航空燃油柱塞泵滑靴副混合润滑特性数值仿真

符江锋; 李华聪; 曾夏青; 刘显为

doi:10.13700/j.bh.1001-5965.2017.0309

航空燃油柱塞泵滑靴副混合润滑特性数值仿真

doi: 10.13700/j.bh.1001-5965.2017.0309

西北工业大学动力与能源学院, 西安 710072

基金项目:

航空科学基金 20150653006

中央高校基本科研业务费专项资金 G2017KY0003

详细信息

作者简介:
符江锋男, 博士, 助理研究员。主要研究方向:航空发动机控制、航空燃油泵建模与仿真

通讯作者:
符江锋, E-mail: fjf@nwpu.edu.cn

中图分类号: V228.1
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- 被引次数: 0
出版历程
- 收稿日期: 2017-05-15
- 录用日期: 2017-08-11
- 网络出版日期: 2018-05-20

Numerical simulation of hybrid lubrication characteristics of slipper pair of aviation fuel piston pump

College of Power and Energy, Northwestern Polytechnical University, Xi'an 710072, China

Funds:

Aeronautical Science Foundation of China 20150653006

the Fundamental Research Funds for the Central Universities G2017KY0003

More Information

Corresponding author: FU Jiangfeng, E-mail: fjf@nwpu.edu.cn

摘要

摘要:
针对航空燃油柱塞泵滑靴副的动静压混合支承下的润滑问题，在滑靴副的运动学和动力学模型基础上，考虑静压支承与滑靴非规则的空间曲线运动特征所产生的动压效应，建立了动静压效应下的滑靴副混合润滑数学模型。基于有限体积法进行了滑靴副的润滑特性仿真计算研究，分别对混合润滑机理下的油膜厚度变化规律、油膜压力分布影响因素和滑靴抗倾覆能力进行了仿真分析研究。仿真结果表明：动静压混合支承所得到的油膜厚度变化趋势更符合滑靴副实际的润滑状态；中心油膜厚度、滑靴最大倾斜角和转子转速主要对动压效应产生影响，而滑靴副进口压力即柱塞泵供油压力主要影响油膜的静压作用；提高滑靴的抗倾覆能力可通过增大滑靴底面工作半径或者减小滑靴中心油池半径来增强油膜的动压效应，抵消滑靴受到的倾覆力矩。
- 燃油柱塞泵 /
- 滑靴副 /
- 动压效应 /
- 润滑特性 /
- 静压支承
Abstract:
The aim of this paper was to solve the slipper pair lubrication problem of the aero fuel piston pump under the mixed support of dynamic and static pressure. Based on the mathematical model of kinematics and dynamics of slipper pair, the mathematical model of the hybrid lubrication of the slipper pair was established based on the dynamic pressure effect caused by the static pressure support and the irregular spatial curve of sliding shoe movement. Then the lubrication characteristics of slipper pair were simulated based on the finite volume method, and the variation law of the oil film thickness, the influence factors of the oil film pressure distribution and the anti-sliding performance of the sliding shoe were analyzed. The simulation results show that the variation trend of the oil film thickness obtained by the hybrid lubrication is consistent with the actual lubrication state, the thickness of the oil film, the maximum inclination angle of the slipper and the rotor speed have an important influence on the dynamic pressure effect, and the inlet pressure of the slipper pair mainly affects the static pressure of the oil film. The anti-overturning ability of the sliding shoe can be enhanced by increasing the working radius of the bottom surface of the sliding shoe or reducing the radius of the oil pool of the sliding shoe center, so as to counteract the overturning moment of the sliding shoe.
- fuel piston pump /
- slipper pair /
- dynamic pressure effect /
- lubrication characteristics /
- static pressure support

HTML全文

图 1 航空燃油柱塞泵滑靴副结构

Figure 1. Slipper pair structure of aviation fuel piston pump

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图 2 滑靴副受力仿真

Figure 2. Force simulation of slipper pair

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图 3 滑靴副中心油膜厚度

Figure 3. Central oil film thickness of slipper pair

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图 4 滑靴最大倾斜角

Figure 4. Maximum inclination angle of slipper

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图 5 α=180°时的油膜厚度分布

Figure 5. Distribution of oil film thickness with α=180°

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图 6 实际情况下的油膜压力分布

Figure 6. Distribution of oil film pressure in actual situation

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图 7 不同中心油膜厚度下的油膜压力分布

Figure 7. Oil film pressure distribution under different central oil film thickness

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图 8 不同最大倾斜角下的油膜厚度及压力分布

Figure 8. Oil film thickness and pressure distribution under different maximum inclination angles

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图 9 不同转子转速下的油膜压力分布

Figure 9. Distribution of oil film pressure under different rotor speeds

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图 10 不同供油压力下的油膜压力分布

Figure 10. Distribution of oil film pressure under different oil supply pressure

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图 11 不同供油压力下的油膜动静压支承力

Figure 11. Dynamic and static bearing force of oil film under different oil supply pressure

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图 12 不同滑靴底面工作半径下的油膜压力分布

Figure 12. Distribution of oil film pressure underdifferent working radius of slipper bottom

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图 13 不同滑靴底面工作半径下的油膜动静压支承力

Figure 13. Dynamic and static bearing force of oil film under different working radiuses of slipper bottom

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图 14 不同中心油池半径下的油膜压力分布

Figure 14. Distribution of oil film pressure under different central oil pool radius

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图 15 不同中心油池半径下的油膜动静压支承力

Figure 15. Dynamic and static bearing forces of oil film under different central oil pool radiuses

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