2800热粗轧机主传动系统改造方案研究
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摘要
2800粗轧机是我国上个世纪自行设计、制造的轧制设备,是某厂的大型关键设备。近年来随着轧制负荷增大,主传动系统在轧制过程中存在轧制力矩不足,电机电流过大,制约了生产的正常进行。针对上述原因拟对2800粗轧机主传动系统扩容改造,并将目前的直流电机变交流电机,在轧制速度保持不变的前提下,增大轧制力矩以满足生产的需求。因而开展2800热粗轧机主传动系统改造方案研究,确定电机扩容改造的最大功率,同时找出主传动系统的薄弱环节,并提出相应的改造措施,具有重要的理论意义和工程实用价值。
本文针对2800粗轧机主传动系统扩容改造,采用经典材料力学理论和有限元法等分析手段,对主传动系统中齿轮座(包括人字齿齿轮、轴、轴承、箱体地脚螺栓等)、联接轴、传动轴、扁头和叉头等关键零部件强度进行了分析计算,得出了将目前2800热粗轧机主传动系统主电机功率从6400 kw(直流电机)提高到7000 kw(交流电机,交交变频),并通过减少人字齿轮上、中、下轴瓦的厚度来提高人字齿轮的中心距,将目前人字齿轮的齿数从22增加到25,齿轮精度从目前的8级提高到7级精度,对齿轮齿高和齿向进行修形;适当增加连接轴左叉头(工作辊侧)几何尺寸以提高强度,适应主传动系统电机功率提高对其强度的要求等结论。
Rough mill 2800 is the key equipment of squeezing and extending in aluminum processing plant, which was designed and machined independently by our country in the last century. Because of the limited design capacity and now growing annual production, the main transmission is becoming vulnerable with the increasing loads, which leads to frequent failure in the system. By now, the main transmission system has the symptoms of deficient roll torque and overload current, and consequently production is compromised. For improving the roll capacity and enhancing competitive ability, the main transmission system needs to be improved according to the current situation. Concrete and comprehensive method is developed to analyze the bearing capacity of weak links which is caused by expansion of power in the main transmission system. Moreover, the method will provide reference to studies on characteristics of transmission system in like rough mills theoretically and practically.
In this paper, key parts (herringbone gear , shaft, bearing, attachment bolts, coupling shaft, notch, palm end) of the main transmission system are analyzed by classic mechanics and computer simulation technology in line with design theory. Based on these analyses, reasonable improvements are proposed. Power of motor will be expanded from 6400KW with direct current to 7000 to 8000KW with alternating current so that roll torque will be strengthened to meet the need of production under the same rolling velocity. By decrease of thick of top、middle、down bush, the center distance of herringbone gear is cut down, number of gear is from 22 to 25 ,the accuracy manufacture of gear is from level 8 to level 7, modified of shape of gear; properly increase of geometry dimension of left notch is for enhance of strength, which is adapt to the increase of power motor.
本文针对2800粗轧机主传动系统扩容改造,采用经典材料力学理论和有限元法等分析手段,对主传动系统中齿轮座(包括人字齿齿轮、轴、轴承、箱体地脚螺栓等)、联接轴、传动轴、扁头和叉头等关键零部件强度进行了分析计算,得出了将目前2800热粗轧机主传动系统主电机功率从6400 kw(直流电机)提高到7000 kw(交流电机,交交变频),并通过减少人字齿轮上、中、下轴瓦的厚度来提高人字齿轮的中心距,将目前人字齿轮的齿数从22增加到25,齿轮精度从目前的8级提高到7级精度,对齿轮齿高和齿向进行修形;适当增加连接轴左叉头(工作辊侧)几何尺寸以提高强度,适应主传动系统电机功率提高对其强度的要求等结论。
Rough mill 2800 is the key equipment of squeezing and extending in aluminum processing plant, which was designed and machined independently by our country in the last century. Because of the limited design capacity and now growing annual production, the main transmission is becoming vulnerable with the increasing loads, which leads to frequent failure in the system. By now, the main transmission system has the symptoms of deficient roll torque and overload current, and consequently production is compromised. For improving the roll capacity and enhancing competitive ability, the main transmission system needs to be improved according to the current situation. Concrete and comprehensive method is developed to analyze the bearing capacity of weak links which is caused by expansion of power in the main transmission system. Moreover, the method will provide reference to studies on characteristics of transmission system in like rough mills theoretically and practically.
In this paper, key parts (herringbone gear , shaft, bearing, attachment bolts, coupling shaft, notch, palm end) of the main transmission system are analyzed by classic mechanics and computer simulation technology in line with design theory. Based on these analyses, reasonable improvements are proposed. Power of motor will be expanded from 6400KW with direct current to 7000 to 8000KW with alternating current so that roll torque will be strengthened to meet the need of production under the same rolling velocity. By decrease of thick of top、middle、down bush, the center distance of herringbone gear is cut down, number of gear is from 22 to 25 ,the accuracy manufacture of gear is from level 8 to level 7, modified of shape of gear; properly increase of geometry dimension of left notch is for enhance of strength, which is adapt to the increase of power motor.
引文
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[29] 李发海,李崇坚等交流电机控制系统的现状与发展动向,电工技术杂志,1993.1
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[31] 郭书祥,冯立富,实用有限元计算方法的若干进展,机械强度,2000No3
[32] 黎景立,轧制工艺参数测试技术,冶金工业出版社,1993 年
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[38] 王延浦主编,轧钢生产,冶金工业出版社 1981
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[40] 曹万昊,轧钢机万向接轴断裂研究,重型机械,1994 2
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[42] 赵志业,金属朔性变形与轧制理论,冶金工业出版社,1991
[43] 李友荣,1000mm 初轧机主传动系统扭转振动,武汉钢铁学院学报 1992 4
[44] 束德林,金属的力学性能,机械工业出版社 1991
[45] 张斗云,初轧机万向接轴头断裂原因分析,重型机械 1999 2
[46] 李崇坚,小型连轧机主传动技术的现状及发展,冶金自动化 1996 5
[47] 黄培文等,2800 四辊轧机主传动系统动态特性研究,重型机械 1993 3
[48] 华林,环件闭式轧制力和力矩上限计算,力学与实践 1994 3
[49] 王秀梅,张弓等,热连轧轧制力模型系数回归的新方法,东北大学学报 1999 l0
[50] 瞿慎安,紧凑式轧机主传动复合减速箱优化设计,山东冶金 1994 10
[51] 黄培文等,1700 带钢冷连轧机主传动系统振动故障诊断,重型机械 1995 2
[2] Turner M J,Dill E H,Murtin H C et al.Large Deflections Subjected to Heating and External Loads. Journal of Aerespace Sciences, February 1960, No27, 97~106
[3] Hisashi Honjgo&Haijime Watanabe, Impact Loading&Vibration of the Slabbing mill, Iron&Steel Eng 1975 No.5
[4] Francis S.Tee, Mechanical Vibrations-Theory & Ppplications Allyn&Bacon,Inc 1978
[5] Charles R. Thomas, Torque Amplification and Torsional Vibration In Large Reversing RillDrives, Iron and Steel Eng,1969 No.5:55~73
[6] Albert J. molnar, Torque amplification factor (TAP) analyses and tests on two bar millstands. Iron and Steel Eng.1981 No.l.
[7] Alexm.Kashsy,J&L-ALSE Torque Amplification and Vibration Inversti -gation Projact. Iron and Steel Eng. 1973 No.7
[8] R. B.RANDALL, Hilbert Transform Techniques In Machine Diagnosticate. Bruel Kjaer Australia Pty Ltd
[9] Luo G W, Xie J H. Hopf bifurcations and chaos of a two-degree-of-freedom vibro-impact system in two strong resonance cases [J]. International Journal of Non-Linear Mechanics, 2002,No37,19~34
[10] Wiercigroch, M, Sin V W T.Experimental study of a symmetrical piecewise base-excited oscillator[J].ASME Journal of Applied Mechanics, 1998,65(5):657~663
[11] wiercigroch M,Krivtsov A M. Frictional chatter in orthogonal metal cutting[J].Philosophical Transactions of the Royal Society of London:Part A,2001,359(1781):713~73
[12] 康贵信,邹家祥,有限单元法在冶金机械中的应用,冶金工业出版社,1991
[13] 王革,邹家祥等,受转矩作用零部件有限元法分析加载及约束方式的研究,冶金设备,1995 No2
[14] 陈大宏,邹家祥,CAD 技术在有限元分析前处理中的应用,北京科技大学学报,1994 No5
[15] 王革,陈大红,孙浩,邹家祥,初轧机滑块式万向接轴叉头应力应变分析及计算机图形显示,冶金设备,1995
[16] 刘安中,李友荣,轧机万向接轴叉头中贯通油孔对其强度的影响,重型机械,1998.3
[17] 钟如涛,轧机万向接轴叉头强度分析,武汉科技大学硕士论文,2001.6
[18] 李友荣,十字轴万向联轴器轴承盖裂纹的研究,武汉科技大学学报,1998.5
[19] 朱以文等,微机有限元前后处理系统及其应用,科学技术文献出版社,1993
[20] 张斗云,初轧机万向接轴扁头断裂原因分析,重型机械,1999 No2
[21] 崔丽红,吴迪平,650 轧机万向接轴强度分析,冶金设备,1998 No6
[22] 王革,汪福元等,万向接轴叉头强度分析,华东冶金学院学报,1995. 7
[23] 吴明强等,靠虑间隙时万向接轴的受力分析,重型机械,1998 .4
[24] 张斗云,初轧机万向接轴头断裂原因分析,重型机械,1999.2
[25] 成大先,机械设计手册(第三版)第 1 卷,化学工业出版社,1998
[26] 徐颧,机械设计手册第 2 卷,机械工业出版社,1991
[27] 唐蓉城,陆玉,机械设计(机械类),机械工业出版社,1993
[29] 李发海,李崇坚等交流电机控制系统的现状与发展动向,电工技术杂志,1993.1
[30] 黄培文,振动系统固有频率与振型的矩阵迭代法,重型机械 1985.10
[31] 郭书祥,冯立富,实用有限元计算方法的若干进展,机械强度,2000No3
[32] 黎景立,轧制工艺参数测试技术,冶金工业出版社,1993 年
[33] 崔朝,藏勇,轧机主传动系统扭振的有限元法研究,重型机械,1999.4
[34] 王冒成,邵敏,有限单元法基本原理和数值方法(第二版),清华大学出版社,1997
[35] 林鹤,4200 厚板轧机扭振动力学研究,北京钢铁学院学报,1981.4
[36] 林鹤,吴继庚,经典模态理论及其在轧钢机扭振中的应用,北京钢铁学院 1990
[37] 邹家祥,轧钢机械冶金工业出版社 1989 年〔第二版)
[38] 王延浦主编,轧钢生产,冶金工业出版社 1981
[39] 周征华,管克智,金属变形阻力,机械工业出版社,1989
[40] 曹万昊,轧钢机万向接轴断裂研究,重型机械,1994 2
[41] 王海文,轧钢机械设计,机械工业出版社,1983
[42] 赵志业,金属朔性变形与轧制理论,冶金工业出版社,1991
[43] 李友荣,1000mm 初轧机主传动系统扭转振动,武汉钢铁学院学报 1992 4
[44] 束德林,金属的力学性能,机械工业出版社 1991
[45] 张斗云,初轧机万向接轴头断裂原因分析,重型机械 1999 2
[46] 李崇坚,小型连轧机主传动技术的现状及发展,冶金自动化 1996 5
[47] 黄培文等,2800 四辊轧机主传动系统动态特性研究,重型机械 1993 3
[48] 华林,环件闭式轧制力和力矩上限计算,力学与实践 1994 3
[49] 王秀梅,张弓等,热连轧轧制力模型系数回归的新方法,东北大学学报 1999 l0
[50] 瞿慎安,紧凑式轧机主传动复合减速箱优化设计,山东冶金 1994 10
[51] 黄培文等,1700 带钢冷连轧机主传动系统振动故障诊断,重型机械 1995 2