Simulation and experimental research for overturning behavior of aviation plunger pump cylinder bodies
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摘要:
航空柱塞泵是航空液压系统的核心，其内部零部件倾覆过大可能会使整个系统性能下降，甚至失效。如何提高航空柱塞泵的稳定性、减小零部件倾覆一直是其高压高速化发展研究的关键问题。为此，从缸体振动位移角度出发，建立一种基于数据驱动的高保真动力学模型，探究柱塞泵出口压力和转速对缸体倾覆的影响，提出减小配流盘腰形槽尺寸的改进措施，并通过数值仿真进行验证。研究结果表明：减小配流盘腰形槽尺寸能使缸体倾覆有所改善；修正后的模型能够反映实际的倾覆状态，与试验测量结果相对误差在5%以内。研究成果为航空柱塞泵的仿真和稳定性研究提供了研究思路，为批产一致性制造提供理论和试验支撑。
Abstract:The aviation plunger pump is the core of the aviation hydraulic system, and excessive overturning of its internal parts may cause the performance of the whole system to degrade and fail. How to improve the stability of the aviation plunger pump and reduce the overturning of the parts has been the key issue in the research of its high-pressure and high-speed development. The impact of outlet pressure and plunger pump speed on cylinder overturning was investigated in this article, which created a data-driven high-fidelity dynamics model from the viewpoint of cylinder vibration displacement. Then, an improvement measure to reduce the waist groove size of the distribution plate was proposed and verified through numerical simulation. The results show that reducing the size of the waist groove on the distribution plate can improve the overturning of the cylinder body. The revised model can reflect the actual tilting state, and the relative error with the experimental measurement results is within 5%. The research findings offer theoretical and experimental support for the reliable manufacturing of batch production, as well as research suggestions for the simulation and stability studies of aeronautical piston pumps.
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Key words:
- aviation plunger pump /
- cylinder overturning /
- vibration displacement /
- co-simulation /
- model updating
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图 3 柱塞滑靴组件运动分析简图
Figure 3. Schematic diagram of piston slide boot assembly motion analysis
图 5 负载压力-负载流量特性曲线对比
Figure 5. Comparison of load pressure-load flow characteristic curves
图 6 主轴-缸体系统多刚体动力学仿真模型
Figure 6. Multi rigid body dynamic simulation model of spindle-cylinder system
图 7 多刚体动力学仿真结果与理论结果的对比
Figure 7. The comparison of multi rigid body dynamics simulation results with theoretical results
图 8 联合仿真结果与理论结果的对比
Figure 8. The comparison between joint simulation results and theoretical results
图 9 主轴-缸体系统刚柔耦合动力学模型
Figure 9. The rigid flexible coupling dynamic model of the spindle-cylinder system
图 13 额定工况和初始状态前4个周期的测量结果
Figure 13. Measurement results for the first four cycles of rated operating conditions and initial state
图 14 额定工况时的缸体倾覆角变化曲线
Figure 14. Cylinder overturning angle variation curve under rated operating conditions
图 15 额定工况时的径向偏离位移变化曲线
Figure 15. Radial deviation displacement variation curve under rated operating conditions
图 17 额定工况时缸体倾覆最剧烈的位置
Figure 17. The position where the cylinder overturns the most severely under rated operating conditions
图 20 压力区包角在一个周期内的变化情况
Figure 20. The variation of pressure zone envelope angle within one cycle
图 21 改进前后数值仿真结果对比
Figure 21. The comparison of numerical simulation results before and after improvement
图 22 径向偏离位移均方根值与修正参数的关系
Figure 22. The relationship between radial deviation displacement root mean square value and correction parameters
图 23 径向偏离位移1倍频幅值与修正参数的关系
Figure 23. The relationship between radial deviation displacement 1 fold frequency amplitude and correction parameters
表 1 电涡流位移传感器的技术指标
Table 1. Technical specifications of eddy current displacement sensors
参数值及
要求探头到缸体
的距离/mm零点/
mm灵敏度/
(V·mm−1)平均灵敏度
误差/%典型分辨
率/μm工作
温度/℃承受
压力/MPa非线性
误差/%探头
直径/mm频响/kHz 探头
长度/mm校核
方式供电
电压/VCWY-DO电涡流
位移传感器参数0.2～1.2 0.2 8 不超过±5 1 −20～120 0.2～0.4 不超过±1 5 0～10 40 铁磁性
校核12～15 试验环境要求 >0.3 ≤1 室温 约0.3 ≤6 >6.92 >21.3 不锈钢
材质+9/±15 
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表 2 相同转速、不同出口压力时缸体径向偏离位移的均方根值和1倍频幅值
Table 2. The root mean square value and 1st harmonic amplitude of radial deviation displacement of cylinder body at the same rotational speed and different outlet pressures
测量
工况径向偏离位移
均方根值/mm径向偏离位移
1倍频幅值/mm10 MPa 0.07104 0.00871 20 MPa 0.03066 0.00156 35 MPa 0.03741 0.00546 75%全流量 0.03931 0.00768 50%全流量 0.03347 0.00579 25%全流量 0.03022 0.00517 0流量 0.03461 0.00698
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表 3 相同出口压力、不同转速时缸体径向偏离位移的均方根值和1倍频幅值
Table 3. The root mean square value and 1st harmonic amplitude of radial deviation displacement of cylinder body at the same outlet pressure and different rotational speeds
测量工况 径向偏离位移
均方根值/mm径向偏离位移
1倍频幅值/mm20%额定转速 0.04589 0.03231 40%额定转速 0.04085 0.01493 60%额定转速 0.04062 0.01110 80%额定转速 0.03949 0.00623 100%额定转速 0.03741 0.00546 110%额定转速 0.03613 0.00596
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表 4 相同转速、不同出口压力时缸体倾覆最剧烈的位置
Table 4. The most severe overturning position of the cylinder body at the same rotational speed and different outlet pressures
测量工况 缸体倾覆最剧烈的位置区间/(°) 10 MPa 130.56～167.59 20 MPa 32.41～57.28 35 MPa 29.61～56.91 75%全流量 48.63～84.39 50%全流量 41.43～73.84 25%全流量 16.12～51.39 0流量 49.89～74.80
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表 5 相同出口压力、不同转速时缸体倾覆最剧烈的位置
Table 5. The most severe overturning position of the cylinder body at the same outlet pressure and different rotational speeds
测量工况 缸体倾覆最剧烈的位置区间/（°） 20%额定转速 40.63～80.13 40%额定转速 57.43～66.77 60%额定转速 9.26～40.90 80%额定转速 45.92～79.81 100%额定转速 29.61～56.91 110%额定转速 44.45～46.96
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