545 橡膠履帶牽引車輛改進(jìn)設(shè)計(jì)（機(jī)械雙功率流轉(zhuǎn)向裝置）（有cad圖）

545 橡膠履帶牽引車輛改進(jìn)設(shè)計(jì)（機(jī)械雙功率流轉(zhuǎn)向裝置）（有cad圖）,545,橡膠履帶牽引車輛改進(jìn)設(shè)計(jì)（機(jī)械雙功率流轉(zhuǎn)向裝置）（有cad圖）,橡膠,履帶,牽引,車輛,改進(jìn),改良,設(shè)計(jì),機(jī)械,功率,流轉(zhuǎn),裝置,cad 橡膠履帶牽引車輛改進(jìn)設(shè)計(jì) （機(jī)械雙功率流轉(zhuǎn)向裝置） 摘 要 隨著科學(xué)技術(shù)發(fā)展的日新月異，農(nóng)業(yè)技術(shù)也在不斷進(jìn)步。為了滿足農(nóng)業(yè)生產(chǎn)的需要，農(nóng)業(yè)機(jī)械功率逐漸增大，于是，功率大、功能強(qiáng)且可以適應(yīng)現(xiàn)代發(fā)達(dá)的公路交通的橡膠履帶式逐漸產(chǎn)生并投入使用。 履帶式車輛的轉(zhuǎn)向機(jī)構(gòu)同一般車輛有著很大區(qū)別，其技術(shù)的發(fā)展也經(jīng)歷了一個(gè)很長的過程。雙功率流轉(zhuǎn)向裝置是相對于單功率流而言的。它除由發(fā)動機(jī)到側(cè)傳動的直駛變速功率流外，還可以分出另一路轉(zhuǎn)向功率流，專門用于造成兩側(cè)輸出轉(zhuǎn)向速度差。這種分直駛轉(zhuǎn)向兩流傳遞功率的履帶車輛傳動系，稱為雙功率傳動。同傳統(tǒng)單功率流傳動機(jī)構(gòu)相比，雙功率流傳動是一個(gè)新的發(fā)展趨勢。機(jī)械雙功率流轉(zhuǎn)向裝置能夠?qū)崿F(xiàn)低擋轉(zhuǎn)向半徑小，高擋轉(zhuǎn)向半徑大的車輛行駛需求；并且可以減少單功率流中過多使用的滑摩工況，減小轉(zhuǎn)向時(shí)能耗；最后，雙流傳動空擋是可以實(shí)現(xiàn)一側(cè)履帶向前、另一側(cè)履帶向后運(yùn)動的原位中心轉(zhuǎn)向。 雙功率流傳動已經(jīng)在現(xiàn)代履帶式車輛上普遍采用，并且隨著液壓技術(shù)的發(fā)展，液壓機(jī)械雙功率流傳動成為一個(gè)新的發(fā)展方向。但機(jī)械雙功率流傳動在履帶車輛的發(fā)展過程中仍是不可或缺的，它是雙功率流傳動發(fā)展過程的基礎(chǔ)階段，其地位是無法取代的。 關(guān)鍵詞：履帶，雙功率流，轉(zhuǎn)向，液壓 RUBBER TRACK TRACTOR IMPROVE DESIGN (MECHANICAL DOUBLE POWER TRANSFER DEVICE) ABSTRACT Along with the development of science and technology changing, agricultural technology has been steadily progressing. To meet the needs of agricultural production, agricultural machinery power is gradually increasing, therefore, power, strong function and can adapt to the modern developed highway traffic rubber crawler gradually produced and put into use. Crawler vehicle's steering bodies and vehicles have great differences, the development of technology has also gone through a very long process. Power-flow device is for single-phase power flow speaking. Apart from its engine to the drive side of the straight ahead speed power flow, we can also set aside another road to power flow, both devoted to the cause output to the speed difference. This appeared to 2 pm flow transfer power transmission system tracked vehicle, known as the dual-power transmission. With the traditional single-power spread Mechanism, the two-power dynamic is a popular new trend of development. Double transfer power to the device to achieve low-block radius to small, high-block radius to large traffic demand; and can reduce the power flow single excessive use of the sliding friction conditions, to reduce energy consumption when; Finally, Shuangliu transmission in neutral gear can be achieved side track forward, the other side of the track backward movement to the center in situ. Double Power has already spread in the modern crawler vehicles generally used, and with the development of hydraulic technology, Hydraulic machinery-power spread to become a dynamic new direction of development. But mechanical power spread-tracked vehicles move in the development process is essential. It is a two-power process of the development and spread of the foundation stage, the status is irreplaceable. KEY WORD：Crawler, double power ，steering, hydraulic 符 號 說 明 P 功率, kW n 轉(zhuǎn)速，n·min-1 T 扭矩，N·m v 線速度，m/s Ft 齒輪所受切向力，N Fr 齒輪所受徑向力，N Fa 齒輪所受軸向力，N 齒輪傳動效率 行星輪系傳動效率 離合器效率 d 齒輪分度圓直徑，mm a 齒輪中心矩，mm m 齒輪模數(shù)，mm z 齒輪齒數(shù) mn 端面模數(shù)，mm 齒輪螺旋角，o 齒輪壓力角，o b 齒寬，mm R 車輛轉(zhuǎn)彎半徑，m M 彎矩，N·m 目 錄 第一章 緒論（或引言或前言）..............................1 第二章 方案分析......................................1 §2.1機(jī)械雙功率流傳動基本原理........................2 §2.2機(jī)械雙功率流傳動分類............................2 §2.3 確定方案........................................3 第三章 圓柱斜齒輪設(shè)計(jì)................................4 §3.1設(shè)計(jì)前預(yù)定參數(shù)值...........................4 §3.2確定傳動比.................................4 §3.3 選擇材料，確定試驗(yàn)齒輪的疲勞極限................5 §3.4按接觸強(qiáng)度初步確定中心距，并初選主要參數(shù).........5 §3.5 校核齒面接觸強(qiáng)度...............................6 §3.6 校核齒根彎曲強(qiáng)度................................8 §3.7 主要幾何尺寸...................................9 第四章 錐齒輪的設(shè)計(jì)....................................10 §4.1 選擇齒輪的材料、齒數(shù)、分錐角等.................10 §4.2 按齒面接觸強(qiáng)度設(shè)計(jì).............................10 §4.3 接觸強(qiáng)度校核...................................12 §4.4 彎曲強(qiáng)度校核...................................13 第五章 圓柱直齒輪......................................15 §5.1 選擇材料確定試驗(yàn)齒輪的極限應(yīng)力.................15 §5.2 按接觸強(qiáng)度計(jì)算小齒輪直徑.......................15 §5.3 校核齒面接觸強(qiáng)度..............................16 §5.4 計(jì)算安全系數(shù)...................................17 §5.5 修正中心距.....................................17 第六章 行星輪系設(shè)計(jì)....................................19 §6.1 初定主要參數(shù)...................................19 §6.2按接觸強(qiáng)度初算a-c傳動的中心距和模數(shù)............19 §6.3 計(jì)算a-c傳動的實(shí)際中心距變動系數(shù)...............20 §6.4 計(jì)算a-c傳動變位系數(shù)...........................20 §6.5 計(jì)算c-b傳動的中心變位系數(shù)和嚙合角...........21 §6.6 計(jì)算c-b傳動變位系數(shù)...........................21 §6.7 幾何尺寸計(jì)算...................................21 第七章 軸的設(shè)計(jì)......................................22 §7.1 選擇材料.......................................22 §7.2 初步確定軸端直徑...............................22 §7.3 鍵的強(qiáng)度校核...................................22 §7.4 計(jì)算支撐反力...................................22 §7.5 校核軸的疲勞強(qiáng)度...............................23 §7.6 軸的靜強(qiáng)度校核.................................26 第八章 結(jié) 論...........................................27 參考文獻(xiàn)...............................................28 致謝...................................................29 VI