根据受力分析,推导了扭振故障下轴系-叶片耦合扭振模型,并应用于某台1000MW机组的轴系-叶片扭振建模.利用数值仿真法,研究了电磁力矩扰动分别为轴系的前三阶次同步振荡、叶片一阶固有频率的0.5倍、叶片一阶固有频率以及叶片一阶固有频率与轴系第五阶固有频率相等时,低压末级叶根所在轮盘的实时角加速度、扭矩.研究结果表明:在上述激励作用下,与轴系的各轴颈相比而言,低压末级叶片等长叶片不是扭振危险部位.%According to the force analysis,the coupling torsional vibration model of shafting-blade was derived,this model was applied to build torsional vibration model of a certain 1000MW unit shafting-blade.Numerical simulation method was used to research real time angular acceleration and torque of wheel disk where low pressure last row blade root located in,when electromagnetic disturbance were first three order subsynchronous oscillation,0.5 times first order natural frequency of blade,first order natural frequency of blade,and first order natural frequency of blade equaled to fifth order natural frequency of shafting respectively.The research results show that long blade are not torsional vibration dangerous position,such as low pressure last row blade and so on,comparing with the axle journal of shafting.
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