# Numerical Investigation of Inlet Distortion on an Axial Flow Compressor Rotor with Circumferential Groove Casing Treatment

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2 Huang Jian et al. / Chinese Journal of Aeronautics 21(2008) It is well-known that casing treatment can improve the stall margin of an axial flow compressor though some losses of isentropic efficiency are usually unavoidable [9-12]. Because the uniformity of inlet flow is always taken as the principal assumption in designing casing treatments, anywhere in published literature could scarcely found the data on a compressor with casing treatment under inlet flow distortion conditions [13]. In this article, the response of an axial flow compressor rotor with circumferential groove casing to the total pressure distortion of a steady inlet flow is numerically investigated by way of unsteady three dimensional Navier-Stokes equations. The general purpose is to investigate the flow fields in detail and enhance the physical understanding of the relationship between the inlet distortion and the casing treatment. It is expected that this will allow more distortion-tolerant designs to be developed in the future. 2 Tested Compressor Rotor with Circumferential Grooves The presented calculation is performed on a high-speed isolated axial flow compressor rotor, as is illustrated in Fig.1. The aerodynamic characteristics of compressor rotors are already available with an extensive database of experimental measurements, and the test rig has been widely used in the investigation of various forms of casing treatments. Table 1 lists the main design specifications of the tested compressor rotor. A circumferential groove casing, which has been proved effective in expanding the operating range, is chosen for the present study (see Fig.2). Fig.1 Cross-sectional view of tested axial flow compressor. Table 1 Specifications of tested compressor rotor Solidity at mid-span Rotor tip radius/mm 149 Hub-tip ratio 0.61 Chord/mm 30 Number of rotor blades 30 Nominal tip clearance of rotor blade/mm 0.3 Mid-span stagger angle/(º) 42.9 Design mass flow/(kg sec 1 ) 5.6 Design isentropic efficiency Design total-to-total pressure ratio Design rotating speed/(r min 1 ) (a) Schematic diagram of casing treatment ring (b) Schematic diagram of casing treatment Fig.2 Configuration of circumferential groove casing treatment. 3 Numerical Simulation Method Numerical simulations are carried out with the aid of commercial code EURANUS, an integral part of the software package NUMECA FINE [14]. The simulation could be divided into two parts: (1) Part 1 with clean inlet, in which numerical simulations are confined only to steady-state simulations on the base of the solution of the three- dimensional RANS equations. Therefore, it is sufficient to limit the computation to a single blade passage domain. Because circumferential grooves are axially symmetrical, they are defined in the rotating

4 Huang Jian et al. / Chinese Journal of Aeronautics 21(2008) Fig.5 Fixed circumferential distortion pattern at inlet of stationary blocks. unsteady interaction between stationary inlet blocks and downstream rotating blocks at an acceptable expense of computational effort. Besides, 20 Newton sub-iterations per real time step is applied in present unsteady calculations. To save CPU time, time-dependent solutions are generally initialized from a corresponding steady solution and only applied under near-stall operating conditions. 4 Numerical Results and Discussions 4.1 Overall performances flows, the total pressure ratio and the isentropic efficiency are converged to be constant and stable; otherwise, it is divergent. The calculated near-stall condition is the convergent solution under the highest back static pressure. As is shown in Fig.6, at 84% of design speed, if compared to the characteristics of the compressor rotor with clean inlet, the calculated total pressure ratio is reduced by 0.45% with the smooth walls and 0.17% with the circumferential groove casing treatment by distortion. The decrease in responding peak efficiency accounts for 0.89% and 0.20% respectively. It is clear that the circumferential groove casing treatment is able to enhance the aerodynamic stability of the compressor rotor either with or without inlet flow distortion. With clean inlet, the circumferential groove casing treatment lowers the stall mass flow by 11.5% and the peak efficiency by 1.1%. Under the inlet distorted condition, compared to the case with smooth walls, the one with the circumferential groove casing treatment shows the stall mass flows down by The overall performances of the compressor rotor with smooth walls and circumferential groove casing are examined at 84% of design speed either with or without inlet distortion (see Fig.6). In order to detect numerical surge boundary of the tested compressor rotor, by running the CFD model under step-wise increasing back static pressures, the simulation is believed to be convergent if the mass Fig.6 Overall performances of tested compressor rotor at 84% of design speed.

5 500 Huang Jian et al. / Chinese Journal of Aeronautics 21(2008) % and the peak efficiency by 0.38%. Although the experiment data are only available to the clean inlet condition without casing treatment, the calculated compressor rotor performance agrees well with the experimental data. The previous work by Chu, et al. [16] also showed the validity of CFD simulations to predict the effects of casing treatment on the compressor rotor under study. while with the circumferential groove casing, the effective suppression of the tip leakage vortex makes the blockage not the main factor to induce stalling. In this case, it is the serious flow separation at the suction surface of blade that leads to compressor flow stall eventually. 4.2 Flow mechanism under near-stall condition with clean inlet Fujita and Takata [17] indicated that the stall margin improvement is always related to the drop in peak efficiency for various types of casing treatments. In their previous study, Lu, et al. [18] showed that this compressor rotor exhibits a spike-type stall inception, which is blamed for the formation and forward movement of the tip leakage vortex in dynamic fluid processes. Fig.7 shows the relative Mach number at 99% span section either with or without circumferential groove casing treatment. In the case with the smooth wall casing, the tip leakage vortex moves forward along the pressure surface almost to the leading edge of blade, e.g. low relative Mach number zone. Consequently the blade passage is blocked by the low velocity zone as a result of the tip leakage vortex without any inflow passing through (see Fig.7(a)). By contrast, in the case with the circumferential groove casing, as is shown in Fig.7(b), the tip leakage vortex is suppressed by the circumferential flow in the grooves. Fig.8 shows the static pressure distribution at 99% span section. It is clear that the circumferential groove casing treatment reduces the static pressure difference between the blade pressure surface and the suction surface. Fig.9 shows the limiting streamlines on the suction surface of the rotor blades. Comparison between Figs.9(a) and 9(b) reveals that the separation line in the case with the circumferential groove casing moves forward farther away from the tailing edge than with the smooth wall casing. As is discussed above, with clean inlet, the formation and forward movement of the tip leakage vortex causes the compressor rotor to stall with the smooth wall casing; (a) With smooth walls (b) With circumferential groove casing treatment Fig.7 Relative Mach number at 99% of span (near stall condition). Fig.8 Static pressure distribution at 99% of span.

6 Huang Jian et al. / Chinese Journal of Aeronautics 21(2008) as the distorted inflow sector is traversed. Therefore, only one third of a period the stretch of time when (a) With smooth walls (b) With circumferential groove casing Fig.9 Limiting streamlines on suction surface. 4.3 Flow mechanism under near-stall conditions with inlet distortion Unsteady calculation is performed in the presence of inlet distortion at a near stall operating point either with or without the circumferential casing treatment. The process to find the time-dependent solution continued until a time periodic solution is perceived to be converged. The analysis of the predicted results is focused on examining the aerodynamic response of the rotor when the distorted inlet sector is encountered. Efforts are made to determine the physical mechanism which would get rid of the negative effects of the distortion, and discover the beneficial effects of the circumferential groove casing treatment, if any, on altering these reactions. Figs show the unsteady absolute total pressure and axial velocity variations at the rotor inlet (100% of chord length upstream from the leading edge) in a period. Obvious disadvantages of absolute total pressure and axial velocity resulting from inlet distortion are illustrated either with or without casing treatment. Fig.12 shows snapshots of relative Mach number and relative velocity vectors at 99% of span for an untreated compressor rotor, which are taken at three different moments when the compressor rotor reaches three different circumferential positions. It should be noted that, the pattern of inlet total pressure distortion is so defined that there are three blade passages in a period, but only one of them is the distorted one, which is denoted by passage 2 in Figs This article will highlight the flow field which changes from passage to passage Fig.10 Unsteady total pressure variations at rotor inlet, under near stall conditions.

7 502 Huang Jian et al. / Chinese Journal of Aeronautics 21(2008) Fig.11 Unsteady axial velocity variations at rotor inlet, under near stall conditions. (a) t = T/6 (b) t = 2T/6 (c) t = 3T/6 Fig.12 Relative Mach number and relative velocity vectors at 99% of span (under near stall conditions with smooth walls).

10 Huang Jian et al. / Chinese Journal of Aeronautics 21(2008) Technical Metnorandm, TMX-30, [6] Joubert H. Flowfield calculation in compressor operating with distorted inlet flow. ASME 90-GT-212, [7] Hah C, Rabe D C, Sullivan T J, et al. Effects of inlet distortion on the flow field in a transonic compressor rotor. ASME Journal of Turbomachinery 1998; 120(2): [8] Rabe D C, Williams C. Inlet flow distortion and unsteady blade response in a transonic axial-compressor rotor. ISABE , [9] Moore R D, Kovich G, Blade R J. Effect of casing treatment on overall performance and blade element performance of a compressor rotor. NASA TN D-6538, [10] Takata H, Tsakada Y. Stall margin improvement by casing treatment- its mechanism and effectiveness. ASME Journal of Engineering for Power 1977; 99(1): [11] Rabe D C, Hah C. Application of casing circumferential grooves for improved stall margin in a transonic axial compressor. ASME 2002-GT-30641, [12] Wilke L, Kau H P. A numerical investigation of the influence of casing treatments on the tip leakage flow in a HPC front stage. ASME 2002-GT-30642, distortion final report. NASA Contractor Report , [14] NUMECA Int. NUMECA s flow integrated environment for turbomachinery and internal flows.user manual version 6.1-1, [15] SAE Aerospace Council Division Technical Committee S-16. Inlet total pressure distortion consideration for gas turbine engines. SAE Aerospace Information Report AIR-1419, [16] Chu W L, Lu X G, Wu Y H. Numerical and experimental investigations of the flow in a compressor with circumferential groove. Journal of Aerospace Power 2006; 21(1): [in Chinese] [17] Fujita H, Takata H. A study on configuration of casing treatment for axial flow compressors. Bulletin of the JSME 1984; 27(230): [18] Lu X G, Chu W L, Zhu J Q. Mechanism of the interaction between casing treatment and tip leakage flow in a subsonic axial compressor. ASME 2006-GT-90077, Biography: Huang Jian Born in 1981, he is a Ph.D. candidate in Northwestern Polytechnical University. His main research interest is aerodynamic turbomachinery. [13] Hall E J, Topp D A, Heidegger N J, et al. End wall treatment inlet

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