【摘要】：自1970年以來(lái),單根多楔帶傳動(dòng)系統(tǒng)在汽車(chē)發(fā)動(dòng)機(jī)前端附件驅(qū)動(dòng)(Front End Accessory Drive,FEAD)系統(tǒng)中得到廣泛的應(yīng)用。多楔帶傳動(dòng)系統(tǒng)是由離散系統(tǒng)(各帶輪和張緊臂)以及連續(xù)系統(tǒng)(柔性多楔帶)組成的混合動(dòng)力學(xué)機(jī)械系統(tǒng),其振動(dòng)型式非常復(fù)雜。其包括各帶輪的旋轉(zhuǎn)振動(dòng)、張緊器的擺動(dòng)、帶的空間三向振動(dòng)(縱向、橫向和側(cè)向振動(dòng))及其與接觸帶輪之間的耦合振動(dòng),以及帶還可能發(fā)生彎曲振動(dòng)及彎扭復(fù)合振動(dòng)等等。除此之外,為了避免系統(tǒng)的共振,系統(tǒng)的固有頻率也是非常受關(guān)注的內(nèi)容。我國(guó)對(duì)多楔帶傳動(dòng)系統(tǒng)的研究起步較晚,現(xiàn)在還處于初期階段,特別是對(duì)其動(dòng)態(tài)特性的研究。于是,針對(duì)多楔帶傳動(dòng)系統(tǒng),作者開(kāi)展了如下研究工作: 其一,以單根多楔帶傳動(dòng)系統(tǒng)為研究對(duì)象,建立了適用于任意布置型式系統(tǒng)的旋轉(zhuǎn)振動(dòng)模型,并給出了其穩(wěn)態(tài)及動(dòng)態(tài)響應(yīng)的求解方法。綜合考慮帶的縱向運(yùn)動(dòng)和各輪的旋轉(zhuǎn)運(yùn)動(dòng),推導(dǎo)了其運(yùn)動(dòng)方程并且給出了系統(tǒng)穩(wěn)態(tài)分析的方法。對(duì)運(yùn)動(dòng)方程關(guān)于系統(tǒng)穩(wěn)態(tài)做線(xiàn)性化處理,得到系統(tǒng)動(dòng)態(tài)方程并給出了系統(tǒng)微幅振動(dòng)響應(yīng)的求解方法。就某發(fā)動(dòng)機(jī)FEAD系統(tǒng),計(jì)算了其振動(dòng)響應(yīng)。并且,對(duì)任意布置型式的輪系,給出了其統(tǒng)一的帶段長(zhǎng)、包角等參數(shù)的公式。 其二,以三輪-帶多楔帶傳動(dòng)系統(tǒng)為研究對(duì)象,建立了梁耦合振動(dòng)模型�；诖四Ｐ�,計(jì)算了帶的橫向振動(dòng)。由于旋轉(zhuǎn)模型主要是分析系統(tǒng)中的旋轉(zhuǎn)振動(dòng),對(duì)于多楔帶這一關(guān)鍵部件,只能間接地分析其縱向伸縮運(yùn)動(dòng)。實(shí)際系統(tǒng)中,多楔帶橫向振動(dòng)對(duì)系統(tǒng)振動(dòng)及帶壽命影響較大。為了預(yù)測(cè)帶的橫向振動(dòng),作者又開(kāi)展了較為復(fù)雜的梁耦合振動(dòng)模型的研究。模型中,帶簡(jiǎn)化為縱向運(yùn)動(dòng)伯努利-歐拉梁,各輪和張緊器簡(jiǎn)化為剛性旋轉(zhuǎn)元件。應(yīng)用邊界值問(wèn)題(BVP)求解技術(shù)計(jì)算了帶橫向位移的穩(wěn)態(tài)解;帶的橫向振動(dòng)位移為時(shí)間與空間的函數(shù),應(yīng)用迦遼金法將其離散為時(shí)間函數(shù)和空間函數(shù)之積,計(jì)算了各帶的橫向振動(dòng)。實(shí)驗(yàn)測(cè)試了一三輪-帶傳動(dòng)系統(tǒng)中帶的橫向振動(dòng)和輪的旋轉(zhuǎn)振動(dòng)。并且通過(guò)對(duì)比計(jì)算結(jié)果與實(shí)測(cè)結(jié)果,驗(yàn)證了文中計(jì)算帶橫向振動(dòng)方法的可行性。
[Abstract]:Since 1970, single multi-wedged belt drive system has been widely used in automobile engine front-end attachment drive (Front End Accessory Drive,FEAD) system. Multi-wedged belt transmission system is a hybrid dynamic mechanical system composed of discrete system (pulley and tension arm) and continuous system (flexible multi-wedged belt). The vibration type of multi-wedged belt transmission system is very complex. It includes the rotating vibration of each pulley, the swing of tensioner, the spatial three-way vibration of the belt (longitudinal, transverse and lateral vibration) and its coupling vibration with the contact pulley, as well as the possible bending vibration and bending-torsional composite vibration of the belt, and so on. In addition, in order to avoid the resonance of the system, the natural frequency of the system is also very concerned. The research on multi-wedged belt transmission system in China started late, and is still in its early stage, especially the study of its dynamic characteristics. Therefore, for the multi-wedged belt transmission system, the author has carried out the following research work: first, taking the single multi-wedged belt transmission system as the research object, the rotating vibration model suitable for any arrangement type system is established, and the solution method of its steady state and dynamic response is given. Considering the longitudinal motion of the belt and the rotating motion of each wheel, the equation of motion is derived and the method of steady state analysis of the system is given. The equation of motion is linearized about the steady state of the system, and the dynamic equation of the system is obtained, and the solution method of the micro-amplitude vibration response of the system is given. The vibration response of an engine FEAD system is calculated. Moreover, for any type of gear train, the unified formulas of band length, package angle and other parameters are given. Secondly, taking the three-wheel-belt multi-wedged belt transmission system as the research object, the beam coupling vibration model is established. Based on this model, the transverse vibration of the band is calculated. Because the rotation model is mainly to analyze the rotating vibration in the system, the longitudinal telescopic motion of the multi-wedged belt can only be analyzed indirectly. In the actual system, the transverse vibration of multi-wedged belt has great influence on the vibration and belt life of the system. In order to predict the transverse vibration of the band, the author also studies the complex beam coupling vibration model. In the model, the belt is simplified to the longitudinal motion Bernoulli Euler beam, and the wheels and tensioners are simplified to rigid rotating elements. The steady state solution of the transverse displacement with transverse displacement is calculated by using the boundary value problem (BVP) solution technique, and the transverse vibration displacement of the band is a function of time and space, which is discretized into the product of time function and spatial function by Galerkin method, and the transverse vibration of each band is calculated. The transverse vibration of the belt and the rotating vibration of the wheel in a three-wheel-belt transmission system are tested. By comparing the calculated results with the measured results, the feasibility of the method for calculating the transverse vibration of the belt is verified.
【學(xué)位授予單位】：華南理工大學(xué)
【學(xué)位級(jí)別】：碩士
【學(xué)位授予年份】：2011
【分類(lèi)號(hào)】：TH132.32

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