摘要
巨型液压机是重型机械制造业的重要设备,其本体根据工艺和级别设计成多种结构。我国300MN模锻水压机主框架是一个多约束系统。本文根据300MN模锻液压机状态监测与故障诊断系统力学机理研究要求,采用现代有限元CAE技术,依托良好的实验平台,展开300MN模锻水压机本体结构的力学行为分析。
采用Solid Works软件建立水压机本体三维模型——本次研究基础。选用ANSYS对比分析活动横梁不同模具、载荷的九个工况的力学行为——各组件应力应变大小和分布,变形规律等。通过测量靠模和加压模间距之差分析动梁的变形,验证计算的正确性。最终推导出动梁正载变形量公式和靠模模间距的变化规律。针对立柱应力检测保护系统的数据,在ANSYS中系统地计算机架立柱300MN正载工况和实验工况的应力应变大小和规律。1)轴向对比立柱应力轴向分布规律。对比测点分析值相对整个立柱长度的水平。2)平行对比比较八根立柱力学行为,判断应力较大的立柱。通过同工况检测数据验证分析正确性。
300MN模锻水压机是圆立柱导向。动梁水平方向偏移倾斜等非正常空间姿态造成机架结构超常附加损伤。本文以现场检测的各向最大偏移值和倾斜扭转角度为输入,应用ANSYS/LS-DYNA定量地计算其接触力学行为。模型简化保留导向结构和框架约束关系,建模设置接触对和施加偏移、倾斜扭转边界条件,修改接触和控制信息,提交LS-DYNA求解器计算。动梁偏移倾斜均引起较大应力和变形,加剧部件间运动干涉。实验研究利用立柱应力检测保护系统数据验证计算正确性。
Large-scale hydraulic press is a major equipment of heavy machinery manufacturing. The bulk of it is designed to a variety of structures according to the forging process. The main frame system of 300MN die forging hydraulic press is multi-constrained. Connected with mechanical mechanism research of giant hydraulic press fault diagnosis and early warning system, used modern advanced finite element analysis CAE technology, based on good experimental platform, mechanical behavior research of 300MN die forging hydraulic press is completed in this paper.
Three-dimensional models of 300MN die forging hydraulic press parts are established in Solid Works, as the base of the mechanical mechanism research. The mechanical behavior of the activity beam under nine conditions with different moulds and loads are analyzed contrastively in ANSYS. The level and distribution of stress-strain of the beam parts, and the level and regularity of deformation in loading direction are concluded. Experiments were done to obtain pressurized and non-pressurized die spacing differences measured, which is used to analyze the deformation of activity beam. According to the simulation and experimental results, an empirical formula about deformation of the beam under central load, and the rule of die spacing are given. The mechanical behavior of hydraulic press rack under extreme conditions of 300MN central load, and contrast condition are calculated using ANSYS, against the stress testing and protecting system of column.1) Axial contrast, the axial variation of every column is calculated. The analysis stress of testing point and the length of column are contrasted.2) Parallel comparison, the column with larger stress is determined through the comparison of all eight columns. The accuracy of analysis is verified by test data under the same conditions.
300MN die hydraulic press is oriented by round column. Additional damage of rack and oriented structure is caused by non-normal space posture of activities beam. Additional contact mechanical behavior is calculated quantitatively in ANSYS/LS-DYNA, using the offset data and tilt angle measured. The oriented architecture and constraint relationship of framework are maintained in model simplification. FEM is established selecting steel and elastic rubber materials related to components, setting loading, offset and tilt boundary conditions and contact pairs. Information of contact and control is amend in key word and then submitted to calculate in LS-DYNA solver. The result of calculate shows the offset and tilt of activities beam cause large stress and deformation, aggravating the movement interference of parts. The correctness of analysis is verified directly and indirectly by stress testing and protecting system.
引文
[1]俞新陆.液压机[M].北京：机械工业出版社,1982：22-23
[2]朱钒,张志,张道富.国内外液压机技术现状及发展趋势[J].机床与液压,2000,1：6-8
[3]潘凤文,焦敬品,林道盛,等.液压机本体CAD的现状及发展[J].锻压机械,2000,35(2)：39-41
[4]三机部三〇一所.国外大型模锻水压机和航空大锻件概况.1974.6
[5]梁米,谭建平,陈晖.300MN水压机活动横梁的变形规律[J].机械设计与研究.2010,26(1)：108-110
[6]潘紫微,邵韦循,王彪等.80MN水压机下梁有限元分析[J].安微工业大学学报,2005,22(2)：145-146
[7]第一机械工业部重型机械研究所.国内外重型锻压设备图册.1964
[8]S. A. Losev. Study of thousand-ton hydraulic press designed by UZTM[J]. Refractories and Industrial Ceramics,1962,3(3):102-104
[9]俞新陆.液压机的设计与应用[M].北京：机械工业出版社,2006
[10]北京重机厂.锻造液压机本体结构发展述评[J].重型机械,1982,3
[11](苏)A.φ.别洛夫等著.水压机模锻(靳辅安等译)[M].北京：国防工业出版社,1981
[12]吴生富.150MN锻造液压机本体组合结构研究[D].河北：燕山大学,2006
[13]吴生富,金淼,聂绍珉.大型锻造液压机全预紧机架的整体性分析[J].燕山大学学报,2006,30(2)：143-146
[14]韩伦.60MN锻造水压机本体关键件结构分析[D].河北：燕山大学,2006
[15]段智勇.巨型模锻液压机整体结构功能评估与优化设计[D].长沙：中南大学,2008
[16]颜永年.预应力钢丝缠绕机架立柱刚度的研究[J].清华大学科学学报,1980
[17]田会然.800MN多向模锻液压机本体结构设计及分析[D].河北：燕山大学,2005
[18]陈胜涛.闭式框架机身压力机的滑块导向机构[J].锻压机械,1992,(1)：10-16
[19]林道盛,杨雨甡,曹桂荣等.锻压机械及其有限元计算[M].北京：北京工业大学出版社,1998,12
[20]曹兴强,黄明辉,湛利华等.大型模锻液压机活动横梁整体工作性能有限元分析[J].现代制造工程,2009(5)：101-105
[21]K. H. Hnebner. The Finite Element Method for Engineers [M], Second Edition. 1982
[22]K.J.Bathe. Numericalmethods in Finite Element Analysis [M].Prentice-hall, Inc, 1976:35-36
[23]Kobayashi S, Oh S I, Altan T. Metal Forming and the Finite-Element Method [M].Oxford:Oxford University Press,1989:55-70
[24]O.C.Zienkiewicz. The Finite Element Method [M]. London:McGraw-Hill, 1977:13-24
[25]Msc.Software.MSC.Marc2005 (Volume A):Theory and User Information. [M] MSC.Software.2005
[26]龚曙光.Ansys基础应用及范例解析[M].北京：机械工业出版社,2003
[27]ANSYS, Inc. ANSYS Structural Analysis Guide Release 5.4[M]. Third Edition. SAS, IP Inc,1997:2-3
[28]余伟炜,高炳军.ANSYS在机械与化工装备中的应用[M].中国水利水电出版社,2007
[29]龚曙光.ANSYS工程应用实例解析[M].北京：机械工业出版社,2003：185-187
[30]美国ANSYS公司北京办事处.ANSYS/LS - DYNA培训手册.北京,2000
[31]Ogi Y, Nakai Y. Practical use of finite element method "structural analysis" and its perspective. Sanken Technical Report [J],2001,33 (1):94-99.
[32]Koc, Muammer; Altan, Taylan. Application of two dimensional (2D) FEA for the tube hydroforming process[J]. International Journal of Machine Tools and Manufacture,2002,42(11):1285-1295
[33]Ghofrani, M.Reza, White, Charles S. Modeling of a precision closed-die forging [J]. American Society of Mechanical Engineers.1996,8
[34]Chenot, Tronel, Soyris. Finite element calculation of thermo-coupled large deformation in hot forging[J]. Conduction, Radiation and Phase Change. 1992:493-511
[35]Gontarz, A.; Weronski, W.S.; Pater, Z. The research of forging process of eccentric part on three slide forging press [J]. Journal of Materials Processing Technology,2006,177(3),214-17
[36]Zhang, Cunhui. Finite element modeling of the frame structure of a 300 MN hydraulic forging press [J]. American Society of Mechanical Engineers,1994,295: 127-131
[37]沈会.多点成形压力机动态特性研究[D].吉林：吉林大学,2006
[38]尹云,孙彩丽,郭康等.50MN锻造水压机整体机架有限元分析[J].计算机应 用,2008,2：88-89
[39]赵希禄,聂绍珉,刘建民等.预紧组合式压力机机身的结构优化设计[J].锻压设备,1994,(1)：48-52；
[40]杨建民.120MN锻造液压机本体整体性研究[D].河北：燕山大学,2007
[41]何强,张大可,赵万军.法兰支承液压缸的应力计算及讨论[J].机械,2007(3)：15-17
[42]刘广君,贾延.4MN液压镦锻机机架有限元模态分析[J].煤矿机械,2008,29(5)：72-75
[43]侯晓望,童水光.基于有限元分析的液压机结构优化[J].重型机械,2005(4)：46-49
[44]李志波,董国疆,吴树亮等.12.5MN双柱快锻液压机机架的有限元分析[J].锻压技术,2008,33(4)：100-104
[45]李范坤,钟掘.300MN模锻水压机侧推力研究[J].中国有色金属学报,1995,5(3)：134-137
[46]张立华.300MN水压机垫板组力学行为研究[J].机械强度,2000,22(2)：113-116.
[47]彭伟波.巨型模锻液压机典型组合结构的承载与变形特性分析[D].长沙：中南大学,2008
[48]王亚军.大型组合承载结构整体建模及八万吨压机主机架结构分析与优化设计[D].长沙：中南大学,2008
[49]Pei, L. Finite element modeling of sliding contact between rough surfaces. Proceedings of the World Tribology Congress Ⅲ-2005,2005:315-316
[50]许耀昌.CAD/CAM基础[M].北京：电子工业出版社,1995：10-13
[51]刘实.新编金属材料实用手册[M].香港：中国科技文化出版社,2007.3
[52]尚晓江,苏建宇,王化锋.ANSYS/LS-DYNA动力分析方向与工程实例[M].北京：中国水利水电出版社,2008
[53]何涛,杨竞,金鑫.ANSYS10.0/LS-DYNA有限元分析实例指导教程[M].北京：机械工业出版社,2007
[54]John O. Hallquist, LS-DYNA THEORETICAL MANUAL, Livermore Software Technology Corporation,1998
[55]Hild, Patrick, Quadratic finite element methods for unilateral contact problems [J]. Applied Numerical Mathematics,2002,41(3):401-421
[56]Wriggers, P. Finite element methods for contact problems with friction [J], Tribology International,1996,29(8):651-658
[57]Asano, Kazuhiro, A method of finite element analysis for elastic contact problem with sliding, Nihon Kikai Gakkai Ronbunshu, A Hen/Transactions of the Japan Society of Mechanical Engineers, Part A,2006,72(5):616-623
[58]周俊峰,谭建平.300MN模锻水压机活动横梁同步检测系统设计[J].机械与电子,2004,(8)：51-53.
[59]LSTC. LS-DYNA KEYWORD USER'S MANUAL. Version 971. Livermore Software Technology Corporation,2007
[60]陈晖,谭建平等.巨型模锻水压机立柱应力检测系统方案研究[J].锻压技术,2009,34(3)：113、116