds): • When.PDHcenter. P < 0. UM and UV Code symbol stamps are also included.4) (2.000 psi. It contains mandatory and non-mandatory appendices detailing supplementary design criteria. and certification. used for calculating the wall thickness and design pressure of pressure vessels. P < 1. As the ratio of t/R increases beyond 0.746 psi Note: Consider the Maximum Allowable Working Pressure (MAWP) = 1. 4. nondestructive examination and inspection acceptance standards. Rules pertaining to the use of the U. © Jurandir Primo Page 12 of 53 . rules for fired or unfired pressure vessels. a more accurate equation is required to determine the thickness.0 – ASME SECTION VIII – Division 1.0) (2. testing.34 – 0) Tube Sheet – P = 15. The formulae and allowable stresses presented in this sketch are only for Division 1. is divided into three divisions to provide requirements applicable to the design.com PDH Course M398 www. paragraph UG-27.000) (1.org Tube Sheet – P = (15. Division 2.34 18. the main code. special considerations must be given as specified in paragraph U-1 (d). fabrication.2 – SECTION VIII – Thick Cylindrical Shells: For internal pressures higher than 3.086 psi (lowest number).70 + 1. Division 1.5. are: a) Circumferential Stress (longitudinal welds): • When. Division 3: The ASME Section VIII.34 – 0)… = 18. inspection. 4.1 – SECTION VIII – Thin Cylindrical Shells: The formulae in ASME Section VIII.000 x 2.www.PDHonline. 125 in. © Jurandir Primo Page 13 of 53 . commonly used. C = Corrosion Allowance (0 for no corrosion. P > 0. Table 1A.www. are: a) For longitudinal stress (longitudinal welds): When.) Z = Dimensionless Factor 4.0 for seamless pipe.385SE: And. Where: R = Design Radius (in. Di = Inside Diameter of Sphere (in).PDHcenter. 0.85 = for welded pipe). Supplementary Design Formulas used for calculating thick wall and design pressure.org The formulae in ASME Appendix 1. S = Maximum Allowable Stress According to ASME Section II.2P L = Di/2 Where: t = Minimum Design Wall Thickness (in). b) For longitudinal stress (circumferential welds): When.25SE: And. 0.0625 in. maximum). P = Design Pressure (psi). The formula for calculation the wall thickness of a segmented plate of a sphere to be welded in a heat exchanger tube is: t= PL…… + C 2SE – 0.com PDH Course M398 www.PDHonline. 0. E = Tube Welding Factor (1. L = Sphere Radius (in). P > 1.3 – SECTION VIII – Tube Spherical Shells: The standard design method uses an increased wall thickness at the equator line of the vessel to support the additional stresses caused by the attachment of the legs. 0) + 10. Calculate the required thickness of the shell.385SE: Calculate the required shell thickness of an accumulator with P = 7.385SE (7. use equation 1.650 x 18………… + 0 (20.125 = 2(15. and joint efficiency is E = 0.85) – 0. + 0.000 psi. and an internal design pressure of 1.0.545 psi) as 1. Example 6 – Thick Cylindrical Shells: a) When P > 0.125 in. © Jurandir Primo Page 14 of 53 .000 psi – allowable stress.6(7. and E = 1.000 = 30. and E = 1. use equation 1.000 = 3 (20. Since P < 0. For P< 0.125 in.650 psi < 7.www.6P Considering the external radius = 48 in.125 in. The corrosion allowance is 0.25) (3 ½ – 1) = 13.000 psi.385SE (6.1. Assume a corrosion allowance of 0..125).25 in.07 in. R = 18 in.385SE (7. Table 1A.545 psi.com PDH Course M398 www.000 x (48 in.7: t = R (Z ½ .PDHonline.1) = Z = (20.3: t= PR… + C SE – 0. S = 20.700 psi) as 7.000 psi at 450 F°.0) – 0. Assume corrosion allowance = 0. ASME Section II.000 psi < 6.000)(1.000)(0.3: t= t= PR… + C SE – 0. use equation 1.000)(1. SA-515-60 = 15.85. Corrosion allowance = 0.9 in.8(1.000) t = 2.000 psi..650) t = 8.0) – 10.6P 7.000)(1. For P > 0. Div. S = 20. t= 1.385SE: Calculate the required shell thickness of an accumulator with P = 10.PDHcenter.000 10. + 0. Example 7 – Thick Cylindrical Shells: b) When P < 0.650 psi.700 psi.700 psi.000 psi > 7.700 psi) as 10. R = 18 in.org Example 5 – Thin Cylindrical Shells: A vertical boiler is constructed of SA-515-60 according to Section VIII-1.000 t = (18 + 0. + 0.0.36 in.. It has an inside diameter of 96 in. stainless steel. State if this thickness meets Code.7: Calculate the shell thickness. Where two radii are used. and other ferrous and nonferrous metals and alloys.0 – SECTION I: Dished Heads Formulae: Flanged and dished heads can be formed from carbon steel.3) is accurate over a wide range of R/t ratios. where the spherical radius is made via the spinning process and the knuckle is created under the flanging method.1 states that the thickness of a blank.650 = 2. the longer shall be taken as the value of L in the formula.www.2 states: “The radius to which the head is dished shall be not greater than the outside diameter of the flanged portion of the head. with a dish radius of 36. 5.650 = 27.9 in.” Example 9 – Segment of a Spherical Dished Head: Calculate the thickness of a seamless.350 t = (18 + 0) (2.1 – Blank. The temperature does not exceed 480°F. shall be calculated by the following formula: ½ .7. 5.0) – 7.0 in.PDHcenter. blank unstayed dished head having pressure on the concave side. spinning & flanging. Pressure vessel heads and dished ends are essentially the same – the end caps of a pressure vessel tank or an industrial boiler. Flanged and dished heads can be formed in a size range from 4 in to 300 in diameter and in thickness range of 14 Gauge to 1-1/2” thick. when it is a segment of a sphere.7 in.org Example 8 – Comparison between Equation 1. The head has an inside diameter of 42.24 t = 8.000)(1.650 12.0) + 7. unstayed dished head with the pressure on the concave side.1) = Where: t = Minimum thickness of head (in) P = maximum allowable working pressure (psi) L = Concave side radius (in) S = Maximum Allowable Working Stress (psi) Paragraph PG-29.1) = Z = (20. The Maximum Allowable Working Pressure (MAWP) is 360 psi and the material is SA-285 A. Dished heads can be manufactured using a combination of processes. t = R (Z ½ .PDHonline.3 and Equation 1.com PDH Course M398 www.24 (20. comparing the equation 1. They are supplied with a flanged edge to make it easier for the fabricator to weld the head to the main body of the tank. © Jurandir Primo Page 15 of 53 . This shows that the “simple use” of equation (1.000)(1. Unstayed Dished Heads: Paragraph PG-29.3 with another answer using equation 1. 11: P = 225 psi L = 45 in S = 13. © Jurandir Primo Page 16 of 53 .5 0.PDHonline.7 = 2(11.67 in.11 P = 360 psi L = 36. Example 10 .com PDH Course M398 www. since 1.5 in with a dish radius of 45 in.19 in. PG-29.947 > 0. The MAWP is 225 psi.7 in y = 0.org Solution: Use equation 1.0 in x 16 in.www.use the next higher temperature). the minimum thickness of piping is: Where: P = 360 psi D = 42.0) + 2 (0.The radius of the dish meets the criteria.8 . Diameter head is 47.8 (11. unstayed dished head with pressure on the concave side.800 psi (450°F .300)(1. Then. shall be of a lesser thickness than that required for a seamless shell of the same diameter. and temperature does not exceed 428°F.4 (Ferritic steel less than 900°F) E = 1. having a flanged-in manhole 6. use equation 1.PDHcenter.300) t = 1.0 (welded) t= 360 x 42. First thing to check: is the radius of the dish at least 80% of the diameter of the shell? Dish Radius = 45 Shell Diameter 47.6 states: “No head. except a full-hemispherical head.” Then. the material is SA-285-C.67. Therefore.19 > 0.4)(360) t = 0. the calculated head thickness meets the code requirements.300 psi – SA-285 A at 480°F t = 5 (360 x 36) = 4.0 in S = 11.Segment of a Spherical Dished Head with a Flanged-in Manhole: Calculate the thickness of a seamless. the thickness must be increased by 0.356 = 2.114 in.2 .5 in.5 = 2 (13. This thickness is for a blank head.800 psi . full-hemispherical head. © Jurandir Primo Page 17 of 53 .Seamless or Full-Hemispherical Head: The thickness of a blank. It does not exceed 35. full-hemispherical head with the pressure on the concave side shall be calculated by the following formula: t = Minimum thickness of head (in) P = Maximum Allowable Working Pressure (psi) L = Radius to which the head was formed (in) S = Maximum Allowable Working Stress (psi) The above formula shall not be used when the required thickness of the head given by the formula exceeds 35.5 in. S = 13. As 0.PDHcenter.764 × 0.3 requires this thickness to be increased by 15% or 0. the required head thickness is.org t = 5 (225 x 45) = 4.90 in. whichever is greater. P = 900 psi L = 7.www..6% of the inside radius = 7. therefore the calculated thickness of the head meets the code requirements.(SA 285-C at 600°F).15 = 0.2 (900) t = 0.764 + 0.800) – 0. 5.5 x 0. The MAWP is 900 psi and the head material is SA 285-C.. unstayed. use the following formula: Example 11 . t = 0.6% of the inside radius.com PDH Course M398 www. t= 900 x 7. PG-29.67 in.Seamless or Full-Hemispherical Head: Calculate the minimum required thickness for a blank.8 (13.125 in. Then.6%.125 in.PDHonline.800) t = 0. The radius to which the head is dished is 7. Check if this thickness exceeds 35. that is less than 0.13. The average temperature of the header is 570°F. Solution: Use equation 1. unstayed. Instead.125 in.764 in.24 in.125 = ~0.. then. 356R or P > 0.0 .PDHcenter. elliptical (or ellipsoidal) and torispherical shapes.PDHonline.Spherical or Hemispherical Heads: a) When t < 0.665SE: Or.9:1) Torispherical Heads Flanged and Dished Heads Flat Dished Heads Non Standard 80-10 Dished Heads Dished Discs Toriconical Heads 6.SECTION VIII-1: Dished Heads Formulae: The Section VIII-1 determines the rules for dished heads.www.665SE: Or. How the shapes are. © Jurandir Primo Page 18 of 53 . make some confusion for beginners and even professionals users of ASME VIII.356R or P < 0.org 6. b) When t > 0.1 .com PDH Course M398 www. To cast a little light on these subjects see the resume below: Semi-Elliptical Heads (2:1) Spherical or Hemispherical Heads Elliptical or Ellipsoidal Heads (1. The most common configurations are spherical. hemispherical. 85) – 0. R = 48 + 0.0) – 15.000 Y = 45.2.0. Determine the design pressure if the allowable stress is 16300 psi. use equation 2.org Example 12 . Example: Spherical Shell: A spherical pressure vessel with an internal diameter of 120 in has a head thickness of 1 in.com PDH Course M398 www.2P 100 x 48.1. Solution: Since t < 0.000)(1. No corrosion allowance is stated to the design pressure. R = 18.125 = 2(20. Example 13 .Spherical or Hemispherical Head: A pressure vessel is built of SA-516-70 material and has an inside diameter of 96 in. Corrosion allowance is 0.125 in. use equation 2.2 is acceptable.www.665SE < P = 9975 psi < 10000 psi.000 = 3 15.0 in.000 t = R (Y1/3 – 1) = 18.PDHcenter.2(1) P = 460 psi The calculated pressure 460 psi is < 0.PDHonline.0 + 0.85)(1) = 60 + 0. t= t= PR = 2SE – 0. S = 15.000) (0.2t P = 2(16.125 = 48. Assume joint efficiency E = 0.0) + 15.665SE (9213 psi). Solution: As 0. © Jurandir Primo Page 19 of 53 . equation 2.3.0 in.665SE > P = 11305 psi > 100 psi.356R use equation 2. The inside radius in a corroded condition is equal to. and joint efficiency is E = 0.14 in.000 psi.300)(0.25 (31/3 – 1) = 8. Corrosion allowance is 0.125 in. What is the required thickness of the hemispherical head if “S” is 20000 psi? Solution: Since 0. The internal design pressure is 100 psi at 450°F.2(100) t = 0. and E = 1. therefore.000)(1.125 in. Y = 2(15.Thick Hemispherical Head: Calculate the required hemispherical head thickness of an accumulator with P = 10000 psi. P= 2SEt = R + 0.85.000 = 2(15.85. 9D and a knuckle radius of 0.(18.9Di) = 16.500 in Radius L .Elliptical or Ellipsoidal Heads: Calculate the head thickness considering the dimensions given below: Inside Diameter of Head (Di): 18.com PDH Course M398 www. t = 8.(18.125.0 x 0.PDHcenter. 6.org This is the minimum thickness for fully corroded state.PDHonline.2 – Elliptical or Ellipsoidal Heads: The commonly used semi-ellipsoidal head has a ratio of base radius to depth of 2:1 (shown in Fig.17Di) in Straight Skirt Length (h): 1.0 x 0. Total head thickness is 8.0 x 0. The actual shape can be approximated by a spherical radius of 0.17D.17Di) = 3.0 + 0. The required thickness of 2:1 heads with pressure on the concave side is given below: Semi-Elliptical or Semi-Ellipsoidal Heads – 2:1: Example 14 .9Di) in Inside Knuckle Radius (ri): (18. 2a).125 in (corrosion allowance).20 in Radius ri .0 in Inside Crown Radius (L): (18.www.06 in © Jurandir Primo Page 20 of 53 .0 x 0. 29 in a) Required Thickness: t= t= PD + corrosion allowance 2SE – 0.2(200) t = 0. b) Maximum Pressure: P = 2SEt = D + 0. is: or © Jurandir Primo Page 21 of 53 . Note: Ellipsoidal heads and all torispherical heads made of materials having a specified minimum tensile strength > 80 000 psi shall be designed using a value of S = 20.85)(0.20/3.000)(0.06 = 5. 6.org Material and Conditions: Material: SA-202 Gr.06 and L = Di.PDHonline.116 in. B (Room Temperature) Internal Pressure: 200 psi Allowable Stress: 20.3 .06D.116) P = 219 psi.000 psi Head Longitudinal Joint Efficiency: 0.000 psi at room temperature (see UG-23).2 (0. commonly referred to as flanged and dished heads (F&D heads).000)(0.85) – 0.PDHcenter.0D and a knuckle radius r of 0.2t P = 2(20.0 + 0.010 in Variable: L/r = L/ri = 16. with a spherical radius L of 1.2P 200 x 18. are according to paragraph UG-32 (e). The required thickness of a Torispherical F&D Head with r/L = 0. • a) Flanged & Dished Head (F&D heads): The dish radius of a Flanged and Dished Head is 1.0 D and the knuckle radius is 0.85 Corrosion Allowance: 0.Torispherical Heads: Shallow heads.010 2(20.06% D.www.com PDH Course M398 www.116) = 18 + 0. cos α) r = Inside Knuckle Radius © Jurandir Primo Page 22 of 53 .org P = Pressure on the concave side of the head S = Allowable stress t = Thickness of the head L = Inside spherical radius E = Joint efficiency factor Example 15 .8. The 80-10 is typically only 66% the thickness of the standard Torispherical Heads. The material is SA 285 Grade A. Dished Torispherical Heads inside radius is 78 in.PDHonline.885 PL = SE – 0.com PDH Course M398 www. t= PD 2 (SE . 6.Torispherical Heads: A drum is to operate at 500°F and 350 psi and to hold 5000 gallons of water. For the required thickness of a Non Standard 80-10 Head. Designing 80-10 Torispherical Heads rather than standard shapes can be achieved by lowering the material costs.54 in.7 and 2.6P) cos α 2.1(350) t = 2.7.www. Assume “S” = 11200 psi and “E” = 0.PDHcenter.85.1P t= 0.9 L = Di / (2 cos α) Di = Internal Diameter (conical portion) = D .4 – Conical or Toriconical Heads: The required thickness of the Conical or Toriconical Head (knuckle radius > 6% OD) shall be determined by formula using internal diameter of shell. α ≤ 30º.2 r (1 . use equation 2.8 Di and the knuckle radius (ri) is 10% of the head diameter.06.85) – 0. • b) Non Standard 80-10 Flanged & Dished Head: On an 80-10 the inside radius (L) is 0.0. Solution: Dished Torispherical Heads with L = Di and r/L = 0.885 (350) (78) = (11200)(0. t = 0. use equations 2. 0.7 -1.3D² P/t² P(0.PDHonline.2t cos α Stress . R = Shell/Head Inside Radius. P ≤ 0.SEt DK + 0. r = Knuckle Radius.S (in) P(R + 0.178D.685 SE t ≤ 0.25 D.2P D√0.PDHcenter.0.0.0.1t 2.885L + 0. 2 ≤ D/h ≤ 6 h/D = 4 M = 3 + (L/r)1/2 / 4 r/L = 0.06.6P) cos α Pressure .0.0.5 – Resume of Pressure Vessels Formulae – ASME Section I & ASME Section VIII: Item Thickness . t = Shell / Head Thickness.2t t²S/0.: α ≤ 30° D = Shell / Head Inside Diameter.www.2t 2.6P PR 2SE .SEt LM + 0.6t 2.2t 2. h = Inside Depth of Head.SEt D + 0.6 .3P/S 0.2t 2. 6.2P PDK 2SE .385 SE Cylindrical Shell Hemispherical Shell (or Head) Flat Flanged Head Torispherical Head (a) Torispherical Head (b) 2:1 Semi-Elliptical Head (a) Ellipsoidal Head (b) Toriconical Head OBS. L ≤ D + 2t t ≤ 0. Notes P ≤ 0.2P PD 2SE .885PL SE .2t) 2t P(DK + 0.SEt R + 0.6t) t P(R + 0.1t) t P(LM + 0.org Toriconical Heads Definitions: 6. P = Internal Pressure.Scope of ASME Section VIII: © Jurandir Primo Page 23 of 53 .com PDH Course M398 www.0. E = Weld Joint Efficiency (0.2t cos α) 2t cos α K = [2 + (D/2h)²] / 6.2t) 2t 0.t (in) PR SE .1P PLM 2SE .SEt cos α D + 1.2P PD 2(SE .P (in) SEt R + 0. S = Allowable Stress.3D² SEt 0.885L + 0. L = Crown Radius.2t) 2Et P(D + 1.2t) 2t P(D + 0.0). identical to Division 1. UB. combination of these. UCI.PDHonline. • Division 3.Above 600°F. Creep Strength. application of heat.000 psi.400°F. Division 1. • Resistance to Hydrogen Attack: -Temperature at 300 . . • Structure of Section VIII. hydrogen attack causes irreparable damage through component thickness. Parts UCS. 2. Parts UW. Alternative Rules . Division 2. ULW. UHT. UF. Does not establish maximum pressure limits of Division 1 or 2 or minimum limits for Division 3. Alternative Rules: 15 psig < P ≤ 3000 psig . monatomic hydrogen forms molecular hydrogen in voids.www.com PDH Course M398 www. Rupture Strength and Corrosion Resistance.Pressure buildup can cause steel to crack. but the different requirements are: – Allowable stress – Stress calculations – Design – Quality control – Fabrication and inspection The choice between Divisions 1 and 2 is based mainly on economics of materials. • Section VIII Division 1: 15 psig < P ≤ 3000 psig • Other exclusions: – Internals (except for attachment weld to vessel) – Fired process heaters – Pressure containers integral with machinery – Piping systems • Section VIII. UCD. ULT. process reaction.High Pressure Vessels: Applications over 10. UHA. . Mandatory and Nonmandatory Appendices • Determination of Material Thickness: • Yield Strength. Subsection B: Requirements based on fabrication method. and 3. UCL. Pressure from external source. Ultimate Tensile Strength. UNF. Division 1: Subsection A: Part UG applies to all vessels. Subsection C: Requirements based on material class. • Brittle Fracture and Fracture Toughness: The conditions that could cause brittle fracture are: © Jurandir Primo Page 24 of 53 .PDHcenter.org • Objective: Minimum requirements for safe construction and operation. PDHonline. 21 & 22.www.Manufacturing and fabrication processes . especially if over repaired area . 1 SA-612. normalized and tempered S A-5 1 6 G r.Arc strikes. SA-216 Gr. C & D SA-336 Gr. SA-285 Gr.Temperature . WCB & WCC for maximum thickness of 2 in. normalized SA 662.org – Typically at “low” temperature – Can occur below design pressure – No yielding before complete failure – High enough stress for crack initiation and growth – Low enough material fracture toughness at temperature – Critical size defect to act as stress concentration • Factors That Influence Fracture Toughness: .Type and chemistry of steel . A. B & C SA-662 Gr. normalized SA-516. Curve B: SA-216 Gr. A & B. 1.PDHcenter. 65 & 70. normalized and tempered. SA-217 Gr. normalized and tempered SA-302 Gr. 1 & 2 SA-738 Gr. not normalized. not normalized SA-533 Gr. WCB & WCC. normalized and tempered or water-quenched and tempered. WCA. Curve C: SA-182 Gr. SA-414 Gr.Stress raisers or scratches in cold formed thick plate • Material Groups – The Most Common Used Materials: Curve A: SA-216 Gr. F21 & F22. A Curve D: SA-203 SA-537 Cl. SA-516 Gr.Temperature Limits: © Jurandir Primo Page 25 of 53 .com PDH Course M398 www. 60. (water-quenched and tempered). normalized and tempered S A-3 8 7 G r. 2 & 3 SA-508 Cl. normalized and tempered. A Common Materials . SA-515 Gr. 55 & 60. 21& 22. normalized SA-524 Cl. WC6. • Additional ASME Code Impact Test Requirements: • For welded construction over 4 in. if MDMT < 120°F • Not required for flanges if temperature -20°F • Required if SMYS > 65 ksi unless specifically exempt.PDHonline.Shell Nozzles – Fundamentals: © Jurandir Primo Page 26 of 53 . or non welded construction over 6 in.org • Bolting: • See the ASME Code Section VIII.0 . 1. E 7. thick. for impact and nuts test for specified material specifications. • Weld Joint Efficiencies.www.com PDH Course M398 www.PDHcenter. Div. thick. • Definitions: • Diameter of Circular Opening... The Code procedure is to relocate the removed material to an area within an effective boundary around the opening.www.PDHonline.org Vessel components are weakened when material is removed to provide openings for nozzles or access openings.PDHcenter. Ar: © Jurandir Primo Page 27 of 53 .com PDH Course M398 www.. Figure bellow shows the steps necessary to reinforce an opening in a pressure vessel.. compensation or reinforcement is required. To avoid failure in the opening area.. d: d = Diameter of Opening – 2 (Tn + Corrosion Allowance) • Required wall thickness of the nozzle (min): tn = PR. SE – 0.6P • Area of Required Reinforcement. com PDH Course M398 www.32 + 0..3825) = 7. + 0.32 in. ts = Minimum required thickness of shell when E = 1.. 40 is t = 0. or finished dimension of opening in plane under consideration.0) – 0. normally 1.PDHonline.0625" Vessel is 100% Radiographed Nozzle does not pass through Vessel Weld Seam Wall thickness of the nozzle (min): tn = tn = PR.625 – 2(0. 60 Nozzle Diameter 8 in. in. Seamless Corrosion Allowance = 0. Circular Opening.17 in (min) – Pipe Sch.0625” = 0...625 – 2 (0. F = Correction factor.0625) = d = 8. Ar: © Jurandir Primo Page 28 of 53 .6P = 300 x 4..000(1.0625 (Corrosion Allowance) 12. in.6(300) tn = 0. Sch.0 Example 16 – Basic Pipe Nozzle: Design Pressure = 300 psig Design Temperature = 200° F Shell Material is SA-516 Gr. 40 Nozzle Material is SA-53 Gr.0.PDHcenter. SE – 0.11” + 0. d: d = Diameter of Opening – 2 (Tn + Corrosion Allowance) d = 8.F (in²) Where: d =Diameter of circular opening..www.org Ar = d. B.ts.312”…….86 in Area of Required Reinforcement. 5 – 1.86 (0.325 + 5. = 0.21 (Use Tn = 1.17)] = 0.5 (1..600)(1.3 = 11.2 Tn (Ts – ts) = As = 8.92 in² < 3.5625 – 0..PDHcenter.0) – 0.925 in² Ar < (As + An) = Ar < (1.0) (1.400(1.21)] = 5.. as larger of As or An: • As = Larger of: d (Ts – ts) ..487) = 0.2 Tn (Ts – ts) = As = 7.5625 (0..600(1.30 (Use Ts = 1. Ar.5 (0.50”) 16.82 in² • Available reinforcement area in shell.5 (Ts) (Tn – tn)] An = 2 [2.6(700) Example 18 – Nozzle Design: © Jurandir Primo Page 29 of 53 .F (in²) Ar = 7.. = 1.2P 700 x 30……..5) (1.org Ar = d.2 (Reqd. 70 • Nozzle – SA 106 Gr.6P 700 x 4..) Therefore..32 – 0.50 + 0..82 in² (Reqd..5625) (0. Example 17 – Basic Shell & Nozzle: Design Pressure = 700 psi Design temperature = 700 °F Nozzle Diameter = 8 in.0”) 14.3) – 2 (1.86 x 0.325 in² An = Smaller of: 2[2.ts.42) = 0.487) – 2x 0.com PDH Course M398 www..2 in² As = Larger of: d (Ts – ts) .ts = 8..6P 700 x 30…….www.42 in² • Ar < (As + An) = Ar < (0.2(700) Required Nozzle Thickness: tn = tn = PR… SE – 0. it´s necessary to increase Ts and / or Tn to attend the premise Ar < (As + An).5625 – 0.925) = 7..5 – 1.625 (1.625 OD) Material: • Shell – SA 516 Gr.0 – 0.0”) 2(16.3) = 1.625 x 1.PDHonline..0 (weld efficiency) Required Shell Thickness: ts = ts = PR… SE – 0. = 0.70 • Head – SA 516 Gr.. Required Head Thickness: th = th = PR…… 2SE – 0.) = d.312”…….25 in² < 11.5 (Ts) (Tn – tn)] An = 2[2.0) – 0.. B • E = 1.64 (Use Th = 1.0 = 3.: Necessary to increase Ts and / or Tn to attend the premise (As + An) > Ar.) OBS.0) – 0. (8.6(700) Opening Reinforcement: Ar (Reqd.50 in² • An = Smaller of: 2 [2.487 x 1. PDHonline.com PDH Course M398 www.org © Jurandir Primo Page 30 of 53 .PDHcenter.www. PDHonline.org © Jurandir Primo Page 31 of 53 .www.PDHcenter.com PDH Course M398 www. org 8. including structural plates.PDHcenter. flanges.1 . castings. fittings. the Tables also help the student how to search the materials MAWP (Maximum Allowable Stress Values) in ASME Section II.PDHonline. Beyond the knowledge of the most common ferrous materials. bolts and nuts. tubes. pipes.0 – ASME Materials: The following Tables indicates the most common ferrous materials used in Pressure Vessels design and fabrication. Table 1A. 8.Carbon Steels: © Jurandir Primo Page 32 of 53 .com PDH Course M398 www.www. forgings. com PDH Course M398 www.www.PDHonline.Low Alloy Steels: © Jurandir Primo Page 33 of 53 .org 8.2 .PDHcenter. www. Part D contains properties of ferrous and nonferrous materials adopted by the Code for the design of boiler.1 – MAWP – Maximum Allowable Stress Values: The Section II.com PDH Course M398 www.PDHonline.PDHcenter. The student must always consult the original tables. © Jurandir Primo Page 34 of 53 . pressure-vessel.org 8. and nuclear-power-plant components including tables of the maximum allowable stresses and design-stress intensities for the materials adopted by various Codebook sections. The tables below are an extract from ASME for the most common ferrous materials for a basic design purpose. www.com PDH Course M398 www.org © Jurandir Primo Page 35 of 53 .PDHonline.PDHcenter. www.org © Jurandir Primo Page 36 of 53 .PDHonline.PDHcenter.com PDH Course M398 www. org © Jurandir Primo Page 37 of 53 .PDHcenter.www.com PDH Course M398 www.PDHonline. www.PDHcenter.com PDH Course M398 www.org © Jurandir Primo Page 38 of 53 .PDHonline. PDHonline.PDHcenter.com PDH Course M398 www.org © Jurandir Primo Page 39 of 53 .www. PDHonline.com PDH Course M398 www.www.org © Jurandir Primo Page 40 of 53 .PDHcenter. com PDH Course M398 www.org 9.PDHcenter.0 – Suplementary ASME Allowable Stress for General Design at Atmospheric Pressure: © Jurandir Primo Page 41 of 53 .www.PDHonline. 80. 2. the use of spiral-seam pipe is prohibited.80.www. Only straight-seam pipe shall be used. Stress values for fusion-welded pipes include a welded-joint efficiecy factor of 0. Stress values for castings include a factor of 0. © Jurandir Primo Page 42 of 53 .PDHcenter. Allowable stress based on Section VIII of the ASME multiplied by the ratio of the design stress factors in this standard.com PDH Course M398 www. 3.PDHonline.org 1. PDHonline.org 9.0 – Extract ASME Section VIII – Division 1 .com PDH Course M398 www.PDHcenter.www.Suplementary Design Formulas: © Jurandir Primo Page 43 of 53 . PDHonline.org © Jurandir Primo Page 44 of 53 .PDHcenter.com PDH Course M398 www.www. PDHcenter.www.PDHonline.com PDH Course M398 www.org © Jurandir Primo Page 45 of 53 . PDHonline.www.PDHcenter.com PDH Course M398 www.org © Jurandir Primo Page 46 of 53 . PDHonline.www.PDHcenter.com PDH Course M398 www.org © Jurandir Primo Page 47 of 53 . PDHcenter.www.com PDH Course M398 www.org Example 19 – MAWP (Maximum Allowable Working Pressure: Example 20 – Thickness of a Cylindrical Shell Considering Internal Pressure: © Jurandir Primo Page 48 of 53 .PDHonline. com PDH Course M398 www.PDHcenter.PDHonline.org © Jurandir Primo Page 49 of 53 .www. org © Jurandir Primo Page 50 of 53 .www.PDHcenter.PDHonline.com PDH Course M398 www. org Example 21 – Design of a Standard Torispherical Head: © Jurandir Primo Page 51 of 53 .PDHcenter.PDHonline.com PDH Course M398 www.www. www.com PDH Course M398 www.org Example 22 – Design of a Non-Standard Torispherical Head © Jurandir Primo Page 52 of 53 .PDHcenter.PDHonline. PDHonline.org © Jurandir Primo Page 53 of 53 .www.PDHcenter.com PDH Course M398 www.