多支承转子系统动力特性分析与试验研究
|
摘要
随着大型汽轮发电机组等大型旋转设备的日益细长化和复杂化,转子系统的支承点的增加,对转子系统的动力特性和状态监测与故障诊断也提出了更高的要求。本文以大型汽轮发电机组的核心部分—多支承转子系统为研究对象,首先以单跨二支承多轮盘转子为引入对象,应用邓柯莱法、传递矩阵法、有限元法对其临界转速进行了计算,并对三种方法的特点与使用范围进行了分析比较。针对转子系统中的各种参数对临界转速的影响,提出了结构参数对临界转速的敏感度概念。进而以搭建的四跨八支承多轮盘转子系统为研究对象,采用ANSYS中的旋转结构模块仿真得到临界转速并提取了临界转速的Campbell图,并分析得到系统各单跨转子与系统转子模态振型及临界转速的关系。通过对瞬态启动响应分析可知：可以通过适当提高启动加速度的方式减小转子系统通过共振区的最大振动幅值,保证其能够更加安全可靠的运行,从而延长使用寿命。
通过单跨二支承单轮盘转子试验台的试验研究,获取了系统幅频特性和波德图,进而得到系统临界转速试验值。将此试验值与通过ANSYS仿真得到得临界转速结果对比分析：结果数据比较吻合,说明利用ANSYS中的旋转结构模块对转子的临界转速计算方法是可行的。
搭建了四跨八支承多轮盘转子试验台中的第四跨转子并安装调试了测试系统,包括对传感器的选用与标定。对课题组自行研制的某二维轴承负荷传感器进行了静态标定试验与静动态仿真标定,可知其静动态特性较好,能够准确地对轴承负荷实施测量。由于提取轴心轨迹中的故障特征能够对转子系统进行监测与故障诊断,试验中提取了两种不同稳态转速下的轴心轨迹,通过去噪处理后与仿真获得的轴心轨迹进行比较分析,得到了轴心轨迹在不同稳态转速下的轨迹特点。
As the large steam turbine-generator and other large rotating equipments are more and more tenuous and sophisticated, the number of rotor support points are increasing, Higher requirements on the technology—the dynamic character of the rotor system and condition monitoring and fault diagnosis—are putted forward.The research object of this article is part-multi-support rotor system, which is the core part of large steam turbine generator. Single span and two supporting roulette rotor is taken as the research object, while DengKe-lai method, transfer matrix method, and the method of finite element are applied to the calculation of critical speed of it. Characteristics and range of application of the three kinds of method are analyzed and compared. According to the influence—the rotor system various parameters produce—on the critical speed, concept of the sensitivity of the structure parameters on the critical speed is putted forward. And then, the eight-supporting multi-bearing rotor system is taken as the research object, the critical speed is obtained by ANSYS simulation module of rotating structure. By the extracting of critical speed Campbell figure, the relationship of each single rotor system on modal shape and critical speed is obtained. The biggest amplitude while rotor system passing the resonant vibration can be reduced by appropriate increasing Start acceleration, and ensure the safety operation, so as to prolong service life.
By the research on rotor, amplitude frequency characteristics and wave DE figure of the system are obtained, and the critical speed system test value is got. This test value and critical speed results by the ANSYS simulation are contrasted and analysed, and showed that:the results data consistent and the calculation method of rotor critical speed by ANSYS rotating structure module of is feasible.
Eight-supporting many roulette rotor test bench and installation debugging the test system which including the selection of sensor with the calibration is built. The static calibration test and calibration of static and dynamic simulation on the two-dimension bearing load sensor,which is developed by a group are realized, which shows that the static and dynamic characteristics is good and be able to accurately measure the bearing load. Fault features, such as axis path, can be used on stator subsystems monitoring and fault diagnosis. Been denoising treated, Axis path—can be got by the system test in two different extracting the steady rotating speed—is compared with that getting by the simulation. As a result, the axis path in the track of the steady-state rotating speed different characteristics can be obtained.
通过单跨二支承单轮盘转子试验台的试验研究,获取了系统幅频特性和波德图,进而得到系统临界转速试验值。将此试验值与通过ANSYS仿真得到得临界转速结果对比分析：结果数据比较吻合,说明利用ANSYS中的旋转结构模块对转子的临界转速计算方法是可行的。
搭建了四跨八支承多轮盘转子试验台中的第四跨转子并安装调试了测试系统,包括对传感器的选用与标定。对课题组自行研制的某二维轴承负荷传感器进行了静态标定试验与静动态仿真标定,可知其静动态特性较好,能够准确地对轴承负荷实施测量。由于提取轴心轨迹中的故障特征能够对转子系统进行监测与故障诊断,试验中提取了两种不同稳态转速下的轴心轨迹,通过去噪处理后与仿真获得的轴心轨迹进行比较分析,得到了轴心轨迹在不同稳态转速下的轨迹特点。
As the large steam turbine-generator and other large rotating equipments are more and more tenuous and sophisticated, the number of rotor support points are increasing, Higher requirements on the technology—the dynamic character of the rotor system and condition monitoring and fault diagnosis—are putted forward.The research object of this article is part-multi-support rotor system, which is the core part of large steam turbine generator. Single span and two supporting roulette rotor is taken as the research object, while DengKe-lai method, transfer matrix method, and the method of finite element are applied to the calculation of critical speed of it. Characteristics and range of application of the three kinds of method are analyzed and compared. According to the influence—the rotor system various parameters produce—on the critical speed, concept of the sensitivity of the structure parameters on the critical speed is putted forward. And then, the eight-supporting multi-bearing rotor system is taken as the research object, the critical speed is obtained by ANSYS simulation module of rotating structure. By the extracting of critical speed Campbell figure, the relationship of each single rotor system on modal shape and critical speed is obtained. The biggest amplitude while rotor system passing the resonant vibration can be reduced by appropriate increasing Start acceleration, and ensure the safety operation, so as to prolong service life.
By the research on rotor, amplitude frequency characteristics and wave DE figure of the system are obtained, and the critical speed system test value is got. This test value and critical speed results by the ANSYS simulation are contrasted and analysed, and showed that:the results data consistent and the calculation method of rotor critical speed by ANSYS rotating structure module of is feasible.
Eight-supporting many roulette rotor test bench and installation debugging the test system which including the selection of sensor with the calibration is built. The static calibration test and calibration of static and dynamic simulation on the two-dimension bearing load sensor,which is developed by a group are realized, which shows that the static and dynamic characteristics is good and be able to accurately measure the bearing load. Fault features, such as axis path, can be used on stator subsystems monitoring and fault diagnosis. Been denoising treated, Axis path—can be got by the system test in two different extracting the steady rotating speed—is compared with that getting by the simulation. As a result, the axis path in the track of the steady-state rotating speed different characteristics can be obtained.
引文
[1]席文奎.多支承转子-轴承系统轴承负荷辨识试验台设计及其动力学分析[D].太原：太原理工大学,2007.
[2]郑凌云.机械振动中临界转速的工程意义及实践应用[J].机械研究与应用,2004,17(2)：19-21.
[3]Lund J W,Stability and Damped Critical Speeds of a Flexible Rotor in Fluid-Film Bearings,J,of Eng, For Industry, Trans, ASME,1974,95(2),509-517.
[4]Nandi, A.On computation of response of a rotor in deformed configuration using three dimensional finite elements[J].Communications in Numerical Methods in Engineering.2003: 179-195.
[5]陈双涛,侯予,陈汝刚等.高速透平膨胀机临界转速的计算与分析[J].西安交通大学学报,2010,44(9)：33-37.
[6]郑韬,田爱梅,王晓军.基于QZ算法的涡轮泵转子临界转速有限元计算[J].推进技术,2004,25(2)：114-117.
[7]柴山,刚宪约,姚福生.计算多转子系统临界转速的整体传递矩阵法[J].上海理工大学学报,2002,24(1)：8-12.
[8]王美令,陈果.转子系统临界转速计算方法[J].交通运输工程学报,2009,9(6):59-62.
[9]李玉峰,李德福,彭琴等.600MW汽轮发电机组转子-轴承系统的模态分析[J].汽轮机技术,2008,50(4)：244-246.
[10]李贞婷ANSYS模态分析在汽轮发电机转子临界转速计算上的应用[J].防爆电机,2009,44(3)：37-39.
[11]王海明,周 淼,王广庭等.华能阳逻电厂600MW机组轴系振动故障诊断及处理[J].湖北电力,2008,32(5)：38-40.
[12]Liu Jinyang. Study on the vibration of flexible rotor due to its initial bending and unbalance[J]. Journal of Vibration, Measurement & Diagnosis, v 1998:282-286.
[13]Ehrich, F.F.Some observation of chaotic vibration phenomena in high speed rotor dynamics [J]. American Society of Mechanical Engineers, Design Engineering Division (Publication) DE.1989:367-376.
[14]郑龙席,李晓丰.计算转子临界转速的两种方法及对比分析[J].风机技术,2009, 33(6)：35-38.
[15]Lee, C. W., and Joh, C. Y.,1994, "Development of the Use of the Directional Frequency Response Functions for the Diagnosis of Anisotropy and Asymme-try in Rotating Machinery: Theory," Mech. Syst. Signal Process.,86, pp.665-678.
[16]缪红燕,高金吉,徐鸿.转子系统瞬态不平衡响应的有限元分析[J].振动与冲击,2004,23(3)：1-4.
[17]郑龙席,李晓丰,秦卫阳.双盘转子系统各参数对转子瞬态响应影响的研究[J].机械科学与技术,2010,29(9)：1257-1267.
[18]袁小阳,朱均.大型汽轮发电机轴系稳定欲度研究[J].西安交通大学学报,1994,28(9)：51-57.
[19]Ishida, Yukio.Nonlinear vibrations and chaos in rotordynamics, JSME International Journal,SeriesC[J]Dynamics,Control,Robotics, Design and Manufacturing.1994:237-245.
[20]Lund J W. Stability and Damped Critical Speeds of a Flexible Rotor in Fluid-Film Bearings[J].American Society of Mechanical Engineers, Design Engineering Division (Publication) DE.1987:1-9.
[21]Nikolajsen J L.The Effect of Misalignment on Rotor Virations,Journal of Engineering Gas Turbines and Powe,1998,120(7):635-640.
[22]呼浩,陈焰.汽轮发电机组轴系稳定性诊断的研究[J].西北电力技术,2005,(1):36-39.
[23]田新启,高亹.二维PSD及其在轴系标高变化测试中的应用[J].传感器与微系统,2010,30(6)：638-641.
[24]杨兆建,丛红,谢友柏.大型汽轮发电机组四可倾瓦轴承负荷传感器的研究[J].机械科学与技术,1998,3(2)：247-249.
[25]杨兆建,谢友柏.大型汽轮发电机组轴承负荷在线监测方法[J].中国机械工程,1997,8(4)：89-91.
[26]施维新.机组振动故障诊断方法的研究[J].中国电力,1996,29(3):15-19.
[27]李录平.汽轮发电机组振动与处理[M].北京：中国电力出版社,2007.
[28]阮跃.国产200MW机组常见故障的诊断和预防[J].汽轮机技术,1997,39(4):200-205.
[29]成大先.轴及其联接[M].械设计手册,2004,32-35.
[30]唐锦茹.阶梯轴的自然频率和临界转速计算[J].起重运输机械,1996,(12):9-10.
[31 ]顾家柳等.转子动力学[M].北京：国防工业出版社,1985.
[32]周亚武.汽轮机转子有限元建模及动力学分析[D].武汉：华中科技大学,2009.
[33]钟一谔等,转子动力学[M],北京：清华大学出版社,1987:69-95.
[34]朱向哲.转子系统稳态和瞬态不平衡响应的有限元分析[J].石油化工设备技术,2007,28(2)：58-61.
[35]郝建山,韩磊,张智伟等.分布多质量转子系统的不平衡响应特征[J].机械设计与制造,2006(7)：34-36.
[36]孙红岩.利用有限元进行转子系统的动力学分析[D].西安：西安建筑科技大学,2008.
[37]席文奎,杨兆建,梁群龙.多支承转子-轴承系统试验台动力学设计[J].太原理工大学学报,2007,38(5)：403-404.
[38]姚大坤,黄文虎,邹经湘.滑动轴承油膜刚度参数的识别[J].动力工程,2005,25(4):484-486.
[39]王龙洋.600MW亚临界机组轴系与单个转子临界转速的关系[J].机械工程师,2009, (4)：102-103.
[40]肖 黎,张咏梅.大型水轮机组瞬态动力时程响应分析[J].长江科学院院报,2008,25(1)：76-79.
[41]杨兆建,王勤贤,黄广龙.大型汽轮机轴承负荷传感器长期稳定性试验研究[J].仪表技术与传感器,2002(2)：46-47.
[42]庞新宇,杨兆建,梁群龙等.转子系统轴承载荷传感器动态特性分析[J].太原理工大学学报,2009,40(5)：461-464.
[43]路海燕.多维轴承载荷传感器结构优化设计[D].太原：太原理工大学,2008.
[44]李鹏飞.轴心轨迹识别及其在汽轮机组振动监测诊断中的应用[D].保定：华北电力大学,2007.
[45]Arun Kr.Jalan, A.R.Mohanty.Model based fault diagnosis of a rotor-bearing system for misalignment and unbalance under steady-state condition,Journal of Sound and Vibration,2009,327:604-622.
[46]K.P.Gertzos,P.G.Nikolakopoulos,A.CChasalevris,C.A.Papadopoulos.Wear identification in rotor-bearing systems by measurements of dynamic bearing characteristics,Computers and Structures,2010,120:635-640.
[2]郑凌云.机械振动中临界转速的工程意义及实践应用[J].机械研究与应用,2004,17(2)：19-21.
[3]Lund J W,Stability and Damped Critical Speeds of a Flexible Rotor in Fluid-Film Bearings,J,of Eng, For Industry, Trans, ASME,1974,95(2),509-517.
[4]Nandi, A.On computation of response of a rotor in deformed configuration using three dimensional finite elements[J].Communications in Numerical Methods in Engineering.2003: 179-195.
[5]陈双涛,侯予,陈汝刚等.高速透平膨胀机临界转速的计算与分析[J].西安交通大学学报,2010,44(9)：33-37.
[6]郑韬,田爱梅,王晓军.基于QZ算法的涡轮泵转子临界转速有限元计算[J].推进技术,2004,25(2)：114-117.
[7]柴山,刚宪约,姚福生.计算多转子系统临界转速的整体传递矩阵法[J].上海理工大学学报,2002,24(1)：8-12.
[8]王美令,陈果.转子系统临界转速计算方法[J].交通运输工程学报,2009,9(6):59-62.
[9]李玉峰,李德福,彭琴等.600MW汽轮发电机组转子-轴承系统的模态分析[J].汽轮机技术,2008,50(4)：244-246.
[10]李贞婷ANSYS模态分析在汽轮发电机转子临界转速计算上的应用[J].防爆电机,2009,44(3)：37-39.
[11]王海明,周 淼,王广庭等.华能阳逻电厂600MW机组轴系振动故障诊断及处理[J].湖北电力,2008,32(5)：38-40.
[12]Liu Jinyang. Study on the vibration of flexible rotor due to its initial bending and unbalance[J]. Journal of Vibration, Measurement & Diagnosis, v 1998:282-286.
[13]Ehrich, F.F.Some observation of chaotic vibration phenomena in high speed rotor dynamics [J]. American Society of Mechanical Engineers, Design Engineering Division (Publication) DE.1989:367-376.
[14]郑龙席,李晓丰.计算转子临界转速的两种方法及对比分析[J].风机技术,2009, 33(6)：35-38.
[15]Lee, C. W., and Joh, C. Y.,1994, "Development of the Use of the Directional Frequency Response Functions for the Diagnosis of Anisotropy and Asymme-try in Rotating Machinery: Theory," Mech. Syst. Signal Process.,86, pp.665-678.
[16]缪红燕,高金吉,徐鸿.转子系统瞬态不平衡响应的有限元分析[J].振动与冲击,2004,23(3)：1-4.
[17]郑龙席,李晓丰,秦卫阳.双盘转子系统各参数对转子瞬态响应影响的研究[J].机械科学与技术,2010,29(9)：1257-1267.
[18]袁小阳,朱均.大型汽轮发电机轴系稳定欲度研究[J].西安交通大学学报,1994,28(9)：51-57.
[19]Ishida, Yukio.Nonlinear vibrations and chaos in rotordynamics, JSME International Journal,SeriesC[J]Dynamics,Control,Robotics, Design and Manufacturing.1994:237-245.
[20]Lund J W. Stability and Damped Critical Speeds of a Flexible Rotor in Fluid-Film Bearings[J].American Society of Mechanical Engineers, Design Engineering Division (Publication) DE.1987:1-9.
[21]Nikolajsen J L.The Effect of Misalignment on Rotor Virations,Journal of Engineering Gas Turbines and Powe,1998,120(7):635-640.
[22]呼浩,陈焰.汽轮发电机组轴系稳定性诊断的研究[J].西北电力技术,2005,(1):36-39.
[23]田新启,高亹.二维PSD及其在轴系标高变化测试中的应用[J].传感器与微系统,2010,30(6)：638-641.
[24]杨兆建,丛红,谢友柏.大型汽轮发电机组四可倾瓦轴承负荷传感器的研究[J].机械科学与技术,1998,3(2)：247-249.
[25]杨兆建,谢友柏.大型汽轮发电机组轴承负荷在线监测方法[J].中国机械工程,1997,8(4)：89-91.
[26]施维新.机组振动故障诊断方法的研究[J].中国电力,1996,29(3):15-19.
[27]李录平.汽轮发电机组振动与处理[M].北京：中国电力出版社,2007.
[28]阮跃.国产200MW机组常见故障的诊断和预防[J].汽轮机技术,1997,39(4):200-205.
[29]成大先.轴及其联接[M].械设计手册,2004,32-35.
[30]唐锦茹.阶梯轴的自然频率和临界转速计算[J].起重运输机械,1996,(12):9-10.
[31 ]顾家柳等.转子动力学[M].北京：国防工业出版社,1985.
[32]周亚武.汽轮机转子有限元建模及动力学分析[D].武汉：华中科技大学,2009.
[33]钟一谔等,转子动力学[M],北京：清华大学出版社,1987:69-95.
[34]朱向哲.转子系统稳态和瞬态不平衡响应的有限元分析[J].石油化工设备技术,2007,28(2)：58-61.
[35]郝建山,韩磊,张智伟等.分布多质量转子系统的不平衡响应特征[J].机械设计与制造,2006(7)：34-36.
[36]孙红岩.利用有限元进行转子系统的动力学分析[D].西安：西安建筑科技大学,2008.
[37]席文奎,杨兆建,梁群龙.多支承转子-轴承系统试验台动力学设计[J].太原理工大学学报,2007,38(5)：403-404.
[38]姚大坤,黄文虎,邹经湘.滑动轴承油膜刚度参数的识别[J].动力工程,2005,25(4):484-486.
[39]王龙洋.600MW亚临界机组轴系与单个转子临界转速的关系[J].机械工程师,2009, (4)：102-103.
[40]肖 黎,张咏梅.大型水轮机组瞬态动力时程响应分析[J].长江科学院院报,2008,25(1)：76-79.
[41]杨兆建,王勤贤,黄广龙.大型汽轮机轴承负荷传感器长期稳定性试验研究[J].仪表技术与传感器,2002(2)：46-47.
[42]庞新宇,杨兆建,梁群龙等.转子系统轴承载荷传感器动态特性分析[J].太原理工大学学报,2009,40(5)：461-464.
[43]路海燕.多维轴承载荷传感器结构优化设计[D].太原：太原理工大学,2008.
[44]李鹏飞.轴心轨迹识别及其在汽轮机组振动监测诊断中的应用[D].保定：华北电力大学,2007.
[45]Arun Kr.Jalan, A.R.Mohanty.Model based fault diagnosis of a rotor-bearing system for misalignment and unbalance under steady-state condition,Journal of Sound and Vibration,2009,327:604-622.
[46]K.P.Gertzos,P.G.Nikolakopoulos,A.CChasalevris,C.A.Papadopoulos.Wear identification in rotor-bearing systems by measurements of dynamic bearing characteristics,Computers and Structures,2010,120:635-640.