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  本文選題：偏置正交面齒輪 + 齒面生成��； 參考：《華南理工大學》2011年碩士論文

【摘要】：面齒輪傳動是一種新型齒輪傳動技術(shù),已經(jīng)在低速輕載傳動系統(tǒng)中得到了廣泛應(yīng)用,并在高速重載的航空航天傳動系統(tǒng)中得到了成功應(yīng)用。面齒輪的齒面形狀非常復(fù)雜,在加工過程中會出現(xiàn)兩種現(xiàn)象:第一種是在輪齒內(nèi)徑處容易產(chǎn)生根切;第二種是在輪齒外徑處會產(chǎn)生齒頂變尖。這樣使得面齒輪的齒寬受到一定的限制,影響其承載能力。此外,面齒輪傳動是一種點接觸傳動,傳統(tǒng)的齒輪強度校核理論已經(jīng)不適用于面齒輪的應(yīng)力分析。有限元法則沒有這個限制,它能計算出輪齒上各處的應(yīng)力和應(yīng)變的變化情況,在面齒輪的應(yīng)力分析中表現(xiàn)出極大的優(yōu)越性。 本文首先建立了偏置正交面齒輪的加工坐標系�；邶X輪嚙合原理,由刀具齒面方程推導出偏置正交面齒輪的齒面方程,計算了偏置正交面齒輪不產(chǎn)生根切和齒頂不變尖的條件,并推導出了偏置正交面齒輪齒面的齒根過渡曲面方程,實現(xiàn)了偏置正交面齒輪齒面的可視化。 然后,在Pro/E軟件中實現(xiàn)了直齒圓柱齒輪的參數(shù)化建模,基于偏置正交面齒輪的齒面方程,對偏置正交面齒輪進行了實體建模,并對偏置正交面齒輪傳動進行了運動仿真分析,檢查傳動模型是否存在體積干涉,且對偏置正交面齒輪進行了壓鑄模設(shè)計。接著,簡單介紹了確定齒輪危險截面位置的幾種常用方法,運用內(nèi)切拋物線法導出了偏置正交面齒輪的危險截面位置的計算方法,并通過實例計算得到偏置正交面齒輪承受最大彎曲應(yīng)力的位置均在齒面中部的結(jié)果。 最后,運用CAE分析軟件ANSYS對直齒圓柱齒輪和偏置正交面齒輪進行了靜態(tài)彎曲應(yīng)力分析。直齒圓柱齒輪的CAE分析結(jié)果表明:在集中載荷作用下,直齒圓柱齒輪承受最大彎曲應(yīng)力的位置均在齒根處;當集中載荷向兩端移動時,直齒圓柱齒輪承受的彎曲應(yīng)力逐漸變大;齒寬越長,直齒圓柱齒輪的抗彎曲性能越好。偏置正交面齒輪的CAE分析結(jié)果表明:在集中載荷作用下,偏置正交面齒輪承受最大彎曲應(yīng)力的位置均在齒面中部;當集中載荷向兩端移動時,偏置正交面齒輪承受的彎曲應(yīng)力逐漸變大;齒寬越長,偏置正交面齒輪的抗彎曲性能越好。
[Abstract]:Surface gear transmission is a new type of gear transmission technology, which has been widely used in low speed light load transmission system, and has been successfully applied in high speed and heavy load aerospace transmission system. The tooth surface shape of the face gear is very complicated and there are two kinds of phenomena in the machining process: the first is the root cutting is easy to be produced at the inner diameter of the gear tooth, and the second is that the top tooth tip will be sharpened at the outer diameter of the gear tooth. In this way, the tooth width of the face gear is limited and its bearing capacity is affected. In addition, the surface gear transmission is a point contact transmission, and the traditional theory of gear strength checking is not suitable for the stress analysis of the face gear. The finite element method has no such limitation. It can calculate the variation of stress and strain everywhere on the gear tooth, and it shows great superiority in the stress analysis of the face gear. In this paper, the machining coordinate system of offset orthogonal face gear is established. Based on the gear meshing principle, the tooth surface equation of the offset orthogonal face gear is derived from the cutter tooth surface equation, and the condition that the offset orthogonal face gear does not produce the root cutting and the tooth top invariant tip is calculated. The equation of tooth root transition surface of offset orthogonal face gear tooth surface is deduced, and the visualization of offset orthogonal face gear tooth surface is realized. Then, the parametric modeling of spur gear is realized in Pro/E software. Based on the tooth surface equation of offset orthogonal face gear, the solid modeling of offset orthogonal face gear is carried out, and the kinematic simulation analysis of offset orthogonal face gear transmission is carried out. Check whether there is volume interference in transmission model and design die casting die for offset orthogonal face gear. Then, several common methods to determine the dangerous section position of gear are introduced, and the calculation method of dangerous section position of offset orthogonal face gear is derived by using the internal tangent parabola method. The results show that the maximum bending stress of the offset orthogonal face gear is in the middle of the tooth surface. Finally, the static bending stress of spur gear and offset orthogonal face gear are analyzed by CAE software ANSYS. The CAE analysis results of spur gear show that the position of maximum bending stress of spur gear is at the root of tooth under the action of concentrated load, and the bending stress of spur gear increases gradually when the concentrated load moves to both ends. The longer the tooth width, the better the bending resistance of spur gear. The results of CAE analysis of offset orthogonal face gear show that the position of maximum bending stress of offset orthogonal face gear is in the middle of tooth surface under the action of concentrated load, and when the concentrated load moves to both ends of gear, the position of maximal bending stress of offset orthogonal face gear is in the middle of tooth surface. The bending stress of the offset orthogonal gear increases gradually, and the longer the tooth width, the better the bending resistance of the offset orthogonal face gear.
【學位授予單位】：華南理工大學
【學位級別】：碩士
【學位授予年份】：2011
【分類號】：TH132.41

【引證文獻】

相關(guān)碩士學位論文 前1條

1 張會會;非正交面齒輪傳動設(shè)計研究[D];山東大學;2012年

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本文編號：1933158