对转压气机中机匣处理的非定常影响

郭彦超; 高丽敏; 茅晓晨; 王磊

doi:10.13224/j.cnki.jasp.20210508

对转压气机中机匣处理的非定常影响

doi: 10.13224/j.cnki.jasp.20210508

郭彦超^{1, 2,},
高丽敏^{1, 2,*, ,},
茅晓晨^{1, 2},
王磊^{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: 国家科技重大专项（J2019-Ⅱ-0016-0037）；国家自然科学基金重大项目（51790512）；西北工业大学博士论文创新基金（CX2022044）

详细信息

作者简介:
郭彦超（1993-），男，博士生，研究领域为叶轮机械气动热力学。E-mail：guo_yc@mail.nwpu.edu.cn

通讯作者:
高丽敏（1973-），女，教授、博士生导师，博士，研究领域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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- 被引次数: 0
出版历程
- 收稿日期: 2021-09-12
- 网络出版日期: 2022-11-24

Unsteady effect on casing treatment in counter-rotating axial flow compressor

GUO Yanchao^{1, 2
,},
GAO Limin^{1, 2,*
, ,},
MAO Xiaochen^{1, 2},
WANG Lei^{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:
为探究不同形式的机匣处理扩稳机理和损失产生区别，以某两级对转压气机（CRAC）为研究对象，通过非定常数值模拟方法开展了自循环机匣处理（SRCT）和轴向槽机匣处理（ASCT）扩稳机理的研究。结果表明：SRCT和ASCT在近失速点均显著提高失速裕度和总压比，在峰值效率点附近增加效率损失；机匣处理通过作用于叶顶泄漏流和抑制压力势流减弱转子间动-动干涉效应；机匣处理槽内流场与转子相对位置相关，转子周期性的扫掠机匣处理槽增加了轴向槽内流动的非定常性，机匣处理槽内流动掺混是效率下降的主要原因。
- 对转压气机 /
- 自循环机匣处理 /
- 轴向槽机匣处理 /
- 非定常 /
- 扩稳机理
Abstract:
In order to reveal the difference between the stability enhancement mechanism and the loss of different forms of casing treatment, a two-stage counter-rotating axial flow compressor (CRAC) was taken as the research object, the stability enhancement mechanism of self-recirculating casing treatment (SRCT) and axial slot casing treatment (ASCT) was studied by unsteady numerical simulations. The results showed that both SRCT and ASCT significantly improved the stall margin and total pressure ratio at the near-stall point, and increased the efficiency loss at the peak efficiency point. The casing treatment reduced the dynamic-dynamic interference effect between the two rotors by acting on the tip leakage flow and suppressing the pressure potential flow. The flow in axial slots was related to the relative position of the rotor. The periodic sweeping of the rotor to the casing treatment slots increased the unsteadiness of flow in casing treatment slots, and the mixing of the flow in casing treatment slots was the main reason for the decrease of efficiency.
- counter-rotating axial flow compressor /
- self-recirculating casing treatment /
- axial slot casing treatment /
- unsteady /
- stability enhancement mechanism

HTML

图 1 两级对转压气机

Figure 1. Two-stage counter-rotating axial flow compressor

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图 2 网格示意图

Figure 2. Schematic diagram of grid

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图 3 网格无关性验证

Figure 3. Grid independence verification

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图 4 数值方法校核

Figure 4. Verification of numerical methods

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图 5 ASCT和SRCT结构示意图

Figure 5. Schematic diagram of SRCT and ASCT

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图 6 ASCT和SRCT网格示意图

Figure 6. Schematic diagram of grids of SRCT and ASCT

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图 7 对转压气机特性线

Figure 7. Characteristic curves of the counter-rotating axial flow compressor

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图 8 NSP2工况下R2叶顶泄漏涡随时间变化

Figure 8. Variation of R2 blade tip leakage vortex with time under the NSP2 condition

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图 9 PEP和NSP1工况下R2转子99%叶高处叶表C_p随时间的变化

Figure 9. Variation of the blade surface C_p at 99% blade span of R2 with time under the PEP and NSP1 conditions

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图 10 NSP1工况下R1和R2转子99%叶高处C_p云图分布

Figure 10. C_p contour distributions at 99% blade span of R1 and R2 under the NSP1 condition

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图 11 NSP1工况下不同时刻R1转子99%叶高处叶表C_p分布

Figure 11. C_p distribution of R1 at 99% blade span at different times under the NSP1 condition

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图 12 不同流量工况下叶表S_u分布

Figure 12. S_u distribution of blade surface under the different mass flow rate conditions

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图 13 NSP1工况下R2叶顶时均三维流线分布

Figure 13. Three-dimensional streamlines distribution at the tip of R2 under the NSP1 condition

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图 14 NSP1工况下R2进口气流角沿叶高变化

Figure 14. Distribution of R2 inlet flow angle under the NSP1 condition

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图 15 PEP工况下子午面熵的时均结果

Figure 15. Time-average result of entropy on z-r plane under the PEP condition

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图 16 PEP工况下R2转子99%叶高熵的时均结果

Figure 16. Time-average result of entropy at 99% blade span of R2 under the PEP condition

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图 17 PEP工况下CT槽内的流场

Figure 17. Flow fields in the CT slot under the PEP condition

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图 18 PEP工况下CT中不同时刻R2的TLF速度分布

Figure 18. Axial distribution of TLF of R2 at different times in the CT under the PEP condition

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表 1 对转压气机主要设计参数

Table 1. Main design parameters of the counter-rotating axial flow compressor

设计参数 IGV R1 R2 OGV

转速/10³ （r/min） 8 −8
叶顶间隙/mm 0.5 0.5
叶尖速度/（m/s） 167.6 167.6
叶片数 22 19 20 32
轮毂比 0.485 0.641

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