Research on dynamic characteristics of aero-engine high-pressure rotor connection component loosening fault
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摘要:
针对航空发动机高压转子在实际工作过程中存在的连接部件松动现象，建立了考虑松动故障特性的高压转子Timoshenko梁模型，探讨了结合面刚度、转速、松动螺栓数量、松动故障位置、拧紧力矩对转子动力学的影响，并对理论分析结果进行了试验验证。结果表明：故障系统升速过程中呈现出明显亚临界共振现象，且临界峰值转速提前；松动螺栓数量越多，系统倍周期分岔现象越明显；松动故障位于转子跨距中间时对系统动力学的影响较大；螺栓拧紧力矩减小，系统第二阶临界峰值转速提前；试验数据与理论分析结果比较吻合，提出的理论方法具有一定的准确性和适用性。研究结果为航空发动机高压转子连接部件松动故障的进一步研究提供了理论和试验基础。
Abstract:To study the effects of the connection component loosening fault in aero-engine high-pressure rotor, a Timoshenko beam model considering loosening fault was established. The influences of joint surface stiffness, speed, number of loose bolts, position of loosening fault and tightening torque on rotor dynamics were discussed. The results of theoretical analysis were verified by experiments. The results showed that there was an obvious subcritical resonance in the speed-up process of the fault system, and the critical peak speed was generated in advance. The more number of loose bolts indicated the more obvious period-doubling bifurcation of the system. The loosening fault was located in the middle of the rotor span, which had a great influence on the system dynamics. When the bolt tightening torque was reduced, the second critical peak speed of the system was generated in advance. The experimental data were in good agreement with the results of theoretical analysis, and the proposed theoretical method had certain accuracy and applicability. The research results provide a theoretical and experimental basis for further study on connection component loosening fault of aero-engine high pressure rotor.
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图 1 航空发动机高压转子二维结构（单位：mm）
Figure 1. Two-dimensional structure of high-pressure rotors in aircraft engines （unit：mm）
图 2 高压转子Timoshenko梁有限元模型
Figure 2. Finite element model of Timoshenko beam for high-pressure rotor
图 7 两种工况下左轴承处y方向稳态响应
Figure 7. Steady-state response in the y-direction at the left bearing under two working conditions
图 10 转子速度为3 141.7 r/ min（1/3倍临界转速）时，左轴承处y方向振动响应
Figure 10. Vibration response in the y direction at left bearing when the rotor speed is 3 141.7 r/min （1/3 times the critical speed）
图 12 转子速度为15 000 r/ min（大于失稳转速）时，左轴承处y方向振动响应
Figure 12. Vibration response in the y direction at left bearing when the rotor speed is 15 000 r/min （greater than the unstable speed）
图 11 转子速度为4 712.5 r/ min（1/2倍临界转速）时，左轴承处y方向振动响应
Figure 11. Vibration response in the y direction at left bearing when the rotor speed is 4 712.5 r/min （1/2 times the critical speed）
图 15 松动螺栓1/12圈时，亚临界转速、转速为15 000 r/min时左轴承处轴心轨迹
Figure 15. Axis center trajectory at left bearing at a subcritical speed of 15 000 r/min when the loose bolts is 1/12 turns
图 16 松动螺栓1/6圈时，亚临界转速、转速为15 000 r/min时左轴承处轴心轨迹
Figure 16. A xis center trajectory at the left bearing at a subcritical speed of 15 000 r/min when the loose bolts is 1/6 turns
表 1 高压转子参数一览表
Table 1. List of high-pressure rotor parameters
参数 数值 弹性模量/1011 （N/m2） 2.1 轴承刚度/107 （N/m） 80（左）、4.01 （右） 轴承阻尼/（N·s/m） 500 密度/（kg/m3） 7810 泊松比 0.3 不平衡质量/（g·mm） 300（相位角为0°） 
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表 2 两种模型固有频率对比
Table 2. Comparison of natural frequencies in two models
固有频率/Hz 第1阶 第2阶 第3阶 第4阶 ANSYS 156.03 456.78 1121.15 1892.26 Timoshenko 158.07 461.01 1128.28 1903.68 误差/% 1.29 0.92 0.63 0.60
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表 3 两种模型临界转速对比
Table 3. Comparison of critical speeds in two models
临界转速/（r/min） 第1阶 第2阶 第3阶 ANSYS有限元模型 9501 28662 86441 Timoshenko梁 9620 29002 87323 误差/% 1.25 1.17 1.01
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表 4 一个周期内结合面开闭变化规律
Table 4. Variation law of the opening and closing of the joint surface within a cycle
松动螺栓数量/圈 高压转子旋转角度ψ/（°） 全部闭合 逐渐张开 全部张开 逐渐闭合 全部闭合 1/12 0～63 63～127 127～233 233～297 297～360 1/9 0～54 54～136 136～224 224～306 306～360 1/6 0～43 43～149 149～211 211～317 317～360 1/4 0～31 32～158 158～203 203～329 329～360
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