本文關(guān)鍵詞： 風(fēng)力發(fā)電 行星齒輪 動(dòng)力學(xué)建模 固有頻率 嚙合剛度　出處：《西華大學(xué)》2011年碩士論文　論文類(lèi)型：學(xué)位論文

【摘要】：隨著全球可再生能源市場(chǎng)的迅速發(fā)展和人類(lèi)對(duì)環(huán)境保護(hù)意識(shí)的增強(qiáng),人們開(kāi)始把目光集中到新能源的開(kāi)發(fā)上來(lái)。風(fēng)力發(fā)電逐漸成為能源工業(yè)新的增長(zhǎng)點(diǎn)。風(fēng)力發(fā)電齒輪箱作為風(fēng)力發(fā)電機(jī)組中傳遞動(dòng)力的重要部件之一,其傳動(dòng)系統(tǒng)的結(jié)構(gòu)與性能,直接影響到整個(gè)風(fēng)力發(fā)電機(jī)組的正常運(yùn)轉(zhuǎn)。齒輪箱的傳動(dòng)系統(tǒng)的結(jié)構(gòu)決定了齒輪箱的整體體積。由于風(fēng)力發(fā)電齒輪箱傳動(dòng)系統(tǒng)在運(yùn)行的過(guò)程中,它的動(dòng)力源是無(wú)時(shí)無(wú)刻在變化的自然風(fēng)。這必然使傳動(dòng)系統(tǒng)產(chǎn)生振動(dòng)。為了減小風(fēng)電齒輪箱的體積和減小傳動(dòng)系統(tǒng)的振動(dòng)、降低噪音,需要對(duì)風(fēng)力發(fā)電齒輪箱的傳動(dòng)系統(tǒng)的結(jié)構(gòu)和模態(tài)進(jìn)行分析。 本文對(duì)1.5MW風(fēng)力發(fā)電齒輪箱傳動(dòng)系統(tǒng)進(jìn)行了結(jié)構(gòu)的選擇和優(yōu)化并在考慮齒輪嚙合剛度的時(shí)變性、外部激勵(lì)和內(nèi)部激勵(lì)等因素的情況下,對(duì)優(yōu)化后的傳動(dòng)系統(tǒng)建立了扭轉(zhuǎn)振動(dòng)動(dòng)力學(xué)模型。在此基礎(chǔ)上,建立了多自由度的自由振動(dòng)線性微分方程,并對(duì)其進(jìn)行求解,得到傳動(dòng)系統(tǒng)的固有頻率和主振型。為下一步對(duì)傳動(dòng)系統(tǒng)的動(dòng)態(tài)響應(yīng)的研究打下基礎(chǔ)。 本文主要做了以下幾方面的工作: (1)設(shè)計(jì)了一種風(fēng)電齒輪箱的傳動(dòng)系統(tǒng),該傳動(dòng)系統(tǒng)采用功率分流式三級(jí)行星齒輪機(jī)構(gòu),第三級(jí)為差動(dòng)行星齒輪。以行星齒輪的總體積作為我們的目標(biāo)函數(shù),以太陽(yáng)輪的齒數(shù)和相關(guān)的比例系數(shù)為設(shè)計(jì)變量,使用MATLAB工具箱里面的fmincon函數(shù)對(duì)我們的傳動(dòng)系統(tǒng)進(jìn)行優(yōu)化。得到我們最終的設(shè)計(jì)齒數(shù)和比例系數(shù)。 (2)計(jì)算出每一級(jí)的模數(shù),使用Pro/e三維建模軟件,建立行星齒輪、行星架,軸的三維模型。并把它們裝配在一起,從而建立起傳動(dòng)系統(tǒng)的三維模型。 (3)采用集中參數(shù)法建立風(fēng)電齒輪箱傳動(dòng)系統(tǒng)的扭轉(zhuǎn)振動(dòng)動(dòng)力學(xué)模型,把相互嚙合的齒輪等效成一根彈簧和一個(gè)阻尼器。采用石川法[1][2]來(lái)計(jì)算齒輪的嚙合剛度。以第二級(jí)太陽(yáng)輪與行星輪的嚙合剛度為例,進(jìn)行了相關(guān)的計(jì)算。使用拉格朗日方程推導(dǎo)出傳動(dòng)系統(tǒng)的扭轉(zhuǎn)振動(dòng)微分方程。 (4)對(duì)風(fēng)電齒輪箱傳動(dòng)系統(tǒng)建立16自由度的自由振動(dòng)線性微分方程,使用MATLAB中的EIG命令來(lái)求出系統(tǒng)的固有頻率和主振型。以上的研究可以為設(shè)計(jì)一種質(zhì)量輕,滿足功率要求、成本低的風(fēng)力發(fā)電齒輪箱提供參考。
[Abstract]:With the rapid development of the global renewable energy market and the enhancement of human awareness of environmental protection. People begin to focus on the development of new energy. Wind power has gradually become a new growth point in the energy industry. Wind power gearbox is one of the important parts in the transmission of power in wind turbines. The structure and performance of its transmission system. It directly affects the normal operation of the whole wind turbine. The structure of the transmission system of the gearbox determines the overall volume of the gearbox. Its power source is the changing natural wind all the time, which inevitably causes the vibration of the transmission system. In order to reduce the volume of the wind power gearbox and reduce the vibration of the transmission system, reduce the noise. It is necessary to analyze the structure and mode of the transmission system of the gearbox of wind power generation. In this paper, the gearbox transmission system of 1.5 MW wind power generation is selected and optimized, and considering the time variation of gear meshing stiffness, external and internal excitation and other factors. The dynamic model of torsional vibration is established for the optimized transmission system. On this basis, the linear differential equation of free vibration with multiple degrees of freedom is established and solved. The natural frequency and the main mode of the transmission system are obtained, which lays a foundation for the further study of the dynamic response of the transmission system. The main work of this paper is as follows: A transmission system of wind power gearbox is designed. The transmission system adopts the three-stage planetary gear mechanism of power shunt type. The third stage is the differential planetary gear. The total volume of the planetary gear is taken as our objective function, and the number of teeth of the solar gear and the relative ratio coefficient are taken as the design variables. The fmincon function in the MATLAB toolbox is used to optimize our transmission system, and the final design tooth number and proportional coefficient are obtained. (2) calculate the modules of each level, use the Pro/e 3D modeling software to build three-dimensional models of planetary gears, planetary frames, and shafts, and assemble them together. Thus the three-dimensional model of transmission system is established. The torsional vibration dynamic model of wind power gearbox transmission system is established by means of lumped parameter method. The meshing gears are equivalent to a spring and a damper. Shi Chuan's method is used. [1]. [Taking the meshing stiffness of the second solar wheel and the planetary wheel as an example, the differential equations of torsional vibration of the transmission system are derived by using Lagrange equation. The linear differential equation of free vibration with 16 degrees of freedom is established for the gearbox transmission system of wind power. The natural frequency and the main mode of the system are obtained by using the EIG command in MATLAB. The above research can provide a reference for the design of a wind power gearbox with light weight, satisfying the power requirement and low cost.
【學(xué)位授予單位】：西華大學(xué)
【學(xué)位級(jí)別】：碩士
【學(xué)位授予年份】：2011
【分類(lèi)號(hào)】：TH132.41

【參考文獻(xiàn)】

相關(guān)期刊論文 前10條

1 張展;風(fēng)力發(fā)電機(jī)組的傳動(dòng)裝置[J];傳動(dòng)技術(shù);2003年02期

2 王龍寶;王貴成;王志;;直齒圓柱齒輪嚙合剛度的影響因素及其規(guī)律性[J];工具技術(shù);2007年05期

3 沈宏;耿超;劉楠;李偉麗;邱軍亮;;國(guó)內(nèi)外風(fēng)電產(chǎn)業(yè)現(xiàn)狀及其發(fā)展前景[J];河南科技學(xué)院學(xué)報(bào)(自然科學(xué)版);2010年01期

4 王旭東;林騰蛟;李潤(rùn)方;劉文;杜雪松;;風(fēng)力發(fā)電機(jī)組齒輪系統(tǒng)內(nèi)部動(dòng)態(tài)激勵(lì)和響應(yīng)分析[J];機(jī)械設(shè)計(jì)與研究;2006年03期

5 陳作炳;劉志善;;直齒輪剛度分析和計(jì)算[J];齒輪;1987年01期

6 何青;張和豪;;齒輪系統(tǒng)動(dòng)力學(xué)模型分析和簡(jiǎn)化[J];齒輪;1989年02期

7 湯克平;風(fēng)電增速箱結(jié)構(gòu)設(shè)計(jì)敘談[J];機(jī)械傳動(dòng);2004年05期

8 王晶晶;吳曉鈴;;風(fēng)電齒輪箱的發(fā)展及技術(shù)分析[J];機(jī)械傳動(dòng);2008年06期

9 劉忠明;尚珍;董進(jìn)朝;張和平;張志宏;;風(fēng)電增速箱齒輪設(shè)計(jì)計(jì)算若干問(wèn)題探討[J];機(jī)械傳動(dòng);2008年06期

10 王剛,張大衛(wèi),黃田,劉繼巖;RV減速機(jī)動(dòng)力學(xué)建模方法研究[J];機(jī)械設(shè)計(jì);1999年03期

相關(guān)碩士學(xué)位論文 前10條

1 朱秋玲;齒輪系統(tǒng)動(dòng)力學(xué)分析及計(jì)算機(jī)仿真[D];蘭州理工大學(xué);2004年

2 岳勇;風(fēng)力發(fā)電機(jī)組機(jī)械零部件抗疲勞設(shè)計(jì)方法的研究[D];新疆農(nóng)業(yè)大學(xué);2005年

3 楊振;轉(zhuǎn)矩分流式齒輪傳動(dòng)系統(tǒng)動(dòng)力學(xué)特性研究[D];西北工業(yè)大學(xué);2007年

4 王龍寶;齒輪剛度計(jì)算及其有限元分析[D];江蘇大學(xué);2007年

5 張義華;水平軸風(fēng)力機(jī)空氣動(dòng)力學(xué)數(shù)值模擬[D];重慶大學(xué);2007年

6 董進(jìn)朝;大型風(fēng)電齒輪箱關(guān)鍵設(shè)計(jì)技術(shù)研究[D];機(jī)械科學(xué)研究總院;2007年

7 孟國(guó)慶;大型水泥設(shè)備多級(jí)齒輪傳動(dòng)系統(tǒng)動(dòng)力學(xué)分析[D];武漢理工大學(xué);2007年

8 陳紹軍;基于虛擬樣機(jī)的大型風(fēng)電機(jī)組齒輪傳動(dòng)系統(tǒng)沖擊特性分析[D];華北電力大學(xué)（北京）;2008年

9 佘勃強(qiáng);風(fēng)力發(fā)電增速裝置的研究[D];西安理工大學(xué);2008年

10 古西國(guó);兆瓦級(jí)風(fēng)力發(fā)電機(jī)齒輪傳動(dòng)系統(tǒng)耦合振動(dòng)分析及優(yōu)化設(shè)計(jì)[D];重慶大學(xué);2008年

，

本文編號(hào)：1492130