基于某二级减速齿轮系统的齿面修形优化

doi:DOI:10.13229/j.cnki.jdxbgxb20210132

Abstract

Abstract:

The prominent vibration and noise problems are commonly exist in the initial design stage of gear system. To solve this problem， this paper takes the two-stage reduction gear system carried by an electric drive system as the research object. The minimum fluctuation of transmission error， minimum root mean square value of vibration acceleration in the direction of meshing line， and minimum load density of discrete points on meshing line are taken as optimization objectives. The tooth surface micro modification parameters are taken as design variable， and the algorithm NSGA-Ⅱ is used to conduct multi-objective optimization. The loaded tooth surface contact analysis（LTCA） is carried out based on the software MASTA. The results show that， compared with unmodified stage， the fluctuation of meshing transmission error and system transmission error after micro modification optimization are significantly reduced， the load distribution on the tooth surface is more uniform， the maximum contact stress and the amplitude of vibration acceleration of the bearing seat are greatly decreased， and the overall dynamic performance of gear system is improved. The research ideas and methods in this paper can provide guidance for wider optimization design of gear system.

Key words: vehicle engineering, gear system, tooth surface modification, genetic algorithm, optimization design

CLC Number:

TH132.41

Hong-bo YANG,Wen-ku SHI,Zhi-yong CHEN,Nian-cheng GUO,Yan-yan ZHAO. Optimization of tooth surface modification based on a two-stage reduction gear system[J].Journal of Jilin University(Engineering and Technology Edition), 2022, 52(7): 1541-1551.

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宏观参数	小齿（第一级/ 第二级）	大齿（第一级/ 第二级）
齿数	15/13	42/40
齿宽/mm	12/20	12/20
齿顶圆直径/mm	27.794/28.087	68.289/75.207
齿根圆直径/mm	21.044/20.212	61.539/67.332
旋向	右旋/左旋	左旋/右旋
螺旋角/（o）	15/5
法向模数/mm	1.5/1.75
法向压力角/（o）	20/20
中心距/mm	45/47.997
端面重合度	2.8/3.08

修形参数	第一级	第二级
齿向起鼓量x₁/μm	5	5
螺旋角修形量x₂/μm	0.3	1.8
齿向左端面修形量x₃/μm	5	10
齿向右端面修形量x₄/μm	2	3
左端面修形长度y₁/mm	1.2	2.4
右端面修形长度y₂/mm	1.2	2.4
齿形起鼓量x₅/μm	3	8
压力角修形量x₆/μm	5	5
齿顶修形量x₇/μm	8	5
齿顶修形长度y₃/mm	0.7	0.7

分析指标	优化前	优化后	减小量
1^st齿轮副啮合传递误差/μm	2.05	1.59	22.44%
2^nd齿轮副啮合传递误差/μm	4.67	2.92	37.47%
系统传递误差/（m·rad）	0.16	0.09	43.75%
1^st齿轮副最大接触应力/MPa	1301.56	1144.50	12.07%
2^nd齿轮副最大接触应力/MPa	1400.01	1287.56	8.03%
轴承座振动加速度幅值/（m·s^-2）	116.54	97.57	16.28%

分析指标	工况	优化前	优化后	减小量
1^st齿轮副啮合传递误差/μm	工况二	3.10	3.00	3.23%
	工况三	4.31	4.03	6.50%
	工况四	6.22	5.18	16.72%
	工况五	7.28	6.02	17.31%
2^nd齿轮副啮合传递误差/μm	工况二	4.08	2.75	32.60%
	工况三	3.57	2.82	21.01%
	工况四	18.04	10.35	42.63%
	工况五	22.51	14.51	35.54%
系统传递误差/（m·rad）	工况二	0.21	0.10	52.38%
	工况三	0.45	0.22	51.11%
	工况四	0.61	0.35	42.62%
	工况五	0.72	0.49	31.94%
1^st齿轮副最大接触应力/MPa	工况二	1736.20	1432.31	17.50%
	工况三	2105.64	1820.14	13.56%
	工况四	2430.22	2050.86	15.61%
	工况五	2700.56	2325.63	13.88%
2^nd齿轮副最大接触应力/MPa	工况二	1840.52	1653.49	10.16%
	工况三	2215.14	1940.02	12.42%
	工况四	2528.55	2185.76	13.56%
	工况五	2802.55	2430.32	13.28%
轴承座振动加速度幅值/（m·s^-2）	工况二	215.92	200.15	7.30%
	工况三	502.43	449.12	10.61%
	工况四	371.01	337.21	9.11%
	工况五	314.33	285.76	9.09%

Optimization of tooth surface modification based on a two-stage reduction gear system

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