WO2014133499A2 - Gestion thermique passive de paliers-feuilles - Google Patents

Gestion thermique passive de paliers-feuilles Download PDF

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Publication number
WO2014133499A2
WO2014133499A2 PCT/US2013/027935 US2013027935W WO2014133499A2 WO 2014133499 A2 WO2014133499 A2 WO 2014133499A2 US 2013027935 W US2013027935 W US 2013027935W WO 2014133499 A2 WO2014133499 A2 WO 2014133499A2
Authority
WO
WIPO (PCT)
Prior art keywords
foil bearing
compliant
foil
bearing system
foils
Prior art date
Application number
PCT/US2013/027935
Other languages
English (en)
Other versions
WO2014133499A3 (fr
Inventor
Robert Bruckner
Original Assignee
United States Of America, As Represented By The Administrator Of The National Aeronautics And Space Administration
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by United States Of America, As Represented By The Administrator Of The National Aeronautics And Space Administration filed Critical United States Of America, As Represented By The Administrator Of The National Aeronautics And Space Administration
Priority to PCT/US2013/027935 priority Critical patent/WO2014133499A2/fr
Publication of WO2014133499A2 publication Critical patent/WO2014133499A2/fr
Publication of WO2014133499A3 publication Critical patent/WO2014133499A3/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/18—Lubricating arrangements
    • F01D25/22—Lubricating arrangements using working-fluid or other gaseous fluid as lubricant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/06—Arrangements of bearings; Lubricating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • F16C17/042—Sliding-contact bearings for exclusively rotary movement for axial load only with flexible leaves to create hydrodynamic wedge, e.g. axial foil bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C37/00—Cooling of bearings
    • F16C37/002—Cooling of bearings of fluid bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F16C17/024—Sliding-contact bearings for exclusively rotary movement for radial load only with flexible leaves to create hydrodynamic wedge, e.g. radial foil bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T50/00—Aeronautics or air transport
    • Y02T50/60—Efficient propulsion technologies, e.g. for aircraft

Definitions

  • This application relates generally to foil bearings and related technology, and more specifically to systems and methods for enhancing the performance of foil bearings through passive cooling.
  • Bearings are used between the rotating and stationary parts of various types of machinery.
  • High speed rotating machinery such as motors, turbines, pumps, and compressors employ anti-friction elements to separate rotating and stationary components.
  • Many traditional antifriction devices such as ball and roller bearings, impose limitations on the size and speed of the rotating machinery.
  • These bearings must be actively cooled and require oil lubrication sub-systems that provide a thin film of oil between the moving parts of the bearing. Oil lubrication sub-systems impose a burden on the primary machine and add a level of unreliability and inefficiency. Without oil, the metal-to-metal contact would cause the machine to grind to a halt.
  • Use of oil-free bearings removes the need for the oil system thus reducing weight, maintenance, and complexity of the engine.
  • Foil bearings are unique anti-friction devices that utilize the working fluid of a machine as a lubricant, typically air for turbines and motors, and liquids for pumps, also act as a coolant to remove excess energy due to frictional heating in the bearings.
  • Conventional foil bearings have been used for a number of years in high speed rotating machinery, air cycle machines for aircraft cabin pressurization, and other small turbomachinery.
  • Foil bearings present an attractive alternative to ball or roller bearings for lightweight machines because they offer numerous system level benefits such as overall simplicity, reduction in weight, reduced friction, enhanced reliability, and zero oil contamination.
  • a foil bearing system comprises a compliant foil bearing mounted to a stationary member and operably disposed between the stationary member and a rotating member, wherein the compliant foil bearing supports the rotating member via a fluid film when the rotating member rotates, a plurality of compliant foils mounted on the compliant foil bearing, the plurality of compliant foils provide passive thermal management of the fluid film.
  • a method of passive cooling of a foil bearing system comprises providing a compliant foil bearing mounted to a stationary member and operably disposed between the stationary member and a rotating member, providing a plurality of compliant foils, wherein the compliant foil bearing supports the rotating member via a fluid film when the rotating member rotates, and disrupting a flow of the fluid film across the plurality of compliant foils.
  • FIG. 1 illustrates the operation of a foil bearing.
  • FIG. 2 illustrates example journal type and thrust type foil bearings.
  • FIG. 3 is an illustration of conventional thrust foil bearings.
  • FIG. 4 is an illustration of a thrust foil bearing in accordance with an embodiment of the disclosure.
  • FIG. 5 is an example representation of a compliant top foil in accordance with an embodiment of the disclosure.
  • FIG. 6 is an example representation of a compliant top foil in accordance with an embodiment of the present disclosure.
  • FIG. 7 is a graph illustrating test results achieved in accordance with embodiments of the disclosed system and method.
  • FIG. 8 is a graph illustrating test results achieved in accordance with embodiments of the disclosed system and method.
  • compliant foil refers to a top foil of a foil bearing.
  • a compliant foil may also be referred to as a top foil or a sector of the foil bearing.
  • the term "fluid" refers to the process fluid of a foil bearing.
  • the fluid may also be referred to as a lubricant or a liquid.
  • the process fluid may comprise air, gases other than air, oil, liquids other than oil, or most any other fluid.
  • foil bearing 100 includes housing 102, compliant foil 104, bump foil 106 and shaft 108.
  • the housing 102 anchors the bearing 100 to a non-rotating portion of a machine (not shown).
  • Compliant foil 104 provides a stationary hydrodynamic surface and acts as a compliant surface that traps and supports the hydrodynamic (fluid) film 1 10 against the rotating shaft 108.
  • Compliant foil 104 comprises a leading edge 112 fixedly engaged with the housing 102 and a trailing edge 1 14.
  • Compliant foil 104 rests on the bump foil 106.
  • Bump foil 106 may comprise, for example, a corrugated foil layer which serves as an elastic spring foundation providing the bearing elasticity.
  • the shaft 108, or runner provides a rotating hydrodynamic surface and may include a surface treatment to enhance hydrodynamic action and reduce friction.
  • fluid 1 16 is drawn into the space between the compliant foil 104 and the moving shaft 108, as shown in FIG. 1.
  • fluid 116 may be drawn into the hydrodynamic film 110 via a viscous dragging mechanism.
  • Fluid 116 may be a process fluid.
  • the hydrodynamic film 110 may be less than about 0.001 in. thick and may support hundreds of pounds.
  • the hydrodynamic film 1 10, comprised of fluid 116, between the moving shaft 108 surface and the stationary top foil 104 surface creates pressure that generates a load-carrying capacity.
  • the foil bearing 100 may provide a stiff, shock-tolerant support for rotating machinery.
  • the trapped fluid 116, i.e hydrodynamic film 110, and its cushioning effect behave similar to air in an automotive shock absorber.
  • Foil air bearings are hydrodynamic bearings that may use ambient air as the fluid 116, instead of oil. Both air and oil are fluids that may perform the job of separating moving metal parts.
  • Foil air bearings maintain the air film 1 10 between moving parts by pumping air 116 between the rotating shaft 108 and the stationary compliant foil surface 104.
  • Foil bearing 100 may comprise a plurality of compliant foils, or sectors, 104.
  • fluid 116 is driven by shear force through the gap between rotating 108 and stationary components 104 and into the hydrodynamic film 110.
  • the primary outcome of this fluidic action is the generation of hydrodynamic pressure, which separates the two parts 108, 104 in relative motion.
  • a secondary effect of this shear force is the frictional heating of the fluid 116.
  • Traditional foil bearings utilize active cooling to remove excess heat. Forced cooling is accomplished, for example, through the bump foil 106 and housing 102. However, conventional forced cooling is inefficient and a significant portion of the heat from one sector of the bearing 100, for example compliant foil 104, is transferred to the next sector or compliant foil. Left unchecked, this mechanism can lead to catastrophic failure of the foil bearing 100.
  • the carryover of fluid 116 and heat from one sector of a foil bearing to the next, and the resulting deleterious effects, may be prevented by passive thermal management. Passive cooling may be accomplished by disrupting the flow of fluid 116 and exploiting fluidic mixing techniques to break apart the hydrodynamic film 110.
  • a foil bearing passive cooling system and method may prevent the carryover of lubricant (e.g. fluid) from the exit of one sector to the inlet of the ensuing sector of the foil bearing.
  • Passive thermal management may increase the load bearing capacity and enhance the reliability of the foil bearing. Operation of passively cooled bearings may be exploited in machine design to improve safety and overall performance and to lessen costly machine downtime. Passive thermal management of foil bearings may result in lower frictional torque when operating at lower (e.g. non-load capacity) loads, thus providing another improvement above conventional foil bearings.
  • bearing geometry may be utilized to both increase load carrying capacity and to provide an inherent and passive cooling mechanism.
  • An illustrative cooling mechanism may function to prevent used (i.e. higher temperature) lubricant from being carried over from the trailing edge of one sector, or compliant foil, into the leading edge of the next sector of the foil bearing.
  • used lubricant i.e. higher temperature
  • the elimination of lubrication carryover and the mixing of used lubricant with surrounding ambient fluid may be accomplished in several ways as discussed in detail below.
  • the subject foil bearing passive cooling systems and methods may prevent problems related to thermal instability due to frictional heat generation, and rotordynamic instability at high rotational speeds.
  • gas dynamic mixing and convection patterns are established to enhance load support and improve the efficiency, reliability, robustness and safety of a foil bearing.
  • a conventional thrust foil bearing 200 may support axial loads and includes housing 202, top foil 204 and bump foil 206 (partially shown). Arrow 208 indicates the direction of rotation of the moving shaft (not shown).
  • the housing 202 anchors the thrust bearing 200 to a non-rotating portion of a machine.
  • Top foil 204 provides a stationary hydrodynamic surface and acts as a compliant surface that traps and supports a hydrodynamic film against the rotating shaft (not shown).
  • Top foil 204 comprises a leading edge 210 anchored, or otherwise fixedly engaged, with the housing 202, and a trailing edge 212. Top foil 204 rests on the bump foil 206.
  • Bump foil 206 may comprise, for example, a corrugated foil layer.
  • the shaft (not shown) provides a rotating hydrodynamic surface.
  • a conventional journal foil bearing may support radial loads and includes housing, or bearing sleeve, 214, top foil 216, a bump foil (not shown) and journal, 218.
  • Top foil 216 rests on the underlying bump foil (not shown).
  • the bump foil which may comprise a corrugated foil layer positioned between the top foil 216 and housing 214.
  • Top foil 216 and the bump foil are anchored to housing 214.
  • Top foil 216 provides a stationary hydrodynamic surface and acts as a compliant surface that traps and supports a hydrodynamic film against journal 218.
  • Top foil 216 comprises a leading edge 220 fixedly engaged with the housing 214, and a trailing edge 222.
  • FIG. 3 is an illustration of conventional thrust foil bearings.
  • Bearing 302 is an example of a conservative design having a top foil trailing edge to leading edge gap of 15 degrees.
  • Bearing 304 utilizes a common approach to increase load capacity by increasing sector area and has a trailing edge to leading edge gap of zero.
  • FIG. 4 is an illustration of a thrust foil bearing in accordance with an embodiment of the subject disclosure.
  • Thrust bearing 400 includes a plurality of top foils 402, 404 having leading edges 406, 408 and trailing edges 410, 412.
  • the trailing edges 410, 412 of the top foils 402, 404 have a shaped profile capable of disrupting the flow 414 of hydrodynamic fluid from one sector (e.g. top foil 402) to the subsequent sector (e.g. top foil 404).
  • the profiles of the trailing edges 410, 412 may comprise rectangular, square, saw-tooth, crescent, chevron, trapezoidal, semicircular, sinusoidal and/or most any other shapes, or combination of shapes, capable of disrupting the flow of fluid from one sector to the subsequent sector and capable of promoting the mixing of surrounding ambient process fluid with the hydrodynamic film.
  • Mixing of cooler ambient process fluid into the hydrodynamic film may dissipate heat energy from the foil bearing, increase the load carrying capacity and enhance performance of the foil bearing, and alleviate a need for forced cooling of the bearing.
  • a surface of the compliant foils may be etched, or otherwise modified, to disrupt the flow of fluid from one sector to the next sector.
  • a surface of the compliant foils may include protrusions or dimples capable of creating turbulence and disrupting the flow of fluid from one compliant foil to the succeeding compliant foil.
  • a wiper or air dam may be formed on a surface of a compliant foil, for example at the leading or trailing edge.
  • the wiper or air dam may encourage gas dynamic mixing and convection patterns to interrupt the flow of fluid from the trailing edge of one compliant foil to the next compliant foil.
  • intersector seals may be disposed between compliant foils allowing cooler ambient process fluid to be included in the hydrodynamic film.
  • the cooler ambient process fluid may dissipate heat energy from the foil bearing.
  • an air curtain may be utilized to disturb the flow of fluid from one sector to the subsequent sector.
  • air, or other fluid may be forced through an outlet in the rotating member and directed to a leading or trailing edge of the compliant foil.
  • the air curtain may be effective to promote the mixing of cooler ambient process fluid into the hydrodynamic film so as to minimize hot lubricant carryover.
  • FIG. 5 is an illustrative top foil 502 of a thrust foil bearing in accordance with an embodiment of the disclosure.
  • Top foil 502 includes trailing edge 504 having a profile comprising a plurality of generally triangular or chevron shapes.
  • FIG. 6 is an illustrative top foil 602 of a thrust foil bearing in accordance with an embodiment of the disclosure.
  • Top foil 602 includes trailing edge 604 having a profile comprising a plurality of generally triangular or chevron shapes.
  • FIG. 7 is a graph illustrating test results achieved in accordance with embodiments of the disclosed system and method.
  • Lines 702 and 704 represent test data collected for conventional thrust foil bearings, 302, 304 respectively, as shown in FIG. 3.
  • Lines 702 and 704 indicate the load capacity of the bearings 302, 304 at low shaft speeds ranging from 0 rpm to about 20,000 rpm.
  • Line 706 represents test data collected for a thrust bearing in accordance with an embodiment of the disclosure including a top foil trailing edge profile as shown in FIG. 4. It can be seen that at approximately 20,000 rpm, the load capacity of the thrust bearing having the trailing edge profile feature is greater than sixty pounds, which is approximately double the load capacity of the traditional thrust foil bearings 702, 704. Therefore, the test data demonstrates that the trailing edge feature has a direct, positive effect on the load capacity of the foil thrust bearing.
  • FIG. 8 is a graph illustrating test results achieved in accordance with embodiments of the disclosed system and method. Lines 802 and 804 represent test data collected for conventional thrust foil bearings, 302, 304 respectively, as shown in FIG. 3. The test data, as indicated by lines 802 and 804, demonstrate the frictional torque of the bearings at shaft speeds ranging from about 20,000 rpm to just under 40,000 rpm.
  • Line 806 represents test data collected for a thrust bearing in accordance with an embodiment of the present disclosure including a top foil trailing edge profile as shown in FIG. 4. It can be seen that the frictional torque of the thrust bearing having the trailing edge profile feature is lower than that of traditional thrust foil bearing 302, as shown by line 802, and significantly lower than traditional thrust bearing 304, as shown by line 804. Therefore, the test data establishes that the trailing edge feature serves to reduce the frictional torque of the foil thrust bearing.
  • Foil bearings in accordance with the disclosure may be useful for many commercial and industrial applications. These applications include, for example, most any high speed rotating machinery, aircraft turbine engines, auxiliary power units, air cycle machines, turbopumps, turbochargers, rocket turbopumps, power conversion units (generators), air conditioning systems, space station ammonia circulators, cryocoolers, pumps, blowers, compressors, electric motors and others.
  • foil bearings of most any type including, for example, both thrust type and journal type foil bearings.
  • the present disclosure is applicable to foil bearing utilizing gas, including air, oil or most any other fluid capable of serving as a hydrodynamic lubricant.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Support Of The Bearing (AREA)

Abstract

La présente invention se rapporte à des systèmes et à des procédés permettant une gestion thermique passive de systèmes de palier-feuille. L'écoulement du film hydrodynamique d'un côté à l'autre de la surface de feuilles souples de palier peut être interrompu pour permettre un refroidissement passif et pour améliorer la performance et la fiabilité du système de palier-feuille.
PCT/US2013/027935 2013-02-27 2013-02-27 Gestion thermique passive de paliers-feuilles WO2014133499A2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/US2013/027935 WO2014133499A2 (fr) 2013-02-27 2013-02-27 Gestion thermique passive de paliers-feuilles

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US2013/027935 WO2014133499A2 (fr) 2013-02-27 2013-02-27 Gestion thermique passive de paliers-feuilles

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WO2014133499A2 true WO2014133499A2 (fr) 2014-09-04
WO2014133499A3 WO2014133499A3 (fr) 2015-06-25

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9896965B2 (en) 2015-12-11 2018-02-20 Hamilton Sundstrand Corporation Thrust bearing assembly with flow path restriction
JP2018519483A (ja) * 2015-11-18 2018-07-19 ハンオン システムズ エアフォイルベアリング
CN111120503A (zh) * 2019-12-16 2020-05-08 北京动力机械研究所 一种弹性支撑结构的推力动压气体轴承

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3957317A (en) * 1975-05-21 1976-05-18 The Garrett Corporation Shaped foil bearing
US4178046A (en) * 1976-05-24 1979-12-11 The Garrett Corporation Foil bearing
US5427455A (en) * 1994-04-18 1995-06-27 Bosley; Robert W. Compliant foil hydrodynamic fluid film radial bearing
US5529398A (en) * 1994-12-23 1996-06-25 Bosley; Robert W. Compliant foil hydrodynamic fluid film thrust bearing
US6752533B2 (en) * 2002-11-15 2004-06-22 Honeywell International Inc. Foil thrust bearing cooling
CN102132052A (zh) * 2008-08-25 2011-07-20 拓博有限公司 推力箔片轴承

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2018519483A (ja) * 2015-11-18 2018-07-19 ハンオン システムズ エアフォイルベアリング
US10415634B2 (en) 2015-11-18 2019-09-17 Hanon Systems Air foil bearing
US10941807B2 (en) 2015-11-18 2021-03-09 Hanon Systems Air foil bearing
US9896965B2 (en) 2015-12-11 2018-02-20 Hamilton Sundstrand Corporation Thrust bearing assembly with flow path restriction
CN111120503A (zh) * 2019-12-16 2020-05-08 北京动力机械研究所 一种弹性支撑结构的推力动压气体轴承

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