本文關(guān)鍵詞： 非圓同步帶 變傳動(dòng)比傳動(dòng) 節(jié)曲線算法 非圓同步帶齒廓　出處：《浙江理工大學(xué)》2017年碩士論文　論文類型：學(xué)位論文

【摘要】：隨著科技的發(fā)展,越來(lái)越多場(chǎng)合需要傳動(dòng)機(jī)構(gòu)實(shí)現(xiàn)變傳動(dòng)比傳動(dòng)。如輯筒式平板印刷機(jī)的自動(dòng)送紙機(jī)構(gòu)在工作過(guò)程中速度是不斷變化的。在紡織機(jī)械中,為獲得特定花紋織物也需要變傳動(dòng)比傳動(dòng)裝置。非圓齒輪傳動(dòng)機(jī)構(gòu)是目前最常用的變傳動(dòng)比傳動(dòng)機(jī)構(gòu),然而非圓齒輪傳動(dòng)裝置只適用于中心距較小的情況�；谏鲜銮闆r,本論文提出了一種三輪式非圓同步帶傳動(dòng)機(jī)構(gòu),并給出了計(jì)算非圓張緊同步帶輪節(jié)曲線算法。提出了一種只需知道非圓節(jié)曲線的數(shù)據(jù)點(diǎn)就能求得張緊輪正確傳動(dòng)關(guān)系的數(shù)值計(jì)算方法——搜索法。提出了圓形同步帶輪齒廓包絡(luò)方法和非圓節(jié)曲線同步帶輪齒廓包絡(luò)方法,以及一種更為簡(jiǎn)單、易于理解的齒廓點(diǎn)獲取算法。本論文主要的工作內(nèi)容如下:1)針對(duì)兩輪非圓帶輪傳動(dòng)機(jī)構(gòu)傳動(dòng)過(guò)程無(wú)法實(shí)現(xiàn)實(shí)時(shí)張緊的問(wèn)題,提出了三輪式非圓同步帶傳動(dòng)機(jī)構(gòu),并根據(jù)傳動(dòng)關(guān)系求得非圓張緊同步帶輪的初始節(jié)曲線。2)在實(shí)際工程計(jì)算時(shí),不能直接得到張緊輪的節(jié)曲線方程,因此無(wú)法采用解析法計(jì)算張緊輪的傳動(dòng)關(guān)系,為此提出了一種數(shù)值計(jì)算方法——搜索法,利用三次非均勻B樣條及傳動(dòng)關(guān)系,計(jì)算非圓張緊輪與主從動(dòng)輪之間的傳動(dòng)關(guān)系。3)基于齒輪傳動(dòng)的共軛嚙合原理,提出了一種非圓同步帶輪齒廓計(jì)算方法,并提出一種更簡(jiǎn)單的齒廓點(diǎn)獲取方法——局部象限法,為非圓同步帶輪齒廓設(shè)計(jì)提供了一種新思路。4)基于MATLAB開發(fā)了三輪式非圓同步帶傳動(dòng)機(jī)構(gòu)的參數(shù)化設(shè)計(jì)平臺(tái),計(jì)算得到各個(gè)參數(shù)的最優(yōu)值以及非圓張緊同步帶輪的最優(yōu)節(jié)曲線、主從動(dòng)輪以及張緊輪的齒廓。5)根據(jù)最優(yōu)參數(shù)對(duì)三輪式非圓同步帶傳動(dòng)機(jī)構(gòu)試驗(yàn)臺(tái)進(jìn)行結(jié)構(gòu)設(shè)計(jì),并進(jìn)行研制和試驗(yàn),將試驗(yàn)結(jié)果與理論計(jì)算結(jié)果進(jìn)行對(duì)比,發(fā)現(xiàn)試驗(yàn)結(jié)果與理論計(jì)算結(jié)果基本吻合,證明了本文提出的三輪式非圓同步帶傳動(dòng)機(jī)構(gòu)的合理性及非圓張緊同步帶輪節(jié)曲線、齒廓設(shè)計(jì)方法的正確性。
[Abstract]:With the development of science and technology, more and more occasions need the transmission mechanism to realize the variable transmission ratio transmission. For example, the speed of automatic paper feeding mechanism is constantly changing in the working process. The non-circular gear transmission mechanism is the most commonly used variable transmission ratio transmission mechanism in order to obtain the specific pattern fabric. However, the non-circular gear drive is only suitable for the case where the center distance is small. Based on the above situation, a three-wheeled non-circular synchronous belt transmission mechanism is proposed in this paper. In this paper, the algorithm of calculating the curve of non-circular tensioning synchronous belt wheel is given. A numerical method of calculating the correct transmission relation of tension wheel is presented, which only needs to know the data point of the curve of non-circular node, and the method of searching for the correct transmission relation of tension wheel is put forward. The method of tooth profile envelope of walking belt wheel and the method of tooth profile envelope of synchronous belt wheel with non-circular joint curve are presented. The main work of this paper is as follows: (1) aiming at the problem that the transmission process of two-wheel non-circular belt transmission mechanism can not realize real-time tension. A three-wheeled non-circular synchronous belt transmission mechanism is proposed, and the initial nodal curve of the non-circular tensioning synchronous belt wheel is obtained according to the transmission relationship. (2) the nodal curve equation of the tensioning wheel cannot be directly obtained in practical engineering calculation. Therefore, the analytical method can not be used to calculate the transmission relationship of the tensioning wheel. For this reason, a numerical calculation method, the search method, is proposed, which uses the cubic nonuniform B-spline and the transmission relation. Based on the conjugate meshing principle of gear transmission, a method for calculating the tooth profile of non-circular synchronous belt wheel is proposed. A more simple method for obtaining tooth profile points, the local quadrant method, is proposed. This paper provides a new idea for the tooth profile design of non-circular synchronous belt gear. (4) based on MATLAB, the parametric design platform of three-wheel non-circular synchronous belt transmission mechanism is developed. The optimal values of each parameter and the optimal nodal curve of non-circular tensioning synchronous belt wheel are obtained. According to the optimum parameters, the structure design of the three-wheeled non-circular synchronous belt driving mechanism test rig is carried out, and the experimental results are compared with the theoretical calculation results. It is found that the experimental results are in good agreement with the theoretical calculation results, which proves the rationality of the three-wheeled non-circular synchronous belt transmission mechanism, the correctness of the curve of the non-circular tensioning synchronous belt wheel joint and the correctness of the design method of the tooth profile.
【學(xué)位授予單位】：浙江理工大學(xué)
【學(xué)位級(jí)別】：碩士
【學(xué)位授予年份】：2017
【分類號(hào)】：TH132.32

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