本文選題：轉(zhuǎn)子系統(tǒng) + 聯(lián)軸器��； 參考：《哈爾濱工業(yè)大學(xué)》2015年碩士論文

【摘要】：旋轉(zhuǎn)機(jī)械是在工業(yè)部門中應(yīng)用最為廣泛的一類機(jī)械設(shè)備,它的穩(wěn)定運(yùn)行影響著整個(gè)工業(yè)的發(fā)展進(jìn)程。而轉(zhuǎn)子系統(tǒng)作為旋轉(zhuǎn)機(jī)械的核心部件,它的動力學(xué)特性直接影響著旋轉(zhuǎn)機(jī)械的結(jié)構(gòu)安全和工作性能。由于轉(zhuǎn)子系統(tǒng)運(yùn)行環(huán)境的惡劣,在實(shí)際工程作業(yè)中轉(zhuǎn)子系統(tǒng)發(fā)生耦合故障是非常常見的,因此轉(zhuǎn)子系統(tǒng)的耦合故障是轉(zhuǎn)子系統(tǒng)非線性動力學(xué)研究的重要內(nèi)容之一。不對中和裂紋故障都是轉(zhuǎn)子系統(tǒng)常見的故障,當(dāng)轉(zhuǎn)子系統(tǒng)在不對中狀態(tài)下運(yùn)行時(shí)可能引起轉(zhuǎn)軸撓曲大變形和轉(zhuǎn)軸磨損,大大增加了轉(zhuǎn)軸上出現(xiàn)裂紋或使轉(zhuǎn)軸上原有的小裂紋加深的可能性;而含較深裂紋的轉(zhuǎn)子系統(tǒng)會使系統(tǒng)的響應(yīng)過大導(dǎo)致不對中故障。因此,本文以某航空發(fā)動機(jī)低壓轉(zhuǎn)子系統(tǒng)為研究對象,對轉(zhuǎn)子系統(tǒng)不對中-裂紋耦合故障的非線性動力學(xué)特性進(jìn)行了研究。首先分析了齒式聯(lián)軸器在不對中狀態(tài)下的運(yùn)動規(guī)律,推導(dǎo)出了聯(lián)軸器平行角度不對中的激振力;比較了裂紋常用的數(shù)學(xué)模型的優(yōu)缺點(diǎn),選取了最適合的裂紋模型;對起支撐作用的滾動軸承進(jìn)行了運(yùn)動分析和載荷分析;利用拉格朗日建模法建立了轉(zhuǎn)子系統(tǒng)不對中-裂紋耦合故障的動力學(xué)微分方程,并對其進(jìn)行了無量綱化。隨后運(yùn)用四階Rugge-Kutta法對該系統(tǒng)進(jìn)行了仿真分析,得到了不對中、裂紋單一故障和不對中-裂紋耦合故障的動力學(xué)特性。當(dāng)轉(zhuǎn)子系統(tǒng)只有聯(lián)軸器不對中故障時(shí),系統(tǒng)響應(yīng)出現(xiàn)了1倍頻和2倍頻,轉(zhuǎn)子系統(tǒng)不僅在臨界轉(zhuǎn)速處出現(xiàn)1倍頻共振,而且在二分之一臨界轉(zhuǎn)速處出現(xiàn)2倍頻共振;當(dāng)轉(zhuǎn)子系統(tǒng)只有裂紋故障時(shí),系統(tǒng)響應(yīng)出現(xiàn)了1倍頻、2倍頻、3倍頻等高頻成分,在臨界轉(zhuǎn)速、二分之一臨界轉(zhuǎn)速和三分之一臨界轉(zhuǎn)速處出現(xiàn)了振動峰值,并且二分之一臨界轉(zhuǎn)速處的振動幅值與三分之一臨界轉(zhuǎn)速處的振動幅值相近。轉(zhuǎn)子系統(tǒng)同時(shí)出現(xiàn)不對中和裂紋故障時(shí),系統(tǒng)響應(yīng)具有1倍頻、2倍頻、3倍頻等高頻成分,在臨界轉(zhuǎn)速、二分之一臨界轉(zhuǎn)速和三分之一臨界轉(zhuǎn)速出現(xiàn)振動峰值,并且二分之一臨界轉(zhuǎn)速處的振動峰值要遠(yuǎn)遠(yuǎn)高于三分之一處的臨界轉(zhuǎn)速。最后利用分岔圖、Poincaré截面圖、時(shí)域波形圖、幅值譜圖分析了含不對中-裂紋耦合故障的轉(zhuǎn)子系統(tǒng)參數(shù)對耦合故障系統(tǒng)響應(yīng)的影響。
[Abstract]:Rotating machinery is the most widely used mechanical equipment in the industrial sector, and its stable operation affects the development process of the whole industry. As the core component of rotating machinery, the dynamic characteristics of rotor system directly affect the structural safety and performance of rotating machinery. Because of the bad operating environment of rotor system, coupling faults of rotor system are very common in practical engineering, so coupling fault of rotor system is one of the important contents of nonlinear dynamics research of rotor system. Misalignment and crack faults are common faults in rotor system. When the rotor system is running under the condition of misalignment, it may cause large deflection and wear of the shaft. It greatly increases the possibility of cracks on the shaft or deepening of the original small cracks on the shaft, while the response of the rotor system with deeper cracks will lead to misalignment fault. Therefore, in this paper, the nonlinear dynamic characteristics of an aero-engine low-pressure rotor system with mismatched mid-crack coupling faults are studied. Firstly, the motion law of gear coupling in misalignment state is analyzed, the exciting force in parallel angle misalignment of coupling is deduced, the advantages and disadvantages of common mathematical models of crack are compared, and the most suitable crack model is selected. The motion analysis and load analysis of rolling bearing are carried out, and the dynamic differential equation of coupling fault of rotor system is established by using Lagrangian modeling method, and it is dimensionless. Then the fourth order Rugge-Kutta method is used to simulate the system, and the dynamic characteristics of single fault and coupling fault are obtained. When the rotor system has only the misalignment fault of the coupling, the response of the rotor system is doubled frequency and 2 times frequency. The rotor system not only has 1 frequency doubling resonance at the critical speed, but also has 2 times frequency resonance at the 1/2 critical speed. When the rotor system has only a crack fault, the response of the rotor system has a high frequency component, such as 1 double frequency, 2 times frequency and 3 times frequency, and the vibration peak occurs at the critical speed, 1/2 critical speed and 1/3 critical speed. The vibration amplitude at 1/2 critical speed is similar to that at 1/3 critical speed. When the rotor system is not neutralized and cracked at the same time, the response of the rotor system has high frequency components, such as frequency doubling, frequency doubling and so on, and the vibration peak occurs at critical speed, 1/2 critical speed and 1/3 critical speed. And the peak value of vibration at 1/2 critical speed is much higher than that at 1/3. Finally, the effects of rotor system parameters on the response of coupled fault system are analyzed by using bifurcation diagram Poincar 茅 section, time-domain waveform diagram and amplitude spectrum diagram.
【學(xué)位授予單位】：哈爾濱工業(yè)大學(xué)
【學(xué)位級別】：碩士
【學(xué)位授予年份】：2015
【分類號】：TH165.3

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本文編號：2018287