An Analytical Anisotropic Model to Analyze Fiber Reinforced Polymer Bolted Flange Joints

2020 ◽  
Author(s):  
Ali Khazraiyan Vafadar ◽  
Abdel-Hakim Bouzid ◽  
Anh Dung Ngô
Keyword(s):  
Numerical Models ◽  
Design Procedure ◽  
Accurate Method ◽  
Pressure Vessels ◽  
Code Design ◽  
Plastic Composite ◽  
Fiber Reinforce Plastic ◽  
Asme Code ◽  
The One ◽  
Bolted Flange

Abstract Fiber Reinforce Plastic composite flanges have recently experienced a spectacular development in the area of pressure vessels and piping. The current procedures used for the design of these flanges are a major concern because of their inappropriateness to address the anisotropic behavior of composite materials. The current ASME code design procedure of composite flanges of section X uses the same analytical method as the one of section VIII division 2 which treat the flanges as isotropic materials such as metallic flanges. This study deals with FRP bolted flange joints integrity and bolt tightness. A new developed analytical FRP model that treats anisotropic flanges with and without a hub is presented. The model is based on the anisotropy and a flexibility analysis of all joint elements including the gasket, bolts and flanges. It is supported experimentally with tests conducted on a real NPS 3 class 150 FRP bolted flange. Furthermore, three different numerical models based on 3D anisotropic layered shell and solid element models were conducted to further compare and verify the results obtained from the new developed analytical approach. The results show that the new model has potential to be used as an alternative tool to FEM if an accurate method to analyses the stresses and deformation of problematic FRP bolted joint applications.

On the Modelling of Anisotropic Fiber Reinforced Polymer Flange Joints

2021 ◽  
Author(s):  
Abdel-Hakim Bouzid ◽  
Ali K. Vafadar ◽  
Anh-Dung Ngo
Keyword(s):  
Numerical Models ◽  
Design Procedure ◽  
Accurate Method ◽  
Pressure Vessels ◽  
Fiber Reinforced ◽  
Plastic Composite ◽  
Asme Code ◽  
Section Viii ◽  
The One ◽  
Bolted Flange

Abstract Fiber Reinforced Plastic composite flanges have recently experienced a spectacular development in the area of pressure vessels and piping. The current procedures used for the design of these flanges are a major concern because of their inappropriateness to address the anisotropic behavior of composite materials. The current ASME code section X related to the design procedure of composite flanges uses the same analytical method as the one of section VIII division 2 which treat the flanges as isotropic materials such as metallic flanges. This study deals with FRP bolted flange joints integrity and bolt tightness. A new developed analytical FRP model that treats anisotropic flanges with and without a hub is presented. The model is based on the anisotropy and a flexibility analysis of all joint elements including the gasket, bolts and flanges. It is supported experimentally with tests conducted on a real NPS 3 class 150 WN FRP bolted flange. Furthermore, three different numerical models based on 3D anisotropic layered shell and solid element models were conducted to further compare and verify the results obtained from the new developed analytical approach. The results show that the new model has potential to be used as an alternative tool to FEM if an accurate method to analyses the stresses and deformation of problematic FRP bolted joint applications.

Limit Loads of Bolted Flange Connections

2021 ◽  
Author(s):  
Finn Kirkemo ◽  
Przemyslaw Lutkiewicz
Keyword(s):  
Calculation Method ◽  
Production Systems ◽  
Pressure Vessels ◽  
Finite Element Analyses ◽  
Limit Loads ◽  
Face To Face ◽  
Structural Capacity ◽  
Process Piping ◽  
Asme Code ◽  
Bolted Flange

Abstract High-pressure applications such as process piping, pressure vessels, risers, pipelines, and subsea production systems use bolted flange connections. Design of flanged joints may be done by design by rules and design by analysis. This paper presents a design by rules method applicable for flanges designed for face-to-face make-up. Limit loads are used to calculate the structural capacity (resistance) of the flanges, bolts, and metallic seal rings. Designers can use the calculation method to size bolted flange connections and calculate the structural capacity of existing bolted flange connections. Finite element analyses have been performed to verify the analytically based calculation method. The intention is to prepare for an ASME code case based on the calculation method presented in this paper.

Flange Joint Bolt Spacing Requirements

2007 ◽  
Author(s):  
William J. Koves
Keyword(s):  
Complex System ◽  
Analytical Solution ◽  
Code Design ◽  
Flange Joint ◽  
Stress Variation ◽  
Design Rules ◽  
Asme Code ◽  
Leak Tightness ◽  
Bolted Flange ◽  
Bolt Spacing

The bolted flange joint assembly is a complex system. System stresses are dependent on elastic and nonlinear interaction between the bolting, flange and gasket. The ASME Code design rules provides a method for sizing the flange and bolts to be structurally adequate for the specified pressure design conditions and are based on an axi-symmetric analysis of a flange. The ASME rules do not address the circumferential variation in gasket and flange stress due to the discrete bolt loads. Proper bolt spacing is important to maintain leak tightness between bolts and to avoid distorting the flange. This paper provides an analytical solution for the gasket and flange stress variation between bolts. The analytical solution is validated with 3-D Finite Element solutions of standard flange designs.

Calculation of Bolted Flange Connections of Floating and Metal-to-Metal Contact Type

2003 ◽  
Author(s):  
M. Schaaf ◽  
J. Bartonicek
Keyword(s):  
Pressure Vessels ◽  
Metal Contact ◽  
Second Step ◽  
European Standard ◽  
Calculation Algorithm ◽  
Contact Type ◽  
Asme Code ◽  
Floating Type ◽  
Bolted Flange

In Europe, in 2001 the new standard EN 1591 for strength and tightness proofs of bolted flange connections (BFC) of floating type flanges was released. In addition, the German nuclear code was revised regarding the calculation of BFC. With this standard not only the floating type but also the metal-to-metal contact type of flanges (MMC) can be treated. Additionally, the ASME code is the basis for the flange calculation in the European standard EN 13445, which is the standard for unfired pressure vessels. In compliance with the goal of the calculation, the different calculation codes can be used. There must be a differentiation between the design of the components, the determination of the prestress values for assembly, the stress analysis and the tightness proof of the BFC. First, all parameters which influence the function of the bolted flange connection are considered. In a second step, the range of use of the different standards and the calculation algorithm are discussed.

Pressure Vessels of Noncircular Cross Section (Commentary on New Rules for ASME Code)

1979 ◽  
Vol 101 (3) ◽  
pp. 255-267 ◽  
Author(s):  
J. H. Faupel
Keyword(s):  
Cross Section ◽  
Heat Exchangers ◽  
Pressure Vessels ◽  
Background Information ◽  
Code Design ◽  
Hospital Service ◽  
Design Procedures ◽  
Noncircular Cross Section ◽  
Asme Code ◽  
Present Design

Background information is given relative to Code design procedures for pressure vessels of noncircular cross section. Such vessels have wide application as component parts of air-cooled heat exchangers, duct work, special piping, extrusion chambers and specialty vessels used in laundry and hospital service and heat transfer applications. Present design coverage is for internal pressure only for unreinforced, reinforced and stayed vessels of rectangular and obround cross section.

Thermomechanical Analysis of Pressure Vessels

2012 ◽  
Author(s):  
Michael Benson ◽  
David Rudland ◽  
Mark Kirk
Keyword(s):  
Thermal Stresses ◽  
Thermomechanical Analysis ◽  
Pressure Vessels ◽  
Pressurized Water ◽  
Asme Code ◽  
Water Reactors ◽  
Inner Vessel ◽  
American Society ◽  
The One ◽  
Technical Basis

Regulatory Guide (RG) 1.161 and American Society of Mechanical Engineers Boiler and Pressure Vessel Code (ASME Code), Section XI, Nonmandatory Appendix K contain stress intensity factor (SIF) equations for both the internal pressure and thermal gradient loading cases. However, the technical basis behind these equations was developed only for Ri/t = 10, were Ri is the inner vessel radius and t is the vessel thickness. While this geometry is appropriate for most pressurized water reactors (PWR), most boiling water reactor (BWR) vessels have Ri/t = 20. This paper explores the validity of applying these SIF equations to BWRs. This confirmatory work includes calculating SIF by independent methods. The one-dimensional heat equation is solved to provide a physical basis for the thermal stresses.

Use of Duplex Stainless Steel in Economic Design of a Pressure Vessel

2006 ◽  
Vol 129 (1) ◽  
pp. 155-161 ◽  
Author(s):  
Milan Veljkovic ◽  
Jonas Gozzi
Keyword(s):  
Stainless Steel ◽  
Duplex Stainless Steel ◽  
Stainless Steels ◽  
Pressure Vessel ◽  
Design Procedure ◽  
High Strength Steels ◽  
High Strength ◽  
Pressure Vessels ◽  
Economic Design ◽  
European Standard

Pressure vessels have been used for a long time in various applications in oil, chemical, nuclear, and power industries. Although high-strength steels have been available in the last three decades, there are still some provisions in design codes that preclude a full exploitation of its properties. This was recognized by the European Equipment Industry and an initiative to improve economy and safe use of high-strength steels in the pressure vessel design was expressed in the evaluation report (Szusdziara, S., and McAllista, S., EPERC Report No. (97)005, Nov. 11, 1997). Duplex stainless steel (DSS) has a mixed structure which consists of ferrite and austenite stainless steels, with austenite between 40% and 60%. The current version of the European standard for unfired pressure vessels EN 13445:2002 contains an innovative design procedure based on Finite Element Analysis (FEA), called Design by Analysis-Direct Route (DBA-DR). According to EN 13445:2002 duplex stainless steels should be designed as a ferritic stainless steels. Such statement seems to penalize the DSS grades for the use in unfired pressure vessels (Bocquet, P., and Hukelmann, F., 2001, EPERC Bulletin, No. 5). The aim of this paper is to present an investigation performed by Luleå University of Technology within the ECOPRESS project (2000-2003) (http://www.ecopress.org), indicating possibilities towards economic design of pressure vessels made of the EN 1.4462, designation according to the European standard EN 10088-1 Stainless steels. The results show that FEA with von Mises yield criterion and isotropic hardening describe the material behaviour with a good agreement compared to tests and that 5% principal strain limit is too low and 12% is more appropriate.

Development of a Fatigue Design Curve for Austenitic Stainless Steels in LWR Environments: A Review

2002 ◽  
Author(s):  
Omesh K. Chopra
Keyword(s):  
Stainless Steels ◽  
Pressure Vessel ◽  
Type Strain ◽  
Nuclear Power ◽  
Austenitic Stainless Steels ◽  
Environmental Parameters ◽  
Light Water Reactor ◽  
Code Design ◽  
Fatigue Design ◽  
Asme Code

The ASME Boiler and Pressure Vessel Code provides rules for the construction of nuclear power plant components and specifies fatigue design curves for structural materials. However, the effects of light water reactor (LWR) coolant environments are not explicitly addressed by the Code design curves. Existing fatigue strain–vs.–life (ε–N) data illustrate potentially significant effects of LWR coolant environments on the fatigue resistance of pressure vessel and piping steels. This paper reviews the existing fatigue ε–N data for austenitic stainless steels in LWR coolant environments. The effects of key material, loading, and environmental parameters, such as steel type, strain amplitude, strain rate, temperature, dissolved oxygen level in water, and flow rate, on the fatigue lives of these steels are summarized. Statistical models are presented for estimating the fatigue ε–N curves for austenitic stainless steels as a function of the material, loading, and environmental parameters. Two methods for incorporating environmental effects into the ASME Code fatigue evaluations are presented. Data available in the literature have been reviewed to evaluate the conservatism in the existing ASME Code fatigue design curves.

Design Formulas of Blind End Closures for High Pressure Vessels

2009 ◽  
Vol 131 (3) ◽  
Author(s):  
R. D. Dixon ◽  
E. H. Perez
Keyword(s):  
High Pressure ◽  
Fatigue Life ◽  
Maximum Stress ◽  
Accurate Determination ◽  
Pressure Vessels ◽  
Stress Distributions ◽  
Fatigue And Fracture ◽  
Asme Code ◽  
Section Viii

The available design formulas for flat heads and blind end closures in the ASME Code, Section VIII, Divisions 1 and 2 are based on bending theory and do not apply to the design of thick flat heads used in the design of high pressure vessels. This paper presents new design formulas for thickness requirements and determination of peak stresses and stress distributions for fatigue and fracture mechanics analyses in thick blind ends. The use of these proposed design formulas provide a more accurate determination of the required thickness and fatigue life of blind ends. The proposed design formulas are given in terms of the yield strength of the material and address the fatigue strength at the location of the maximum stress concentration factor. Introduction of these new formulas in a nonmandatory appendix of Section VIII, Division 3 is recommended after committee approval.

Air Characteristics in Air Turbine Spindle of Ultra Precision Machines

2010 ◽  
Vol 297-301 ◽  
pp. 396-401
Author(s):  
Mehrdad Vahdati ◽  
E. Azimi ◽  
Ali Shokuhfar
Keyword(s):  
High Speed ◽  
Design Procedure ◽  
Inlet Pressure ◽  
Cylindrical Shape ◽  
Air Inlet ◽  
Wind Turbine System ◽  
Air Turbine ◽  
Ultra Precision ◽  
The One ◽  
Precision Machines

Air Spindles have been used in ultra precision machines for several years due to their advantages such as high speed rotation, low friction, and low vibration, [1]. Air spindles are widely used in these machines for producing precise work pieces. Although, spindles function on a very complicated theoretical basis, [2, 3], their structure is very simple and consists of mainly a rotor and a stator. The rotor/stator could be made of different shapes. A cylindrical shape is the one commonly in use. The spindle designed in this work has a spherical configuration. It has been designed so that it could be moved without application of electric motor and only by a wind turbine system, [4]. The spindle studied in this research uses compressed air for rotor suspension, and has an air turbine for rotating its shaft. A thin air film acts as bearing layer between rotor and stator. In design procedure, operation parameters such as air inlet pressure for turbine, air inlet pressure for bearing, diameter of turbine nuzzles, diameter of bearing nuzzles, clearance between rotor and stator and etc. have been considered, [5]. A prototype spindle has been manufactured using design criteria. The influence of above mentioned parameters have been recognized through experiments.

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