【正文】 致謝影響著每個學生的畢業(yè)，對我們極為重要的畢業(yè)設計終于完成了。 the two angles are equal for a 90deg. Shaft angle.When gears are to be used to transmit motion between intersecting shaft, some of bevel gear is required. Although bevel gear are usually made for a shaft angle of 90 deg. They may be produced for almost any shaft angle. The teeth may be cast, milled, or generated. Only the generated teeth may be classed as accurate. In a typical bevel gear mounting, one of the gear is often mounted outboard of the bearing. This means that shaft deflection can be more pronounced and have a greater effect on the contact of teeth. Another difficulty, which occurs in predicting the stress in bevelgear teeth, is the fact the teeth are tapered. Straight bevel gears are easy to design and simple to manufacture and give very good results in service if they are mounted accurately and positively. As in the case of squr gears, however, they bee noisy at higher values of the pitchline velocity. In these cases it is often good design practice to go to the spiral bevel gear, which is the bevel counterpart of the helical gear. As in the case of helical gears, spiral bevel gears give a much smoother tooth action than straight bevel gears, and hence are useful where high speed are encountered. It is frequently desirable, as in the case of automotive differential applications, to have gearing similar to bevel gears but with the shaft offset. Such gears are called hypoid gears because their pitch surfaces are hyperboloids of revolution. The tooth action between such gears is a bination of rolling and sliding along a straight line and has much in mon with that of worm gears.A shaft is a rotating or stationary member, usually of circular cross section, having mounted upon it such elementsas gears, pulleys, flywheels, cranks, sprockets, and other powertransmission elements. Shaft may be subjected to bending, tension, pression, or torsional loads, acting singly or in bination with one another. When they are bined, one may expect to find both static and fatigue strength to be important design considerations, since a single shaft may be subjected to static stresses, pletely reversed, and repeated stresses, all acting at the same time.The word “shaft” covers numerous variations, such as axles and spindles. Anaxle is a shaft, wither stationary or rotating, nor subjected to torsion load. A shirt rotating shaft is often called a spindle.When either the lateral or the torsional deflection of a shaft must be held to close limits, the shaft must be sized on the basis of deflection before analyzing the stresses. The reason for this is that, if the shaft is made stiff enough so that the deflection is not too large, it is probable that the resulting stresses will be safe. But by no means should the designer assume that they are safe。參考文獻[1] 李占權，李白寧，[J]. 煤礦機械,200011.[2] 王太晨 .，1995.[3] ，20097.[4] ，1996.[5] 孫桓，陳作模，（第七版）.高等教育出版社，20065.[6] [J].無錫職業(yè)技術學院學報，20053.[7] （第四版）.高等教育出版社，1997.[8] 劉海霞，王泉祥，2010.[9] 彭定，江熒，20065.[10] ，20079.[11] ，19996.[12] ：國防工業(yè)出版社，1994.外文翻譯英文原文：GEAR AND SHAFT INTRODUCTIONAbstract: The important position of the wheel gear and shaft cant falter in traditional machine and modern wheel gear and shafts mainly install the direction that delivers the dint at the principal axis passing to process to make them can is divided into many model numbers, useding for many situations we must be the multilayers to the understanding of the wheel gear and shaft in many ways .Key words: Wheel gear。在查閱了大量資料后，確定了此課題的主要設計依據和內容。綜上所述，各表面以及孔加工余量和工序尺寸如表442。根據“先面后孔”“先粗后精”的原則，應把銑平面放在鏜孔鉆孔之前，特別是重要表面的粗加工，更應該排在前面，以便及時發(fā)現(xiàn)原料缺陷和防止浪費次要表面的加工工時。HT200材料適合用鑄造獲得毛坯。轉矩作用時的安全因數(shù) 式()式中——45鋼扭轉疲勞極限，由前知=155MPa ——切應力幅, 查參考文獻得抗扭截面系數(shù)——平均切應力，——扭剪有效應力集中因數(shù)，按配合（H7/r6）查得=——表面質量因數(shù)，軸徑車削加工，按參考文獻查得=——尺寸因數(shù)，按參考文獻查得 =——材料扭轉時的平均應力折算因數(shù)，按參考文獻[2]=c. 截面D的疲勞強度安全因數(shù) 式()由參考文獻知, ，S該軸截面D的疲勞強度足夠。代入參考文獻[1]公式（）計算內齒輪e的輪齒彎曲應力，即 式 ()可得，；取和。帶入公式（），則得所以 再按參考文獻[12]公式（）計算大齒輪g 的齒輪彎曲應力，即 式（）仿上，據，由參考文獻[12]圖71和參考文獻[12]圖72可查得，則由參考文獻[1]表77得，；同理，和?，F(xiàn)將該3K型傳動按照三個齒輪副ag、bg和ef分別驗算如下： ag 齒輪副先按參考文獻[12]公式（）計算小齒輪a的齒輪彎曲應力，即 式（）已求得小齒輪傳遞的轉矩 為 式（）載荷系數(shù)K可按參考文獻[12]公式（）求得: K=。但是，隨著其傳動比的增大，當e輪輸入而進行逆運轉時，該行星減速器將會產生自鎖。由參考文獻[12]表77初步選取D=470N/mm2。圖21 3K 型行星齒輪減速器結構示意圖 根據給定的傳動比確定各輪的齒數(shù)根據已給定的傳動比i=210，且選取行星輪數(shù)目=3。適用于任何工況下大小率的傳動，工作制度不限。對通用減速器而言，除了普遍采用硬齒面技術外，模塊化設計技術已成為其發(fā)展的一個主要方向。行星齒輪傳動的缺點是： 材料優(yōu)質、結構復雜、制造和安裝較困難?？傊?，行星齒輪傳動具有質量小，體積小，傳動比及效率高的優(yōu)點。因此，努力提高各類減速器的設計制造水品，更好的滿足各類用戶的廣泛需求，仍是廣大齒輪工作者的長期任務。通用減速器由于實現(xiàn)了系列化和標準化，具有便于組織專業(yè)化生產，容易形成批量和規(guī)模生產，有利于提高產品的生產水品和質量，降低設計和制造成本，縮短供貨周期，容易獲得備件，便于維修等許多優(yōu)點，而成為一般用戶的首選產品。對行星齒輪減速器傳動機構的基本參數(shù)和尺寸進行了選擇和計算。在查閱了大量關于行星齒輪減速器設計的資料和參考了某公司生產的3K 型行星齒輪減速器后，確定了此行星齒輪減速器的設計方案。只有在特殊用途或選不到合適的產品時才考慮設計和選用專用減速器。 行星齒輪傳動的特點：（1）體積小，質量小，結構緊湊，承載能力大。因此，行星齒輪傳動現(xiàn)已廣泛應用于工程機械，冶金機械，起重運輸機械，礦山機械，輕工機械，石油化工機械，機床，機器人，汽車，輪船儀表和儀器等各個方面，行星傳動不僅適用于高轉速，大功率，而且在低速大轉矩的傳動裝置上也已經獲得了應用。 齒輪減速器的現(xiàn)狀及發(fā)展趨勢20世紀70年代末以來，世界減速器技術有了很大發(fā)展。它旨在追求高性能的同時，盡可能的減少零件及毛胚的各種規(guī)格和數(shù)量，以便于組織生產，形成批量，降低成本，獲得規(guī)模效益?？勺鳛闇p速，增速及差速裝置。查參考文獻[1]表64得各輪齒數(shù)=18, =198, =189, =90, =81其傳動比為i=210,其傳動比誤差 為 式()故滿足傳動比誤差要求。初選b*=2。由自鎖條件； 式（）可得； 由此可見，當3K型行星傳動的傳動比時，其逆運動才可能產生自鎖。由參考文獻[1]=；再由參考文獻[12]公式（）得 式（） 式中 式（）按 8 級精度和 值由參考文獻[12]表73 查得動載荷系數(shù)，取。因行星齒輪g為承受雙向對稱載荷的齒輪。同理。 軸的靜強度安全因數(shù)校核計算確定危險截面，根據載荷較大，截面較小，選取D截面進行靜強度校合a. 彎矩作用時的安全因數(shù) 式()式中s ——45鋼材料正應力屈服點，由參考文獻查得=