基于非连续性特点的盘式拉杆转子轴承系统弯振动力学研究
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摘要
随着燃气轮机技术的不断发展,盘式拉杆转子获得了较为广泛的应用。该类转子具有非连续性和非整体性的结构特点,这使得该种转子的振动特性与一般连续整体转子有较大区别。现有转子动力学的研究对象主要为连续整体转子,对盘式拉杆转子做振动计算时往往以连续整体转子对待,或用刚度系数修正的办法做近似处理,所得结果均不太理想,难以满足工程实际的需求。因此,有必要从理论上对这一课题做进一步深入的研究和探讨。
针对盘式拉杆转子非连续性和非整体性的结构特点,本文对盘式拉杆转子各耦合接触处(轮盘接触界面、拉杆与轮盘耦合接触处)提出了三条基本力学假设。在将键合图模态分析法推广到连续梁弯曲振动模态分析的基础上,结合力学假设,建立了盘式拉杆转子弯曲振动的键合图耦合动力学分析理论模型。用所建模型对一试验盘式拉杆转子进行理论计算,所得结果与试验结果对比分析表明本文所建模型计算结果与实测结果吻合较好,且计算精度比以往用连续整体转子模型或用刚度系数修正法计算有较大提高,同时各计算结果对比也表明盘式拉杆转子的结构特点会使其固有频率有所降低,其值对轮盘接触面间当量弯曲刚度值较敏感。在进一步考虑轴承效应后,建立了盘式拉杆转子轴承系统动力学理论分析模型。计算表明,盘式拉杆转子的结构特点对其临界转速同样有着较大的影响,是计算中不可忽视的因素,其中轮盘表面加工精度的提高、拉杆预紧力的增大和轮盘级数的减少会使其临界转速值提高,而拉杆尺寸的增大将使其临界转速值降低。
以上研究结果解决了工程实际中计算盘式拉杆转子轴承系统振动特性精度不高的问题,同时也给拉杆转子的设计提供了一定的参考,具有重要的应用价值。
With the development of gas turbine techniques, disc-type rod fastening rotor is getting use. Its major structural characteristics are that a rotor is not continuous and not integral, this causing the rotor type to present different vibration characteristics from general continuous and integral rotors. At present, study on rotor dynamics mainly focuses on continuous and integral rotors. When calculating vibration characteristics, disc-type rod fastening rotors are often regarded as continuous integral rotors or correction is conduced with a stiffness modified coefficients. The results from doing so are not satisfactory. So it is necessary to make a further study on this subject.
In view of the structural characteristics that a disc-type rod fastening rotor is not continuous and not integral, we put forward several basic mechanical assumptions for coupling and contact points of disc-type rod fastening rotors. We establish a bond graph coupling dynamic analytical model for disc-type rod fastening rotors based on the application of bond graph modal analysis method to bending vibration modal analysis for continuous beam and in combination with mechanical assumptions. With this model, we perform theoretical calculation for a experimental rod fastening rotor and comparison between the calculation result and measurement result shows that the calculation result agree with the measurement result well, the calculation accuracy is improved to a great extent in comparison with the previous calculation with the model for continuous and integral rotors or stiffness modified coefficient method. In addition, the comparison between various calculation results also shows that the structural characteristics of disc-type rod fastening rotors results in a reduced natural frequency and such frequency is sensitive to equivalent bending stiffness on inter-contact contact surface. After further considering bearing effect, we establish a dynamic analytical model for bearing system for disc-type rod fastening rotors. The calculation shows that the structural characteristics of disc-type rod fastening rotors influence its critical speed in such way with natural frequency and its critical speed is lower than the one of continuous integral rotor-bearing system with the same size.
The above study solve the problem how to improve the vibration characteristics computational accuracy for disc-type rod fastening rotor-bearing system in engineering practice and therefore has significant application value.
针对盘式拉杆转子非连续性和非整体性的结构特点,本文对盘式拉杆转子各耦合接触处(轮盘接触界面、拉杆与轮盘耦合接触处)提出了三条基本力学假设。在将键合图模态分析法推广到连续梁弯曲振动模态分析的基础上,结合力学假设,建立了盘式拉杆转子弯曲振动的键合图耦合动力学分析理论模型。用所建模型对一试验盘式拉杆转子进行理论计算,所得结果与试验结果对比分析表明本文所建模型计算结果与实测结果吻合较好,且计算精度比以往用连续整体转子模型或用刚度系数修正法计算有较大提高,同时各计算结果对比也表明盘式拉杆转子的结构特点会使其固有频率有所降低,其值对轮盘接触面间当量弯曲刚度值较敏感。在进一步考虑轴承效应后,建立了盘式拉杆转子轴承系统动力学理论分析模型。计算表明,盘式拉杆转子的结构特点对其临界转速同样有着较大的影响,是计算中不可忽视的因素,其中轮盘表面加工精度的提高、拉杆预紧力的增大和轮盘级数的减少会使其临界转速值提高,而拉杆尺寸的增大将使其临界转速值降低。
以上研究结果解决了工程实际中计算盘式拉杆转子轴承系统振动特性精度不高的问题,同时也给拉杆转子的设计提供了一定的参考,具有重要的应用价值。
With the development of gas turbine techniques, disc-type rod fastening rotor is getting use. Its major structural characteristics are that a rotor is not continuous and not integral, this causing the rotor type to present different vibration characteristics from general continuous and integral rotors. At present, study on rotor dynamics mainly focuses on continuous and integral rotors. When calculating vibration characteristics, disc-type rod fastening rotors are often regarded as continuous integral rotors or correction is conduced with a stiffness modified coefficients. The results from doing so are not satisfactory. So it is necessary to make a further study on this subject.
In view of the structural characteristics that a disc-type rod fastening rotor is not continuous and not integral, we put forward several basic mechanical assumptions for coupling and contact points of disc-type rod fastening rotors. We establish a bond graph coupling dynamic analytical model for disc-type rod fastening rotors based on the application of bond graph modal analysis method to bending vibration modal analysis for continuous beam and in combination with mechanical assumptions. With this model, we perform theoretical calculation for a experimental rod fastening rotor and comparison between the calculation result and measurement result shows that the calculation result agree with the measurement result well, the calculation accuracy is improved to a great extent in comparison with the previous calculation with the model for continuous and integral rotors or stiffness modified coefficient method. In addition, the comparison between various calculation results also shows that the structural characteristics of disc-type rod fastening rotors results in a reduced natural frequency and such frequency is sensitive to equivalent bending stiffness on inter-contact contact surface. After further considering bearing effect, we establish a dynamic analytical model for bearing system for disc-type rod fastening rotors. The calculation shows that the structural characteristics of disc-type rod fastening rotors influence its critical speed in such way with natural frequency and its critical speed is lower than the one of continuous integral rotor-bearing system with the same size.
The above study solve the problem how to improve the vibration characteristics computational accuracy for disc-type rod fastening rotor-bearing system in engineering practice and therefore has significant application value.
引文
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[2]M.A.Prohl.A General Method for Calculating Critical Speeds of Flexible Rotors,J.of Appl.Mech.Mech.Trans.ASME,1945,vol.12
[3]G.C.Horner and W.D.Pilkey.The Riccati Transfei Matrix Method.J.of Mech.Des.Trans.ASME,1978,vol.4
[4]王正.Riccati传递矩阵法在转子动力学中的应用.清华大学工程力学系理论教研组,1982.7
[5]R.L.Ruhl and J,F,Booker.A Finite Element Model for Distributed Parameter Turborotor Systems.J.of.Eng.for Indus.Trans ASME.Feb,1972
[6]Hurty W C.Dynamic Analysis of Structural Systerm Using Component Modes,AIAA.JM,1965,Vol.3
[7]郑兆昌.复杂结构振动研究的模态综合技术.振动与冲击.第一卷第一期,1982,Vol.11
[8]王文亮,杜作润.结构振动与动态子结构方法.复旦大学出版社,1985
[9]张文.复合回转系统临界转速分析.复旦学报(自然科学版),1977,No.1:32-41
[10]刘方杰,安永民.双转子系统动力特性的子结构分析.全国第二届转子动力学学术讨论文集.江西九江,1989:9-15
[11]Lund J W.Springy and Damping Coefficients for The Tilting Pad Journal Bearing.Trans.ASLE,1964,7:342-352
[12]Yu Lie,Xie You Bai,Zhu Zhen,et al.Self-Excited Vibrations of Rotor System With Tilting-Pad Bearings.中国机械工程学报(英文版),1990,3(2)
[13]张鄂,朱均.径向滑动轴承稳定性的计算及研究.润滑与密封,1990(2)
[14]Aostino L.Effect of Vapor/has Bubble on The Rotor Dynamic for Cesin Bearings.IN:Proceeding of the 1996 ASME Fluids Enineer in Division Summe Meeting.Part1(B)Jul,1996,15(1):337-343
[15]Symposium of the Second International Conference on Vibrations in Rotating Machinery,Cambridge.Sept.1980
[16]Smith D N.Journal Bearing Dynamic Characteristic effect of Inertia of Lubricant.Imech M Conf.on Lub.and Wear,1965:37-44
[17]Bently D B,Muszynska A.Perturbation Tests of Bearing Seal for Evaluation of Dynamic Coefficients.Rotor Dynamic Instability,ASME AMD,1983:55
[18]Fayolle P,Childs D W.Rotor Dynamic Evaluation of a henced-Land Hybrid Bearing.Journal of rriboloy,Trans.ASME,2003,121(1):133-139
[19]Renshaw A A.Vibriation Considerations In Foil-bearing Design.Journal of Applied Mechanics,Trans.ASME,2003,66(2):432-438
[20]Olmes R.The Control of Engine Vibration Using Squeeze Film Dampers.Trans.ASME.Journal of Engineering Power,2002,105:525-529
[21]R.Holmes,J.E.H.Sykes.The vibration of an aero-engine rotor incorporating two squeeze-film dampers,Proceedings of the Institution of Mechanical Engineers,1996:103-107
[22]Rabinowitze M D.Hahn E J.Steady State Performance of Squeeze Film Damper Supported Flexible Rotor.J.of engineering.Power.Oct,2000:552-558
[23]Zhan S P.Yan L T.Development of Parou Squeeze Film Damper Bearings For Improving The Blade Loss Dynamics of Rotor Support Systems.J.of Vibration and Acoustics,2001,125:114
[24]Gu J L.Ren X M.Active Control of Vibration of Rotor Support Systems by The Control Led Squeeze Film Dampe Bearings.In.Proc.3rd Intl.Conference on Rotor Dynamics,IFToMM,Lyon,France,1990:327-332
[25]张俊红,于镒隆,高宏阁.多支承转子系统弯曲振动分析方法研究.机械工程学报,2004,Vol.7
[26]Mend G,Guo Y C.The Influence of Fluid Inertia Forces on The Sudden Unbalance Responses of Squeeze Film Damper Support Rotors.Journal of Enineerin rriboloy,2000,212(5):353-357
[27]钟一愕,何衍宗等.转子动力学.北京:清华大学出版社,1987:36-83
[28]Eswards S,Lees A W.Fault Diagnosis of Rotating Machinery.Shock and Vibration Digest,2001,30(1):4-13
[29]Farrar C R,Dufey T A.Vibration-based Dampered Etectionin Rotating Machinery.Key Engineering Materials,2001,167:224-235
[30]韩捷,张瑞林.旋转机械故障机理及诊断技术.北京:机械工业出版社,1997
[31]Ranadall RB.Some Developments In Machine Condition Monitoring.ln:Proc.Sth International Conf.on Rotor Dynamics,Gemany,sept.2002:83-95
[32]Messal E E,Bonthron R J.Subharmonic Rotor Stability Due to Elastic Asymmetry.J.En}r.for Industry,1972,94(1):185-192
[33]Taylor D h,Kuma B R.Nonlinear Responses of Short Squeeze Film Dampers.Trans.ASME,J.Lubrication Technology,1980,102:51-58
[34]Ehrich F F.Some Observations of Chaotic Vibration and Acoustics,2000,113:50-57
[35]Ishida Y.Nonlinear Vibrations An Chaos In Rotor Dynamics.JSME International Journal.Series C:Dynamics,Control,Robotics,Design and Manufacturing,1994,37(2):237-245
[36]Zhen J B,Mend G.Bifurcation and Chaos Response of Nonlinear Crack Rotors.Intel.J.of Bifurcation&Chaos,2002,8(3):597-607
[37]Heun Soo Kim,Maenhyo Cho.Stability Analysis of a Turbine Rotor System with Alford Forces.Journal of Sound and Vibration,2003:167-182
[38]Yaasaki K.Chaos in a Weakly Nonlinear Oscillator with Parametric and External Resonances.ASME J.of Appl.Mech,1990,112(2):209-217
[39]H.Xie,G.T.Flowers,L.Fend.Steady-State Dynamic Behavior of Flexible Rotor with Auxiliary Support from a Clearance Bearing.ASME Journal of Vibration and Acoustic,2001,121:78-83
[40]糜洪元.国外燃气轮机发电技术的发展现况与展望.电力设备,2006.Vol.7
[41]张树治.燃气轮机发电机组的开发与应用.电信科学,1999.Vol.6
[42]马少林,王为民.M701F重型燃气轮机国产化研制.电力设备,2006,vol.7:17-19
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