动压气体止推轴承间隙气动热及流动特性分析

乔湘云; 张镜洋; 陈卫东; 吕元伟; 罗欣洋

doi:10.13224/j.cnki.jasp.20210541

动压气体止推轴承间隙气动热及流动特性分析

doi: 10.13224/j.cnki.jasp.20210541

乔湘云^1,,
张镜洋^2,*, ,,
陈卫东^{1, 2},
吕元伟²,
罗欣洋³

1.
南京航空航天大学机械结构力学及控制国家重点实验室，南京 210016
2.
南京航空航天大学航天学院，南京 211106
3.
中国航空工业集团有限公司金城南京机电液压工程研究中心航空机电系统综合航空科技重点实验室，南京 211106

基金项目: 航空基金（201928052008）；中央高校基本科研业务费专项资金（NT2020021）

详细信息

作者简介:
乔湘云（1997-），女，硕士生，主要研究方向为传热与传质

通讯作者:
张镜洋（1981-），男，副教授，博士，主要研究方向为传热与传质。E-mail：zjy@nuaa.edu.cn

中图分类号: V229⁺.2；TH133.37
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出版历程
- 收稿日期: 2021-09-25
- 网络出版日期: 2022-12-22

Analysis of thermo-aerodynamic heat and flow characteristics in clearance of dynamic pressure gas thrust bearing

1.
State Key Laboratory of Mechanics and Control of Mechanical Structures， Nanjing University of Aeronautics and Astronautics，Nanjing 210016，China
2.
College of Astronautics，Nanjing University of Aeronautics and Astronautics，Nanjing 211106，China
3.
Aviation Key Laboratory of Science and Technology on Aero Electromechanical System Integration，Jincheng Nanjing Engineering Institute of Aircraft Systems， Aviation Industry Corporation of China, Limited，Nanjing 211106，China

摘要

摘要:
以波箔型动压气体止推轴承为研究对象，建立变截面气膜间隙润滑模型，研究了有无黏性耗散时动压气体止推轴承间隙压力场及温度场分布，获得几何参数以及转速对轴承间隙气膜压力和温度的影响规律。结果表明：考虑黏性耗散时，在收敛段末端和平直段外缘形成高温区；无黏性耗散时，轴承气膜高温区位于收敛间隙末端；轴承气膜温升随转速线性增加；考虑黏性耗散时，气膜温升随楔形因子的增加而减小，无黏性耗散热时则与之相反；气膜厚度越大，温升越小，厚度对轴承气膜温度分布无影响。本文参数范围内，黏性耗散产生的温升占比达90%。该研究证实了黏性耗散对动压气体止推轴承热流动物理机制有重要的影响，可为动压气体轴承设计和高效运行提供理论基础。
- 气体止推轴承 /
- 黏性耗散 /
- 温度场 /
- 转速 /
- 楔形因子
Abstract:
In order to reveal the thermo-aerodynamic characteristics of foil-type dynamic pressure gas thrust bearings in the presence or absence of viscosity dissipation, the lubrication models in the cross-section air film gap were built, and the term of viscosity dissipation and pressure variation term in the energy equations were decoupled and discussed respectively. The effects of wedge factor, air film thickness and rotation speed on flow field of the air film were obtained. The temperature distributions in air film between the presence and absence of viscosity dissipation were presented and compared. Results showed that the peak temperature in the air film was located near the circumferential air outlet and the side of outer diameter in the presence of viscosity dissipation, while the peak value took place near the end of the convergence channel in the absence of viscosity dissipation. Contrary to the case without viscosity dissipation, the magnitude of temperature rise in the air film increased with the increase of wedge factor in the presence of viscosity dissipation. The magnitude of temperature rise increased with the increase of the rotational speed, and had no effect on the variation of air film thickness. This study confirmed that viscosity dissipation played a significant role in the temperature rise and flow field of the foil-type dynamic pressure gas thrust bearings. In high-speed working conditions, the temperature rise in the presence of viscosity dissipation accounted for more than 90%. The results are of significant importance by providing basic design guidelines for temperature rise of the air film.
- gas thrust bearing /
- viscous dissipation /
- temperature field /
- rotational speed /
- wedge factor

HTML

图 1 动压气体止推轴承结构

Figure 1. Structure of dynamic pressure gas thrust bearing

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图 2 工作流体域边界条件

Figure 2. Boundary conditions for the working fluid region

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图 3 气膜间隙内流动示意图

Figure 3. Schematic diagram of flow in the gas clearance

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图 4 顶箔侧传热示意图

Figure 4. Schematic diagram of heat transfer at the top foil

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图 5 网格划分

Figure 5. Mesh generation

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图 6 计算流程图

Figure 6. Calculation Flowchart

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图 7 本文承载力计算结果与侯安平等^[21]实验结果对比

Figure 7. Comparison of bearing capacity numerical calculation results between in this paper and in Hou, et al^[21]

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图 8 本文温度计算结果与Liu等^[22]实验结果对比

Figure 8. Comparison of temperature numerical calculation results between in this paper and in Liu, et al^[22]

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图 9 无量纲气膜温度分布

Figure 9. Dimensionless gas film temperature distribution with different circumstances

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图 10 无量纲气膜压力分布

Figure 10. Dimensionless gas film pressure distribution

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图 11 气体无量纲密度和黏度分布

Figure 11. Distribution of gas dimensionless density and viscosity

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图 12 楔形因子对气膜最高无量纲温度和承载力影响

Figure 12. Effect of wedge factors on the film maximum dimensionless temperature and load capacity

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图 13 考虑黏性耗散时不同楔形因子条件下无量纲气膜温度分布

Figure 13. Dimensionless film temperature distribution on different wedge factors with viscous dissipation

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图 14 考虑压缩温升时不同楔形因子条件下无量纲气膜温度分布

Figure 14. Dimensionless film temperature distribution on different wedge factors with compression heat

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图 15 初始最小气膜厚度对气膜最高无量纲温度和承载力的影响

Figure 15. Effect of original minimal film thicknesses on the maximum dimensionless film temperature and loadcapacity of the bearings

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图 16 考虑黏性耗散时，不同初始最小气膜厚度条件下无量纲温度分布

Figure 16. Dimensionless gas film temperature distribution on different original minimal film thicknesses with viscous dissipation

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图 17 考虑压缩温升时，不同初始最小气膜厚度条件下无量纲温度分布

Figure 17. Dimensionless gas film temperature distribution on different original minimal film thicknesses with compression heat

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图 18 转速对气膜最高无量纲温度和承载力的影响

Figure 18. Effect of rotational speed on the maximum dimensionless film temperature and load capacity

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图 19 考虑黏性耗散热时，不同转速条件下气膜无量纲温度分布

Figure 19. Dimensionless film temperature distribution on different rotational speeds with viscous dissipation

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图 20 考虑压缩温升时，不同转速条件下气膜无量纲温度分布

Figure 20. Dimensionless film temperature distribution on different rotational speeds with compression heat

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表 1 计算工况

Table 1. Parameters of the calculation operating condition

参数	数值
初始最小气膜厚度h₂/μm	8～36
楔形因子h_f=h₃/h₂	2～8
转速n/10⁴ （r/min）	2～10
轴承外半径R₂/mm	21.5
轴承内半径R₁/mm	12
扇形瓦张角β/（°）	60
节距比b	0.5
箔片数N	6

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