545 橡膠履帶牽引車輛改進設計（機械雙功率流轉向裝置）（有cad圖）

545 橡膠履帶牽引車輛改進設計（機械雙功率流轉向裝置）（有cad圖）,545,橡膠履帶牽引車輛改進設計（機械雙功率流轉向裝置）（有cad圖）,橡膠,履帶,牽引,車輛,改進,改良,設計,機械,功率,流轉,裝置,cad 橡膠履帶牽引車輛改進設計 （機械雙功率流轉向裝置） 摘 要 隨著科學技術發(fā)展的日新月異，農業(yè)技術也在不斷進步。為了滿足農業(yè)生產的需要，農業(yè)機械功率逐漸增大，于是，功率大、功能強且可以適應現代發(fā)達的公路交通的橡膠履帶式逐漸產生并投入使用。 履帶式車輛的轉向機構同一般車輛有著很大區(qū)別，其技術的發(fā)展也經歷了一個很長的過程。雙功率流轉向裝置是相對于單功率流而言的。它除由發(fā)動機到側傳動的直駛變速功率流外，還可以分出另一路轉向功率流，專門用于造成兩側輸出轉向速度差。這種分直駛轉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)單功率流傳動機構相比，雙功率流傳動是一個新的發(fā)展趨勢。機械雙功率流轉向裝置能夠實現低擋轉向半徑小，高擋轉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，減小轉向時能耗；最后，雙流傳動空擋是可以實現一側履帶向前、另一側履帶向后運動的原位中心轉向。 雙功率流傳動已經在現代履帶式車輛上普遍采用，并且隨著液壓技術的發(fā)展，液壓機械雙功率流傳動成為一個新的發(fā)展方向。但機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)展過程的基礎階段，其地位是無法取代的。 關鍵詞：履帶，雙功率流，轉向，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，mm z 齒輪齒數 mn 端面模數，mm 齒輪螺旋角，o 齒輪壓力角，o b 齒寬，mm R 車輛轉彎半徑，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機械雙功率流傳動基本原理........................2 §2.2機械雙功率流傳動分類............................2 §2.3 確定方案........................................3 第三章 圓柱斜齒輪設計................................4 §3.1設計前預定參數值...........................4 §3.2確定傳動比.................................4 §3.3 選擇材料，確定試驗齒輪的疲勞極限................5 §3.4按接觸強度初步確定中心距，并初選主要參數.........5 §3.5 校核齒面接觸強度...............................6 §3.6 校核齒根彎曲強度................................8 §3.7 主要幾何尺寸...................................9 第四章 錐齒輪的設計....................................10 §4.1 選擇齒輪的材料、齒數、分錐角等.................10 §4.2 按齒面接觸強度設計.............................10 §4.3 接觸強度校核...................................12 §4.4 彎曲強度校核...................................13 第五章 圓柱直齒輪......................................15 §5.1 選擇材料確定試驗齒輪的極限應力.................15 §5.2 按接觸強度計算小齒輪直徑.......................15 §5.3 校核齒面接觸強度..............................16 §5.4 計算安全系數...................................17 §5.5 修正中心距.....................................17 第六章 行星輪系設計....................................19 §6.1 初定主要參數...................................19 §6.2按接觸強度初算a-c傳動的中心距和模數............19 §6.3 計算a-c傳動的實際中心距變動系數...............20 §6.4 計算a-c傳動變位系數...........................20 §6.5 計算c-b傳動的中心變位系數和嚙合角...........21 §6.6 計算c-b傳動變位系數...........................21 §6.7 幾何尺寸計算...................................21 第七章 軸的設計......................................22 §7.1 選擇材料.......................................22 §7.2 初步確定軸端直徑...............................22 §7.3 鍵的強度校核...................................22 §7.4 計算支撐反力...................................22 §7.5 校核軸的疲勞強度...............................23 §7.6 軸的靜強度校核.................................26 第八章 結 論...........................................27 參考文獻...............................................28 致謝...................................................29 VI