發(fā)布時(shí)間：2018-07-18 09:34

【摘要】：齒輪傳動(dòng)系統(tǒng)應(yīng)用于工業(yè)和生活的各個(gè)領(lǐng)域,是機(jī)械傳動(dòng)方式中的重要傳動(dòng)方式之一。在鐵路領(lǐng)域,隨著高鐵的高速發(fā)展,列車速度的提高對(duì)其中的齒輪傳動(dòng)的平穩(wěn)性的要求很高,對(duì)齒輪的強(qiáng)度要求和其壽命要求嚴(yán)格。我國(guó)的高鐵有一定的自主研發(fā)技術(shù),然而面對(duì)高速工作條件,如何進(jìn)行精確的齒輪修設(shè)計(jì),提高高鐵齒輪的傳動(dòng)精度,提高承載能力、減小齒面接觸力和延長(zhǎng)壽命成為高鐵領(lǐng)域難點(diǎn)之一,而高鐵齒輪箱在高速工況下工作,對(duì)結(jié)構(gòu)的疲勞強(qiáng)度要求嚴(yán)格,所以對(duì)高鐵齒輪箱的結(jié)構(gòu)優(yōu)化的意義同樣重大。本文結(jié)合大連理工大學(xué)和南車戚墅堰所合作申請(qǐng)的國(guó)家支撐計(jì)劃,提出一套針對(duì)高鐵斜齒輪的齒廓修形設(shè)計(jì)方法,通過(guò)理論和仿真相結(jié)合方法進(jìn)行齒廓修形參數(shù)計(jì)算,用動(dòng)態(tài)仿真軟件DYNA對(duì)設(shè)計(jì)結(jié)果進(jìn)行驗(yàn)算認(rèn)證,證明本設(shè)計(jì)的精準(zhǔn)性和科學(xué)性,最后對(duì)高鐵齒輪箱進(jìn)行結(jié)構(gòu)優(yōu)化設(shè)計(jì),對(duì)高鐵齒輪和箱體的設(shè)計(jì)制造意義較大。具體內(nèi)容如下： 首先對(duì)斜齒輪進(jìn)行模型建立和接觸有限元分析,計(jì)算了斜齒輪的安全系數(shù),并驗(yàn)證齒輪的在四中工況下的接觸強(qiáng)度安全系數(shù)和彎曲安全系數(shù)都達(dá)到高可靠度要求,根據(jù)分析需要對(duì)齒輪進(jìn)行修形。介紹了齒輪嚙合沖擊的原因和齒廓修形三要素的概念,利用理論和有限元相結(jié)合的方法計(jì)算出啟動(dòng)工況下齒廓修緣量,以及修形長(zhǎng)度和修形曲線起始圓半徑,并通過(guò)MATALAB軟件設(shè)計(jì)出齒廓修形曲線。根據(jù)修形曲線在UG中建立了修形齒輪模型。并用ANSYS/LS-DYNA有限元工具對(duì)修形齒輪進(jìn)行嚙合動(dòng)態(tài)仿真,分析齒廓修形三要素對(duì)齒面接觸力的影響。得出了二次和正弦曲線修形的齒面接觸力大小和嚙入嚙出沖擊較小,修形效果較好；當(dāng)齒頂修形量為0.027mm,頂修形長(zhǎng)度為3.5mm時(shí),最大接觸力為6865N,比未修形齒輪減小30.0%；并通過(guò)計(jì)算得到主被動(dòng)輪齒頂同時(shí)修形方式效果差于主動(dòng)輪齒頂和齒根同時(shí)修形方式。這對(duì)高鐵動(dòng)車組傳動(dòng)齒輪箱設(shè)計(jì)有一定的意義。 最后通過(guò)對(duì)整體齒輪箱進(jìn)行動(dòng)力學(xué)分析,得到齒輪箱的十階振型和固有頻率,以及在各階固有頻率下齒輪箱各零件的變形,并進(jìn)一步對(duì)齒輪箱外殼進(jìn)行動(dòng)力學(xué)分析,通過(guò)分析結(jié)果對(duì)齒輪箱外殼進(jìn)行結(jié)構(gòu)改進(jìn)設(shè)計(jì),最后對(duì)改進(jìn)后的結(jié)構(gòu)進(jìn)行動(dòng)力學(xué)分析,結(jié)果表明變形量比改進(jìn)前的模型減少,證明了優(yōu)化方案的科學(xué)性。
[Abstract]:Gear transmission system is one of the important transmission modes in mechanical transmission, which is applied in various fields of industry and life. In the field of railway, with the rapid development of high-speed railway, the improvement of train speed requires the smoothness of gear transmission, and the strength and lifetime of gear are strictly required. The high-speed railway in our country has certain independent R & D technology. However, in the face of high-speed working conditions, how to carry out the precise gear repair design, improve the transmission accuracy of the high-speed gear, and improve the bearing capacity, Reducing tooth contact force and prolonging service life have become one of the difficulties in high-speed rail field, and the high speed gearbox working at high speed condition requires the fatigue strength of the structure strictly, so it is also important to optimize the structure of high-speed rail gear box. Combined with the national support plan applied by Dalian University of Technology and Nanqichuan Qishuyan Institute, this paper presents a design method of tooth profile modification for high speed helical gears, and calculates the tooth profile modification parameters by combining theory with simulation. The dynamic simulation software DYNA is used to verify the design results, which proves that the design is accurate and scientific. Finally, the structure optimization design of high speed gear box is carried out, which is of great significance to the design and manufacture of high speed gear and box. The main contents are as follows: firstly, the safety factor of helical gear is calculated by modeling and contact finite element analysis. It is verified that the contact strength safety coefficient and bending safety factor of gear under four medium working conditions meet the requirements of high reliability, and the gear profile is modified according to the need of analysis. This paper introduces the reason of gear meshing impact and the concept of three elements of tooth profile modification. By using the method of combination of theory and finite element method, the tooth profile modification margin, the modification length and the starting circle radius of the modification curve are calculated under the starting condition. The tooth profile modification curve is designed by MATLAB software. According to the modification curve, the modified gear model is established in UG. The meshing dynamic simulation of modified gear is carried out with ANSYS / LS-DYNA finite element tool, and the influence of three elements of tooth profile modification on tooth surface contact force is analyzed. The results show that the tooth surface contact force of quadratic and sinusoidal curve modification is small and the effect is better when the tooth top modification is 0.027 mm and the top modification length is 3.5mm, the maximum contact force is 6865 Ns, which is 30.0 less than that of unmodified gear. The results show that the effect of simultaneous modification of active and passive gear top is worse than that of active gear top and tooth root simultaneously. This is of significance to the design of transmission gearbox of high speed EMU. Finally, through the dynamic analysis of the whole gearbox, the tenth order vibration mode and natural frequency of the gearbox and the deformation of the parts of the gearbox under each order natural frequency are obtained, and the dynamic analysis of the gearbox shell is carried out. The structural improvement design of the gear box shell is carried out by the analysis results, and the dynamic analysis of the improved structure is carried out at last. The result shows that the deformation is less than the model before the improvement, which proves the scientific nature of the optimized scheme.
【學(xué)位授予單位】：大連理工大學(xué)
【學(xué)位級(jí)別】：碩士
【學(xué)位授予年份】：2012
【分類號(hào)】：TH132.41

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