面向汽车传动系统多挡共振的多级吸振器参数设计方法

doi:10.13229/j.cnki.jdxbgxb.20230347

摘要/Abstract

摘要：

针对汽车动力传动系统多个挡位存在扭转共振的问题，本文提出了一种多级并联动力吸振器的参数设计方法。首先，建立四自由度动力传动系统扭振模型并进行模态分析，基于共振模态的等效系统推导了n级并联动力吸振器的频响函数；然后，以4级并联动力吸振器为例，将传动系统3个挡位的振动角位移和振动角加速度作为优化目标，采用改进的非支配排序遗传算法对吸振器组的定调比和阻尼比进行优化，利用熵值法联合逼近理想解的排序法对Pareto解进行排序；最后，通过与3种传统的动力吸振器优化方法进行对比，并进行时域和频域仿真分析，验证了本文设计方案的有效性。本文方法可为固有频率可变振动系统的动力吸振器优化设计提供参考。

关键词: 车辆工程, 汽车传动系, 扭转振动, 动力吸振器, 多目标优化, 多频率减振

Abstract:

A parameter design method of multiple parallel dynamic vibration absorbers is proposed in order to suppress the powertrain system torsional resonance that exists in various gears of automotive. First， a four degrees of freedom powertrain model is presented， and the expression of the frequency response functions of the vibration system are derived based on the equivalent system with n parallel dynamic vibration absorbers attached. Then， the Nondominated Sorting Genetic Algorithm II is adopted to optimize the frequency ratios and damping ratios of the four parallel dynamic vibration absorbers in order to minimize the angular displacement and acceleration of the vibration system under three different gear ratio conditions. The Technique for Order Preference by Similarity to an Ideal Solution combined with the Entropy Weight Method is utilized to sort the Pareto solutions. Finally， the proposed optimization method is validated effective by comparing with three other traditional methods， and the time and frequency domain simulations are also implemented for the validation. The proposed method can provide references for the optimal parameter design of the dynamic vibration absorber when the eigenvalue of the target system is variable.

Key words: vehicle engineering, automotive powertrain system, torsional vibration, dynamic vibration absorber, multi-objective optimization, multi-frequency vibration damping

中图分类号:

U461.1

曲俊龙,史文库,玄圣夷,陈志勇. 面向汽车传动系统多挡共振的多级吸振器参数设计方法[J]. 吉林大学学报(工学版), 2025, 55(2): 444-455.

Jun-long QU,Wen-ku SHI,Sheng-yi XUAN,Zhi-yong CHEN. Parameter design method of multiple dynamic vibration absorbers for suppressing multi-frequency resonance of automotive powertrain[J]. Journal of Jilin University(Engineering and Technology Edition), 2025, 55(2): 444-455.

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参数	挡位
参数	4挡	5挡	6挡
J₁/（kg·m²）	0.733	0.733	0.733
J₂/（kg·m²）	0.040	0.063	0.094
J₃/（kg·m²）	0.349	0.628	1.006
J₄/（kg·m²）	13.962	25.108	40.231
k₁/（Nm·rad）	3.44×10³	3.44×10³	3.44×10³
k₂/（Nm·rad）	1.07×10³	1.92×10³	3.08×10³
k₃/（Nm·rad）	5.56×10³	1.0×10⁴	1.60×10⁴
c₁/［Nm·（s·rad^-1）］	0.9	0.9	0.9
c₂/［Nm·（s·rad^-1）］	0.501	0.9	1.442
c₃/［Nm·（s·rad^-1）］	0.006	0.01	0.016

项目	挡位
项目	4挡	5挡	6挡
试验测试/Hz	54.33	51.93	44.20
仿真计算/Hz	54.41	47.62	43.20
误差/%	+0.15	-8.29	-2.26

参数		方案1 （C_i =0.720 7）	方案2 （C_i =0.718 6）	方案3 （C_i =0.712 1）
定调比	α₁	0.710 0 0.816 6 0.950 5 1.264 3	0.691 9 0.819 0 0.944 9 1.260 5	0.679 1 0.935 8 0.824 3 1.264 3
	α₂
	α₃
	α₄
阻尼比	ζ₁	0.150 3 0.152 8 0.196 8 0.280 9	0.150 6 0.152 8 0.196 5 0.280 4	0.148 6 0.194 9 0.153 0 0.287 1
	ζ₂
	ζ₃
	ζ₄
max［H_e6（λ）］/10^-4 rad·（Nm）^-1		3.679 2	3.696 3	3.723 4
max［H_e5（λ）］/10^-4 rad·（Nm）^-1		3.811 7	3.849 4	3.913 7
max［H_e4（λ）］/10^-4 rad·（Nm）^-1		4.087 9	3.935 7	3.866 9
max［H_a₆（λ）］/ rad·s^-2·（Nm）^-1		28.191 1	28.433 6	28.907 1
max［H_a₅（λ）］/ rad·s^-2·（Nm）^-1		36.411 5	36.646 9	37.351 4
max［H_a₄（λ）］/ rad·s^-2·（Nm）^-1		54.221 3	54.503 7	54.382 9