發(fā)布時(shí)間：2018-07-29 06:04

【摘要】：課題來(lái)源于國(guó)防科工委“十一五”民用航天預(yù)研項(xiàng)目—“空間環(huán)境下的高性能摩擦副與高效傳動(dòng)機(jī)構(gòu)技術(shù)”（C4220061319）、國(guó)家教育部“長(zhǎng)江學(xué)者和創(chuàng)新團(tuán)隊(duì)發(fā)展計(jì)劃”項(xiàng)目—“高性能機(jī)電傳動(dòng)系統(tǒng)的創(chuàng)新設(shè)計(jì)理論、方法與技術(shù)”（IRT0763）、國(guó)家自然科學(xué)基金重點(diǎn)項(xiàng)目—“新型高性能傳動(dòng)件及系統(tǒng)的可靠性設(shè)計(jì)理論與方法”（50735008）。 減速器系統(tǒng)的工作狀態(tài)極其復(fù)雜，不僅載荷工況和動(dòng)力裝置多樣，且對(duì)于齒輪傳動(dòng)系統(tǒng)，由于時(shí)變嚙合剛度、傳動(dòng)誤差、齒側(cè)間隙等因素的影響，引起輪齒接觸 脫離 接觸周期性、強(qiáng)非線性耦合振動(dòng)，對(duì)傳動(dòng)系統(tǒng)的平穩(wěn)性、可靠性產(chǎn)生嚴(yán)重影響。因此對(duì)其進(jìn)行動(dòng)態(tài)特性、間隙非線性振動(dòng)行為及影響因素的研究，為高性能齒輪系統(tǒng)的設(shè)計(jì)、分析、制造提供了一定的理論依據(jù)與實(shí)驗(yàn)參考。 論文以NN型少齒差行星減速器為對(duì)象，，先分析其結(jié)構(gòu)及傳動(dòng)原理，用有限元法分析其固有頻率及模態(tài)振型，用集中質(zhì)量法建立減速器系統(tǒng)非線性振動(dòng)模型與方程，通過(guò)數(shù)值求解分析減速器非線性振動(dòng)特性以及參數(shù)對(duì)它的影響。最后對(duì)其模態(tài)特性和振動(dòng)響應(yīng)進(jìn)行實(shí)驗(yàn)研究。 論文主要研究?jī)?nèi)容如下： （1）分析該減速器的結(jié)構(gòu)、傳動(dòng)原理，計(jì)算某常見(jiàn)工況下各傳動(dòng)件的理論轉(zhuǎn)速。求得兩級(jí)傳動(dòng)的理論嚙合頻率、嚙合阻尼。詳細(xì)分析各滾動(dòng)軸承的變形、剛度、阻尼等動(dòng)特性參數(shù)。 （2）推導(dǎo)內(nèi)齒副單齒剛度計(jì)算式，考慮理論重合度，計(jì)算多對(duì)齒嚙合剛度。將兩級(jí)傳動(dòng)多對(duì)齒時(shí)變嚙合剛度擬合為8階Fourier級(jí)數(shù)的形式。分別以各級(jí)傳動(dòng)嚙合角頻率為角速度的正弦函數(shù)模擬各級(jí)齒輪誤差。 （3）采用ABAQUS建立該減速器有限元自由模態(tài)分析模型，其中輪齒嚙合部位采用綁定約束，用彈簧單元模擬軸承。采用Lanczos特征值求解器對(duì)該減速器進(jìn)行自由模態(tài)求解，獲得該減速器前20階固有頻率及模態(tài)振型。 （4）綜合考慮齒輪嚙合剛度、傳動(dòng)誤差、齒側(cè)間隙及支撐剛度和阻尼，用集中質(zhì)量法建立多自由度、多間隙、變參數(shù)、彎 扭耦合的兩級(jí)齒輪系統(tǒng)非線性振動(dòng)模型，用Lagrange方程推導(dǎo)齒輪系統(tǒng)的非線性振動(dòng)微分方程組。用四階五級(jí)的RKF法對(duì)非線性微分方程組求解，系統(tǒng)地分析該減速器各齒輪振動(dòng)位移、速度響應(yīng)，以及振動(dòng)位移 速度相圖、Poincaré截面。進(jìn)一步計(jì)算得齒輪彈粘嚙合力、軸承動(dòng)載荷、振動(dòng)加速度響應(yīng)。最后分析各參數(shù)對(duì)減速器非線性振動(dòng)特性的影響。 （5）用LMS Test. Lab對(duì)該減速器進(jìn)行錘擊法自由模態(tài)實(shí)驗(yàn)，驗(yàn)證理論分析結(jié)果的正確性。用三向加速度傳感器采集減速器殼體振動(dòng)信號(hào)，由FFT變換得到相應(yīng)的振動(dòng)頻率，經(jīng)1/3倍頻處理分析振動(dòng)加速度級(jí)結(jié)構(gòu)噪聲，經(jīng)積分處理得到振動(dòng)速度及位移響應(yīng)。
[Abstract]:The subject comes from the "11th Five-Year" Civil Aerospace Pre-Research Program of the National Commission for National Defense Science, Technology of High-Performance friction pairs and High-efficiency Transmission mechanisms in Space Environment (C4220061319), and the National Ministry of Education "Yangtze River Scholars and Innovation team Development Plan" -"innovative design theory for high performance electromechanical transmission systems, Methods and techniques "(IRT0763), key item of National Natural Science Foundation -" Theory and method of Reliability Design for New High performance Transmission parts and Systems "(50735008). The working state of the reducer system is extremely complex, not only the load working conditions and power devices are various, but also the gear transmission system is affected by the time-varying meshing stiffness, transmission error, tooth side clearance and so on. The gear tooth contact is caused by the periodic and strong nonlinear coupling vibration, which has a serious effect on the stability and reliability of the transmission system. Therefore, the study of the dynamic characteristics, the nonlinear vibration behavior of clearance and the influencing factors provide a certain theoretical basis and experimental reference for the design, analysis and manufacture of high performance gear system. In this paper, the structure and transmission principle of NN type planetary reducer with less tooth difference are analyzed, its natural frequency and modal mode are analyzed by finite element method, and the nonlinear vibration model and equation of reducer system are established by means of lumped mass method. The nonlinear vibration characteristics of reducer and the influence of parameters on it are analyzed numerically. Finally, the modal characteristics and vibration response are studied experimentally. The main contents of this paper are as follows: (1) the structure and driving principle of the reducer are analyzed. The theoretical meshing frequency and meshing damping of the two-stage transmission are obtained. The parameters of deformation, stiffness and damping of rolling bearings are analyzed in detail. (2) the calculation formula of single tooth stiffness of internal gear pair is derived, and the meshing stiffness of multiple pairs of teeth is calculated considering the degree of theoretical coincidence. The time-varying meshing stiffness of multi-pair teeth of two-stage transmission is fitted to the form of eighth order Fourier series. The sinusoidal function with the angular frequency of meshing angle of each transmission is used to simulate the errors of gear at all levels. (3) the finite element free modal analysis model of the reducer is established by using ABAQUS, in which the gear tooth meshing part is bound constrained. Use spring element to simulate bearing. The Lanczos eigenvalue solver is used to solve the free mode of the reducer, and the first 20 natural frequencies and modal modes of the reducer are obtained. (4) the gear meshing stiffness, transmission error, tooth side clearance and support stiffness and damping are considered synthetically. The nonlinear vibration model of a two-stage gear system with multiple degrees of freedom, multiple clearances, variable parameters and coupled bending and torsion is established by means of the lumped mass method. The nonlinear vibration differential equations of the gear system are derived by using the Lagrange equation. The fourth order five-stage RKF method is used to solve the nonlinear differential equations. The vibration displacement, velocity response and velocity phase diagram of each gear in the reducer are systematically analyzed. The gear elastic engagement force, bearing dynamic load and vibration acceleration response are further calculated. Finally, the influence of the parameters on the nonlinear vibration characteristics of the reducer is analyzed. (5) LMS Test is used. The free mode experiment of hammering method is carried out by Lab to verify the correctness of the theoretical analysis. The vibration signal of the reducer shell is collected by three direction acceleration sensor and the corresponding vibration frequency is obtained by FFT transform. The structural noise of vibration acceleration level is analyzed by 1 / 3 frequency doubling processing, and the vibration velocity and displacement response are obtained by integral processing.
【學(xué)位授予單位】：重慶大學(xué)
【學(xué)位級(jí)別】：博士
【學(xué)位授予年份】：2013
【分類號(hào)】：TH132.46

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