Centrifugal inertia effects in high-speed hydrostatic air thrust bearings

A modified Reynolds equation for compressible flow is used to model the dynamics of pressurised air bearings in a simplified axisymmetric geometry. The formulation incorporates the effect of centrifugal inertia for high-speed operation. A steady-state analysis is presented with a fixed rotor–stator clearance. The load-carrying capacity of the bearing is assessed for both inward and outward pressurisation and the air-flow characteristics are seen to depend on the level and direction of pressurisation. A critical shaft speed is identified that maintains no-net flow by balancing inertia and pressurisation effects. The nonlinear air–rotor–stator dynamics are investigated by modelling the axial stator position using a spring–mass–damper system coupled to the air-film dynamics. Solutions are presented to illustrate the effect of various frequencies and amplitudes of forcing for a range of rotation speeds. The time-averaged axial force and mass flow of air are used as characteristic measures of bearing performance, and further numerical results are presented as part of a parameter space analysis. Using the method of arc-length continuation key measures of the numerical solutions are tracked for changing values of the physical parameters. The minimum rotor–stator clearance is used to evaluate the limit of stable periodic operation without resonant stator dynamics and incorporating high operating speeds.

[1]  S. B. Malanoski,et al.  Experimental Investigation of Air Bearings for Gas Turbine Engines , 1973 .

[2]  W. E. Langlois Isothermal squeeze films , 1961 .

[3]  Noël Brunetière,et al.  The Effect of Inertia on Radial Flows—Application to Hydrostatic Seals , 2006 .

[4]  T. A. Stolarski,et al.  Load-carrying capacity generation in squeeze film action , 2006 .

[5]  Sir Geoffrey Taylor Effects of Compressibility at Low Reynolds Number , 1957 .

[6]  Milton Abramowitz,et al.  Handbook of Mathematical Functions with Formulas, Graphs, and Mathematical Tables , 1964 .

[7]  Noël Brunetière,et al.  Influence of Fluid Flow Regime on Performances of Non-Contacting Liquid Face Seals , 2002 .

[8]  Marc Bonis,et al.  Prediction of the stability of air thrust bearings by numerical, analytical and experimental methods , 1996 .

[9]  I. Bucher,et al.  Coupled dynamics of a squeeze-film levitated mass and a vibrating piezoelectric disc: numerical analysis and experimental study , 2003 .

[10]  I. Etsion,et al.  Dynamic Analysis of Noncontacting Face Seals , 1982 .

[11]  M. Abramowitz,et al.  Handbook of Mathematical Functions With Formulas, Graphs and Mathematical Tables (National Bureau of Standards Applied Mathematics Series No. 55) , 1965 .

[12]  E. O. J. Salbu,et al.  Compressible Squeeze Films and Squeeze Bearings , 1964 .

[13]  T. A. Stolarski,et al.  Self-levitating sliding air contact , 2006 .

[14]  H. Power,et al.  A compressible flow model for the air-rotor–stator dynamics of a high-speed, squeeze-film thrust bearing , 2010, Journal of Fluid Mechanics.

[15]  E. Hasegawa,et al.  Inertia effects due to lubricant compressibility in a sliding externally pressurized gas bearing , 1982 .

[16]  H. Power,et al.  A numerical scheme for solving a periodically forced Reynolds equation , 2011 .

[17]  Abdulnaser I. Sayma,et al.  Aeroelasticity analysis of air-riding seals for aero-engine applications , 2002 .

[18]  T. A. Stolarski,et al.  Inertia effect in squeeze film air contact , 2008 .

[19]  John Munson,et al.  Development of film riding face seals for a gas turbine engine , 1992 .

[20]  S. Orszag,et al.  Advanced mathematical methods for scientists and engineers I: asymptotic methods and perturbation theory. , 1999 .

[21]  Keun Ryu,et al.  Gas Bearing Technology for Oil-Free Microturbomachinery: Research Experience for Undergraduate (REU) Program at Texas A&M University , 2009 .

[22]  Luis San Andrés,et al.  Effect of Frequency Excitation on Force Coefficients of Spiral Groove Gas Seals , 1999 .