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Research Papers

Stability Enhancement With Self-Recirculating Injection in Axial Flow Compressor

[+] Author and Article Information
Jichao Li

Key Laboratory of Advanced Energy and Power,
Institute of Engineering Thermophysics,
Chinese Academy of Sciences,
Beijing 100190, China
e-mail: lijichao@iet.cn

Juan Du

Key Laboratory of Advanced Energy and
Power,
Institute of Engineering Thermophysics,
Chinese Academy of Sciences,
Beijing 100190, China
e-mail: dujuan@iet.cn

Zhiyuan Li, Feng Lin

Key Laboratory of Advanced Energy and Power,
Institute of Engineering Thermophysics,
Chinese Academy of Sciences,
Beijing 100190, China

1Corresponding author.

Manuscript received August 25, 2016; final manuscript received February 28, 2018; published online May 10, 2018. Assoc. Editor: Nicole L. Key.

J. Turbomach 140(7), 071001 (May 10, 2018) (13 pages) Paper No: TURBO-16-1208; doi: 10.1115/1.4039806 History: Received August 25, 2016; Revised February 28, 2018

Self-recirculating injection, which bleeds air from the downstream duct of the last blade row and injects air as a wall jet upstream of the first rotor blade row, is experimentally investigated after the design of its structure in single- and three-stage axial flow compressors. External injection and outlet bleed air are selected for comparison. Results show that self-recirculating injection can improve the stall margin by 13.67% and 13% on the premise of no efficiency penalty in single- and three-stage axial flow compressors with only 0.7% and 4.2% of the total injected momentum ratio recirculated near stall, respectively. The self-recirculating injection is the best among all the three cases if the influence on pressure rise coefficient and efficiency is comprehensively considered. Moreover, findings indicate that the upstream injection plays an important role in terms of stability-enhancement. The details of the flow field are captured using a collection of pressure transducers on the casing with circumferential and chordwise spatial resolution. A detailed comparative analysis of the endwall flow indicates that the self-recirculating injection can postpone the occurrence of stalling in the proposed compressor by delaying the forward movement of the interface between the tip leakage flow (TLF) and main stream flow (MF), weakening the unsteadiness of TLF (UTLF), and sharply decreasing the circumferentially propagating speed dominated by the UTLF that triggers the spike-type stall inception. Finally, the stall control concept on the stage that first generates stall inception using self-recirculating injection is proposed. This study helps to guide the design of self-recirculating injection in actual application.

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Figures

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Fig. 1

Arrangement of the sensors and self-recirculating device: 1. inlet static pressure; 2. position of the injector; 3. pressure transducers; 4. position of the bleed port; 5. outlet static pressure.

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Fig. 2

Stall margin improvement versus injected momentum ratios cited from Li et al. [11] in single rotor compressor

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Fig. 3

Structure of injector

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Fig. 4

Structure of bleed port

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Fig. 5

Characteristic line with SC in single-stage axial flow compressor: (a) Ψ–Φ and (b) η–Φ

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Fig. 6

PRMS contours with SC: (a) Φ = 0.55, (b) Φ = 0.50, and (c) Φ = 0.48

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Fig. 7

Power spectrum density distribution with different flow coefficients under SC

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Fig. 8

Power spectrum density distribution of the dynamic pressure located at 26% Cax in the throttling process

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Fig. 9

Contours of the pressure signal with characteristic frequency band

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Fig. 10

Circumferential propagation of TLF with different flow coefficients under SC: (a) Φ = 0.58, (b) Φ = 0.53, (c) Φ = 0.50, (d) Φ = 0.46, and (e) stalling process

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Fig. 11

Stall margin improvement versus injected momentum ratio in the single-stage axial flow compressor

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Fig. 12

Characteristic curve line in single-stage axial flow compressor: (a) Ψ–Φ and (b) η–Φ

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Fig. 13

PRMS contours under different cases: (a) SC, (b) self-recirculating injection, and (c) external tip air injection

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Fig. 14

Power spectrum density distributions under different cases (Ф = 0.48)

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Fig. 15

Circumferentially propagating speed under different cases

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Fig. 16

Schematic diagram of the self-recirculating injection in three-stage axial flow compressor

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Fig. 17

Stall margin improvement as a function of injected momentum ratio in three-stage axial flow compressor

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Fig. 18

Characteristic curve line in three-stage axial flow compressor: (a) Ψ–Φ and (b) η–Φ

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Fig. 19

PRMS contours under different cases: (a) SC, (b) self-recirculating injection, and (c) tip air injection

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Fig. 20

Power spectrum density distribution under different cases in three-stage axial flow compressor

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Fig. 21

Circumferentially propagating speed with different cases

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Fig. 22

Pressure rise characteristic under different cases

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Fig. 23

Stalling process in three-stage axial flow compressor: (a) no-injection and (b) tip air injection

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