航空滑油系统旋板泵空化特性及对泵性能影响

王格; 王怡锦; 贺登辉; 阳丽娜; 曹明; 白博峰

doi:10.13224/j.cnki.jasp.20240106

航空滑油系统旋板泵空化特性及对泵性能影响

doi: 10.13224/j.cnki.jasp.20240106

王格^{1, 2,},
王怡锦^{1, 2},
贺登辉^{1, 2, 3,*, ,},
阳丽娜^{4, 5},
曹明^{4, 5},
白博峰³

1.
西安理工大学省部共建西北旱区生态水利国家重点实验室，西安 710048
2.
西安理工大学水利水电学院动力工程系，西安 710048
3.
西安交通大学动力工程多相流国家重点实验室，西安 710049
4.
中国航发商用航空发动机有限责任公司，上海 200241
5.
上海市商用航空发动机工程技术研究中心，上海 200241

基金项目: 国家自然科学基金面上项目（52376031）

详细信息

作者简介:
王格（2000-），女，硕士生，研究领域为航空滑油泵空化特性。E-mail：gewangxaut@163.com

通讯作者:
贺登辉（1986-），男，副教授，博士，研究领域为航空油泵多相流动及故障诊断。E-mail：hedenghui@xaut.edu.cn

中图分类号: V233.4
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出版历程
- 收稿日期: 2024-02-27
- 网络出版日期: 2024-09-02

Cavitation characteristics of rotary vane pump in aeroengine lubricating oil system and their effects on pump performance

WANG Ge^{1, 2
,},
WANG Yijin^{1, 2},
HE Denghui^{1, 2, 3,*
, ,},
YANG Lina^{4, 5},
CAO Ming^{4, 5},
BAI Bofeng³

1.
State Key Laboratory of Eco-hydraulic in Northwest Arid Region of China，Xi’an University of Technology，Xi’an 710048，China
2.
Department of Power Engineering，Institute of Water Resources and Hydro-electric Engineering，Xi’an University of Technology，Xi’an 710048，China
3.
State Key Laboratory of Multiphase Flow in Power Engineering，Xi’an Jiaotong University，Xi’an 710049，China
4.
Commercial Aircraft Engine Company Limited，Aero Engine Corporation of China，Shanghai 200241，China
5.
Shanghai Center of Research for Commercial Aircraft Engine Engineering Techniques，Shanghai 200241，China

摘要

摘要:
为满足大推力、高转速航空发动机滑油系统对高性能滑油泵的需求，针对新型高速旋板式滑油泵开展了数值模拟研究，采用Mixture多相流模型，Singhal全空化模型和renormalization group（RNG） k-ε湍流模型开展数值计算，并通过实验验证数值模拟方法的可靠性，进而分析不同入口压力和油液温度条件下旋板泵空化特性及对泵性能影响规律。结果表明：空化气体主要分布在吸油侧容积腔内，以及旋板吸力面和贴近转子内壁处。随着入口压力的降低和油液温度的升高，旋板泵内空化现象加剧，空化气体增多，进而使得泵出口平均排油流量减小，容积效率降低；当入口压力降低至40 kPa，温度升至373.15 K时，泵出口平均排油流量和容积效率均显著降低；监测点压力脉动呈现低频高幅脉动的特点。旋板泵的空化不仅影响其排油量和容积效率，而且也直接影响泵的稳定可靠工作。
- 滑油系统 /
- 旋板泵 /
- 空化 /
- 流量特性 /
- 容积效率 /
- 压力脉动
Abstract:
To meet the demand for high-performance oil pumps in the lubricating oil system of high thrust and high-speed aeroengines, numerical simulation was conducted on a new high-speed rotary vane oil pump. The Mixture multiphase flow model, Singhal full cavitation model, and renormalization group（RNG） k-ε turbulence model were employed for numerical calculation, and the reliability of the numerical simulation method was verified through experiments. Then, cavitation characteristics of the rotary vane pump and its impact on pump performance under different inlet pressure and oil temperature conditions were analyzed. The results showed that the cavitation gas was mainly distributed in the volume chamber on the oil suction side, as well as on the suction surface of the rotary vane and near the inner wall of the rotor. With the decrease of inlet pressure and the increase of oil temperature, the cavitation phenomenon inside the rotary vane pump intensified, and the cavitation gas increased, which in turn led to a decrease in the average oil discharge flow rate at the pump outlet and a decrease in volumetric efficiency. When the inlet pressure dropped to 40 kPa and the temperature rose to 373.15 K, the average oil discharge flow rate and volumetric efficiency at the pump outlet both significantly decreased. The pressure pulsation at the monitoring point exhibited low-frequency and high-amplitude pulsation characteristics. The cavitation of the rotary vane pump affected not only its oil discharge and volumetric efficiency, but also the stable and reliable operation of the pump.
- lubricating oil system /
- rotary vane pump /
- cavitation /
- flow characteristics /
- volumetric efficiency /
- pressure pulsation

HTML

图 1 旋板泵三维模型示意图

Figure 1. 3D geometry model of rotary vane pump

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图 2 计算网格无关性验证

Figure 2. Grid independence verification

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图 3 旋板泵网格划分示意图

Figure 3. Mesh division for rotary vane pump

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图 4 实验系统图

Figure 4. Experimental system diagram

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图 5 出口流量的数值模拟结果与实验对比

Figure 5. Comparison of outlet flowrate between numerical simulation and experimental results

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图 6 特征截面选择示意图

Figure 6. Internal section of the rotary vane pump

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图 7 不同入口压力下特征截面空化云图

Figure 7. Characteristic cross-section cavitation cloud map under different inlet pressures

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图 8 不同入口压力下旋板泵出口平均流量-效率曲线

Figure 8. Average outlet flowrate-efficiency curves of rotary vane pump under different inlet pressures

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图 9 出油侧压力脉动监测点分布示意图

Figure 9. Distribution of pressure fluctuation monitoring points on the oil outlet side

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图 10 各个压力监测点压力脉动曲线（101 kPa, 393.15 K）

Figure 10. Pressure fluctuation of different monitoring points （101 kPa, 393.15 K）

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图 11 不同入口压力下监测点2压力脉动时域曲线

Figure 11. Time domain diagram of pressure pulsation at monitoring point 2 under different inlet pressures

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图 12 不同入口压力下监测点2压力脉动频域曲线

Figure 12. Frequency domain diagram of pressure pulsation at monitoring point 2 under different inlet pressures

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图 13 不同油液温度下旋板泵空化云图

Figure 13. Cavitation cloud map under different oil temperatures

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图 14 不同油液温度下旋板泵出口平均流量-效率曲线

Figure 14. Average outlet flowrate-efficiency curves of rotary vane pump under different temperature

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图 15 不同油液温度下监测点2压力脉动时域曲线

Figure 15. Time domain diagram of pressure pulsation at monitoring point 2 under different temperatures

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图 16 不同油液温度监测点2压力脉动频域曲线

Figure 16. Frequency domain diagram of pressure pulsation at monitoring point 2 under different temperatures

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表 1 润滑油物性

Table 1. Physical properties of lubricating oil

温度/K	密度/（kg/m³）	动力黏度/（Pa·s）	饱和蒸汽压/Pa
393.15	918.7	0.00349	4716
373.15	933.7	0.00502	3665
353.15	948.7	0.0078	2359
333.15	963.7	0.01333	1391.05
313.15	978.7	0.02574	594.42

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表 2 计算工况表

Table 2. Calculation conditions

影响因素	数值
入口压力/kPa	101、80、60、40、25、15
油液温度/K	393.15、373.15、353.15、333.15、313.15

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表 3 不同入口压力对应的主频

Table 3. Main frequencies corresponding to different inlet pressures

入口压力/kPa	101	80	60	40	25	15
主频/Hz	1f_n1	1f_n1	1f_n1	4f_n1	4f_n1	4f_n1

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表 4 不同油液温度对应的主频

Table 4. Main frequencies corresponding to different inlet pressures

油液温度/K	393.15	373.15	353.15	333.15	313.15
主频/Hz	1f_n1	1f_n1	1f_n1	1f_n1	1f_n1

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