拖拉机液压机械无级变速器箱体的轻量化设计
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摘要
以一款拖拉机液压机械无级变速器箱体为研究对象,提出了基于折衷规划多目标拓扑优化方法的箱体轻量化设计方案,同时考虑固有频率和箱体刚度对箱体进行轻量化设计。基于优化结果对变速器箱体进行详细设计,通过在轴承座孔上施加加强筋,降低该区域的最大集中应力值,以达到兼顾箱体轴承座结构刚度强度和减轻箱体质量的目的。研究结果表明:优化后的变速器箱体质量为243. 4kg,较初始箱体质量418. 2kg降低了41%;优化后箱体的最大位移为0. 158 mm,较初始设计箱体的最大位移0. 219 mm降低了23%。
This paper takes the hydro-mechanical continuously variable transmission box as the research object,proposes a multi-objective topology optimization design method based on the compromised programming method,and does the lightweight design of the box by considering both the natural frequency and the box stiffness. Based on the optimized results,the hydro-mechanical continuously variable transmission box is designed in detail. The ribs are applied on the bearing seat hole to reduce the maximum concentrated stress in the area,so as to achieve both the rigidity of the box housing and the weight of the box. The results show that the weight of the optimized transmission box is 243.4 kg,which is 41% lower than the initial box weight of 418.2 kg,and the maximum displacement of the optimized box is 0.158 mm,which is 23% lower than the maximum displacement of the original design box of 0.219 mm.
This paper takes the hydro-mechanical continuously variable transmission box as the research object,proposes a multi-objective topology optimization design method based on the compromised programming method,and does the lightweight design of the box by considering both the natural frequency and the box stiffness. Based on the optimized results,the hydro-mechanical continuously variable transmission box is designed in detail. The ribs are applied on the bearing seat hole to reduce the maximum concentrated stress in the area,so as to achieve both the rigidity of the box housing and the weight of the box. The results show that the weight of the optimized transmission box is 243.4 kg,which is 41% lower than the initial box weight of 418.2 kg,and the maximum displacement of the optimized box is 0.158 mm,which is 23% lower than the maximum displacement of the original design box of 0.219 mm.
引文
[1]万晓飞,刘献栋,马维金.基于静动态测试分析的变速器壳体开裂故障分析[J].噪声与振动控制,2016,36(1):163-167.
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[6]徐岩,陈宇东,杨志军,等.载重汽车变速器壳体加强筋布置的优化设计[J].哈尔滨工业大学学报,2009,41(3):157-160.
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[11]朱剑峰,林逸,陈潇凯,等.汽车变速器箱体结构拓扑优化设计[J].吉林大学学报:工学版,2013,43(3):584-589.
[12]郑松林,屈金茜.电动车变速器壳体结构优化[J].机械强度,2015,37(6):1168-1172.
[13]梅超,褚超美,繆国.基于折衷规划的汽车变速器壳体拓扑优化方法研究[J].机械设计与制造,2016(8):58-60.
[14].蔡春杰.汽车变速器箱体有限元分析与拓扑优化设计[D].镇江:江苏大学,2017.
[15]冯翠云.旋耕机变速箱体强度有限元分析及优化[J].制造业自动化,2013,35(11):138-148.
[2] Sonsino C M. Structural durability of cast alumunium gearbox housings of underground railway vehicles under variable amplitude loading[J]. International Journal of Fatigue,2005,27:944-953.
[3] Morgado T L,Branco C M. A failure study of housing of the gearboxes of series 2600 locomotives of the Portuguese railway company[J]. Engineering Failure Analysis,2008,46(24):154-164.
[4]张越.新能源汽车发展现状及未来展望[J].汽车工业研究,2013(2):39-41.
[5]曹凤利,李国璋,傅建平.基于有限元的履带车辆变速箱体强度分析[J].机械工程师,2006(7):108-110.
[6]徐岩,陈宇东,杨志军,等.载重汽车变速器壳体加强筋布置的优化设计[J].哈尔滨工业大学学报,2009,41(3):157-160.
[7]郭能,周友国,雷刚,等.重型汽车变速器箱体拓扑优化[J].重庆理工大学学报:自然科学版,2010,24(12):106-109.
[8]许佳音,崔国敏,王刚. YB1502型变速器箱体的轻量化探索[J].工程机械,2011(10):32-35.
[9]刘辉,项昌乐,张喜清.多工况变速器箱体静动态联合拓扑优化[J].汽车工程,2012,34(2):143-148.
[10]闵海涛,高娟,马天飞.汽车变速器箱体结构强度分析与优化设计[J].中国机械工程,2012,23(20):2514-2519.
[11]朱剑峰,林逸,陈潇凯,等.汽车变速器箱体结构拓扑优化设计[J].吉林大学学报:工学版,2013,43(3):584-589.
[12]郑松林,屈金茜.电动车变速器壳体结构优化[J].机械强度,2015,37(6):1168-1172.
[13]梅超,褚超美,繆国.基于折衷规划的汽车变速器壳体拓扑优化方法研究[J].机械设计与制造,2016(8):58-60.
[14].蔡春杰.汽车变速器箱体有限元分析与拓扑优化设计[D].镇江:江苏大学,2017.
[15]冯翠云.旋耕机变速箱体强度有限元分析及优化[J].制造业自动化,2013,35(11):138-148.