基于POD方法的对转压气机叶顶非定常流场分析

王磊; 高丽敏; 茅晓晨; 郭彦超; 俞一波

doi:10.13224/j.cnki.jasp.20220896

基于POD方法的对转压气机叶顶非定常流场分析

doi: 10.13224/j.cnki.jasp.20220896

王磊^{1, 2,},
高丽敏^{1, 2,*, ,},
茅晓晨^{1, 2},
郭彦超^{1, 2},
俞一波^{1, 2}

1.
西北工业大学动力与能源学院，西安 710129
2.
西北工业大学翼型、叶栅空气动力学国家级重点实验室，西安 710129

基金项目: 国家自然科学基金（52106057）；国家科技重大专项（J2019-Ⅱ-0016-0037）；国家自然科学基金重大专项（51790512）；国家级重点实验室稳定支持项目（D5050210015）

详细信息

作者简介:
王磊（1997-），男，博士生，研究方向为叶轮机械气动热力学。E-mail：wanglei304@mail.nwpu.edu.cn

通讯作者:
高丽敏（1973-），女，教授、博士生导师，博士，研究方向为叶轮机械气动热力学。E-mail：gaolm@nwpu.edu.cn

中图分类号: V231.3
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出版历程
- 收稿日期: 2022-11-22
- 网络出版日期: 2024-05-07

Analysis of tip unsteady flow field in a counter-rotating compressor based on POD method

WANG Lei^{1, 2
,},
GAO Limin^{1, 2,*
, ,},
MAO Xiaochen^{1, 2},
GUO Yanchao^{1, 2},
YU Yibo^{1, 2}

1.
School of Power and Energy，Northwestern Polytechnical University，Xi’an 710129，China
2.
The National Key Laboratory of Aerodynamic Design and Research，Northwestern Polytechnical University，Xi’an 710129，China

摘要

摘要:
为深入研究对转压气机内的非定常流动特征及其流动机理，基于非定常数值模拟和本征正交分解（POD）方法开展了对转压气机近失速工况下的叶顶非定常流场分析。结果表明：上游转子（R1）叶顶非定常流场的主导频率为1BPF（叶片通过频率），其主导结构主要是由下游势流的影响以及相邻叶片叶尖泄漏流及二次泄漏流冲击作用导致的，并且下游转子（R2）的势流作用对转子R1的非定常流动影响较大；在转子R2叶顶流场中，POD方法成功捕捉到了叶片前缘进口通道处由泄漏流溢流所导致的主要流动结构，其主导频率为0.8BPF，并且在转子R2非定常流场中起主导作用。同样转子R2受到两排转子干涉的影响，模态的主导频率为1BPF。此外，通过POD模态进行叶顶流场重构进一步反映出了对非定常流场起主导作用的流动结构。
- 对转压气机 /
- 本征正交分解（POD）方法 /
- 非定常流场 /
- POD模态 /
- 近失速流场
Abstract:
In order to investigate the unsteady flow characteristics and its flow mechanism in a counter-rotating compressor, a two-stage counter-rotating compressor was used as the research object, and the tip unsteady flow field analysis was carried out under the near-stall condition of the counter-rotating compressor based on the unsteady numerical simulation method in combination with the proper orthogonal decomposition (POD) method. The results showed that 1BPF (blade passing frequency) under near-stall conditions was taken as the dominant frequency of tip unsteady flow field in the upstream rotor, and its dominant structure was mainly caused by the influence of downstream potential flow and the impact of leakage flow and secondary leakage flow from the adjacent blade tip. Moreover, the potential flow of the downstream rotor had a greater influence on the unsteady flow in rotor R1. In the tip flow field in rotor R2, the POD modes succeeded in capturing the dominant flow structure at the inlet passage of the blade leading edge caused by spillage from the leakage flow with a dominant frequency of 0.8BPF, which played a dominant role in the unsteady flow field of rotor R2. Similarly, rotor R2 was affected by the interference of the two rotor rows, with a dominant frequency of 1BPF. In addition, the tip flow field reconstructed by the POD modes further reflected the dominant flow structure of unsteady flow field.
- counter-rotating compressor /
- proper orthogonal decomposition (POD) method /
- unsteady flow field /
- POD modes /
- flow field at near-stall condition

HTML

图 1 双级对转压气机视图

Figure 1. Views of two-stage counter-rotating compressor

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图 2 转子叶片网格图

Figure 2. Diagram of rotor blade grid

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图 3 实壁机匣实验和数值结果的总性能对比

Figure 3. Overall performance comparison between numerical and experimental results of solid casing

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图 4 近失速工况下转子99%叶高熵及流线分布

Figure 4. Distribution of entropy and streamlines of 99% blade span at near-stall condition

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图 5 近失速工况下转子叶尖间隙泄漏流分布

Figure 5. Distribution of blade tip leakage flow under near-stall condition

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图 6 2T/4时刻转子R1叶尖间隙泄漏流分布

Figure 6. Distribution of tip leakage flow in the R1 at 2T/4

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图 7 50%和99%叶高下的S_u分布

Figure 7. Distribution of S_u at 50% and 99% blade span

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图 8 静压监测位置示意图

Figure 8. Diagram of static pressure monitoring locations

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图 9 转子R1叶片99%叶高静压探针对应的频谱图

Figure 9. Spectrogram corresponding to static pressure probes at 99% blade span in rotor R1

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图 10 转子R2叶片99%叶高静压探针对应的频谱图

Figure 10. Spectrogram corresponding to static pressure probes at 99% blade span in rotor R2

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图 11 转子R1模态的特征值及其能量占比分布

Figure 11. Distribution of eigenvalues and energy ratio of modes in rotor R1

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图 12 转子R2模态的特征值及其能量占比分布

Figure 12. Distribution of eigenvalues and energy ratio of modes in rotor R2

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图 13 转子R1叶顶压力场的前7阶POD模态云图

Figure 13. Contours of the first seventh order POD modes at tip pressure field in rotor R1

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图 14 转子R2叶顶压力场的前7阶POD模态云图

Figure 14. Contours of the first seventh order POD modes at tip pressure field in rotor R2

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图 15 50%叶高下转子R1压力场的前5阶POD模态云图

Figure 15. Contours of the first fifth order POD modes of pressure field at 50% blade span in rotor R1

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图 16 50%叶高下转子R2压力场的前6阶POD模态云图

Figure 16. Contours of the first sixth order POD modes of pressure field at 50% blade span in rotor R2

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图 17 POD模态时间系数对应的频谱图

Figure 17. Spectrograms corresponding to time coefficients of POD modes

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图 18 转子R1内原始流场与POD模态重构流场对比

Figure 18. Comparison of original flow field and POD modes reconstructed flow field in rotor R2

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图 19 转子R2内原始流场与POD模态重构流场对比

Figure 19. Comparison of original flow field and POD modes reconstructed flow field in rotor R2

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表 1 转子主要设计参数

Table 1. Main design parameters of rotors

设计参数	数值
设计参数	R1	R2
转速N/（r/min）	8000	−8000
叶片数n	19	20
叶顶间隙τ/mm	0.5	0.5
叶尖弦长C/mm	83.2	76.9
叶尖速度/（m/s）	167.6	167.6
进口轮毂比	0.485	0.641

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