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变速条件下流体动压效应稳健性分析

张泽斌 景世钊 袁少朋 石明辉

张泽斌,景世钊,袁少朋,等. 变速条件下流体动压效应稳健性分析[J]. 北京航空航天大学学报,2024,50(4):1219-1228 doi: 10.13700/j.bh.1001-5965.2022.0480
引用本文: 张泽斌,景世钊,袁少朋,等. 变速条件下流体动压效应稳健性分析[J]. 北京航空航天大学学报,2024,50(4):1219-1228 doi: 10.13700/j.bh.1001-5965.2022.0480
ZHANG Z B,JING S Z,YUAN S P,et al. Robust analysis of hydrodynamic performance under variable rotation speeds[J]. Journal of Beijing University of Aeronautics and Astronautics,2024,50(4):1219-1228 (in Chinese) doi: 10.13700/j.bh.1001-5965.2022.0480
Citation: ZHANG Z B,JING S Z,YUAN S P,et al. Robust analysis of hydrodynamic performance under variable rotation speeds[J]. Journal of Beijing University of Aeronautics and Astronautics,2024,50(4):1219-1228 (in Chinese) doi: 10.13700/j.bh.1001-5965.2022.0480

变速条件下流体动压效应稳健性分析

doi: 10.13700/j.bh.1001-5965.2022.0480
基金项目: 国家自然科学基金(12272354);河南省自然科学基金(222300420547);河南省高等学校重点科研项目计划(20A460004)
详细信息
    通讯作者:

    E-mail:zebin.zhang@zzu.edu.cn

  • 中图分类号: TH117

Robust analysis of hydrodynamic performance under variable rotation speeds

Funds: National Natural Science Foundation of China (12272354); Natural Science Foundation of Henan Province (222300420547); Key Scientic Research Project of Colleges and Universities in Henan Province (20A460004)
More Information
  • 摘要:

    以油膜作为中间介质,对于高速旋转机械传动系统的可靠性、稳定性的提升有显著优势。而高速轴承-转子系统在加工制造和运行过程中,不可避免地存在影响系统承载性能的不确定性因素,影响油膜形状,导致承载性能发生变化,实际工作性能偏离设计目标。以高速动压油膜为研究对象,为掌握几何参数和转速对油膜承载性能波动的影响,进行稳健优化和分析,提取油膜性能稳健优化结果的特征区域。针对传动系统的不同需求,采用计算流体力学方法求解不同转速下的动压滑动轴承油膜压力场,进而求解其主要性能指标:承载力和摩擦功耗。建立研究目标的Kriging近似模型,并在样本点临近区域选择稳健目标计算的子空间,计算目标均值和方差。利用非支配排序遗传算法(NSGA-II)求解不同目标组合的Pareto最优解集。结合自组织映射图(SOM)方法进行相关性分析,提取设计目标与几何参数、转速之间的相关性特征,分析最优特征区域中偏心率对目标稳健性的影响,最终确定稳健性好的特征区域,并选择个别结果进行仿真计算验证。结果表明:所提出的最优性分析方法能够清晰展现出稳健最优性区域在设计空间中的分布情况,便于降低几何参数和转速的波动对油膜性能的影响;所提方法能提升优化设计结果的可实现性,有效促进理论设计与工程实际的衔接。

     

  • 图 1  动压滑动轴承结构示意

    Figure 1.  Illustration of dynamic plain bearing structure

    图 2  稳健性优化分析流程

    Figure 2.  Flowchart of robust optimization and analysis

    图 3  Pareto前沿及摩擦功耗−承载力满意度曲线

    Figure 3.  Pareto front and satisfactory curve of mean of friction power consumption and carrying capacity

    图 4  承载力均值和摩擦功耗均值最优解集的四维数据折线图

    Figure 4.  4D fold lines diagram of Pareto solutions of mean of friction power consumption and carrying capacity

    图 5  承载力均值及其标准差最优解集的四维数据折线图

    Figure 5.  4D fold lines diagram of Pareto solutions of mean and standard deviation of carrying capacity

    图 6  摩擦功耗均值及其标准差最优解集的四维数据折线图

    Figure 6.  4D fold lines diagram of Pareto solutions of the mean and standard deviation of friction power consumption

    图 7  承载力标准差和摩擦功耗标准差最优解集的四维数据折线图

    Figure 7.  4D fold lines diagram of Pareto solutions of standard deviation of friction power consumption and carrying capacity

    图 8  4目标最优解集的六维数据折线图

    Figure 8.  6D fold lines diagram of Pareto solutions of four objectives

    图 9  六维数据SOM及最优设计结果

    Figure 9.  SOM visualization of 6D data and optimal design solutions

    表  1  多目标优化结果

    Table  1.   Multi-objective optimization results

    设计方案 偏心率ε 转速N/(r·min−1) Fr/N Hf/W Fr相对误差/% Hf相对误差/%
    初始设计范围 [0.1,0.9] [103,104]
    初始设计 0.50 5 500 2 444 486.3
    优化“方案1” 0.79 3 051 4 209 218.7 5.6 21.3
    方案1-CFD结果 0.79 3 051 3 985 180.2
    优化“方案2” 0.67 3 045 3 257 195.1 1.3 9.8
    方案2-CFD结果 0.67 3 045 3 300 177.8
     注:滑动轴承轴颈直径为40 mm,半径间隙为0.05 mm。
    下载: 导出CSV
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出版历程
  • 收稿日期:  2022-06-11
  • 录用日期:  2022-08-15
  • 网络出版日期:  2022-08-29
  • 整期出版日期:  2024-04-29

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