大直径盲孔法兰连接在螺栓载荷和内压作用下的应力和变形分析.docx
大直径盲孔法兰连接在螺栓载荷和内压作用下的外文文献翻译、中英文翻译
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大直径盲孔法兰连接在螺栓载荷和内压作用下的外文文献翻译、中英文翻译,直径,法兰,连接,螺栓,载荷,作用,外文,文献,翻译,中英文
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1 Copyright 2011 by ASME Proceedings of the ASME 2011 Pressure Vessels & Piping Division Conference PVP2011 July 17-21, 2011, Baltimore, Maryland, USA PVP2011-57813 STRESS AND DEFORMATION ANALYSES OF LARGE DIAMETER BLIND FLANGE CONNECTIONS SUBJECTED TO BOLT LOADS AND INTERNAL PRESSURE Takashi KOBAYASHI Numazu National College of Technology , Numazu , Shizuoka ,Japan kobayashnumazu-ct.ac.jp Masahiro KOGASAKA Numazu National College of Technology , Numazu , Shizuoka Japan Kengou NISHIURA Mitsubishi Chemical Corporation , Kurashiki , Okayama Japan Uchiyama KAZUAKI Nichias Corporation , Minato-ku , Tokyo Japan ABSTRACT Leakage problems caused in large diameter gasketed flanged connections in piping systems are closely related to deformation of flanges caused by the high thrust force and rather low rigidity of the flanges. Therefore, it is necessary to understand the deformation characteristics of flanged connections when they are tightened and pressurized. In this study, experiments were carried out using a 16-inch gasketed flanged connection to examine the stress and strain in the flanges. In order to clarify the deformation characteristics of the gasketed flanged connection, a method to analyze stresses and deformations of a gasketed flanged connection was demonstrated using the classical theory by Timoshenko. Recently, finite element analysis (FEA) has widely been used in the analysis of gasketed flanged connections. However, analyses of flanged connection based on the analytical method using strength of materials are still important when parametric calculations of flanged connection are necessary. The experimental results and the analytical ones were compared and discussed to clarify the sealing behaviors of large diameter gasketed flanged connection. INTRODUCTION Gasketed flanged connections have widely been used in refinery plants, power plants, chemical plants and other industrial plants. The sealing behaviors of gasketed flanged connections should be considered in design, assembly, use and maintenance of gasketed flanged connections. Furthermore, due to recent increase of environmental concern, the fugitive emission from the gasketed flanged connection becomes important issue. Large diameter gasketed flanged connections are widely used, as well as small diameter gasketed flanged connections. However, the sealing behaviors of the large diameter gasketed flanged connections have not been fully understood. Therefore, the effects of deformation characteristic of the gasketed flanged connection on the sealing behaviors must be clarified. A test method for the sealing behaviors of gaskets, JIS B 2490, was established in Japan 1. This method focuses on the sealing behaviors of small diameter gaskets. The sealing behaviors of the small diameter gasketed flanged connection have been tested using the results obtained by JIS B 2490 2. In the cases of large diameter gasketed flanged connection, the deformation characteristics such as flange rotation make this problem more complex. In this paper, the strain distributions in large diameter gasketed flanged connection were measured using strain gauges. Two kinds of PTFE gaskets were used for the tests. It is found that the strain in large diameter gakseted flanged connection is low when a stiff gasket is used. Stresses and deformations of a large diameter gasketed flanged connection were calculated using the classical theory by Timoshenko. The experimental results were verified by the analysis. EXPERIMENT Gasket test using platens (JIS B 2490) Firstly, the characteristics of gasket were tested in accordance with the gasket test method JIS B 2490. In this test, a gasket is compressed between the upper and lower platens. The size of the test gaskets is 10K 50A (JIS B 2404). The pressure-temperature rating and nominal diameter approximately correspond to ASME B16.5 Class150 NPS2. The platens have raised faces of 96 mm OD and the surface Proceedings of the ASME 2011 Pressure Vessels & Piping Division Conference PVP2011 July 17-21, 2011, Baltimore, Maryland, USA PVP2011-57813 Downloaded From: / on 01/20/2016 Terms of Use: /about-asme/terms-of-use 2 Copyright 2011 by ASME roughness of the platens is 1.63.2 mRa. Two kinds of gaskets, PTFE with filler (Gasket A) and expanded PTFE (Gasket B), were used in the experiment. The thickness of the gaskets were 3.0 mm. Measurement of strain distributions of blind flange connections In order to measure the strain distributions of the gasketed flanged connection, a large diameter gasketed flanged connection (material: SS400), with pressure-temperature rating and the nominal diameter 10K 400A (JIS B 2404), were chosen for this experiment. The pressure-temperature rating and nominal diameter approximately correspond to ASME B16.5 Class150 NPS16. Figure 1 shows the experimental setup for the large diameter gasketed flanged connection (JIS 10K 400A). Sixteen bolts (material: SS400, size: M24) were used to tighten the flanged connection. For eight bolts out of the sixteen bolts, strain gages were installed at the center of the bolts to measure the bolt load. The bolt load was controlled using a torque wrench. Molybdenum lubricant was applied to the bolts, nut and contact surface of the flanged connection. The nut factor was determined by experiment to be 0.091. EXPERIMENTAL RESULTS AND CONSIDERATIONS Characteristics of gaskets (JIS B 2490) Figure 2 shows the stress-deflection curve for Gasket A and B obtained by gasket test method JIS B 2490. In the case of Gasket A, the deflection at step S8 is small compared with that of Gasket B. When the gaskets are unloaded from Step S8 to S9, the elastic recovery of gasket is small in the case of Gasket A. It can be said that Gasket A is stiff compared with Gasket B. Figure 3 shows the sealing behaviors for Gasket A and B. From the view point of sealing performance, Gasket A is approximately ten times tighter than Gasket B, namely the leak rate of Gasket A is small compared with Gasket B. The differences of gasket behaviors stems from the material properties. The material of the Gasket B is expanded PTFE and it has porous structure. Due to the porous structure of the gasket, the deformation of gasket is large and the leak rate becomes high. Figure 1 Experimental setup (a) Gasket A (b) Gasket B Figure 2 Stress-deflection curve of gasket (a) Gasket A (b) Gasket B Figure 3 Sealing behavior as a function of gasket stress S2S3S4S6S71.00E-061.00E-051.00E-041.00E-031.00E-021.00E-011.00E+0001020304050Gasket stress e N/mm2Leak rate L0 Pa m3/sS10S1S2S3 S4S5S6 S7 S8S11051015202530354045500.0000.400.500.60Thickness changes of gasket mmGasket stress e N/mm2S9S10S11 S8S7 S6 S4 S5 S3 S2S11.00E-061.00E-051.00E-041.00E-031.00E-021.00E-011.00E+0001020304050Gasket stress e N/mm2Leak rate L0 Pa m3/sS9 S10S11S8S7 S6 S4S5S3 S2S1051015202530354045500.0000.400.500.60Thickness changes of gasket mmGasket stress e N/mm2S8S9S10S1 S5 S11S2S3S4S6S7Downloaded From: / on 01/20/2016 Terms of Use: /about-asme/terms-of-use 3 Copyright 2011 by ASME Strain of flange Figure 4 shows the strain distributions in the flanged connection at initial tightening in the case of Gasket A, as an example. Figures 4 (a) and (b) are the radial strain r and the circumferential strain, respectively. With increasing the tightening torque, the strains increased. However, it is noted that the strain distributions are almost uniform. Figure 5 shows the strain distributions when pressurized in the case of Gasket A, as an example. The initial tightening torque was 100 Nm and the internal pressure was increased to 1.5 MPa. Figures 5(a) and (b) are the radial strain r and the circumferential strain, respectively. With increasing the internal pressure, the strains near the center of the gasketed flanged connection increased. This is because the flange was bent by the thrust force due to the internal pressure. In the case of Gasket B, as the tendencies were almost the same as those of Gasket A, the results are not shown. Stress of flange Based on the measured strains shown in Fig4 and 5, stresses r and were calculated using the following equation: rrrEE2211 (1) Furthermore, the von Mises stress can be calculated using the following equation: (2) Figure 6 demonstrates the von Mises stress near the center of gasketed flanged connection(r=25mm). The changes of stresses in the initial tightening state and the pressurized state(internal pressure 1.0MPa) in the cases of Gasket A and B are shown. It is noted that the von Mises stresses of Gasket B are high compared with those of Gasket A. This is related to the deformation characteristics of gaskets shown in Fig.2 and those of flanges. The gasketed flanged connection is deformed by the bolt load and the thrust force due to the internal pressure. As Gasket A is stiff compared with Gasket B, the gasket stress becomes high at the outer circumference of the gasket when the flanged connection is deformed. Because of this, the length of the lever arm becomes short and the stress in the case of Gasket B becomes less. (a) radial strain r (b) circumferential strain Figure 4 Strain distribution at initial tightening (the case of Gasket A) (a) radial strain r (b) circumferential strain Figure 5 Strain distribution when pressurized (the case of Gasket A, tightening torque 100Nm)-2000200400600800050100150200250300Distance from center r mmStrain r strain50N100Nm150NmTightening torque -2000200400600800050100150200250300Distance from center r mmStrain strain50N100Nm150NmTightening torque-2000200400600800050100150200250300Distance from center r mmStrain strain0MPa0.5MPa1.0MPa1.5MPaInternal pressure -2000200400600800050100150200250300Distance from center r mmStrain strain0MPa0.5MPa1.0MPa1.5MPaInternal pressurerreq22Downloaded From: / on 01/20/2016 Terms of Use: /about-asme/terms-of-use 4 Copyright 2011 by ASME Figure 6 Comparisons of von Mises stress near the center of the gasketed flanged connection Analysis of flange deformation In order to clarify the deformation characteristics of the gasketed flanged connection, an analysis using the classical theory by Timoshenko was carried out. Figure 7 shows the model for analysis of the gasketed flanged connection. Nomenclature is as follows: a : Inner radius of gasket b : Radius of center of width of gasket c : Radius of bolt pitch circle d : Radius of blind flange t : Flange thickness The flange is divided into four parts: Part I, II, III and IV. Each part can be analyzed by the theory of bending of plates3. Part I, II, III and IV are connected each other at points A, B and C. For simplicity, only the flange was modeled in this study. It is assumed that the flange is fixed at the center of the width of gasket (r=b) and that the bolt load is applied continuously on the bolt pitch circle. The boundary conditions are summarized in Table 1. The analytical method is based on the method by the authors 4. Figure 8 demonstrates the analytical result of deflection curve of the gasketed flanged connection. The tightening torque is 100 Nm. Then, the internal pressure 1 MPa is applied. The gasketed flanged connection is bent by the bolt load and the thrust force increases the deflection in the gasketed flanged connection. Due to this deformation, the gasket compression in the radial direction cannot be uniform. Thus, the deformation characteristics of gasketed flanged connection affect the sealing behaviors of gasketed flanged connections. Although the deformation characteristics of the gasket are not considered in this study, we need to consider those in our future studies. In Fig. 9, analytical results concerning strains of the gasketed flanged connection are compared with experimental ones in the case of Gasket B. The analytical results agree well with the experimental ones. In the future studies, we will examine the effects of the deformation characteristics of gasketed flanged connection on the sealing performance using the analytical method shown in this paper. Table 1 Matrix of boundary conditions considered w:deflection, M:moment Figure 7 Model for analysis of blind flange Connecting point Distance from center Boundary condition Deflection Slope Moment (radial) A r = a IIIww drdwdrdwIII IIIMM B r = b 0IIIIIww drdwdrdwIIIIIIIIIIMMC r = c IVIIIww drdwdrdwIVIIIIVIIIMMD r = d - - 0IVM 050100150200250050100150200Mises stress eq N/mm2Tightening torque T NmGasket AGasket BGasket AGasket BDownloaded From: / on 01/20/2016 Terms of Use: /about-asme/terms-of-use 5 Copyright 2011 by ASME Figure 8 Analytical result of deflection curve (Tightening torque 100Nm, Internal pressure 1MPa) (a) radial strain r (b) circumferential strain Figure 9 Strain distribution when pressurized (The case of Gasket B) CONCLUSION The deformation characteristic of gasketed flanged connection was discussed in this study. Results obtained are as follows: (1) It is shown that the stress and strain of gasketed flanged connection is affected by the deformation characteristics of gaskets. The stresses of gasketed flanged connection become low when stiff gaskets are used. (2) A simplified analytical method of gasketed flanged connection was demonstrated. The analytical results concerning strain distributions agreed well with the experimental ones. REFERENCES 1 JIS B 2490 2008, ”Test method for sealing behavior of gaskets for pipe flanges” ,(in Japanese), Japanese Industrial Standers 2 T. Kobayashi, M. Kiichi, K. Nishiura, H. Shibata, 2010,”Method to Estimate the Bolt Loads to Satisfy Tightness Criteria for Gasketed Bolted Flanged Connection”, ASME PVP-25614. 3 S. Timoshenko, Strength of Materials Part II: Advanced theory and problems, Third Edition 1956, D. Van Nostrand Company, New York. 4 T. Kobayashi et al., 2010,” Stress and Deformation Analyses of Flanges Subjected to Bolt Loads and Internal Pressure”, ASME PVP-25622. -2000200400600800050100150200250300Distance from center r mmStrain r strainAnalytical Experimental -2000200400600800050100150200250300Distance from center r mmStrain strainAnalyticalExperimental -0.60-0.40-0.200.000.200.400.600.80050100150200250300Deflection w mmDistance from center r mmPressurisedInitial tighteningCenter of gasketDownloaded From: / on 01/20/2016 Terms of Use: /about-asme/terms-of-use外文题目 Stress and Deformation Analyses of Large Diameter Blind Flange Connections Subjected to Bolt Loads and Internal Pressure 译文题目 在螺栓载荷和内压作用下大直径盲孔法兰连接的 应力和变形分析 外文出处 ASME 2011 Pressure Vessels and Piping Conference 大直径盲孔法兰连接在螺栓载荷和内压作用下的应力和变形分析作者：Takashi KOBAYASHI沼津国立技术学院，Kengou NISHIURA三菱化学株式会社Masahiro KOGASAKA 沼津沼津国立技术学院 ，Uchiyama KAZUAKI 日本日亚化工摘要管道系统中大直径垫片法兰连接引起的泄漏问题，与较大的法兰轴向力和较低的凸缘刚度造成的法兰变形密切相关。因此，有必要了解法兰连接在加压收紧时的变形特性。在这项研究中，使用16英寸垫片法兰连接进行实验，以检测法兰中的应力和应变。为了阐明密封法兰连接的变形特性，运用Timoshenko经典理论，分析密封法兰连接的应力和变形的方法。近来，有限元分析（FEA）已被广泛使用于法兰连接的分析中。然而，当需要法兰连接的参数计算时，基于材料强度的分析方法仍然很重要。本文对实验结果和分析结果进行了比较和讨论，以阐明大直径垫片法兰连接的密封性能。1. 介绍密封法兰连接已广泛用于炼油厂，发电厂，化工厂和其他工业厂房。在密封法兰连接的设计，组装，使用和维护中其密封性能都应被考虑。 此外，由于近来环境问题的日益恶化，密封法兰连接的泄露已成为重要问题。尽管大直径垫片法兰连接和小直径垫片法兰连接一样被广泛的使用。但是，大直径垫片法兰连接的密封性能尚未完全了解。 因此，必须明确垫片法兰连接件的变形特性对密封性能的影响。日本制定了密封垫圈的密封性能试验方法JIS B 24901。该方法主要用于小直径垫圈的密封性能。根据JIS B 2490测试小直径垫片法兰连接件的密封性能2。在大直径垫片法兰连接的情况下，法兰转角等变形特性使得这个问题更为复杂。在本文中，使用应变仪测量两种PTFE垫圈大直径垫片法兰连接处的应变分布。研究发现当使用刚性垫片时，大直径垫片（密封）法兰连接处的应变较低。 使用Timoshenko的经典理论计算大直径垫片法兰连接的应力和变形。通过分析验证了实验结果。2. 实验使用压板的垫片测试（JIS B 2490）首先，根据JIS B 2490垫片测试方法，测试垫片的特性。在该测试中，垫片在上下压板之间被压缩。测试垫片的尺寸是10K 50A（JIS B 2404）。压力温度额定值和公称直径大致对应于ASME B16.5 Class150 NPS2。压板的凸面外径为96mm，压板表面粗糙度为1.63.2mRa。 实验中使用了两种垫片，PTFE填充物（垫片A）和膨胀PTFE（垫片B）， 垫片的厚度是3.0mm。图1 试验装置（a） 垫片A（b）垫片B图2. 垫圈的应力应变曲线（a） 垫片A（b） 垫片B图3. 密封性能与垫圈应力的函数关系3. 测量盲孔法兰连接的应变分布为了测量密封法兰连接的应变分布，本实验选择了压力温度为额定值和公称直径为10K 400A（JIS B 2404）的大直径衬垫法兰连接（材料：SS400）。压力温度额定值和公称直径大致对应于ASME B16.5 章150 NPS16。 图1显示了大直径垫片法兰连接（JIS 10K 400A）的实验装置。使用十六个螺栓（材料：SS400，尺寸：M24）来拧紧法兰。在十六个螺栓中的，应变计安装在其中八个螺栓的中心以测量螺栓载荷。使用扭矩扳手控制螺栓载荷。法兰连接的螺栓，螺母和接触表面使用钼润滑剂。螺栓系数通过实验确定为0.091。4. 实验结果和结论垫片特性（JIS B 2490）图2展示了通过JIS B 2490垫圈试验方法获得的垫圈A和B的应力变形曲线。在垫圈A中，S8点的挠度比垫片B的挠度小。当垫圈从S8到S9，垫片A的弹性恢复很小。因此可以看出垫片A比垫片B硬度大。图3显示了垫圈A和B的密封性能。从密封性能的观点来看，垫圈A的密封性能大约是垫圈B的 10倍，即垫圈A的泄漏率比垫圈B小。垫圈性能的差异源于材料的特性。垫片B的材料是具有多孔结构的膨体聚四氟乙烯。由于垫片是多孔结构，所以垫片的形变较大，泄漏率较高。5. 法兰应变如图4所示，垫圈A在初始紧固时的法兰连接中的应变分布。图4（a）和（b）分别是径向应变和周向应变。随着拧紧扭矩的增加，应变增加。但是，应该指出的是，应变分布几乎是均匀的。如图4所示，垫圈A在加压时的应变分布。 初始紧固扭矩为100 Nm，内部压力逐渐增加到1.5 MPa。 图5（a）和（b）分别是径向应变和圆周应变。 随着内部压力的增加，密封法兰连接中心附近的应变也随之增加。 这是因为法兰因受内压的作用而弯曲。 在垫片B中，由于趋势与垫片A的趋势几乎相同，所以结果未显示。6. 法兰应力基于图4和图5所示的测
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