液体动静压轴承承载特性的分析与实验研究
|
摘要
现代工业的发展对高速重载和稳定性提出了越来越高的要求,动静压轴承也因其特有的性能得到了越来越广泛的应用。动静压轴承综合了静压轴承和动压轴承的优点,即在低速和高速时都具有较好的承载能力和动态性能,有较宽的速度范围和无摩擦工作区域,较高的位置精度和旋转精度,有较好的稳定性等一系列优点。它在结构上同时实现了两种轴承的功效,相互弥补不足。在工业领域特别是精密机床行业具有广阔的应用前景。
本文首先介绍了动静压轴承的理论知识和计算流体力学的数值理论,然后对动静压轴承节流器的工作原理和结构性能进行数值分析,以此为基础,着重分析了动静压轴承承载性能与各参数之间的关系,对结构参数、润滑介质以及节流器的各参数对动静压轴承承载特性的影响做了深入的分析。
其次,在动静压轴承特性分析上主要从轴承结构和节流器结构入手,以计算流体力学理论为基础,以四油腔对置浅腔动静压轴承为主要研究对象,并以FLUENT6.3为工具,主要研究了节流器结构、轴承供油压力、主轴转速、宽径比、偏心率等参数对轴承油膜的承载特性、压力分布、偏位角、油膜刚度等相关参数的影响。
通过对比不同参数下得出的汕膜承载特性曲线,提出相应的提高油膜承载能力的措施,提高了数值模拟在动静滑动轴承设计计算中的可靠性,为全而研究油膜轴承的动静态特性和润滑介质的流动情况提供了有效的手段。
The development of modern industry put forward more and more high demand of stability and high-speed overloaded, The Hybrid Bearing has been applied more and more because of the special performance. The Hybrid Bearing composite of the dynamic pressure bearing and hydrostatic bearing's advantages, which is good carrying capacity and the nice dynamic performance in both the low speed and high speed, have a wide range of speed and no friction work area, have high position precision and rotation precision, and has better stability and so on. The structure of the Hybrid Bearings obtains the effect of two bearings, Supplement each other. The Hybrid Bearing has wide application prospects in industry field especially precision machine tool industry field.
At the beginning, this paper introduced the Hybrid Bearing's theoretical knowledge and numerical theory of computational fluid dynamics, and then made numerically analysis of the work principle and the structure performance of the hybrid bearing throttling, based on above, this paper focusing on the analysis of the relationship between the hybrid bearing's properties and the parameters, made further analysis of the influence that structure parameters, the throttle and the lubrication neurogen on the hybrid bearing's load carrying characteristics.
Secondly, after the analysis on the characteristics of Hybrid Bearing, we starting with the main operating parameters of hybrid bearings, based on CFD, take the four-chamber hybrid bearings as the research object, take FLUENT6.3as tools, the study focuses on the effect of throttling structure, oil supply pressure, spindle speed, eccentricity and width diameter ratio of bearings on bearing capacity character, oil pressure distribution, attitude angle, oil film stiffness and other related parameters.
By comparing and analyzing the oil film bearing capacity character under the different input parameters, the improve oil film bearing capacity measures are proposed to increase reliability of numerical simulation in calculation of the design of hybrid sliding bearings, and provide an effective means to the comprehensive study of static and dynamic characteristics of oil film bearings and lubrication flow of media.
本文首先介绍了动静压轴承的理论知识和计算流体力学的数值理论,然后对动静压轴承节流器的工作原理和结构性能进行数值分析,以此为基础,着重分析了动静压轴承承载性能与各参数之间的关系,对结构参数、润滑介质以及节流器的各参数对动静压轴承承载特性的影响做了深入的分析。
其次,在动静压轴承特性分析上主要从轴承结构和节流器结构入手,以计算流体力学理论为基础,以四油腔对置浅腔动静压轴承为主要研究对象,并以FLUENT6.3为工具,主要研究了节流器结构、轴承供油压力、主轴转速、宽径比、偏心率等参数对轴承油膜的承载特性、压力分布、偏位角、油膜刚度等相关参数的影响。
通过对比不同参数下得出的汕膜承载特性曲线,提出相应的提高油膜承载能力的措施,提高了数值模拟在动静滑动轴承设计计算中的可靠性,为全而研究油膜轴承的动静态特性和润滑介质的流动情况提供了有效的手段。
The development of modern industry put forward more and more high demand of stability and high-speed overloaded, The Hybrid Bearing has been applied more and more because of the special performance. The Hybrid Bearing composite of the dynamic pressure bearing and hydrostatic bearing's advantages, which is good carrying capacity and the nice dynamic performance in both the low speed and high speed, have a wide range of speed and no friction work area, have high position precision and rotation precision, and has better stability and so on. The structure of the Hybrid Bearings obtains the effect of two bearings, Supplement each other. The Hybrid Bearing has wide application prospects in industry field especially precision machine tool industry field.
At the beginning, this paper introduced the Hybrid Bearing's theoretical knowledge and numerical theory of computational fluid dynamics, and then made numerically analysis of the work principle and the structure performance of the hybrid bearing throttling, based on above, this paper focusing on the analysis of the relationship between the hybrid bearing's properties and the parameters, made further analysis of the influence that structure parameters, the throttle and the lubrication neurogen on the hybrid bearing's load carrying characteristics.
Secondly, after the analysis on the characteristics of Hybrid Bearing, we starting with the main operating parameters of hybrid bearings, based on CFD, take the four-chamber hybrid bearings as the research object, take FLUENT6.3as tools, the study focuses on the effect of throttling structure, oil supply pressure, spindle speed, eccentricity and width diameter ratio of bearings on bearing capacity character, oil pressure distribution, attitude angle, oil film stiffness and other related parameters.
By comparing and analyzing the oil film bearing capacity character under the different input parameters, the improve oil film bearing capacity measures are proposed to increase reliability of numerical simulation in calculation of the design of hybrid sliding bearings, and provide an effective means to the comprehensive study of static and dynamic characteristics of oil film bearings and lubrication flow of media.
引文
[1]张直明,张言羊,谢友柏等,滑动轴承的流体动力润滑理论[M],北京：高等教育出版社,1986
[2]郭力,刘建宁,盛晓敏,高速加工机床及关键技术的新进展[J],机械加工与自动化,2001年第3期
[3]张伯霖,超高速切削的关键技术[J],机床,1993,(11)：3-6
[4]郭新贵,李从心,高速切削技术的研究与应用[J],模具技术,2001 No.5
[5]徐灏,邱宣怀等,机械设计手册.第4卷.北京：机械工业出版社,1992
[6]邱宣怀.机械设计(第三版).北京：高等教育出版社,1991.
[7]陈燕生.液体静压支承原理和设计[M].国防工业出版社.
[8]伍良生等.大型汽轮发电机组转子系统轴承安装位置的优化.华中理工大学报.1993(1).
[9]路甫样.中国制造科技的现状与发展.中国科学基金,2006(5)
[10]L.Costa, M. Fillon, A.S.Miranda, J.C.P.Clam. An Experimental Investigation of the Effect of Groove Location and Supply Pressure on the THD Performance of a Steadily Loaded Journal Bearing. Journal of Tribology,2000(122):162-168.
[11]丁振乾.我国机床液体静压技术的发展历史及现况[J].精密制造与自动化.2003(3)
[12]武弘毅.浅谈液体动静压轴承.机械工人(冷加工).2003(5)：8-10.
[13]杨沛然.流体润滑数值分析[M].国防工业出版社.1998.10
[14]钟洪,张冠坤.液体静压动静压轴承设计使用手册[M].电子工业出版社,2007.
[15]林成森.数值分析[M].科学出版社.2006：50-55.
[16]杨金福,刘占生,解永波,于达仁.关于Reynolds方程求解的动态边界条件研究.哈尔滨工业大学,2004,10.
[17]De Kraker. Alex, Van Ostayen,Ron A J, Rixen, Daniel J,Calculation of Stribeck Curves for (water) Lubrication Journal Bearings[J].Tribology International. Vol.40, no.3, pp459-469. Mar.2007
[18]Majumdar,B-C.; Pai,R.; Hargreaves, D.J. Analysis of water-lubricated journal bearings with multiple axial grooves[J].Proceedings of the institution of Mechanical Engineers J,Jounral of Engineering Tribology.Vol.218,no J2,pp.135-146.A pr.2004
[19]张也影,流体力学LM1,北京：高等教育出版社,2000
[20]王锐昌,黄秋波,段志达,用有限元方法计算新型可逆式动压推力轴承的温度场[J],重型机械,2002,(6)：38-41
[21]PinkusO.Thermal Aspects of Fluid Film Tribology[R].ASME Press.NewYork,1990:506
[22]MonmousseauP, FillonM FreneJ. Transient Thermo elasto-hydrodynamic Study of Tilting-Pad Journal Bearings-Comparison between Experimental Data and Theoretical Results[J].journal of Tirbology,1997,119:401-407.
[23]章本照,流体力学中的有限元法[M],北京：机械工业出版社,1986
[24]蒋立军,俞炳丰,孟祥兆,高强,朱均,推力轴承热稳定性非线性分析及周期稳态解的全局特性研究[J],摩擦学学报,第22卷第5期
[25]富彦丽,径向滑动轴承瞬态热弹性流体动力润滑性能的研究[D],西安：西安交通 大学,2003：100-112
[26]逢春伟,新型内反馈节流动静压轴承性能及应用研究[D],北京：北京航空航天大学,2006
[27]许尚贤.液体静压和动静压滑动轴承设计[M].南京.东南大学出版社.1989.5
[28]丁振乾.流体静压支承设计[M].上海.上海科学技术出版社.1989.4
[29]庄礼贤等.流体力学[M].合肥.中国科学技术大学出版社.1991：101-102.
[30]张元林.工程数学[M].高等教育出版社.2004.
[31]沃斯克列辛斯基.滑动轴承设计和计算[M].国防工业出版社.1986：56-56.
[32]周春良.刘占生.刘顺隆.船舶娓管轴承润滑流场数值分析,润滑与密封.2006(11)：39-43.
[33]秦平,沈钱,徐华,朱均,考虑进油压力的滑动轴承非线性液膜力数据库[J],摩擦学学报,第24卷第3期
[34]杨建玺,樊红朝,曲廷敏,刘巧方,液膜袖承的承载性能分析与比较[Jl,轴承2004年第8期
[35]Ikeda, Kazunori; Hirano,Toshio;Yamashita,Tatsuo;Mikami,Makoto;Sakakida Hitoshi. An experimental study of static and dynamic characteristics of a 580mm(22.8in.) diameter direct lubrication tilting pad journal bearing [J].Jounral of Tribology v128,n1,January,2006,pl 46-154
[36]邹茜,孟永钢,温诗铸等.流体动压轴承主轴系统的动态特性实验研究[J],摩擦学学报,2002,22(3)
[37]S.X.Zhao,X.D.Dai,G.Meng and J.Zhu. An experimental study of nonlinear oil-film forces of a journal bearing[J]. Journal of Sound and Vibration, Volume 287,Issues4-5,4November2005,Pages827-843
[38]Castelli V.Shapiro W. Improved Method for Numerical Solution of the General Incompressible Fluid Film Lubrication Problem[J],ASME. Journal of Lubrication Technology 1967,8,71-79.Yoshikawa H, Ota T, Higashino K, Numerical Analysis on.
[39]蒋小文.顾伯勤.收敛楔形间隙中流体流动的数值模拟[J].润滑与密封2004(3)：47-49.
[40]叶荣学.孙伟.张敏全.油膜刚度变化对转子振动特性的影响[J],汽轮机技术,2006(4)：114～115.
[41]陈志澜.巨型推力轴承的三维热弹流动力润滑性能研究[D].西安：西安交通大学.1998.
[42]F.T Barwell著.西安交通大学机械原理与机械零件教研室译,轴承系统一理论与实践[M],机械工业出版社.
[43]徐海洋.曹清香.易勇.水润滑轴承的研究现状及进展[J].机械加工工艺与装备.2003(3)：39-43.
[44]PYP Chen. E J Hahn. Use of Computational Fluid Dynamics in Hydrodynamic Lubrication [C].Proc Instn Mech Engr 1998.212.427-435.
[45]朱明道.油膜厚度与滑动轴承精度的讨论[J].上海电力学院学报.1998.9.25-29.
[46]陈伯贤.裘祖干.张慧生.流体润滑理论及其应用[M].北京：机械工业出版社,1991.
[47]陈云飞.许尚贤.浅液腔动静压轴承动特性分析[J].机械设计1994.4：30-32.
[48]袁惠群.吴英祥.李东.滑动轴转子-定子系统祸合故障的非线性动力学特性[J].东北大学学报(自然科学版).第27卷第5期.
[49]San Andes L. Analysis of turbulent hydrostatic bearings with a barotropic cryogenic fluid cryogenic [J]. Journal of Tribology.1992,114 (4):755-765.
[50]FLUENT Inc. FLUENT User's Guide. Fluent Inc.2003.
[51]Fluent Inc. GAMBIT User Defined Function Manual. Fluent Inc.2003.
[52]钟英杰.都晋燕.张雪梅.CFD技术及在现代工业中的应用[J].浙江工业大学学报.2003(6)：284-289.
[53]赵镇南.传热学[M].北京：高等教育出版社.2008.
[54]帕坦卡.传热与流体流动的数值计算[M].北京：科技出版社.1984.
[55]胡伟.动静压混合轴承温度场的理论和实验研究[D].北京航空航天大学.1988.
[56]机械工程手册,第22篇,第6章.润滑材料.机械工业出版社.1978.
[57]D.Dowson:A Generalized Reynolds Equation for Fluid-Film Lubrication, Int.J. mech. sci., Vol.4,1962, p.159-160.
[58]李庆扬.王能超.易大义.数值分析.武汉：华中工学院出版社.1982.
[59]Phan-Thien N.On the Effects of the Reynolds and stokes surface Roughnesses in a Two-Dimensional Slider Bearing [J].Proc R Soc London serA,1981,37,349-362.
[60]朱均.虞烈.流体润滑理论[Z].西安：西安交通大学润滑理论及轴承研究所.
[61]Odyck van DEA. Stockes Flow in Thin Films [J].Ph D thesis University of Twente,The Nedrerland 2001.10:265-276.
[62]Ms Petra Brajdic-Mitideri. Project Advance Modeling of Elasto hydrodynamics Lubrication [OL] SKF Engineering & Research Center B.V.1998.9:153-158.
[63]Noordmans J. Solutions of Highly Anisotropic Stokes Equations for Lubrication Problems [J].ECCOMAS 1996.5:49-53.
[64]周春良.刘顺隆.郑洪涛.船舶舰管轴承内部流场数值分析.船舶工程.2006(3)：26-29.
[65]周春良.袁士勤.刘顺隆.郑洪涛.穆勇.轴向槽船舶舰管轴承内部流场数值仿真.润滑与密封.2006.
[66]QR朗格.斯泰因希尔伯编著.王成熹.曹永上译.滑动轴承.北京：机械工业出版社,1986.
[2]郭力,刘建宁,盛晓敏,高速加工机床及关键技术的新进展[J],机械加工与自动化,2001年第3期
[3]张伯霖,超高速切削的关键技术[J],机床,1993,(11)：3-6
[4]郭新贵,李从心,高速切削技术的研究与应用[J],模具技术,2001 No.5
[5]徐灏,邱宣怀等,机械设计手册.第4卷.北京：机械工业出版社,1992
[6]邱宣怀.机械设计(第三版).北京：高等教育出版社,1991.
[7]陈燕生.液体静压支承原理和设计[M].国防工业出版社.
[8]伍良生等.大型汽轮发电机组转子系统轴承安装位置的优化.华中理工大学报.1993(1).
[9]路甫样.中国制造科技的现状与发展.中国科学基金,2006(5)
[10]L.Costa, M. Fillon, A.S.Miranda, J.C.P.Clam. An Experimental Investigation of the Effect of Groove Location and Supply Pressure on the THD Performance of a Steadily Loaded Journal Bearing. Journal of Tribology,2000(122):162-168.
[11]丁振乾.我国机床液体静压技术的发展历史及现况[J].精密制造与自动化.2003(3)
[12]武弘毅.浅谈液体动静压轴承.机械工人(冷加工).2003(5)：8-10.
[13]杨沛然.流体润滑数值分析[M].国防工业出版社.1998.10
[14]钟洪,张冠坤.液体静压动静压轴承设计使用手册[M].电子工业出版社,2007.
[15]林成森.数值分析[M].科学出版社.2006：50-55.
[16]杨金福,刘占生,解永波,于达仁.关于Reynolds方程求解的动态边界条件研究.哈尔滨工业大学,2004,10.
[17]De Kraker. Alex, Van Ostayen,Ron A J, Rixen, Daniel J,Calculation of Stribeck Curves for (water) Lubrication Journal Bearings[J].Tribology International. Vol.40, no.3, pp459-469. Mar.2007
[18]Majumdar,B-C.; Pai,R.; Hargreaves, D.J. Analysis of water-lubricated journal bearings with multiple axial grooves[J].Proceedings of the institution of Mechanical Engineers J,Jounral of Engineering Tribology.Vol.218,no J2,pp.135-146.A pr.2004
[19]张也影,流体力学LM1,北京：高等教育出版社,2000
[20]王锐昌,黄秋波,段志达,用有限元方法计算新型可逆式动压推力轴承的温度场[J],重型机械,2002,(6)：38-41
[21]PinkusO.Thermal Aspects of Fluid Film Tribology[R].ASME Press.NewYork,1990:506
[22]MonmousseauP, FillonM FreneJ. Transient Thermo elasto-hydrodynamic Study of Tilting-Pad Journal Bearings-Comparison between Experimental Data and Theoretical Results[J].journal of Tirbology,1997,119:401-407.
[23]章本照,流体力学中的有限元法[M],北京：机械工业出版社,1986
[24]蒋立军,俞炳丰,孟祥兆,高强,朱均,推力轴承热稳定性非线性分析及周期稳态解的全局特性研究[J],摩擦学学报,第22卷第5期
[25]富彦丽,径向滑动轴承瞬态热弹性流体动力润滑性能的研究[D],西安：西安交通 大学,2003：100-112
[26]逢春伟,新型内反馈节流动静压轴承性能及应用研究[D],北京：北京航空航天大学,2006
[27]许尚贤.液体静压和动静压滑动轴承设计[M].南京.东南大学出版社.1989.5
[28]丁振乾.流体静压支承设计[M].上海.上海科学技术出版社.1989.4
[29]庄礼贤等.流体力学[M].合肥.中国科学技术大学出版社.1991：101-102.
[30]张元林.工程数学[M].高等教育出版社.2004.
[31]沃斯克列辛斯基.滑动轴承设计和计算[M].国防工业出版社.1986：56-56.
[32]周春良.刘占生.刘顺隆.船舶娓管轴承润滑流场数值分析,润滑与密封.2006(11)：39-43.
[33]秦平,沈钱,徐华,朱均,考虑进油压力的滑动轴承非线性液膜力数据库[J],摩擦学学报,第24卷第3期
[34]杨建玺,樊红朝,曲廷敏,刘巧方,液膜袖承的承载性能分析与比较[Jl,轴承2004年第8期
[35]Ikeda, Kazunori; Hirano,Toshio;Yamashita,Tatsuo;Mikami,Makoto;Sakakida Hitoshi. An experimental study of static and dynamic characteristics of a 580mm(22.8in.) diameter direct lubrication tilting pad journal bearing [J].Jounral of Tribology v128,n1,January,2006,pl 46-154
[36]邹茜,孟永钢,温诗铸等.流体动压轴承主轴系统的动态特性实验研究[J],摩擦学学报,2002,22(3)
[37]S.X.Zhao,X.D.Dai,G.Meng and J.Zhu. An experimental study of nonlinear oil-film forces of a journal bearing[J]. Journal of Sound and Vibration, Volume 287,Issues4-5,4November2005,Pages827-843
[38]Castelli V.Shapiro W. Improved Method for Numerical Solution of the General Incompressible Fluid Film Lubrication Problem[J],ASME. Journal of Lubrication Technology 1967,8,71-79.Yoshikawa H, Ota T, Higashino K, Numerical Analysis on.
[39]蒋小文.顾伯勤.收敛楔形间隙中流体流动的数值模拟[J].润滑与密封2004(3)：47-49.
[40]叶荣学.孙伟.张敏全.油膜刚度变化对转子振动特性的影响[J],汽轮机技术,2006(4)：114～115.
[41]陈志澜.巨型推力轴承的三维热弹流动力润滑性能研究[D].西安：西安交通大学.1998.
[42]F.T Barwell著.西安交通大学机械原理与机械零件教研室译,轴承系统一理论与实践[M],机械工业出版社.
[43]徐海洋.曹清香.易勇.水润滑轴承的研究现状及进展[J].机械加工工艺与装备.2003(3)：39-43.
[44]PYP Chen. E J Hahn. Use of Computational Fluid Dynamics in Hydrodynamic Lubrication [C].Proc Instn Mech Engr 1998.212.427-435.
[45]朱明道.油膜厚度与滑动轴承精度的讨论[J].上海电力学院学报.1998.9.25-29.
[46]陈伯贤.裘祖干.张慧生.流体润滑理论及其应用[M].北京：机械工业出版社,1991.
[47]陈云飞.许尚贤.浅液腔动静压轴承动特性分析[J].机械设计1994.4：30-32.
[48]袁惠群.吴英祥.李东.滑动轴转子-定子系统祸合故障的非线性动力学特性[J].东北大学学报(自然科学版).第27卷第5期.
[49]San Andes L. Analysis of turbulent hydrostatic bearings with a barotropic cryogenic fluid cryogenic [J]. Journal of Tribology.1992,114 (4):755-765.
[50]FLUENT Inc. FLUENT User's Guide. Fluent Inc.2003.
[51]Fluent Inc. GAMBIT User Defined Function Manual. Fluent Inc.2003.
[52]钟英杰.都晋燕.张雪梅.CFD技术及在现代工业中的应用[J].浙江工业大学学报.2003(6)：284-289.
[53]赵镇南.传热学[M].北京：高等教育出版社.2008.
[54]帕坦卡.传热与流体流动的数值计算[M].北京：科技出版社.1984.
[55]胡伟.动静压混合轴承温度场的理论和实验研究[D].北京航空航天大学.1988.
[56]机械工程手册,第22篇,第6章.润滑材料.机械工业出版社.1978.
[57]D.Dowson:A Generalized Reynolds Equation for Fluid-Film Lubrication, Int.J. mech. sci., Vol.4,1962, p.159-160.
[58]李庆扬.王能超.易大义.数值分析.武汉：华中工学院出版社.1982.
[59]Phan-Thien N.On the Effects of the Reynolds and stokes surface Roughnesses in a Two-Dimensional Slider Bearing [J].Proc R Soc London serA,1981,37,349-362.
[60]朱均.虞烈.流体润滑理论[Z].西安：西安交通大学润滑理论及轴承研究所.
[61]Odyck van DEA. Stockes Flow in Thin Films [J].Ph D thesis University of Twente,The Nedrerland 2001.10:265-276.
[62]Ms Petra Brajdic-Mitideri. Project Advance Modeling of Elasto hydrodynamics Lubrication [OL] SKF Engineering & Research Center B.V.1998.9:153-158.
[63]Noordmans J. Solutions of Highly Anisotropic Stokes Equations for Lubrication Problems [J].ECCOMAS 1996.5:49-53.
[64]周春良.刘顺隆.郑洪涛.船舶舰管轴承内部流场数值分析.船舶工程.2006(3)：26-29.
[65]周春良.袁士勤.刘顺隆.郑洪涛.穆勇.轴向槽船舶舰管轴承内部流场数值仿真.润滑与密封.2006.
[66]QR朗格.斯泰因希尔伯编著.王成熹.曹永上译.滑动轴承.北京：机械工业出版社,1986.