Design and Experimental Study of Stiffness Self-tuning Wideband Dynamic Vibration Absorbers

doi:10.3969/j.issn.1004-132X.2025.11.014

Abstract

Abstract:

To address the issues of traditional dynamic absorbers losing resonance and exhibiting a significant decline in vibration reduction performance when the external excitation frequency shifted， a novel wideband dynamic vibration absorber was designed that altered the stiffness to change the natural frequency， and to broaden the vibration absorption bandwidth. The vibration absorption and frequency adjustment mechanism of the absorbers were theoretically analyzed， followed by PID parameter optimization by using an ISSA， finally， an ISSA-PID controller was employed to adjust the structural parameters of the absorbers， achieving adaptive wideband vibration absorption. Simulation results indicate that the ISSA optimization requires fewer iterations and demonstrates greater optimization capability compared to the sparrow search algorithm（SSA） optimization. The control scheme optimized by ISSA reduces the overshoot by 44.8% compared to that of the pre-optimization condition and reduces by 33.3% compared to that of the SSA-optimized scheme. In addition， the settling time of the control scheme optimized by ISSA is reduced by 16.2% compared to that of the SSA-optimized scheme. The testing results indicate that the wideband dynamic vibration absorber has a wide vibration absorption bandwidth and significant vibration reduction effectiveness， demonstrating substantial engineering application value.

Key words: dynamic vibration absorber, wideband, parameter optimization, improved sparrow search algorithm（ISSA）, PID control

摘要：

为解决传统动力吸振器在外界激振力频率发生偏移时失谐、减振效果急剧下降的问题，设计了一种通过调节自身刚度来改变其固有频率以扩宽吸振频带的新型宽频动力吸振器。对吸振器的吸振及频率调节机理进行了理论分析，采用改进麻雀搜索算法（ISSA）进行PID参数优化，最后使用ISSA-PID控制器调节吸振器结构参数，实现自适应宽频吸振。仿真结果表明，ISSA寻优比麻雀搜索算法（SSA）寻优的迭代次数更少，寻优能力更强；ISSA优化后的控制方案超调量比优化前减少44.8%，比SSA优化后减少33.3%；ISSA优化后的控制方案调整时间比SSA优化后缩短16.2%。试验结果表明，该宽频动力吸振器吸振频带宽且减振效果显著，有较高工程应用价值。

关键词: 动力吸振器, 宽频, 参数优化, 改进麻雀搜索算法（ISSA）, PID控制

CLC Number:

TB535.1

Zhi WANG, Shanfu LI, Jing TIAN, Mengkang YUE. Design and Experimental Study of Stiffness Self-tuning Wideband Dynamic Vibration Absorbers[J]. China Mechanical Engineering, 2025, 36(11): 2593-2600.

王志, 李善夫, 田晶, 岳梦康. 刚度自调谐宽频动力吸振器设计与试验研究[J]. 中国机械工程, 2025, 36(11): 2593-2600.

Figures/Tables 21

Fig.1 Principle diagram of a dynamic vibration absorber

Fig.2 Frequency response function of the vibration absorber at different damping ratios （μ=0.1）

Fig.3 Mechanical model diagram of continuous mass constant section cantilever beam

Fig.4 Wideband cantilever beam dynamic vibration absorber

Fig.5 PID controller system structure

Fig.6 Levy flight strategy

Fig.7 ISSA-optimized PID controller process

Fig.8 Fitness function iteration curve

Fig.9 Values of Kp after SSA and ISSA tuning

Fig.10 Values of Ki after SSA and ISSA tuning

Fig.11 Values of Kd after SSA and ISSA tuning

Tab.1 Values of PID parameter before and after optimization

优化方式	K_p值	K_i值	K_d值
优化前	0.500	0.080	0.080
SSA优化后	0.373	0.055	0.717
ISSA优化后	0.050	0.039	0.051

Tab.2 Main system and absorber parameters

结构	质量/kg	刚度/（N·m^-1）	阻尼/（N·s·m^-1）
主系统	3.28	6.84 $×$ 10⁴	30
吸振器	0.328	实时计算	5

Tab.2 Main system and absorber parameters

结构	质量/kg	刚度/（N·m^-1）	阻尼/（N·s·m^-1）
主系统	3.28	6.84 $×$ 10⁴	30
吸振器	0.328	实时计算	5

Fig.12 Natural frequency tracking curve

Fig.13 Time-domain and frequency-domain plots of the main system’s vibration displacement equipped with a traditional dynamic absorber

Fig.14 Time-domain and frequency-domain plots of main system’s vibration displacement equipped with a wideband dynamic absorber

Fig.15 Vibration reduction test bench of wideband dynamic vibration absorber test bench

Fig.16 Vibration acceleration of the main system at 28.1 Hz （measurement point 1）

Fig.17 Vibration acceleration of the main system at 30 Hz （measurement point 1）

Fig.18 Vibration acceleration of the main system at 31.3 Hz （measurement point 1）

Fig.19 Comparison chart of vibration reduction effects

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