本文選題：汽輪發(fā)電機(jī)轉(zhuǎn)子軸系　切入點(diǎn)：傳遞矩陣　出處：《華北電力大學(xué)》2014年碩士論文　論文類型：學(xué)位論文

【摘要】：隨著我國(guó)電力工業(yè)的發(fā)展,我國(guó)現(xiàn)今的火電機(jī)組普遍采用單機(jī)容量為600MW-1000MW的大型汽輪發(fā)電機(jī)組。由于機(jī)組容量的增大和電網(wǎng)峰谷差日益增大,使得大型火力發(fā)電機(jī)組不可避免地參與調(diào)峰運(yùn)行,機(jī)組軸系的扭振問(wèn)題變得日益突出。本文以某國(guó)產(chǎn)600MW超臨界機(jī)組軸系為研究對(duì)象,用集總參數(shù)法建立軸系的多段集中質(zhì)量模型,用傳遞矩陣法對(duì)機(jī)組軸系的扭振特性進(jìn)行研究分析。本文的主要工作和結(jié)論如下： 1)用集總參數(shù)法對(duì)轉(zhuǎn)子軸系進(jìn)行離散簡(jiǎn)化,并用傳遞矩陣法計(jì)算軸系的扭振固有模態(tài),并計(jì)算了軸系前三階共振時(shí)的應(yīng)力分布,一階共振時(shí)扭應(yīng)力的最大值出現(xiàn)在1#低壓轉(zhuǎn)子和2#低壓轉(zhuǎn)子的軸頸之間,二階共振的最大扭應(yīng)力出現(xiàn)在2#低壓轉(zhuǎn)子和發(fā)電機(jī)轉(zhuǎn)子的軸頸之間,三階共振時(shí)軸系最大扭應(yīng)力出現(xiàn)在高中壓轉(zhuǎn)子和1#低壓轉(zhuǎn)子之間。 2)學(xué)習(xí)整理了國(guó)內(nèi)三大電機(jī)廠生產(chǎn)的600MW級(jí)汽輪發(fā)電機(jī)組的軸系結(jié)構(gòu),繪制出軸系的結(jié)構(gòu)簡(jiǎn)圖,介紹了汽輪發(fā)電機(jī)組的運(yùn)行特性和國(guó)內(nèi)的主要調(diào)峰方式。 3)將傳遞矩陣法和數(shù)值積分方法相結(jié)合,計(jì)算軸系的扭振響應(yīng),通過(guò)對(duì)計(jì)算結(jié)果得到軸系的最大應(yīng)力出現(xiàn)在低壓2#轉(zhuǎn)子與發(fā)電機(jī)轉(zhuǎn)子的聯(lián)軸器處。應(yīng)用局部應(yīng)力應(yīng)變法對(duì)軸系疲勞壽命損耗進(jìn)行分析,得出機(jī)組軸系在發(fā)電機(jī)出口處發(fā)生兩相短路時(shí),引起的軸系扭振疲勞損耗最大。 4)計(jì)算軸系在機(jī)組快速變負(fù)荷時(shí)的扭振響應(yīng),通過(guò)對(duì)計(jì)算結(jié)果的時(shí)域和頻域分析,得出結(jié)論：軸系在快速變負(fù)荷時(shí),軸系的扭矩波形圖的主要頻率成分包含了軸系的前三階扭振固有頻率,不包含工頻。
[Abstract]:With the development of electric power industry in China, large turbogenerator units with a single unit capacity of 600MW-1000MW are widely used in our country. Due to the increase of unit capacity and the increasing difference between peak and valley of power grid, The torsional vibration problem of shafting becomes more and more prominent due to the inevitable participation of large thermal power generating units in peak shaving operation. In this paper, the shafting of a domestic 600MW supercritical unit is taken as the research object. The multi-stage mass model of shafting is established by lumped parameter method, and the torsional vibration characteristics of shafting system are analyzed by transfer matrix method. The main work and conclusions are as follows:. 1) the rotor shaft system is discretized simplified by lumped parameter method, and the natural mode of torsional vibration of shaft system is calculated by transfer matrix method, and the stress distribution of the first three order resonance of shaft system is calculated. The maximum torsional stress of the first order resonance occurs between the journal of the 1# low voltage rotor and the 2# low pressure rotor, and the maximum torsional stress of the second order resonance occurs between the 2# low voltage rotor and the generator rotor journal. The maximum torsional stress of the shaft appears between the high pressure rotor and the 1# low pressure rotor during the third order resonance. 2) the shafting structure of 600MW class turbine-generator set produced by three major electric power plants in China has been studied, and the schematic diagram of the shafting structure has been drawn. The operation characteristics of the turbogenerator unit and the main peak shaving methods in China have been introduced. 3) the transfer matrix method and numerical integration method are combined to calculate the torsional vibration response of shafting. The results show that the maximum stress of shafting appears in the coupling of low-voltage rotor and generator rotor. The fatigue life loss of shafting is analyzed by using local stress-strain method. It is concluded that when two phase short circuit occurs at generator outlet, the fatigue loss of shaft system torsional vibration is the largest. 4) the torsional vibration response of shafting under fast load change is calculated. By analyzing the calculated results in time domain and frequency domain, it is concluded that the shafting is under fast load changing. The main frequency components of the shafting torque waveform include the first three natural frequencies of the shafting torsional vibration, not the power frequency.
【學(xué)位授予單位】：華北電力大學(xué)
【學(xué)位級(jí)別】：碩士
【學(xué)位授予年份】：2014
【分類號(hào)】：TM311

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