發(fā)布時(shí)間：2018-03-30 09:27

  本文選題：直齒錐齒輪　切入點(diǎn)：實(shí)體建模　出處：《濟(jì)南大學(xué)》2011年碩士論文

【摘要】：差速器作為汽車的關(guān)鍵部件對(duì)其各項(xiàng)性能都有重要影響,而齒輪傳動(dòng)系統(tǒng)是差速器的主要組成部分,因此齒輪傳動(dòng)的工作性能將直接影響汽車的性能指標(biāo)。本文圍繞差速器齒輪傳動(dòng)系統(tǒng)減振、降噪以及輪齒應(yīng)力分布改善為目的,采用有限元?jiǎng)討B(tài)嚙合仿真的方法,研究了漸開線直齒錐齒輪修形(包括齒向修形和齒廓修形)技術(shù)。 直齒錐齒輪漸開線不同于圓柱齒輪的平面漸開線,為空間球面漸開線。由于空間球面漸開線復(fù)雜的空間結(jié)構(gòu),使其建模在CAD軟件里難以直接實(shí)現(xiàn),在進(jìn)行直齒錐齒輪嚙合傳動(dòng)分析時(shí)常采用圓弧曲線、背錐平面漸開線近似代替,因此將不可避免的產(chǎn)生建模誤差,從而影響齒輪仿真分析結(jié)果的準(zhǔn)確度。針對(duì)這一問題,本文運(yùn)用Matlab和SolidWorks聯(lián)合建模的方法實(shí)現(xiàn)了直齒錐齒輪的精確造型。模型是通過參數(shù)化程序建立起來的,因此只需修改尺寸參數(shù),如壓力角、齒數(shù)、模數(shù)、球面半徑等,就可以得到不同參數(shù)的類似錐齒輪模型。建模效率和模型精度得到提高,而且方便模型的修改。 本文提出基于SolidWorks-ANSYS-LS-DYNA聯(lián)合建模求解技術(shù),詳細(xì)介紹了錐齒輪動(dòng)態(tài)仿真分析有限元模型的建立過程,給出了動(dòng)態(tài)嚙合仿真的約束及邊界條件的施加方法。采用LS-PREPOST后處理器提取嚙合應(yīng)力、加速度等仿真信息,該方法可提供以滿足提高齒輪副工作性能為目標(biāo)的修形設(shè)計(jì)方法依據(jù)。 齒輪輪齒的變形以及制造、安裝誤差的存在,使嚙合過程中輪齒的法節(jié)不再相等,從而造成輪齒嚙合的振動(dòng)和沖擊,因此,必須對(duì)輪齒進(jìn)行齒廓修形。本文給出了齒廓修形的方法,經(jīng)仿真分析得到齒廓修形錐齒輪嚙合傳動(dòng)的時(shí)間歷程信息。齒廓修形可以很好的改善輪齒嚙合的沖擊,從而起到減振、降噪的作用。輪齒的端嚙現(xiàn)象說明齒向修形的必要性,錐齒輪齒向修形時(shí),鼓形齒的鼓形量、鼓形位置難以調(diào)整,且其工藝很難實(shí)現(xiàn),限制了修形技術(shù)在錐齒輪上的應(yīng)用,本文提出齒向等距修形的概念,通過改變等距修形廓形的位置和修形量的大小來控制錐齒輪副的接觸區(qū)。該方法同通過調(diào)整機(jī)床獲得的齒形鼓形的方法相比,既方便得到理想的修形位置,又可得到理想的修形量,為得到滿足不同類型、精度、工況條件下的修形齒形,提供了方便、可行的途徑。
[Abstract]:As the key component of the automobile, the differential gear transmission system is the main component of the differential gear transmission system, so the performance of the gear transmission will directly affect the performance index of the automobile.The involute of straight bevel gear is different from the planar involute of cylindrical gear and is a space spherical involute.Because of the complex space structure of the involute of the space sphere, it is difficult to realize the modeling in the CAD software directly. In the analysis of the meshing transmission of the straight bevel gear, the arc curve is often used, and the involute of the back cone plane is approximately replaced by the involute of the back cone plane.Therefore, modeling errors will inevitably occur, which will affect the accuracy of gear simulation analysis.The model is built by parameterization program, so the similar bevel gear model with different parameters can be obtained by modifying the dimension parameters, such as pressure angle, tooth number, modulus, spherical radius, etc.The efficiency and precision of the model are improved, and the modification of the model is convenient.In this paper, a joint modeling and solving technique based on SolidWorks-ANSYS-LS-DYNA is proposed. The establishment of finite element model for dynamic simulation analysis of bevel gears is introduced in detail. The constraint of dynamic meshing simulation and the method of applying boundary conditions are given.The deformation, manufacture and installation errors of gear teeth make the normal joints of gear teeth no longer equal in the course of meshing, resulting in the vibration and impact of gear teeth meshing. Therefore, tooth profile modification must be carried out.In this paper, the method of tooth profile modification is given, and the time history information of tooth profile modification bevel gear meshing transmission is obtained by simulation analysis.Tooth profile modification can improve the impact of gear meshing, so as to reduce vibration and noise.The phenomenon of end gnawing of gear tooth shows the necessity of tooth modification. When bevel gear tooth profile is modified, it is difficult to adjust the drum shape and position of drum tooth, and its technology is difficult to realize, which limits the application of shape modification technology in bevel gear.In this paper, the concept of tooth offset modification is proposed, and the contact area of bevel gear pair is controlled by changing the position of equidistant modification profile and the size of modification.Compared with the method of adjusting the tooth shape and drum shape obtained by the machine tool, this method can not only obtain the ideal modification position but also obtain the ideal modification quantity, which provides convenience for obtaining the tooth shape modification under different types, accuracy and working conditions.A viable path.
【學(xué)位授予單位】：濟(jì)南大學(xué)
【學(xué)位級(jí)別】：碩士
【學(xué)位授予年份】：2011
【分類號(hào)】：TH132.41

【參考文獻(xiàn)】

相關(guān)期刊論文 前10條

1 汪強(qiáng) ,周錦進(jìn);齒輪修形技術(shù)及工藝的發(fā)展[J];電加工與模具;2001年05期

2 金俊松;夏巨諶;胡國安;王新云;陳霞;李大才;胡明發(fā);;轎車圓錐齒輪閉式冷精鍛凹模的優(yōu)化設(shè)計(jì)[J];鍛壓技術(shù);2006年03期

3 崔煥勇,舒其馥,付志剛;直齒圓錐齒輪精鍛模電極齒輪的化銑修形技術(shù)[J];鍛壓裝備與制造技術(shù);2003年04期

4 何常青,夏巨諶,王新云,胡國安,吳忠鳴,陳霞;轎車直齒圓錐齒輪冷精鍛試驗(yàn)研究[J];鍛壓裝備與制造技術(shù);2005年02期

5 唐增寶,鐘毅芳,周建榮;直齒圓柱齒輪傳動(dòng)系統(tǒng)的振動(dòng)分析計(jì)算[J];華中理工大學(xué)學(xué)報(bào);1993年04期

6 唐增寶，，鐘毅芳，陳久榮;修形齒輪的最佳修形量和修形長度的確定[J];華中理工大學(xué)學(xué)報(bào)(社會(huì)科學(xué)版);1995年02期

7 唐增寶，陳久榮;齒輪動(dòng)態(tài)性能最佳的齒廓修形曲線和參數(shù)[J];華中理工大學(xué)學(xué)報(bào);1995年11期

8 楊生華;齒輪接觸有限元分析[J];計(jì)算力學(xué)學(xué)報(bào);2003年02期

9 宋樂民;;漸開線鼓形齒的鼓形量[J];齒輪;1981年02期

10 楊廷力;葉新;王玉璞;錢臬鶴;;漸開線高速齒輪的齒高修形(一)[J];齒輪;1982年03期

相關(guān)博士學(xué)位論文 前1條

1 陳霞;直齒錐齒輪修形方法研究[D];華中科技大學(xué);2006年

相關(guān)碩士學(xué)位論文 前1條

1 田希杰;精鍛直齒錐齒輪齒形修形設(shè)計(jì)技術(shù)研究[D];山東大學(xué);2009年

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