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Journal articles on the topic 'Pressure Vessels and Piping Division'

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Published: 4 June 2021

Last updated: 1 February 2022

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1

Farr, J. R. "The ASME Pressure Vessels and Piping Division—25 Years of Progress." Journal of Pressure Vessel Technology 113, no. 2 (May 1, 1991): 122–26. http://dx.doi.org/10.1115/1.2928735.

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1991 is the Silver Anniversary of the ASME Pressure Vessels and Piping Division. The PVP Division was formed 25 years ago to serve as a focal point for mechanical engineering as related to the pressure vessels and piping industry. Through the PVP Division’s extensive publications, conferences, short courses, and tutorial lectures, pressure vessel and piping technology and new development information has been disseminated throughout the world. This chronological essay of significant events and contributing people has been written for posterity to record the first 25 years of the Division. May the next 25 years bring equal or greater success to the ASME Pressure Vessels and Piping Division!

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2

Zamrik, Sam Y., and James R. Farr. "Historical Development—The Pressure Vessels and Piping Division." Journal of Pressure Vessel Technology 122, no. 3 (May 17, 2000): 226–28. http://dx.doi.org/10.1115/1.556177.

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Historical information concerning the Pressure Vessels and Piping Division was presented by James Farr at the 25th Anniversary Celebration, describing events from 1966 through 1991. Further developments since 1991 are briefly summarized in this presentation for the Millennium Issue. The PVP Senate has been the historian of the Division’s growth and activities. [S0094-9930(00)02803-1]

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3

Pai, D. H. "Pressure Vessel and Piping Technology: Two Decades of Progress and Future Challenges." Journal of Pressure Vessel Technology 109, no. 4 (November 1, 1987): 363–67. http://dx.doi.org/10.1115/1.3264917.

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The organizational and technological advances of the last two decades in the U.S. Pressure Vessel and Piping (PVP) Technology are first traced. Highlights of growth in the major organizations supporting PVP technology: ASME Boiler and Pressure Vessel Code, Pressure Vessel Research Committee, and the ASME Pressure Vessels and Piping Division, are given, along with highlights in the technological advances in Design Analysis, Materials and Fabrication. Future challenges in key technological areas for PVP engineers are discussed, including the role of the PVP engineer in developing technologies such as BIOTECHNOLOGY, SUPERCONDUCTIVITY, MICRO-ELECTRONICS, ENERGY, ENVIRONMENTAL ENGINEERING, and ADVANCED MATERIALS. This paper concludes with a discussion of two major institutional challenges of our times: winning public acceptance of technology; competitiveness and foreign trade.

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4

Vasilescu, Serban, and Costin Ilinca. "A Strength Calculation of a Nozzle Using Comparative Methods." Key Engineering Materials 601 (March 2014): 84–87. http://dx.doi.org/10.4028/www.scientific.net/kem.601.84.

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The stresses and deflections developed due to all piping loads produce some significant deformation in the nozzles of the pressure vessels. In this paper a spherical pressure vessel with two cylindrical nozzles are analyzed. The stresses in the nozzles are evaluated using two comparative methods: one of them represents the classical way of using the superposition of the axial, bending and torsional loads; the other one is based on the requirements of the ASME Boiler and Pressure Vessel Cod, Section VIII, Division 2 and is developed by a FE analysis. In order to obtain the loads (forces and moments) at the end of the nozzle a specialized finite element program has been used. This program (Coade Caesar 5.30) allows studying the strength and flexibility behavior of the pipes that connect the analyzed nozzle with the rest of the plant. The results obtained are compared in order to find when the using of the classical methods of strength of materials can be used as conservative approaches. The finite element method is applied in order to check the most important load cases that appear during the interaction between pipes and shell. In this respect the sustained (proper gravity loads), expansion (thermal loads) and occasional (wind and seismic loads) are combined in order to check all the requirements of ASME. This study contains also the effect of the pressure trust and the influence of the real geometry of the junction (nozzle-shell) in the peaks of the stresses.

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5

Fanous, Ihab F. Z., and R. Seshadri. "Stress Classification Using the r-Node Method." Journal of Pressure Vessel Technology 129, no. 4 (June 28, 2006): 676–82. http://dx.doi.org/10.1115/1.2767357.

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The ASME Code Secs. III and VIII (Division 2) provide stress-classification guidelines to interpret the results of a linear elastic finite element analysis. These guidelines enable the splitting of the generated stresses into primary, secondary, and peak. The code gives some examples to explain the suggested procedures. Although these examples may reflect a wide range of applications in the field of pressure vessel and piping, the guidelines are difficult to use with complex geometries. In this paper, the r-node method is used to investigate the primary stresses and their locations in both simple and complex geometries. The method is verified using the plane beam and axisymmetric torispherical head. Also, the method is applied to analyze 3D straight and oblique nozzles modeled using both solid and shell elements. The results of the analysis of the oblique nozzle are compared with recently published experimental data.

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6

Kendall, David P. "Comparison of Methods for Calculating Stress Intensity Factors for the Thread of a Pressure Vessel Closure and of a Gun Breech Ring." Journal of Pressure Vessel Technology 125, no. 3 (August 1, 2003): 326–29. http://dx.doi.org/10.1115/1.1593699.

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Non-mandatory Appendix D of Section VIII, Division 3 of the ASME Boiler and Pressure Vessel Code provides a method for calculating the stress intensity factors for the region of a thread root of a threaded closure. This method involves calculation of the distribution of stress acting on a plane normal to the axis of the thread. This distribution is fitted with several different cubic equations for different regions and the coefficients of these cubic equations are entered into an equation to calculate the distribution of stress intensity factor for each region. The values of stress intensity factor for each region after the first one are shifted to obtain a continuous distribution. In a paper to be presented at the August 2002 ASME Pressure Vessel and Piping Conference (Kendall 2002) the author compared the stress intensity factors calculated by the above Code method with those determined by Neubrand and Burns, 1999, using a weight function method. In Kendall, 2002, the stress intensity factors for this same closure design were calculated using the Code method and also calculated using a proposed modification of this method. The results showed slightly better agreement for the proposed modification of the Code method. This paper will report the details of these calculation methods and the results from Kendall, 2002. It will also give a comparison of the stress intensity factor results of these methods for a thread of a typical gun breech ring, and a comparison of the calculated fatigue crack growth lives.

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7

Penny, R. K., and J. Gryzagoridis. "Holographic NDE in pressure vessels and piping." International Journal of Pressure Vessels and Piping 58, no. 2 (January 1994): 223–30. http://dx.doi.org/10.1016/0308-0161(94)90087-6.

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8

Chao, Y. J. "Minimum Stress Design of Nozzles in Pressure Vessel Heads." Journal of Pressure Vessel Technology 110, no. 4 (November 1, 1988): 460–63. http://dx.doi.org/10.1115/1.3265630.

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In the early design stage of pressure vessels the configuration of the piping systems is not yet established; hence forces transmitted by the piping systems to the nozzles in the pressure vessels cannot be determined. This often leads to the design of nozzles in pressure vessels guided by consideration of pressure loadings such as the area-replacement method. However, it is true that in many cases the stresses due to external loads can be more critical than those due to the internal pressure. Therefore, engineers often redesign the piping system several times by adding more pipe bends or special restraints for a hot piping system to reduce the reactions at a previously designed nozzle so that the resulting stresses at the nozzle are within the acceptable limit. This paper introduces a rational mechanism whereby the stresses due to the unforeseen external loads can be minimized in the early design stage of the nozzle. An appropriate analysis is discussed which is based on the classical thin shell theory. Analyses using this method allow one to obtain the minimum stresses at a nozzle in a pressure vessel head or a spherical vessel for moment and thrust loadings.

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9

Pérez, Iván Uribe, Tito Luiz da Silveira, Tito Fernando da Silveira, and Heloisa Cunha Furtado. "Graphitization in Low Alloy Steel Pressure Vessels and Piping." Journal of Failure Analysis and Prevention 11, no. 1 (December 2, 2010): 3–9. http://dx.doi.org/10.1007/s11668-010-9414-z.

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10

Selz, A. "Recertification of Pressure Vessels and Pressure Systems." Journal of Pressure Vessel Technology 108, no. 4 (November 1, 1986): 514–17. http://dx.doi.org/10.1115/1.3264822.

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There are strong economic and safety incentives to recertify pressure vessels, pressure components, and piping for continued service after their nominal original design life has been exhausted. No specific rules, and certainly no national consensus standards exist for doing this. Therefore, methods have been developed to rank vessels as to urgency for recertification, and a five-step recertification process has been devised. The five steps are: 1) gathering design and operating information, 2) performing basic analysis to establish maximum allowable working pressure (MAWP) and to identify high-stress areas, 3) performing visual and nondestructive examination, concentrating NDT in high stress areas, 4) performing detailed stress analysis to confirm MAWP, and 5) performing flaw-growth analysis to establish the interval between inspections. Experience has shown that recertification costs are between 10 and 15 percent of replacement costs and that recertification adds greatly to confidence in the safety and availability of equipment.

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11

Kim, Yun-Jae, Tae-Kwang Song, and Kuk-Hee Lee. "Life Assessment Procedures and Codes for Pressure Vessels and Piping." Journal of the Korean Welding and Joining Society 28, no. 2 (April 30, 2010): 22–26. http://dx.doi.org/10.5781/kwjs.2010.28.2.022.

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12

Guodong, Chen. "Exact solutions of toroidal shells in pressure vessels and piping." International Journal of Pressure Vessels and Piping 19, no. 2 (January 1985): 101–15. http://dx.doi.org/10.1016/0308-0161(85)90020-1.

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13

Jaske, Carl E. "Fatigue-Strength-Reduction Factors for Welds in Pressure Vessels and Piping." Journal of Pressure Vessel Technology 122, no. 3 (April 17, 2000): 297–304. http://dx.doi.org/10.1115/1.556186.

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Fatigue-strength-reduction factors (FSRFs) are used in the design of pressure vessels and piping subjected to cyclic loading. This paper reviews the background and basis of FSRFs that are used in the ASME Boiler and Pressure Vessel Code, focusing on weld joints in Class 1 nuclear pressure vessels and piping. The ASME Code definition of FSRF is presented. Use of the stress concentration factor (SCF) and stress indices are discussed. The types of welds used in ASME Code construction are reviewed. The effects of joint configuration, welding process, cyclic plasticity, dissimilar metal joints, residual stress, post-weld heat treatment, the nondestructive inspection performed, and metallurgical factors are discussed. The current status of weld FSRFs, including their development and application, are presented. Typical fatigue data for weldments are presented and compared with the ASME Code fatigue curves and used to illustrate the development of FSRF values from experimental information. Finally, a generic procedure for determining FSRFs is proposed and future work is recommended. The five objectives of this study were as follows: 1) to clarify the current procedures for determining values of fatigue-strength-reduction factors (FSRFs); 2) to collect relevant published data on weld-joint FSRFs; 3) to interpret existing data on weld-joint FSRFs; 4) to facilitate the development of a future database of FSRFs for weld joints; and 5) to facilitate the development of a standard procedure for determining the values of FSRFs for weld joints. The main focus is on weld joints in Class 1 nuclear pressure vessels and piping. [S0094-9930(00)02703-7]

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14

Tseng, Chun-Pin, Cheng-Wu Chen, and Kevin F. R. Liu. "RETRACTED: Risk control allocation model for pressure vessels and piping project." Journal of Vibration and Control 18, no. 3 (July 13, 2011): 385–94. http://dx.doi.org/10.1177/1077546311403182.

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15

Naijie, Shen, Zhu Jitao, and Lu Wenge. "Stress state in the saddle zone of pressure vessels and piping." International Journal of Pressure Vessels and Piping 63, no. 2 (January 1995): 155–64. http://dx.doi.org/10.1016/0308-0161(94)00045-k.

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16

Pogodin, V. K., L. B. Tsvik, and Yu L. Vainapel'. "Calculating the interaction of parts of detachable joints on pressure vessels and pressure piping." Chemical and Petroleum Engineering 31, no. 4 (April 1995): 212–17. http://dx.doi.org/10.1007/bf01152300.

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17

Yagawa, Genki, and Shinobu Yoshimura. "A study on probabilistic fracture mechanics for nuclear pressure vessels and piping." International Journal of Pressure Vessels and Piping 73, no. 1 (August 1997): 97–107. http://dx.doi.org/10.1016/s0308-0161(97)00039-2.

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18

Bray, Don E. "Ultrasonic Stress Measurement and Material Characterization in Pressure Vessels, Piping, and Welds." Journal of Pressure Vessel Technology 124, no. 3 (July 26, 2002): 326–35. http://dx.doi.org/10.1115/1.1480825.

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A pressure vessel has been constructed for demonstrating the LCR ultrasonic technique for indicating changes in wall and weld stress. A special contoured LCR probe was designed and constructed, and the pressure vessel was fitted with strain gauges for monitoring the wall stress. At low wall stresses, below 4 ksi (26 MPa), the ultrasonic data showed considerable scatter. There is similar scatter in the zero pressure travel-times at individual locations around the vessel. At wall stresses of 4 ksi (26 MPa) and above, however, there is an almost linear relationship of stress and travel-time change. Measurements adjacent to an end weld also showed very good trends. Plots of travel times approaching a weld predict −27.5 ksi (−190 MPa) at 1 in. (25 mm) from the weld, compared to zero stress at 5.6 in. (142 mm) away from the weld. These results are consistent with results obtained by others on a similar weld using the blind hole drilling method.

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19

Harth, G. H., and T. P. Sherlock. "Monitoring the Service-Induced Damage in Utility Boiler Pressure Vessels and Piping Systems." Journal of Pressure Vessel Technology 107, no. 3 (August 1, 1985): 226–29. http://dx.doi.org/10.1115/1.3264440.

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Electric utilities are becoming more concerned about extending the life of older fossil-fueled power plants. Of particular interest are methods for estimating the remaining useful life of steam headers and main steam piping. This paper discusses different methodologies for determining exhausted and remaining life of these components. An example of a header which was found to have exhausted its useful life is also presented.

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20

Abdul‐Mihsein, M. J., A. A. Bakr, and R. T. Fenner. "Stress analysis of pressure vessels and piping using the boundary integral equation method." Engineering Computations 2, no. 4 (April 1985): 335–43. http://dx.doi.org/10.1108/eb023633.

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21

Yoshimura, Shinobu. "Some structural integrity studies of pressure vessels and piping in Japan—a review." International Journal of Pressure Vessels and Piping 65, no. 2 (January 1996): 101–7. http://dx.doi.org/10.1016/0308-0161(94)00165-f.

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22

Ying, F. Q., J. Z. Xia, and Y. Liu. "Application of Papkovich-Neuber function in stress calculation of pressure vessels and piping." International Journal of Pressure Vessels and Piping 68, no. 3 (October 1996): 273–77. http://dx.doi.org/10.1016/0308-0161(95)00065-8.

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23

IWAMATSU, Fuminori. "Participation Report of the ASME Pressure Vessels & Piping 2020 Conference (PVP 2020)." JOURNAL OF THE JAPAN WELDING SOCIETY 90, no. 3 (2021): 215–17. http://dx.doi.org/10.2207/jjws.90.215.

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24

Cheta, Ayman M., and Richard Brodzinski. "Comparative Study for Stresses in Nozzle and Flange Welds Generated During Conventional Pressure Testing and Local Pressure Testing Using Bolted Devices." Journal of Pressure Vessel Technology 129, no. 4 (November 22, 2006): 775–80. http://dx.doi.org/10.1115/1.2767372.

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Weld repairs and alterations of pressure vessels and piping built to ASME codes may require pressure testing to prove the integrity of the weld and/or design. Conventional hydrostatic pressure testing requires filling an entire vessel or piping system with water and pressurizing it to the test pressure. In recent years, several designs were developed to employ bolted devices to perform local pressure testing of flange-to-nozzle, flange-to-pipe, and nozzle-to-shell attachment welds. Due to the cost and equipment downtime associated with performing a full conventional pressure test and the desire to reduce repair costs, several petrochemical companies adopted the use of such devices. The purpose of this paper is to compare the stress values and stress distribution associated with conventional and local pressure testing techniques. The advantages and disadvantages of both approaches are discussed and the conclusions are supported by a practical example.

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25

Seshadri, R. "Integrity Assessment of Pressure Components With Local Hot Spots." Journal of Pressure Vessel Technology 127, no. 2 (May 1, 2005): 137–42. http://dx.doi.org/10.1115/1.1858923.

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Local hot spots can occur in some pressure vessels and piping systems used in industrial processes. The hot spots could be a result of, for instance, localized loss of refractory lining on the inside of pressure components or due to a maldistribution of process flow within vessels containing catalysts. The consequences of these hot spots on the structural integrity of pressure components are of considerable importance to plant operators. The paper addresses structural integrity issues in the context of codes and standards design framework. Interaction of hot spots, as is the case when multiple hot spots occur, is addressed. An assessment method, suitable for further development of a Level 2 “Fitness-for-Service” methodology, is discussed and applied to a commonly used pressure component configuration.

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26

Riccardella, P. C., and S. Yukawa. "Twenty Years of Fracture Mechanics and Flaw Evaluation Applications in the ASME Nuclear Code." Journal of Pressure Vessel Technology 113, no. 2 (May 1, 1991): 145–53. http://dx.doi.org/10.1115/1.2928739.

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The paper presents a retrospective on the development and applications of fracture mechanics-based toughness requirements and flaw evaluation methodology in Sections III and XI of the ASME Code. Section III developments range from the rules and requirements for thick section Class 1 pressure vessels to thinner section components in other Classes. Section XI applications include flaw acceptance standards and evaluation methodology for various components ranging from pressure vessels to thin section piping of carbon and austenitic steels. The experience gained in operating plant applications of these rules and procedures are also discussed.

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27

Blach, A. E., V. S. Hoa, C. K. Kwok, and A. K. W. Ahmed. "Rectangular Pressure Vessels of Finite Length." Journal of Pressure Vessel Technology 112, no. 1 (February 1, 1990): 50–56. http://dx.doi.org/10.1115/1.2928587.

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Design Rules in the ASME Code, Section VIII, Division 1, cover the design of unreinforced and reinforced rectangular pressure vessels. These rules are based on “infinitely long” vessels of non-circular cross section and stresses calculated are based on a linearized “small deflection” theory of plate bending. In actual practice, many pressure vessels can be found which are of finite length, often operating successfully under pressures two to three times as high as those permitted under the Code rules cited. This paper investigates the effects of finite length on the design formulae given by the ASME Code, and also a design method based on “large deflection” theory coefficients for short rectangular pressure vessels. Results based on analysis are compared with values obtained from finite element computations, and with experimental data from strain gage measurements on a test pressure vessel.

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28

Mackerle, J. "Finite elements in the analysis of pressure vessels and piping, an addendum (1996–1998)." International Journal of Pressure Vessels and Piping 76, no. 7 (June 1999): 461–85. http://dx.doi.org/10.1016/s0308-0161(99)00012-5.

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29

Feng, Ding-Zhong, and Qi-Chao Hong. "Investigation of surface crack opening displacement and its application in pressure vessels and piping." International Journal of Pressure Vessels and Piping 52, no. 2 (January 1992): 227–39. http://dx.doi.org/10.1016/0308-0161(92)90018-b.

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30

Mackerle, Jaroslav. "Finite elements in the analysis of pressure vessels and piping—a bibliography (1976–1996)." International Journal of Pressure Vessels and Piping 69, no. 3 (December 1996): 279–339. http://dx.doi.org/10.1016/0308-0161(96)00011-7.

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31

Short, W. E. "Design and Analysis of Piping, Pressure Vessels, and Components (ASME Special Publication PVP-Vol. 120)." Journal of Pressure Vessel Technology 109, no. 4 (November 1, 1987): 472. http://dx.doi.org/10.1115/1.3264937.

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32

Azegami, H., A. Okitsu, T. Ogihara, and A. Takami. "An Adaptive Growth Method for Shape Refinement: Methodology and Applications to Pressure Vessels and Piping." Journal of Pressure Vessel Technology 114, no. 1 (February 1, 1992): 87–93. http://dx.doi.org/10.1115/1.2929017.

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A simple shape refinement technique for improving strength has been developed. The technique is to deform shapes with growth bulk strain which springs up in proportion with deflection of a strength measure to a basic value in all parts of a body. The scheme for the shape refinement consists of the iteration of the two steps with finite element method: 1) analysis step of a strength measure distribution, and 2) growth deformation step with the growth bulk strain. Numerical experiments on static and dynamic test problems and practical problems of pressure vessel and piping system indicate the effectiveness of this technique for improving strength.

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33

Parsons, Michael G., and Richard W. Harkins. "Investigation of Fuel Injection System Cavitation Problems on the MV James R. Barker, MV Mesabi Miner, and MV William J. De Lancey." Marine Technology and SNAME News 22, no. 03 (July 1, 1985): 219–37. http://dx.doi.org/10.5957/mt1.1985.22.3.219.

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Cavitation erosion has long been recognized as a potential problem in the components and piping of diesel engine fuel injection systems. Specific cavitation erosion problems have been experienced recently in the fuel injection systems of the Colt-Pielstick PC2 engines of the Great Lakes bulk carriers MV James R. Barker, MV Mesabi Miner, and MV William J. De Lancey. Similar damage has been found in the injection systems of PC2 engines onboard other U.S.-flag vessels. The experience on the subject vessels and the efforts being taken to eliminate or minimize these problems are described. The modeling and methods used in a digital computer simulation of the fuel injection system on these vessels are presented. This simulation is being developed to study the effects of the delivery valve spring characteristics and performance, system pressures, and various system details and potential modifications on the overall performance of the fuel injection system. Special emphasis has been placed upon the factors which can be causing the cavitation damage within the high-pressure injection piping and injector bodies. Example simulation results are presented. The simulation will provide a practical and economical way to evaluate potential modifications.

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34

Kannan, P., KS Amirthagadeswaran, and T. Christopher. "Development and validation of a leak before break criterion for cylindrical pressure vessels." Proceedings of the Institution of Mechanical Engineers, Part L: Journal of Materials: Design and Applications 231, no. 3 (July 16, 2015): 285–96. http://dx.doi.org/10.1177/1464420715595538.

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Leak before break is a fail–safe design concept for application in pressure vessels and piping of power and process plants. A quantitative maximum allowable flaw size is required to establish to set acceptance/rejection limit to predict whether the specific cracked pipe will leak or break. A new modification and its boundary based on Modified Two Parameter Fracture Criterion is capable of separating the leak and break cases distinctly in order to predict the behavior of cracked cylinders, pipelines and pressure vessels in advance for taking necessary precautions by the plant operator and also very much handy for the designers. For the given operating pressure under the observed crack dimensions, whether the crack will leak or break can be assessed from the boundary generated for the material concerned using Modified Two Parameter fracture assessment procedure.

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35

Sandström, Rolf, Peter Langenberg, and Henrik Sieurin. "Erratum to “Analysis of the brittle fracture avoidance model for pressure vessels in European standard” [Int J Pressure Vessels and Piping 82 (2005) 872–881]." International Journal of Pressure Vessels and Piping 82, no. 12 (December 2005): 941. http://dx.doi.org/10.1016/j.ijpvp.2005.09.001.

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36

Sundaramoorthy, T. R., and S. C. Chetal. "Selection of Appropriate Division of ASME Section VIII for Welded Pressure Vessels." Indian Welding Journal 27, no. 1 (January 1, 1994): 22. http://dx.doi.org/10.22486/iwj.v27i1.148285.

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37

Fishburn, John D. "A Single Technically Consistent Design Formula for the Thickness of Cylindrical Sections Under Internal Pressure." Journal of Pressure Vessel Technology 129, no. 1 (March 7, 2006): 211–15. http://dx.doi.org/10.1115/1.2389035.

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Within the current design codes for boilers, piping, and pressure vessels, there are many different equations for the thickness of a cylindrical section under internal pressure. A reassessment of these various formulations, using the original data, is described together with more recent developments in the state of the art. A single formula, which can be demonstrated to retain the same design margin in both the time-dependent and time-independent regimes, is shown to give the best correlation with the experimental data and is proposed for consideration for inclusion in the design codes.

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38

Mackerle, Jaroslav. "Finite elements in the analysis of pressure vessels and piping, an addendum: a bibliography (1998–2001)." International Journal of Pressure Vessels and Piping 79, no. 1 (January 2002): 1–26. http://dx.doi.org/10.1016/s0308-0161(01)00128-4.

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39

Mackerle, Jaroslav. "Finite elements in the analysis of pressure vessels and piping, an addendum: A bibliography (2001–2004)." International Journal of Pressure Vessels and Piping 82, no. 7 (July 2005): 571–92. http://dx.doi.org/10.1016/j.ijpvp.2004.12.004.

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40

Pastor, T. P., and D. A. Osage. "Modernization of Pressure Vessel Design Codes ASME Section VIII, Division 2, 2007 Edition." Journal of Pressure Vessel Technology 129, no. 4 (September 14, 2007): 754–58. http://dx.doi.org/10.1115/1.2794737.

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The technology for pressure equipment design continues to advance each and every day. The ASME Boiler and Pressure Vessel Code has been keeping pace with these advances over the last 92 years. As far back as the 1960s, it was recognized that the special requirements for design of pressure vessels operating at pressures over 2000 psi (13.7 MPa) called for special rules, and ASME issued Sec. VIII, Division 2 of Alternative Rules for Pressure Vessels. Since that time, the understanding of failure mechanisms and advances in material science, nondestructive testing, and computer-aided design has progressed to the stage where a new approach was needed not only in the content of design codes but in the way they are presented and organized. This paper introduces the newly issued ASME Sec. VIII, Division 2 of 2007 edition and explores the technical concepts included and the new format designed for ease of use. Included are results of test exercises sponsored by ASME giving actual applications of the new Code for design of vessels. This paper demonstrates ASME’s commitment to provide manufacturers and users of pressure equipment with the most up-to-date technology in easy to use standards that service the international market.

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41

Wong, F. M. G., W. J. Craft, and G. H. East. "Stresses and Displacements in Vessels due to Loads Imposed by Single and Multiple Piping Attachments." Journal of Pressure Vessel Technology 107, no. 1 (February 1, 1985): 51–59. http://dx.doi.org/10.1115/1.3264404.

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The Fourier solution for thin shell equations models pressure vessels as continuous simply connected surfaces with local loads. The technique allows placement of tractions with combinations of radial, shear, and axial components. Unlike Bijlaard, the solution in this paper includes loads placed at any position along the cylinder. Stiffness and the enhanced load-carrying capacity that internal pressure gives to thin vessels can be simulated. Numerical convergence problems are reduced by an improved displacement-load algorithm, and by use of load sites that allow the circular functions to be compactly grouped. A variety of loading distributions may be analyzed including large and small nozzles near and away from centerlines. Both rectangular and circular attachments are simulated. Through superposition, multiple attachments with their own loads may be examined. The attachments to the vessel may be either rigid or soft. A comparison to analytical results from Bijlaard shows excellent agreement. Comparisons with experimental tests on an API-650 nozzle on a storage tank are in good agreement. Variations between experimental and calculated results are primarily caused by assuming a simply supported base in the calculation, whereas in the experimental test, the base is more nearly fixed.

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42

Bernsen, Sidney, Bryan Erler, Dana K. Morton, and Owen Hedden. "The Code Builders." Mechanical Engineering 136, no. 05 (May 1, 2014): 36–41. http://dx.doi.org/10.1115/1.2014-may-2.

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This article elaborates the evolution of code and standards for nuclear power plants. In the 1950s, need was felt for a revised set of design and fabrication rules to facilitate the development of safe, economically competitive water-cooled reactors contained in pressure vessels. These rules were codified in the first edition of the ASME Boiler and Pressure Vessel Code Section III, which was completed in 1963 and published in 1964. From the outset, both regulators and industry realized that the best way to develop many of the needed rules for the design, construction, and operation of nuclear facilities was the national standards consensus process. This process, followed by the American National Standards Institute and other recognized standards-issuing bodies such as ASME, brings together the expertise of individuals from government, industry, academia, and other stakeholders. In the years following the first publication of Section III, the coverage of the Code expanded to incorporate piping requirements, pressure-retaining components for pumps and valves, equipment and piping supports, reactor vessel internal structures, and other features of nuclear power plants.

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Chaaban, A., and M. Jutras. "Static Analysis of Buttress Threads Using the Finite Element Method." Journal of Pressure Vessel Technology 114, no. 2 (May 1, 1992): 209–12. http://dx.doi.org/10.1115/1.2929031.

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The finite element method has been used to investigate the stress field in threaded end closures of thick-walled high pressure vessels. A set of elastic analyses of vessels with 5, 8, 11, 15, 20 and 25 standard Buttress threads was used to propose a method for predicting the load distribution along the length of the thread. Root stress index factors in the region of the first three active threads are also included. The results of the present work contribute to the development of the new division of the ASME Pressure Vessel Code which is related to thick-walled high pressure vessels.

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Tsukimori, Kazuyuki. "Theoretical Modeling of Creep Behavior of Bellows and Some Applications." Journal of Pressure Vessel Technology 123, no. 2 (August 3, 2000): 179–90. http://dx.doi.org/10.1115/1.1320817.

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The use of bellows expansion joints is an effective method to rationalize various piping systems in industry. In the structural design, the requirements for preventing failures such as ratcheting, fatigue, and buckling should be satisfied. The mechanisms of some failure modes of bellows are different from those of vessels and piping components, which makes it difficult to estimate the behaviors. In the case of high-temperature operation, creep behavior of bellows should be considered. In this paper, a simplified theoretical modeling of creep behavior of bellows is presented. The formulation is developed by using Norton’s law for creep property of bellows material and assuming meridional bending stress is dominant. According to this modeling, bellows convolution dimensions are considered directly. The excessive creep deformation problem of bellows under internal pressure and the elastic follow-up behavior problem of a piping system with bellows expansion joints are examined as the applications of this modeling. The results are compared with detailed analysis results by FEM, and the applicability and the validity of this modeling is discussed.

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45

Liu, P. F., B. J. Zhang, and J. Y. Zheng. "Finite Element Analysis of Plastic Collapse and Crack Behavior of Steel Pressure Vessels and Piping Using XFEM." Journal of Failure Analysis and Prevention 12, no. 6 (October 19, 2012): 707–18. http://dx.doi.org/10.1007/s11668-012-9623-8.

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46

Onizawa, Kunio, Hiroyuki Nishikawa, and Hiroto Itoh. "Development of probabilistic fracture mechanics analysis codes for reactor pressure vessels and piping considering welding residual stress." International Journal of Pressure Vessels and Piping 87, no. 1 (January 2010): 2–10. http://dx.doi.org/10.1016/j.ijpvp.2009.11.011.

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Rana, M. D. "Structural Integrity Assessment of Carbon and Low-Alloy Steel Pressure Vessels Using a Simplified Fracture Mechanics Procedure." Journal of Pressure Vessel Technology 116, no. 3 (August 1, 1994): 324–30. http://dx.doi.org/10.1115/1.2929596.

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This paper describes a simplified fracture analysis procedure which was developed by Pellini to quantify fracture critical-crack sizes and crack-arrest temperatures of carbon and low-alloy steel pressure vessels. Fracture analysis diagrams have been developed using the simplified analysis procedure for various grades of carbon and low-alloy steels used in the construction of ASME, Section VIII, Division 1 pressure vessels. Structural integrity assessments have been conducted from the analysis diagrams.

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Indermohan, H., and R. Seshadri. "Fitness-for-Service Methodology Based on Variational Principles in Plasticity." Journal of Pressure Vessel Technology 127, no. 1 (February 1, 2005): 92–97. http://dx.doi.org/10.1115/1.1849230.

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A variational formulation in plasticity has been used to develop improved limit load estimation technique, such as the m-alpha method. Lower bound limit load estimates are especially germane to design and fitness-for-service assessments. The concept of “integral mean of yield” has been applied to problems involving locally thinned areas (LTA) and local hot spots in the context of industrial pressure vessels and piping. Simplified procedures for “fitness-for-service” assessment, suitable for use by plant engineers, have been developed. The results are compared with the corresponding inelastic finite elastic analyses.

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Sharma, C. B. "Proceedings Review : FLOW STRUCTURE VIBRATION AND SLOSHING Pressure Vessels and Piping Conference June 19-21, 1990, Nashville, TN." Shock and Vibration Digest 23, no. 10 (October 1, 1991): 17. http://dx.doi.org/10.1177/058310249102301009.

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Hossain, M. M., and R. Seshadri. "Simplified fitness-for-service assessment of pressure vessels and piping systems containing thermal hot spots and corrosion damage." International Journal of Pressure Vessels and Piping 87, no. 7 (July 2010): 381–88. http://dx.doi.org/10.1016/j.ijpvp.2010.04.001.

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