火箭推进

针对涡轮泵转子的具体结构特点,解决了高速运行试验过程中的支承、驱动、轴承润滑冷却、振动测量、转子高速动平衡及轴向力加载控制等问题。结合旋转机械故障诊断技术,提出了高速动平衡效率、转子支承状态及轴向力加载状态的优化方法,并在试验过程中对该优化方法进行了验证,实现了涡轮泵转子的高速稳定运行。结果表明:涡轮泵转子高速运行试验应采用刚性连接的柔性联轴器; 涡轮泵转子高速轴承需采用高压直喷式供油; 通过平衡效率优化可将非线性振动影响下的转子一次平衡效率由30%提高至73.7%; 为避免高速运行时产生基础松动,试验中滚动轴承外环应采用紧配合安装; 轴向力应沿轴承周向均匀加载,其大小应根据轴承-转子系统具体结构及运行状态综合分析确定。

According to the specific structural characteristics of turbo pump rotor, the problems of supporting, driving, bearing lubrication and cooling, vibration measurement, high speed rotor dynamic balance, axial force loading and control of rolling bearing rotor system during high-speed operation test were solved.Combined with the fault diagnosis technology of rotating machinery, the optimization methods of high speed dynamic balancing efficiency, rotor supporting state and axial force loading sate have been put forward, and the experimental verification has also been carried out.Finally, the high speed and stable operation of turbo pump rotor has been achieved.The results show that flexible coupling with rigid connection should be used when turbine pump rotor runs at high speed.High-speed bearing of the turbo-pump rotor requires high pressure and direct injection oil supply.By optimizing the balance efficiency, the primary balance efficiency of the rotor under the influence of nonlinear vibration can be increased from 30% to 73.7%.In order to avoid loosening of the foundation during high speed, the outer ring of rolling bearing should be installed with a tight fit during the test.The axial force should be uniformly loaded along the bearing circumference, and its magnitude should be determined according to the comprehensive analysis of the specific bearing rotor system structure and the running state.

引言
1 涡轮泵轴系结构
2 试验系统及试验方法
3 涡轮泵转子高速运行状态优化
4 结论

图1 涡轮泵轴系示意图<br/>Fig.1 Schematic diagram of the turbo-pump shafting

图1 涡轮泵轴系示意图
Fig.1 Schematic diagram of the turbo-pump shafting

图2 转子动力学试验系统组成<br/>Fig.2 Composition of the rotor dynamics test system

图2 转子动力学试验系统组成
Fig.2 Composition of the rotor dynamics test system

图3 平衡效率优化流程<br/>Fig.3 Optimization process of balance efficiency

图3 平衡效率优化流程
Fig.3 Optimization process of balance efficiency

图4 平衡效率优化前后平衡效果对比曲线<br/>Fig.4 Comparison curves of balance effect before and after optimization of balance efficiency

图4 平衡效率优化前后平衡效果对比曲线
Fig.4 Comparison curves of balance effect before and after optimization of balance efficiency

图5 轴承座支承状态下转子系统示意图<br/>Fig.5 Schematic diagram of rotor system with the bearing pedestal

图5 轴承座支承状态下转子系统示意图
Fig.5 Schematic diagram of rotor system with the bearing pedestal

图6 轴承座支承状态下转子1f振动位移变化曲线<br/>Fig.6 Displacement curve of rotor 1f vibration

图6 轴承座支承状态下转子1f振动位移变化曲线
Fig.6 Displacement curve of rotor 1f vibration

图7 多次重复运行涡轮端径向振动位移1对比<br/>Fig.7 Comparison of radial vibration displacement of turbine end in repeated operation

图7 多次重复运行涡轮端径向振动位移1对比
Fig.7 Comparison of radial vibration displacement of turbine end in repeated operation

图8 多次重复运行离心轮端径向振动位移1对比<br/>Fig.8 Comparison of radial vibration displacement of pump end in repeated operation

图8 多次重复运行离心轮端径向振动位移1对比
Fig.8 Comparison of radial vibration displacement of pump end in repeated operation

图9 轴承及温度传感器划痕<br/>Fig.9 Scratches of bearing and temperature sensor

图9 轴承及温度传感器划痕
Fig.9 Scratches of bearing and temperature sensor

图10 支承状态优化结果示意图<br/>Fig.10 Schematic diagram of supporting state optimization results

图10 支承状态优化结果示意图
Fig.10 Schematic diagram of supporting state optimization results

图11 两种轴向力加载方式对比<br/>Fig.11 Comparison of two axial force loading methods

图11 两种轴向力加载方式对比
Fig.11 Comparison of two axial force loading methods

图12 0～25 000 r/min升速过程中转子振动位移变化曲线<br/>Fig.12 Curves of rotor vibration displacement during 0～25 000 r/min run-up process

图12 0～25 000 r/min升速过程中转子振动位移变化曲线
Fig.12 Curves of rotor vibration displacement during 0～25 000 r/min run-up process

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备注

引言

1 涡轮泵轴系结构

2 试验系统及试验方法

3 涡轮泵转子高速运行状态优化

4 结论

期刊信息