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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

符江锋, 李华聪, 曾夏青, 等 . 航空燃油柱塞泵滑靴副混合润滑特性数值仿真[J]. 北京航空航天大学学报, 2018, 44(5): 939-950. doi: 10.13700/j.bh.1001-5965.2017.0309
引用本文: 符江锋, 李华聪, 曾夏青, 等 . 航空燃油柱塞泵滑靴副混合润滑特性数值仿真[J]. 北京航空航天大学学报, 2018, 44(5): 939-950. doi: 10.13700/j.bh.1001-5965.2017.0309
FU Jiangfeng, LI Huacong, ZENG Xiaqing, et al. Numerical simulation of hybrid lubrication characteristics of slipper pair of aviation fuel piston pump[J]. Journal of Beijing University of Aeronautics and Astronautics, 2018, 44(5): 939-950. doi: 10.13700/j.bh.1001-5965.2017.0309(in Chinese)
Citation: FU Jiangfeng, LI Huacong, ZENG Xiaqing, et al. Numerical simulation of hybrid lubrication characteristics of slipper pair of aviation fuel piston pump[J]. Journal of Beijing University of Aeronautics and Astronautics, 2018, 44(5): 939-950. doi: 10.13700/j.bh.1001-5965.2017.0309(in Chinese)

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
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

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

Funds: 

Aeronautical Science Foundation of China 20150653006

the Fundamental Research Funds for the Central Universities G2017KY0003

More Information
  • 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。

     

  • 图 1  航空燃油柱塞泵滑靴副结构

    Figure 1.  Slipper pair structure of aviation fuel piston pump

    图 2  滑靴副受力仿真

    Figure 2.  Force simulation of slipper pair

    图 3  滑靴副中心油膜厚度

    Figure 3.  Central oil film thickness of slipper pair

    图 4  滑靴最大倾斜角

    Figure 4.  Maximum inclination angle of slipper

    图 5  α=180°时的油膜厚度分布

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

    图 6  实际情况下的油膜压力分布

    Figure 6.  Distribution of oil film pressure in actual situation

    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

    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

    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

    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

    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

    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

    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

    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

    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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出版历程
  • 收稿日期:  2017-05-15
  • 录用日期:  2017-08-11
  • 刊出日期:  2018-05-20

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