Tip Clearance Actuation With Magnetic Bearings for High-Speed Compressor Stall Control

Magnetic bearings are widely used as active suspension devices in rotating machinery, mainly for active vibration control purposes. The concept of active tip-clearance control suggests a new application of magnetic bearings as servo-actuators to stabilize rotating stall in axial compressors. This paper presents a first-of-a-kind feasibility study of an active stall control experiment with a magnetic bearing servo-actuator in the NASA Glenn high-speed single-stage compressor test facility. Together with CFD and experimental data a two-dimensional, incompressible compressor stability model was used in a stochastic estimation and control analysis to determine the required magnetic bearing performance for compressor stall control. The resulting requirements introduced new challenges to the magnetic bearing actuator design. A magnetic bearing servo-actuator was designed that fulfilled the performance specifications. Control laws were then developed to stabilize the compressor shaft. In a second control loop, a constant gain controller was implemented to stabilize rotating stall. A detailed closed loop simulation at 100 percent corrected design speed resulted in a 2.3 percent reduction of stalling mass flow, which is comparable to results obtained in the same compressor by Weigl et al. (1998. ASME J. Turbomach. 120, 625-636) using unsteady air injection. The design and simulation results presented here establish the viability of magnetic bearings for stall control in aeroengine high-speed compressors. Furthermore, the paper outlines a general design procedure to develop magnetic bearing servo-actuators for high-speed turbomachinery.

[1]  Edward M. Greitzer,et al.  Active suppression of aerodynamic instabilities in turbomachines , 1989 .

[2]  L. Reid,et al.  Performance of single-stage axial-flow transonic compressor with rotor and stator aspect ratios of 1.63 and 1.78, respectively, and with design pressure ratio of 1.82 , 1978 .

[3]  E. Greitzer,et al.  A Method for Assessing Effects of Circumferential Flow Distortion on Compressor Stability , 1987 .

[4]  Alfons Traxler Eigenschaften und Auslegung von berührungsfreien elektromagnetischen Lagern , 1986 .

[5]  L. San Andres,et al.  Imbalance response of a rotor supported on open-ends integral squeeze film dampers , 1999 .

[6]  D. C. Wisler,et al.  Effects of Non-Axisymmetric Tip Clearance on Axial Compressor Performance and Stability , 1997 .

[7]  F. Moore,et al.  A Theory of Post-Stall Transients in Axial Compression Systems: Part I—Development of Equations , 1986 .

[8]  L. Reid,et al.  Design and overall performance of four highly loaded, high speed inlet stages for an advanced high-pressure-ratio core compressor , 1978 .

[9]  Raoul Herzog,et al.  Unbalance compensation using generalized notch filters in the multivariable feedback of magnetic bearings , 1996, IEEE Trans. Control. Syst. Technol..

[10]  John J. Adamczyk,et al.  Simulation of three-dimensional viscous flow within a multistage turbine , 1990 .

[11]  Edward M. Greitzer,et al.  1997 Best Paper Award—Controls and Diagnostics Committee: Active Stabilization of Rotating Stall and Surge in a Transonic Single-Stage Axial Compressor , 1998 .

[12]  Kenneth A. Gordon Three-dimensional rotating stall inception and effects of rotating tip clearance asymmetry in axial compressors , 1999 .

[13]  Alan H. Epstein,et al.  Active Stabilization of Rotating Stall and Surge in a Transonic Single Stage Axial Compressor , 1997 .