本文選題：行星機(jī)構(gòu) + 齒輪計算�。� 參考：《吉林大學(xué)》2012年碩士論文

【摘要】：在市場需求發(fā)生重大變化的背景下，重型變速器產(chǎn)品副箱使用行星結(jié)構(gòu)已成為發(fā)展趨勢。為了順應(yīng)市場的發(fā)展這一形勢，我公司的行星機(jī)構(gòu)變速箱也在緊鑼密鼓的開發(fā)，適應(yīng)市場需求。行星齒輪機(jī)構(gòu)后副箱具有結(jié)構(gòu)緊湊、承載能力大、傳動效率高、傳動速比大、性能可靠等顯著的優(yōu)點(diǎn)，行星齒輪機(jī)構(gòu)后副箱作為重型商用車變速器重要的組成部分之一，承載能力大小，結(jié)構(gòu)設(shè)計是否合理都將直接影響變速器整體的可靠性。因此，對后副箱行星齒輪機(jī)構(gòu)的技術(shù)進(jìn)行深入研究，掌握行星機(jī)構(gòu)的設(shè)計及計算方法，，對提升公司產(chǎn)品的核心競爭力有重要的意義。 由于行星機(jī)構(gòu)的結(jié)構(gòu)復(fù)雜，設(shè)計計算困難，因此本文對變速箱行星機(jī)構(gòu)簡化成太陽輪與行星輪、行星輪與大齒圈兩對嚙合副進(jìn)行計算，討論了安裝條件、同心條件、鄰接條件等行星機(jī)構(gòu)齒輪齒數(shù)應(yīng)該滿足的條件，根據(jù)設(shè)定的開發(fā)目標(biāo)，根據(jù)速比設(shè)定目標(biāo)，進(jìn)行配齒計算，計算出中心距，然后進(jìn)行配齒計算、齒輪幾何參數(shù)計算、齒輪強(qiáng)度計算，根據(jù)確定的齒輪參數(shù)進(jìn)行配齒驗算。在滿足使用要求的情況下，對載荷譜的收集和確定制定了方法。利用常規(guī)路面按比例采集方案及采用計數(shù)法進(jìn)行數(shù)據(jù)處理，確定了載荷譜，通過臺架測試，獲取齒輪破損或未破損數(shù)據(jù)，最終確定出我公司特有的S-N曲線。通過臺架試，根據(jù)載荷譜、S-N曲線對齒輪強(qiáng)度進(jìn)行了校核，設(shè)計安全率1以上，符合設(shè)計目標(biāo)。對行星機(jī)構(gòu)關(guān)鍵零件太陽輪、行星輪、行星架和大齒圈結(jié)構(gòu)進(jìn)行了探討，對市場上現(xiàn)有變速器行星機(jī)構(gòu)的結(jié)構(gòu)進(jìn)行了調(diào)查，分析其優(yōu)缺點(diǎn)，選擇了便于加工、能夠保證性能的結(jié)構(gòu)。最后根據(jù)循環(huán)次數(shù)對試驗條件進(jìn)行制定，通過疲勞試驗試驗驗證，確定行星機(jī)構(gòu)設(shè)計滿足開發(fā)目標(biāo)。 本文還對變速器副箱行星機(jī)構(gòu)的開發(fā)對開發(fā)流程進(jìn)行了梳理。首先對競品分析，制定開發(fā)目標(biāo)及壽命目標(biāo)，在行星機(jī)構(gòu)設(shè)計中根據(jù)速比進(jìn)行配齒計算，確定中心距，進(jìn)行參數(shù)計算及配齒驗算，并對行星機(jī)構(gòu)齒輪壽命的標(biāo)準(zhǔn)制定的方法進(jìn)行的探討和總結(jié)。最后根據(jù)設(shè)計壽命目標(biāo)，制定疲勞試驗大綱，驗證設(shè)計能夠達(dá)到使用目標(biāo)。對于行星機(jī)構(gòu)變速器開發(fā)流程及設(shè)計計算進(jìn)行了一定程度的總結(jié)，具有一定指導(dǎo)意義。
[Abstract]:Under the background of great changes in market demand, the use of planetary structure in the secondary box of heavy-duty transmission products has become a development trend. In order to adapt to the development of the market, our company's planetary gearbox is also in intensive development to meet the needs of the market. The rear auxiliary box of planetary gear mechanism has many advantages, such as compact structure, large bearing capacity, high transmission efficiency, large transmission speed ratio, reliable performance and so on. As one of the important parts of heavy commercial vehicle transmission, the rear auxiliary box of planetary gear mechanism is one of the most important parts. Bearing capacity and structural design will directly affect the reliability of the transmission as a whole. Therefore, it is of great significance to study the technology of the planetary gear mechanism of the rear auxiliary box and to master the design and calculation methods of the planetary mechanism to enhance the core competitiveness of the company's products. Because the structure of the planetary mechanism is complex and the design and calculation are difficult, the gearbox planetary mechanism is simplified into two pairs of meshing pairs: solar wheel and planetary wheel, planetary gear and large gear ring, and the installation conditions and concentric conditions are discussed. According to the set development target, according to the speed ratio setting target, the tooth matching calculation is carried out, the center distance is calculated, then the tooth matching calculation is carried out, and the gear geometric parameters are calculated. Gear strength calculation, according to the determination of gear parameters for gear matching calculation. The method of collection and determination of load spectrum is developed under the condition of satisfying the requirement of application. The load spectrum is determined by using the routine pavement proportional collection scheme and the counting method, and the data of gear breakage or non-breakage are obtained by bench test. Finally, the unique S-N curve of our company is determined. According to the load spectrum S-N curve, the gear strength is checked through the bench test. The design safety rate is more than 1, which accords with the design goal. The structure of solar wheel, planetary rack and large gear ring, the key parts of planetary mechanism, are discussed. The structure of planetary mechanism of transmission in the market is investigated, and its advantages and disadvantages are analyzed. Structure that ensures performance. Finally, the test conditions are determined according to the cycle times, and the design of the planetary mechanism is determined to meet the development goal through fatigue test. This paper also combs the development process of the planetary mechanism of transmission sub-box. First of all, the paper analyzes the competitive products, formulates the development goal and life target, calculates the gear matching according to the speed ratio in the planetary mechanism design, determines the center distance, calculates the parameters and the tooth matching checking calculation. The method of establishing the standard of gear life of planetary mechanism is discussed and summarized. Finally, according to the design life goal, the fatigue test outline is developed to verify that the design can achieve the purpose. This paper summarizes the development process and design calculation of planetary transmission to a certain extent and has certain guiding significance.
【學(xué)位授予單位】：吉林大學(xué)
【學(xué)位級別】：碩士
【學(xué)位授予年份】：2012
【分類號】：U463.212;TH132.46

【參考文獻(xiàn)】

相關(guān)期刊論文 前10條

1 黃微,陳艷麗,張麗娟;修形齒輪彎曲強(qiáng)度的計算與實驗研究[J];鞍山鋼鐵學(xué)院學(xué)報;2000年03期

2 楊照山,陳明;漸開線行星齒輪傳動的研究現(xiàn)狀及發(fā)展方向[J];中國紡織大學(xué)學(xué)報;1998年05期

3 陳東升,鐘其水,陳欣;車輛變速箱齒輪彎曲疲勞壽命的估算[J];機(jī)械設(shè)計;2002年05期

4 張英爽;王國強(qiáng);王繼新;賈海波;章二平;;工程車輛傳動系載荷譜編制方法[J];農(nóng)業(yè)工程學(xué)報;2011年04期

5 鮑警予;運(yùn)用道路模擬機(jī)進(jìn)行道路譜分析[J];汽車工程;1991年04期

6 陳欣,項昌樂,鄭慕僑;車輛傳動系多工況隨機(jī)載荷譜的統(tǒng)計處理方法[J];汽車工程;1999年04期

7 田文春;汽車試驗場可靠性試驗強(qiáng)化系數(shù)的研究[J];汽車技術(shù);1997年02期

8 楊立;;變速箱速比的合理確定[J];汽齒科技;2008年01期

9 彭為,靳曉雄,孫士煒;道路模擬試驗中道路載荷譜的選擇方法[J];上海工程技術(shù)大學(xué)學(xué)報;2004年01期

10 綦力;ZF-Ecosplit 16擋同步器型變速器[J];商用汽車;2003年10期

相關(guān)碩士學(xué)位論文 前3條

1 符代竹;基于載荷譜的MT變速器疲勞設(shè)計及試驗研究[D];重慶大學(xué);2006年

2 鄭明國;汽車機(jī)械式變速器現(xiàn)代設(shè)計方法應(yīng)用研究[D];吉林大學(xué);2007年

3 王英嬌;乘用車機(jī)械式變速器（MT）試驗加載技術(shù)的研究[D];合肥工業(yè)大學(xué);2007年

本文編號：2045810