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1 Parametric Study of Bump Foil Gas Bearings for Industrial Applications 2011 ASME Turbo Expo Congress & Exhibition GT2011-46767

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Presentation on theme: "1 Parametric Study of Bump Foil Gas Bearings for Industrial Applications 2011 ASME Turbo Expo Congress & Exhibition GT2011-46767"— Presentation transcript:

1 1 Parametric Study of Bump Foil Gas Bearings for Industrial Applications 2011 ASME Turbo Expo Congress & Exhibition GT Oscar De Santiago CIATEQ A.C. Queretaro, Qro, Mexico Luis San Andres Texas A&M University College Station, TX, USA

2 2 Oil-Free Bearings for Turbomachinery Justification Current advancements in vehicle turbochargers and midsize gas turbines need of proven gas bearing technology to procure compact units with improved efficiency in an oil-free environment. Also, Oil-free turbomachinery and subsea compression are among major focuses in modern energy industry. DOE, DARPA, NASA interests range from applications as portable fuel cells (< 60 kW) in microengines to midsize gas turbines (< 250 kW) for distributed power and hybrid vehicles. Gas Bearings allow weight reduction, energy and complexity savings higher temperatures, without needs for cooling air improved overall engine efficiency

3 3 Magnetic bearings Available Bearing Technologies Low to medium temperatures Moderate loads Need control systems Need back-up bearings Long history of operation in some specific industrial applications Current Magnetic Bearing solution is expensive and even more expensive (and difficult) to make it reliable Schweitzer/Maslen

4 4 Oil-Free NO DN limit Low friction and power loss Thermal management GAS BEARINGS AIAA Gas Foil Bearing GT Flexure Pivot Bearing AIAA Rolling element bearings PowerMEMS 2003 Low temperatures Low DN limit (< 2 M) Need lubrication system NICH Center, Tohoku University Herringbone grooved bearing Precision fabrication process Low load capacity and stiffness and little damping Available Bearing Technologies

5 5 Microturbomachinery as per IGTI ASME Paper No. GT Honeywell, Hydrogen and Fuel Cells Merit Review Automotive turbochargers, turbo expanders, compressors, Distributed power (Hybrid Gas turbine & Fuel Cell), Hybrid vehicles Drivers: deregulation in distributed power, environmental needs, increased reliability & efficiency International Gas Turbine Institute Max. Power ~ 250 kWatt

6 6 Micro Gas Turbines MANUFACTURER OUTPUT POWER (kW) Bowman 25, 80 Capstone 30, 60, 200 Elliott Energy Systems 35, 60, 80, 150 General Electric 175 Ingersoll Rand 70, 250 Turbec, ABB & Volvo 100 Microturbine Power Conversion Technology Review, ORNL/TM-2003/74. Cogeneration systems with high efficiency Multiple fuels (best if free) 99.99X% Reliability Low emissions Reduced maintenance Lower lifecycle cost 60kW MGT Hybrid System : MGT with Fuel Cell can reach efficiency > 60% Ideal to replace reciprocating engines. Low footprint desirable

7 7 Examples of commercial applications Micro Turbines Capstone of California Turbo chargers Honeywell on the race

8 8 Industrial Air Compressors Samsungs successful Micro Turbo Master line of compressors feature gas foil bearings Pressures up to 130 psig Powers up to 0.13 MW Samsung has another line (Turbo Master) of air compressors with pressures up to 300 psig and power up to 2.4 MW (~20x larger). Run on TPJB. Whats next ?? Examples of commercial applications 2011

9 9 Largest power to weight ratio, Compact & low # of parts High energy density Reliability and efficiency, Low maintenance Extreme temperature and pressure Environmentally safe (low emissions) Lower lifecycle cost ($ kW) High speed Materials Manufacturing Processes & Cycles Fuels Rotordynamics & (Oil-free) Bearings & Sealing Coatings: surface conditioning for low friction and wear Ceramic rotors and components Automated agile processes Cost & number Low-NOx combustors for liquid & gas fuels TH scaling (low Reynolds #) Best if free (bio-fuels) MTM – Needs, Hurdles & Issues

10 10 Gas Bearings for Oil-Free MTM Advantages of gas bearings over oil-lubricated bearings –Process gas is cleaner and eliminates contamination by buffer lubricants –Gases are more stable at extreme temperatures and speeds (no lubricant vaporization, cavitation, solidification, or decomposition) –Gas bearing systems are lower in cost: less power usage and small friction, enabling savings in weight and piping Gas Bearings Must Be Simple!

11 11 Ideal gas bearings for MTM Simple – low cost, small geometry, low part count, constructed from common materials, manufactured with elementary methods. Load Tolerant – capable of handling both normal and extreme bearing loads without compromising the integrity of the rotor system. High Rotor Speeds – no specific speed limit (such as DN) restricting shaft sizes. Small Power losses. Good Dynamic Properties – predictable and repeatable stiffness and damping over a wide temperature range. Reliable – capable of operation without significant wear or required maintenance, able to tolerate extended storage and handling without performance degradation. +++ Modeling/Analysis (anchored to test data) available

12 12 Gas Bearings for MTM What are the needs? Make READY technology for industrial application by PUSHING development to make out of the shelf item with proven results for a wide range of applications; engineered product with well known manufacturing process; known (verifiable) performance with solid laboratory and field experiences

13 13 Gas Bearings Research at TAMU Thrust: Investigate conventional bearings of low cost, easy to manufacture (common materials) and easy to install & align. Combine hybrid (hydrostatic/hydrodynamic) bearings with low cost coating to allow for rub-free operation at start up and shut down Major issues: Little damping, Wear at start & stop, Nonlinear behavior (subsync. whirl) See References at end

14 14 Gas Bearing Research at TAMU 2001/2 - Three Lobe Bearings 2003/4 - Rayleigh Step Bearings Flexure Pivot Tilting Pad Bearings : Bump-type Foil Bearings : Metal Mesh Foil Bearings Stability depends on feed pressure. Stable to 80 krpm with 5 bar pressure Worst performance to date with grooved bearings Stable to 93 krpm w/o feed pressure. Operation to 100 krpm w/o problems. Easy to install and align. Industry standard. Reliable but costly. Models anchored to test data. Cheap technology. Still infant. Users needed See References at end

15 15 Gas Foil Bearings

16 16 Gas Foil Bearings Advertised advantages: high load capacity (>20 psig), rotordynamically stable, tolerance of misalignment and shocks

17 17 Gas Foil Bearings – Bump type Series of corrugated foil structures (bumps) assembled within a bearing sleeve. Integrate a hydrodynamic gas film in series with one or more structural layers. Applications: APUs, ACMs, micro gas turbines, turbo expanders Reliable Tolerant to misalignment and debris, also high temperature Need coatings to reduce friction at start-up & shutdown Damping from dry-friction and operation with limit cycles

18 18 Foil Bearings (+/-) Increased reliability: load capacity (< 20 psi) No lubricant supply system, i.e. reduce weight High and low temperature capability (> 1,000 C) No scheduled maintenance Tolerate high vibration and shock load. Quiet operation Endurance: performance at start up & shut down (lift off speed) Little test data for rotordynamic force coefficients & operation with limit cycles (sub harmonic motions) Thermal management for high temperature applications (gas turbines, turbochargers) Predictive models lack validation for GFB operation at HIGH TEMPERATURE

19 19 Computational analysis

20 20 Theoretical basis Solve Reynolds equation for compressible flow (isothermal case). Coupled to bump metal sheet deformation (non- linear stiffness and damping). Iterative solution to find bearing equilibrium position. Perturbation analysis to find dynamic performance (frequency-dependent stiffness and damping coefficients). Refs: San Andrés (2009), Arghir (2004), Iordanoff (1999), Heshmat (1992)

21 21 The computational program Code: XL_GFB THD Windows OS and MS Excel 2003 (minimum requirements) Fortran 99 Executables for FE underspring structure and gas film analyses. Prediction of forced – static & dynamic- performance. Excel® Graphical User Interface (US and SI physical units). Input & output (graphical) Compatible with XL TRC 2 and XL ROTOR codes

22 22 Graphical User Interface Worksheet: Shaft & Bearing models (I)

23 23 Graphical User Interface Worksheet: Shaft & Bearing models (II)

24 24 Graphical User Interface Worksheet: Top Foil and Bump Models

25 25 Graphical User Interface Worksheet: Foil Bearing (Operation and Results)

26 26 Parametric Study

27 27 Results Bump unit area stiffness lowers as bump pitch increases Bump unit area stiffness increases with foil thickness Example bearing (Ref [3]) :

28 28 Results Benchmarking with independent experiments – Generation 1 bearing (Ref [3]). Used to find practical limit of film thickness Measured load capacity (Ref [3]) 31 psi Calibration point 2 Calibration point 1 Current predictions, constant load of 31 psi

29 29 Results Base bearing (Ref [3]) :

30 30 Rule of thumb for design Bearing scaling: use Della Corte´s rule: W ~ N L D^2 Bump scaling: K new = K orig / f ; f is de diameter scale factor From observations of bump stiffness and bearing performance predictions:

31 31 Application example Rotor Diameter, D132 mm (5.21 in) Length, L169 mm (6.64 in) Radial clearance, c* 96 µm (3.8 mil) Load, W1,421 N (319 lb) W/LD0.636 bar (9.21 psi) Industrial compressor for injection service 8 impellers, 640 lb rotor Re-configured rotor – move bearings INBOARD of gas seals Use larger diameter at bearing location Expected speed range: 3 to 20 krpm krpm MCOS most typical Bearing characteristics

32 32 Application - rotordynamics 5th Linear stability analysis Predicted stiffness range Compressor can´t cross these speeds (requires more damping)

33 33 Observations –Conceptually, scaled gas foil bearings can support an industrial, flexible rotor. –Re-location of bearings is necessary to decrease unit load, but it is feasible in the compressor working environment. –Rotor-bearing system requires additional damping to control shaft vibration at critical speeds.

34 34 Closure Dominant challenges for gas bearing technology: –Low gas viscosity requires minute clearances to generate load capacity. –Damping & rotor stability are crucial –Inexpensive coatings to reduce drag and wear – Bearing design & manufacturing process well known –Adequate thermal management to extend operating envelope into high temperatures

35 35 Closure Other pressing challenges for gas bearing technology: intermittent contact and damaging wear at startup & shut down, and temporary rubs during normal operating conditions Current research focuses on coatings (materials), rotordynamics (stability) & high temperature (thermal management ) Need Low Cost & Long Life Solution!

36 36 References Oil-Free Bearings for Turbomachinery

37 37 References Foil Bearings ASME GT De Santiago, O., and San Andrés, L., 2011, Parametric Study of Bump Foil Gas Bearings for Industrial Applications ASME GT San Andrés, L.., and Ryu, K., 2011, On the Nonlinear Dynamics of Rotor-Foil Bearing Systems: Effects of Shaft Acceleration, Mass Imbalance and Bearing Mechanical Energy Dissipation. ASME GT NASA/TM Howard, S., and San Andrés, L., 2011, A New Analysis Tool Assessment for Rotordynamic Modeling of Gas Foil Bearings, ASME J. Eng. Gas Turbines and Power, v133 ASME GT San Andrés, L., Ryu, K., and Kim, T-H, 2011, Thermal Management and Rotordynamic Performance of a Hot Rotor-Gas Foil Bearings System. Part 2: Predictions versus Test Data, ASME J. Eng. Gas Turbines and Power, v133 ASME GT San Andrés, L., Ryu, K., and Kim, T-H, 2011, Thermal Management and Rotordynamic Performance of a Hot Rotor-Gas Foil Bearings System. Part 1: Measurements, ASME J. Eng. Gas Turbines and Power, v133 8th IFToMM Int. Conf. on Rotordynamics San Andrés, L., Camero, J., Muller, S., Chirathadam, T., and Ryu, K., 2010, Measurements of Drag Torque, Lift Off Speed, and Structural Parameters in a 1st Generation Floating Gas Foil Bearing, Seoul, S. Korea (Sept.) ASME GT San Andrés, L., Kim, T.H., Ryu, K., Chirathadam, T. A., Hagen, K., Martinez, A., Rice, B., Niedbalski, N., Hung, W., and Johnson, M., 2009, Gas Bearing Technology for Oil-Free Microturbomachinery – Research Experience for Undergraduate (REU) Program at Texas A&M University AHS 2009 paperKim, T. H., and San Andrés, L., 2010, Thermohydrodynamic Model Predictions and Performance Measurements of Bump-Type Foil Bearing for Oil-Free Turboshaft Engines in Rotorcraft Propulsion Systems, ASME J. of Tribology, v132

38 38 References Foil Bearings ASME GT San Andrés, L., and Kim, T.H., 2010, Thermohydrodynamic Analysis of Bump Type gas Foil Bearings: A Model Anchored to Test Data, ASME J. Eng. Gas Turbines and Power, v132 IJTC Kim, T.H., and San Andrés, L., 2009, "Effects of a Mechanical Preload on the Dynamic Force Response of Gas Foil Bearings - Measurements and Model Predictions," Tribology Transactions, v52 ASME GT IJTC Kim, T. H., and San Andrés, L., 2009, Effect of Side End Pressurization on the Dynamic Performance of Gas Foil Bearings – A Model Anchored to Test Data, ASME J. Eng. Gas Turbines and Power, v Best PAPER Rotordynamics IGTI ASME GT San Andrés, L., and Kim, T.H., 2009, Analysis of Gas Foil Bearings Integrating FE Top Foil Models, Tribology International, v42 AIAA San Andrés, L., and T.H. Kim, 2007, Issues on Instability and Force Nonlinearity in Gas Foil Bearing Supported Rotors, 43 rd AIAA/ASME/SAE/ASEE Joint Propulsion Conference, Cincinnati, OH, July 9-11 ASME GT Kim, T.H., and L. San Andrés, 2008, Heavily Loaded Gas Foil Bearings: a Model Anchored to Test Data, ASME J. Eng. Gas Turbines and Power, v130 ASME GT San Andrés, L., D. Rubio, and T.H. Kim, 2007, Rotordynamic Performance of a Rotor Supported on Bump Type Foil Gas Bearings: Experiments and Predictions, ASME J. Eng. Gas Turbines and Power, v129 ASME GT San Andrés, L., and D. Rubio, 2006, Bump-Type Foil bearing Structural Stiffness: Experiments and Predictions, ASME J. Eng. Gas Turbines and Power, v128

39 39 References ASME GT San Andrés, L., and Chirathadam, T., 2011, Metal Mesh Foil Bearings: Effect of Excitation Frequency on Rotordynamic Force Coefficients ASME GT San Andrés, L., and Chirathadam T.A., 2010, Identification of Rotordynamic Force Coefficients of a Metal Mesh Foil Bearing Using Impact Load Excitations. ASME GT San Andrés, L., Chirathadam, T. A., and Kim, T.H., 2009, Measurements of Structural Stiffness and Damping Coefficients in a Metal Mesh Foil Bearing. AHS PaperSan Andrés, L., Kim, T.H., Chirathadam, T.A., and Ryu, K., 2009, Measurements of Drag Torque, Lift-Off Journal Speed and Temperature in a Metal Mesh Foil Bearing, American Helicopter Society 65th Annual Forum, Grapevine, Texas, May Other ASME DETC Gjika, K., C. Groves, L. San Andrés, and G. LaRue, 2007, Nonlinear Dynamic Behavior of Turbocharger Rotor-Bearing Systems with Hydrodynamic Oil Film and Squeeze Film Damper in Series: Prediction and Experiment. Metal mesh foil bearings

40 40 CIATEQ´s full-size rotordynamic rig

41 41 Acknowledgments Thanks to NSF ( Grant # ) NASA GRC ( Program NNH06ZEA001N-SSRW2 ), Capstone Turbines, Inc., Honeywell Turbocharging Systems, Korea Institute of Science and Technology (Dr. Tae- Ho Kim) Foster-Miller, MiTI, TAMU Turbomachinery Research Consortium (TRC) CIATEQ A.C. Learn more:

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