【摘要】：隨著動(dòng)力裝置朝小型化、輕量化和高轉(zhuǎn)速化方向發(fā)展,其振動(dòng)與噪聲問(wèn)題越來(lái)越突出。振動(dòng)與噪聲的存在不僅影響動(dòng)力裝置的工作效率,同時(shí)還影響其使用壽命。傳統(tǒng)的被動(dòng)減振方法由于不能應(yīng)對(duì)外激勵(lì)頻率的變化,無(wú)法在全頻率范圍內(nèi)對(duì)振動(dòng)實(shí)施有效控制。為解決被動(dòng)減振方法存在的不足,主動(dòng)控制方法已成為當(dāng)前減振研究的熱點(diǎn)。主動(dòng)吸振器是實(shí)施主動(dòng)控制方法的執(zhí)行機(jī)構(gòu),其性能和控制方法對(duì)減振效果有直接影響。本文主要圍繞電磁式主動(dòng)吸振器中電磁作動(dòng)器的結(jié)構(gòu)設(shè)計(jì)、主動(dòng)控制算法以及特性試驗(yàn)等方面開展研究。論文首先根據(jù)主動(dòng)吸振器的工作原理,將電磁式主動(dòng)吸振器振動(dòng)系統(tǒng)簡(jiǎn)化為有阻尼受迫振動(dòng)的單自由度系統(tǒng),并建立了所對(duì)應(yīng)的動(dòng)力學(xué)模型。由MATLAB仿真得出,當(dāng)頻率比遠(yuǎn)大于1時(shí),振動(dòng)系統(tǒng)所需的作用力與電磁作動(dòng)器產(chǎn)生的電磁力相等。確定了電磁作動(dòng)器各組成部分的材料。通過(guò)電磁場(chǎng)仿真分析,優(yōu)化了磁路結(jié)構(gòu),分析了永磁鐵厚度與氣隙大小對(duì)電磁力輸出的影響,確定了電磁作動(dòng)器整體結(jié)構(gòu)方案,同時(shí)采用有限元分析方法對(duì)其運(yùn)動(dòng)部件進(jìn)行了強(qiáng)度校核。其次,研究了PID控制算法的參數(shù)整定原則,分析了加速度誤差與誤差變化率對(duì)參數(shù)整定的影響。通過(guò)對(duì)系統(tǒng)動(dòng)力學(xué)模型進(jìn)行分析,獲得了系統(tǒng)的傳遞函數(shù),以被控系統(tǒng)的加速度級(jí)作為控制目標(biāo),設(shè)計(jì)了兩輸入三輸出的模糊控制器,并與PID控制相結(jié)合設(shè)計(jì)出模糊-PID控制器,用MATLAB/Simulink模塊對(duì)模糊-PID控制進(jìn)行了仿真分析。結(jié)果表明在模糊-PID控制下,系統(tǒng)的超調(diào)量為0.3mm,調(diào)整時(shí)間為80ms,上升時(shí)間為20ms。最后,對(duì)電磁作動(dòng)器進(jìn)行了試驗(yàn)研究,結(jié)果表明彈簧片剛度為54N/mm,符合初始設(shè)計(jì)要求。完成電磁作動(dòng)器動(dòng)態(tài)力測(cè)試試驗(yàn),驗(yàn)證作動(dòng)力與電流電壓頻率變化之間的關(guān)系。完成試驗(yàn)臺(tái)架的組裝,結(jié)合控制算法進(jìn)行臺(tái)架主動(dòng)控制試驗(yàn)。結(jié)果表明,電磁式主動(dòng)吸振器能夠在模糊-PID控制策略下振動(dòng)加速度級(jí)平均下降21.1d B。
[Abstract]:With the development of power plant towards miniaturization, lightweight and high speed, the problems of vibration and noise become more and more prominent. The existence of vibration and noise not only affects the working efficiency of power plant, but also affects its service life. The traditional passive vibration reduction method can not control the vibration effectively in the whole frequency range because it can not respond to the change of external excitation frequency. In order to solve the deficiency of passive vibration reduction method, active control method has become a hot spot in the research of vibration reduction. Active vibration absorber is the executive mechanism of active control method, and its performance and control method have direct influence on the effect of vibration reduction. This paper focuses on the structure design, active control algorithm and characteristic test of the electromagnetic actuator in the electromagnetic active vibration absorber. Firstly, according to the working principle of active vibration absorber, the vibration system of electromagnetic active vibration absorber is simplified to a single degree of freedom system with damping forced vibration, and the corresponding dynamic model is established. The MATLAB simulation shows that when the frequency ratio is far greater than 1, the force required for the vibration system is equal to the electromagnetic force generated by the electromagnetic actuator. The material of each component of electromagnetic actuator is determined. Through the electromagnetic field simulation analysis, the magnetic circuit structure is optimized, the influence of the permanent magnet thickness and the air gap size on the electromagnetic force output is analyzed, and the whole structure scheme of the electromagnetic actuator is determined. At the same time, the finite element analysis method is used to check the strength of its moving parts. Secondly, the parameter tuning principle of PID control algorithm is studied, and the effects of acceleration error and error rate on parameter tuning are analyzed. By analyzing the dynamic model of the system, the transfer function of the system is obtained, and the fuzzy controller with two inputs and three outputs is designed with the acceleration level of the controlled system as the control target. The fuzzy PID controller is designed in combination with PID control, and the fuzzy PID control is simulated by MATLAB/Simulink module. The results show that under the fuzzy PID control, the overshoot is 0.3 mm, the adjustment time is 80 Ms, and the rising time is 20 Ms. Finally, the electromagnetic actuator is experimentally studied. The results show that the stiffness of the spring plate is 54 N / mm, which meets the initial design requirements. The dynamic force test of the electromagnetic actuator is completed to verify the relationship between the dynamic force and the change of current, voltage and frequency. Complete the assembly of the test bench and carry out the active control test with the control algorithm. The results show that the electromagnetic active vibration absorber can decrease the vibration acceleration level by 21.1 dB under the fuzzy PID control strategy.
【學(xué)位授予單位】：湘潭大學(xué)
【學(xué)位級(jí)別】：碩士
【學(xué)位授予年份】：2017
【分類號(hào)】：TB535.1

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本文編號(hào)：2367981