【摘要】：目前大型風(fēng)電裝機(jī)容量穩(wěn)定增長,機(jī)組國產(chǎn)化程度不斷提高,而其齒輪箱故障率高,使用壽命短,運(yùn)行穩(wěn)定性差。振動(dòng)和齒輪疲勞是引起以上問題的重要影響因素,因此本文分別從振動(dòng)和疲勞兩方面對風(fēng)電齒輪箱進(jìn)行深入的分析和研究,主要工作體現(xiàn)在一下幾個(gè)方面： (1)本文以某兆瓦級風(fēng)電齒輪箱的設(shè)計(jì)圖紙為依據(jù),使用三維實(shí)體建模軟件PRO/E,采用參數(shù)化建模方法建立風(fēng)電齒輪箱傳動(dòng)鏈各部件的三維實(shí)體模型,并根據(jù)圖紙所示傳動(dòng)鏈中各部件的相對位置,將各部件合理準(zhǔn)確裝配,建立風(fēng)電齒輪箱傳動(dòng)系統(tǒng)的三維實(shí)體模型,導(dǎo)入ADAMS生成剛體模型；然后通過ANSYS有限元軟件將內(nèi)齒圈、行星架、行星輪和高速軸柔性化,生成模態(tài)中性文件,再導(dǎo)入ADAMS中替換相應(yīng)的剛體部件,從而建立齒輪箱傳動(dòng)鏈的剛?cè)狁詈隙囿w動(dòng)力學(xué)模型。 (2)在ADAMS/Vibration平臺對風(fēng)電機(jī)組齒輪箱剛?cè)狁詈夏Ｐ褪┘雍侠淼募s束,以功率譜密度方式(PSD)分別在行星架外連點(diǎn)(interface node)施加波動(dòng)輸入轉(zhuǎn)速激勵(lì)和在高速軸的外連點(diǎn)添加波動(dòng)負(fù)載轉(zhuǎn)矩激勵(lì),然后設(shè)置好裝配狀態(tài)點(diǎn)獲取方式、仿真步數(shù)和頻率范圍進(jìn)行受迫振動(dòng)計(jì)算。分別從系統(tǒng)模態(tài)、模態(tài)參與因子、頻率響應(yīng)曲線等分析了系統(tǒng)的振動(dòng)特性和設(shè)計(jì)可行性。 (3)在ADAMS/View平臺,對模型施加合理的約束和力,分別在恒定載荷和波動(dòng)載荷下進(jìn)行動(dòng)力學(xué)仿真。傳動(dòng)比、嚙合力、齒輪接觸應(yīng)力和彎曲應(yīng)力的仿真結(jié)果與理論計(jì)算結(jié)果對比基本一致,驗(yàn)證了模型、約束和力的合理性。提取出兩種工況下應(yīng)力應(yīng)變前十個(gè)熱點(diǎn)和應(yīng)力應(yīng)變最大點(diǎn)的隨時(shí)間變化曲線,總結(jié)了其變化規(guī)律,指出轉(zhuǎn)速和負(fù)載的突變會(huì)給結(jié)構(gòu)帶來巨大的強(qiáng)度失效破壞。 (4)取兩種工況下關(guān)鍵部件的應(yīng)力仿真結(jié)果,利用雨流計(jì)數(shù)法、材料的P-S-N曲線和Miner疲勞累積損傷理論通過MATLAB編程計(jì)算兩種工況各部件的疲勞壽命,并對結(jié)果進(jìn)行分析,驗(yàn)證了該設(shè)計(jì)滿足疲勞壽命要求,但除了行星架外其它部件疲勞壽命遠(yuǎn)大于設(shè)計(jì)壽命20年,可以適當(dāng)優(yōu)化設(shè)計(jì),降低成本。
[Abstract]:At present, the installed capacity of large scale wind power is increasing steadily, and the degree of domestication of the unit is increasing continuously. However, its gearbox has high failure rate, short service life and poor operation stability. Vibration and gear fatigue are the important factors that cause the above problems. Therefore, this paper makes a deep analysis and research on the wind power gearbox from the aspects of vibration and fatigue. The main work is as follows: (1) based on the design drawings of a megawatt wind power gearbox, the 3D solid modeling software PRO/E, is used in this paper. The three-dimensional solid model of the components of the transmission chain of the wind power gearbox is established by using the parameterized modeling method. According to the relative position of the components in the transmission chain shown in the drawings, the components are assembled reasonably and accurately. The three-dimensional solid model of wind power gearbox transmission system is established, and the rigid body model is generated by ADAMS. Then, the inner gear ring, planetary frame, planetary gear and high-speed axis are flexible by ANSYS finite element software, and the modal neutral files are generated, and then imported into ADAMS to replace the corresponding rigid body parts, thus the rigid-flexible coupling multi-body dynamic model of the gearbox transmission chain is established. (2) the rigid-flexible coupling model of wind turbine gearbox is constrained reasonably on ADAMS/Vibration platform. The power spectral density (PSD) method is applied to the planetary frame external connection point (interface node) respectively to exert the fluctuation input speed excitation and to add the ripple load torque excitation at the external connection point of the high speed shaft, and then set up the assembly state point acquisition method. The forced vibration is calculated in the range of simulation steps and frequency. The vibration characteristics and design feasibility of the system are analyzed from the system modes, modal participation factors and frequency response curves. (3) on the ADAMS/View platform, the model is subjected to reasonable constraints and forces, and the dynamic simulation is carried out under constant load and fluctuating load, respectively. The simulation results of transmission ratio, meshing force, contact stress and bending stress are in good agreement with the theoretical results, and the rationality of the model, constraint and force is verified. The time-dependent curves of the first ten hot spots of stress and strain and the maximum point of stress and strain under two working conditions were extracted, and the variation rules were summarized. It was pointed out that the sudden change of rotational speed and load would bring great failure to the strength of the structure. (4) taking the stress simulation results of the key components under two working conditions, using the rain flow counting method, the P-S-N curve of the material and the Miner fatigue cumulative damage theory, the fatigue life of the components under two working conditions is calculated by MATLAB programming. The results show that the design meets the requirement of fatigue life, but the fatigue life of other components except the planetary frame is much longer than the design life of 20 years, so the design can be optimized properly and the cost can be reduced.
【學(xué)位授予單位】：華北電力大學(xué)
【學(xué)位級別】：碩士
【學(xué)位授予年份】：2014
【分類號】：TM315

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