大型辊式磨摇臂系统动力学分析研究
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摘要
辊式磨是一种高效的粉磨设备,广泛应用于水泥、化工等领域,它是利用料床粉磨的原理来进行粉磨物料。近年来,水泥生产需求增大,越来越多的大型辊式磨机应用于水泥生产中。而随着磨机的大型化,辊式磨的一些主要部件,如磨辊、摇臂、摆臂等的重量和尺寸都达到前所未有的程度,磨机振动引起的动载荷也相当大。磨机振动不仅会导致磨机停机,使磨机运转效率降低,收尘器的废气温度变化大,影响收尘效率以及废料增多,还会造成拉伸杆断裂和减速机、选粉机和风机等辅助设备的损坏。
立柱、摇臂、摆臂和磨辊等是辊式磨的主要部件之一,在物料粉磨的过程中受到的动载荷、冲击载荷作用。其结构动态特性对辊式磨的整机性能影响很大,因此对于机身摇臂系统这样的复杂结构,在设计中只对其进行传统的静力分析不能准确的反映系统结构内部的动态特性,还必须考虑其动态特性。
本文以某TRMΦ4000/1990型生料辊式磨(锥辊—平盘式、磨辊平均直径为1800mm)液压加压式摇臂系统为研究对象,通过分析其结构形式和振动情况,对其摇臂系统进行简化,建立动力学模型和系统运动微分方程并进行理论求解。然后利用有限元分析技术对摇臂系统进行模态分析,得到系统及主要部件的固有频率和主振型,两种方法的主要结果基本吻合。然后在此基础上进行谐响应分析,得到系统的共振频率范围及其它动态特征。
为了提高系统的动态性能和可靠性,计算得到的这些动态参数可作为理论分析中的模型修正和结构动力学修改的基本依据,根据结构动力修改准则,采用能量平衡法分析技术,对结构系统进行了动力学修改,提出三种结构修改方案并对修改后的结构系统进行分析。解决传统静态设计的不足,为使辊式磨具有更好的动态性能的优化及再设计提供参考依据。
Roller mill is a highly efficient grinding equipment which is widely used in cement, chemical industry. It based on the principle of material bed to grinding materials. In recent years, as the increased demand for cement production, a growing number of large roller mills are used in cement production. With the large scale mills, some major components of roller mill's weight and size have reached unprecedented levels, such as roller, rocker, etc. Mill’s vibration caused by the dynamic load is quite large, mill vibration will not only leading to mill shutdown, so that reduces the efficiency of mills operations, dust collector exhaust temperature changes, affecting the efficiency of dust collection and waste increase. At the same time, they will result in tensile fracture and gear lever, separator, fan and other auxiliary equipment damage.
Column, rocker, roller, etc. are ones of the main components of roller mill, in the process of grinding materials,they are affected by dynamic loads and impact loads. Their structural dynamic characteristics have great effects on the machine performances of roller mill. Therefore, for the complex structures as body rocker arm system, carried out only in the design of their traditional static analysis does not accurately reflect the internal dynamic characteristics of the structure, their dynamic properties must also be considered.
In this paper, take hydraulic pressure type of TRM, raw rocker roller mill body (Φ4000/1990 roller cone - flat disc, its average diameter is 1800mm.) as a study. The dynamic model and the differential equations of motion for the rocker arm system of TRM raw materials roller mill are established by analyzing its structure and vibration and of simplifying its arm system assumptions. Based on the dynamic model and the differential equations of motion as above, the modal analysis of the rocker arm system is done and the major components and its system’s natural frequencies and vibration mode are obtained. Two methods’results were generally consistent with the principal. Then the dynamic performance and the harmony response analysis are completed by means of finite element analysis, the resonance frequency range of system and other dynamic features are found.
In order to improve the dynamic performance and reliability, these dynamic parameters can be used as the fundamental basis of theoretical modified model and structural dynamic modifications. According to dynamic modification criteria, used the energy balance analysis, proposed three kinds of structural modifications to the program and the revised structure of the system are analyzed. Solved the shortage of traditional static design, all of these results are beneficial for optimized and re-design of the roller mill so that it has better dynamic performance.
立柱、摇臂、摆臂和磨辊等是辊式磨的主要部件之一,在物料粉磨的过程中受到的动载荷、冲击载荷作用。其结构动态特性对辊式磨的整机性能影响很大,因此对于机身摇臂系统这样的复杂结构,在设计中只对其进行传统的静力分析不能准确的反映系统结构内部的动态特性,还必须考虑其动态特性。
本文以某TRMΦ4000/1990型生料辊式磨(锥辊—平盘式、磨辊平均直径为1800mm)液压加压式摇臂系统为研究对象,通过分析其结构形式和振动情况,对其摇臂系统进行简化,建立动力学模型和系统运动微分方程并进行理论求解。然后利用有限元分析技术对摇臂系统进行模态分析,得到系统及主要部件的固有频率和主振型,两种方法的主要结果基本吻合。然后在此基础上进行谐响应分析,得到系统的共振频率范围及其它动态特征。
为了提高系统的动态性能和可靠性,计算得到的这些动态参数可作为理论分析中的模型修正和结构动力学修改的基本依据,根据结构动力修改准则,采用能量平衡法分析技术,对结构系统进行了动力学修改,提出三种结构修改方案并对修改后的结构系统进行分析。解决传统静态设计的不足,为使辊式磨具有更好的动态性能的优化及再设计提供参考依据。
Roller mill is a highly efficient grinding equipment which is widely used in cement, chemical industry. It based on the principle of material bed to grinding materials. In recent years, as the increased demand for cement production, a growing number of large roller mills are used in cement production. With the large scale mills, some major components of roller mill's weight and size have reached unprecedented levels, such as roller, rocker, etc. Mill’s vibration caused by the dynamic load is quite large, mill vibration will not only leading to mill shutdown, so that reduces the efficiency of mills operations, dust collector exhaust temperature changes, affecting the efficiency of dust collection and waste increase. At the same time, they will result in tensile fracture and gear lever, separator, fan and other auxiliary equipment damage.
Column, rocker, roller, etc. are ones of the main components of roller mill, in the process of grinding materials,they are affected by dynamic loads and impact loads. Their structural dynamic characteristics have great effects on the machine performances of roller mill. Therefore, for the complex structures as body rocker arm system, carried out only in the design of their traditional static analysis does not accurately reflect the internal dynamic characteristics of the structure, their dynamic properties must also be considered.
In this paper, take hydraulic pressure type of TRM, raw rocker roller mill body (Φ4000/1990 roller cone - flat disc, its average diameter is 1800mm.) as a study. The dynamic model and the differential equations of motion for the rocker arm system of TRM raw materials roller mill are established by analyzing its structure and vibration and of simplifying its arm system assumptions. Based on the dynamic model and the differential equations of motion as above, the modal analysis of the rocker arm system is done and the major components and its system’s natural frequencies and vibration mode are obtained. Two methods’results were generally consistent with the principal. Then the dynamic performance and the harmony response analysis are completed by means of finite element analysis, the resonance frequency range of system and other dynamic features are found.
In order to improve the dynamic performance and reliability, these dynamic parameters can be used as the fundamental basis of theoretical modified model and structural dynamic modifications. According to dynamic modification criteria, used the energy balance analysis, proposed three kinds of structural modifications to the program and the revised structure of the system are analyzed. Solved the shortage of traditional static design, all of these results are beneficial for optimized and re-design of the roller mill so that it has better dynamic performance.
引文
[1]刘建寿,赵红霞.水泥生产粉碎过程设备[M].武汉:武汉理工大学出版社,2005.
[2]王仲春.水泥工业粉磨工艺技术[M].北京:中国建材工业出版社,2000.
[3]李立华,徐靖,曹酒毓,等.KSVM型辊式磨开发应用有限元分析[J].中国水泥,2009,(10):73-74.
[4]王结富.MPS3150辊式磨在生料粉磨中的应用[J].水泥技术,1994,(06):22-26.
[5]彭猛,唐果宁.振动磨机碎磨动力学模型比较研究[J].湖南科技大学学报(自然科学版),2009,24(01):32-36.
[6]徐再贵.辊式磨在粉磨水泥、矿渣中存在的问题及对策[J].水泥装备,2001,(04):10-11.
[7]申占民.辊式磨在水泥工业中的发展及应用[J].水泥技术,2002,(04):56-59.
[8]梁颖涵.国内大型生料辊磨的应用现状和技术分析[J].水泥技术,2002,(01):31-33.
[9]张跟胜,丁千,陈予恕.轴向摩擦双盘转子的振动分析[J].机械强度,2009,31(5):712-718.
[10]杜平安.结构有限元分析建模方法,北京:机械工业出版社,1998.
[11]毕金龙,朱永彬.中速碾辊式磨煤机振动大的原因分析及消除措施[J].河北电力技术,2006,(08):27-28.
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[14]屈维德,唐恒龄.机械振动手册[M].北京:机械工业出版社,2000,4.
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[16] Schaefer. H.U. Loesche vertical roller mills for the comminution of ores and minerals[J]. Mineral Engineering, 2001, 14(10):1155-1160.
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[18]张海涛.某自动机械系统动力学分析研究[D].南京:南京理工大学硕士学位论文,2004.
[19]李文英.大型振动筛动力学分析及动态设计[D].太原:太原理工大学博士学位论文,2004.
[20] Fujita. K, Saito .T. Unstable vibration of roller mills [J]. Journal of Sound and Vibration, 2006,297(06):329-350.
[21]赵厚继,刘厚根,王宇奇,等.基于ANSYS机械增压器主动轴的动态特性分析[J].机械传动,2009,33(3):1-3
[22] Singiresu S.Rao. Mechanical Vibrations [M].Pezrson Education,Inc.,2004.
[23] Gao .H, Qu. L.G. 3D design and analysis of the crushing roller of a high-pressure grinding roller [J]. Journal of Materials Processing Technology, 2002,129(09): 649-652
[24]钱学毅,吴双.连杆动态应力有限元仿真分析[J].机械传动,2009,33(2):83-85.
[25]陈作炳,曾芳,范涛,等.Φ4. 6 m×15. 5 m滑履磨机有限元分析研究[J].武汉理工大学学报, 2007,29(8):139-142.
[26]程琛,马胜钢,李大磊.盘辊式磨粉机设计中核心技术问题的分析与研究[J].煤矿机械,2007,(08):65-67.
[27]刘鸿文.材料力学[M].北京:高等教育出版社,2004,1.
[28]高航,张耀满.基于UG的CAD/CAM技术,北京:清华大学出版社,2005.
[29]周建兴,岂兴明,矫津毅,等.MATLAB从入门到精通.北京:人民邮电出版社,2008.
[30]王建立.弹簧隔振汽机基础的动力学分析与应用[D].山东:山东大学硕士学位论文,2008.
[31]杨帅.非线性共振筛的动力学分析[D] .天津:天津大学硕士学位论文,2006.
[32]李献杰.门座起重机组合臂架系统强度和动力学分析[D].大连:大连交通大学硕士学位论文,2008.
[33] Leonard Meirovitch. Elements of vibration analysis [M].McGraw-Hill,1986.
[34] Eberhard Gock, Karl-Eugen Kurrer. Eccentric vibratory mills—theory and practice[J]. Powder Technology,1999,105(10):302-310.
[35]高士容.原料立磨振动跳停浅析[J].矿山机械,2008,(05):80-82.
[36] Meng Ling-qi. Vertical rolling mill's twist vibration[C]. Wuhan: Internationa. Conference on Computer Science and Software Engineering, 2008:1024-1027.
[37]博弈创作室.ANSYS9.0经典产品基础教程与实例详解[M].中国水利水电出版社,2006.
[38]王岩.基于ANSYS软件的疲劳试验机动力学分析[D].吉林:吉林大学硕士学位论文,2003
[39]王富耻,张朝晖.ANSYS10.0有限元分析理论与工程应用[M].电子工业出版社,2006.
[40] E.Villar-Cocin, E.Valencia-Morales, R.Gonzalez-Rodr?guez, Kinetics of the pozzolanic reaction between lime and sugar cane straw ash by electrical conductivity measurement: A kinetic–diffusive model[J]. Cement and Concrete Research, 2003,33(7):517-524.
[41] Dong-Woo Lee , Seok-Swoo Cho , Won-Sik Joo. Safety evaluation of table liner for vertical roller mill by modified fatigue limit[J]. Engineering Failure Analysis, 2008,15(4):989-999.
[42]邵忍平,何大为,黄欣娜.机械系统动力学[M].北京:机械工业出版社,2005,7.
[43]徐燕申.机械动态设计[M].北京:机械工业出版社,1992,11.
[2]王仲春.水泥工业粉磨工艺技术[M].北京:中国建材工业出版社,2000.
[3]李立华,徐靖,曹酒毓,等.KSVM型辊式磨开发应用有限元分析[J].中国水泥,2009,(10):73-74.
[4]王结富.MPS3150辊式磨在生料粉磨中的应用[J].水泥技术,1994,(06):22-26.
[5]彭猛,唐果宁.振动磨机碎磨动力学模型比较研究[J].湖南科技大学学报(自然科学版),2009,24(01):32-36.
[6]徐再贵.辊式磨在粉磨水泥、矿渣中存在的问题及对策[J].水泥装备,2001,(04):10-11.
[7]申占民.辊式磨在水泥工业中的发展及应用[J].水泥技术,2002,(04):56-59.
[8]梁颖涵.国内大型生料辊磨的应用现状和技术分析[J].水泥技术,2002,(01):31-33.
[9]张跟胜,丁千,陈予恕.轴向摩擦双盘转子的振动分析[J].机械强度,2009,31(5):712-718.
[10]杜平安.结构有限元分析建模方法,北京:机械工业出版社,1998.
[11]毕金龙,朱永彬.中速碾辊式磨煤机振动大的原因分析及消除措施[J].河北电力技术,2006,(08):27-28.
[12]徐业宜.机械系统动力学[M].北京:机械工业出版社,1990.
[13]丛家勇.直升机尾传动系统的动力学分析[D].南京:南京航空航天大学硕士学位论文,2008.
[14]屈维德,唐恒龄.机械振动手册[M].北京:机械工业出版社,2000,4.
[15]郭应龙.机械动力学[M].水利电力出版社,1994,6.
[16] Schaefer. H.U. Loesche vertical roller mills for the comminution of ores and minerals[J]. Mineral Engineering, 2001, 14(10):1155-1160.
[17]张策.机械动力学[M].北京:高等教育出版社,2000.4
[18]张海涛.某自动机械系统动力学分析研究[D].南京:南京理工大学硕士学位论文,2004.
[19]李文英.大型振动筛动力学分析及动态设计[D].太原:太原理工大学博士学位论文,2004.
[20] Fujita. K, Saito .T. Unstable vibration of roller mills [J]. Journal of Sound and Vibration, 2006,297(06):329-350.
[21]赵厚继,刘厚根,王宇奇,等.基于ANSYS机械增压器主动轴的动态特性分析[J].机械传动,2009,33(3):1-3
[22] Singiresu S.Rao. Mechanical Vibrations [M].Pezrson Education,Inc.,2004.
[23] Gao .H, Qu. L.G. 3D design and analysis of the crushing roller of a high-pressure grinding roller [J]. Journal of Materials Processing Technology, 2002,129(09): 649-652
[24]钱学毅,吴双.连杆动态应力有限元仿真分析[J].机械传动,2009,33(2):83-85.
[25]陈作炳,曾芳,范涛,等.Φ4. 6 m×15. 5 m滑履磨机有限元分析研究[J].武汉理工大学学报, 2007,29(8):139-142.
[26]程琛,马胜钢,李大磊.盘辊式磨粉机设计中核心技术问题的分析与研究[J].煤矿机械,2007,(08):65-67.
[27]刘鸿文.材料力学[M].北京:高等教育出版社,2004,1.
[28]高航,张耀满.基于UG的CAD/CAM技术,北京:清华大学出版社,2005.
[29]周建兴,岂兴明,矫津毅,等.MATLAB从入门到精通.北京:人民邮电出版社,2008.
[30]王建立.弹簧隔振汽机基础的动力学分析与应用[D].山东:山东大学硕士学位论文,2008.
[31]杨帅.非线性共振筛的动力学分析[D] .天津:天津大学硕士学位论文,2006.
[32]李献杰.门座起重机组合臂架系统强度和动力学分析[D].大连:大连交通大学硕士学位论文,2008.
[33] Leonard Meirovitch. Elements of vibration analysis [M].McGraw-Hill,1986.
[34] Eberhard Gock, Karl-Eugen Kurrer. Eccentric vibratory mills—theory and practice[J]. Powder Technology,1999,105(10):302-310.
[35]高士容.原料立磨振动跳停浅析[J].矿山机械,2008,(05):80-82.
[36] Meng Ling-qi. Vertical rolling mill's twist vibration[C]. Wuhan: Internationa. Conference on Computer Science and Software Engineering, 2008:1024-1027.
[37]博弈创作室.ANSYS9.0经典产品基础教程与实例详解[M].中国水利水电出版社,2006.
[38]王岩.基于ANSYS软件的疲劳试验机动力学分析[D].吉林:吉林大学硕士学位论文,2003
[39]王富耻,张朝晖.ANSYS10.0有限元分析理论与工程应用[M].电子工业出版社,2006.
[40] E.Villar-Cocin, E.Valencia-Morales, R.Gonzalez-Rodr?guez, Kinetics of the pozzolanic reaction between lime and sugar cane straw ash by electrical conductivity measurement: A kinetic–diffusive model[J]. Cement and Concrete Research, 2003,33(7):517-524.
[41] Dong-Woo Lee , Seok-Swoo Cho , Won-Sik Joo. Safety evaluation of table liner for vertical roller mill by modified fatigue limit[J]. Engineering Failure Analysis, 2008,15(4):989-999.
[42]邵忍平,何大为,黄欣娜.机械系统动力学[M].北京:机械工业出版社,2005,7.
[43]徐燕申.机械动态设计[M].北京:机械工业出版社,1992,11.