Effect of probe support wake on vibration characteristics of compressor rotor blade
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摘要: 针对某轴流压气机试验中出现的第一级转子叶片振动应变信号突增现象，开展了不同构型探针支杆尺寸对压气机转子叶片振动特性影响的对比试验。通过对比不同构型探针支杆尺寸、不同安装布局下转子叶片振动信号的变化，证实了进口探针支杆尺寸是诱发转子叶片异常振动的主要原因。同时采用流固耦合数值模拟方法，分析了探针支杆尾迹诱发转子叶片共振的流动机理。研究结果表明：支杆直径为10 mm的圆柱形探针诱发转子叶片发生整转速阶次激振的一阶共振，当探针支杆尺寸减小后，转子叶片振动响应水平显著降低。探针支杆诱发压气机转子叶片共振的扰动频率来源于支杆尾迹诱导频率与支杆通过频率的共同作用，支杆尾迹脱落涡会引起转子叶片进气攻角产生大幅值脉动。Abstract: In order to understand the abnormal phenomenon of sudden increase of the vibration strain of the first rotor blade in an axial flow compressor experiment, the comparison experiment of the effects of different kinds of inlet measurement probes on vibration characteristics of the rotor blades was conducted. By comparing the variation of the rotor blade vibration signals under different installation layouts of inlet measurement probes, it is verified that the abnormal vibration of the rotor blade is caused by the inlet measurement probes. The flow mechanism of the probe support wake inducing the resonance of rotor blade was also analyzed using the fluid-structure coupling numerical simulation method. The investigation results show that the first order resonance of the rotor blade of the axial flow compressor emerges under an engine order excitation condition, which is induced by the cylindrical probe support with the diameter of 10 mm. As the size of the probe support decreases, the level of the rotor blade vibration response is reduced evidently. The disturbance frequency of the probe-support-induced-compressor-rotor-blade-resonance originates from the combined effect of the wake induction frequency and the passing frequency of the probe support. The shedding vortex of the probe support wake can cause large amplitude fluctuation of the inlet attack angle of the rotor blade.
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图 1 进口测量截面探针安装位置示意图
Figure 1. Schematic diagram of installed position of inlet measurement probes
图 3 转子叶片表面应变片粘贴位置
Figure 3. Installed position of strain gauges on rotor blade surface
图 4 振动应变测量系统原理图
Figure 4. Schematic diagram of the vibration strain measurement system
图 6 转子叶片在安装圆柱形方向探针前后振动应变时域变化(4900 r/min)
Figure 6. Variation of the vibration strain time domain of rotor blade with and without cylindrical orientation probe (4900 r/min)
图 7 安装不同类型方向探针后转子叶片振动应变时域变化(5150 r/min)
Figure 7. Variation of the vibration strain time domain of rotor blade with different types of probes (5150 r/min)
图 8 转子叶片在安装圆柱形方向探针前后振动应变频域变化(4900 r/min)
Figure 8. Variation of the vibration strain frequency domain of rotor blade with and without cylindrical orientation probe (4900 r/min)
图 9 安装不同类型探针后转子叶片振动应变频域变化(5150 r/min)
Figure 9. Variation of the vibration strain frequency domain of rotor blade with different type of probes (5150 r/min)
图 12 探针支杆诱导三维流场结构
Figure 12. Three dimensional flowfield structure induced by probe support
图 13 不同叶高截面探针支杆脱落涡静熵云图
Figure 13. Static entropy distributions of shedding vortex induced by probe support with different radial sections
图 14 探针支杆尾缘监测点压力频谱结果
Figure 14. Variation of the fluctuating pressure frequency domain behind probe support trailing edge
图 16 不同叶高截面转子压力系数沿流向变化
Figure 16. The pressure coefficient of rotors with different radial sections varies along flow direction
表 1 转子叶片振动对比试验结果
Table 1. Experimental results of rotor blade vibration
序号 总压探针 方向探针 附面层探针 运行转速/(r·min-1) 振动信号 1 3 3 1 4457 突增 2 2 1 0 5150 突增 3 1 1 0 5150 突增 4 0 0 0 7691 正常 5 2 0 0 7691 正常 6 2 1(L型) 0 7691 正常 
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