USRE39190E1 - Compliant foil fluid film radial bearing - Google Patents

Compliant foil fluid film radial bearing Download PDF

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USRE39190E1
USRE39190E1 US09/895,568 US89556801A USRE39190E US RE39190 E1 USRE39190 E1 US RE39190E1 US 89556801 A US89556801 A US 89556801A US RE39190 E USRE39190 E US RE39190E
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compliant
radial bearing
retainers
interior bore
fluid film
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US09/895,568
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Dennis H. Weissert
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Capstone Green Energy Corp
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Capstone Turbine Corp
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Assigned to GOLDMAN SACHS SPECIALTY LENDING HOLDINGS, INC. reassignment GOLDMAN SACHS SPECIALTY LENDING HOLDINGS, INC. SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: CAPSTONE TURBINE CORPORATION
Assigned to CAPSTONE TURBINE CORPORATION reassignment CAPSTONE TURBINE CORPORATION RELEASE BY SECURED PARTY (SEE DOCUMENT FOR DETAILS). Assignors: WESTERN ALLIANCE BANK
Assigned to CAPSTONE GREEN ENERGY CORPORATION F/K/A CAPSTONE TURBINE CORPORATION reassignment CAPSTONE GREEN ENERGY CORPORATION F/K/A CAPSTONE TURBINE CORPORATION RELEASE BY SECURED PARTY (SEE DOCUMENT FOR DETAILS). Assignors: GOLDMAN SACHS SPECIALTY LENDING GROUP, L.P.
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    • 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
    • F16C43/00—Assembling bearings
    • F16C43/02—Assembling sliding-contact 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
    • F16C2360/23—Gas turbine engines
    • 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
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/02—Sliding-contact bearings

Definitions

  • This invention relates to the general field of compliant foil fluid film bearings and more particularly to an improved multi segment compliant foil fluid film radial bearing.
  • Compliant foil fluid film radial bearings are currently being utilized in a variety of high speed rotor applications. These bearings are generally comprised of a bushing, a rotating element such as a rotor or shaft adapted to rotate within the bushing, non-rotating compliant fluid foil members mounted within the bushing and enclosing the rotating element, and non-rotating compliant spring foil members mounted within the bushing underneath the non-rotating compliant fluid foil members.
  • the space between the rotating element and the bushing is filled with fluid (usually air) which envelops the foils.
  • the compliant fluid foil elements are divided into a plurality of individual compliant foils to form a plurality of wedge shaped channels which converge in thickness in the direction of the rotation of the rotor.
  • the motion of the rotating element applies viscous drag forces to the fluid in the converging wedge channels. This results in increases in fluid pressure, especially near the trailing end of the wedge channels. If the rotating element moves toward the non-rotating element, the convergence angle of the wedge channel increases, causing the fluid pressure rise along the channel to increase. Conversely, if the rotating element moves away, the pressure rise along the wedge channel decreases. Thus, the fluid in the wedge channels exerts restoring forces on the rotating element that vary with and stabilize running clearances and prevent contact between the rotating and non-rotating elements of the bearing. Flexing and sliding of the foils causes coulomb damping of any axial or overturning motion of the rotating element of the bearing.
  • the rotating element of the bearing is typically in physical contact with the fluid foil members of the bearing at low rotational speeds. This physical contact results in bearing wear. It is only when the rotor speed is above what is termed the lift-off/touch-down speed that the fluid dynamic forces generated in the wedge channels assure a running gap between the rotating and non-rotating elements.
  • Compliant foil fluid film radial bearings typically rely on backing springs to preload the fluid foils against the relatively movable rotating element so as to control foil position/nesting and to establish foil dynamic stability.
  • the bearing starting torque (which should ideally be zero) is directly proportional to these preload forces.
  • These preload forces also significantly increase the rotor speed at which the hydrodynamic effects in the wedge channels are strong enough to lift the rotating element of the bearing out of physical contact with the non-rotating members of the bearing.
  • These preload forces and the high lift-off/touchdown speeds result in significant bearing wear each time the rotor is started or stopped.
  • the present invention is directed to a multi-segment radial bearing generally comprising a bushing, a shaft or rotor, a plurality of compliant foils, and a like plurality of foil undersprings.
  • the interior bore of the bushing includes a plurality of anti-rotation retainers that are equally spaced and extend the axial length of the interior bore, which may be either cylindrical or contoured. These generally T-shaped retainers divide the interior bore of the bushing into a like plurality of lobes, with each lobe having a compliant foil and foil underspring disposed therein between adjacent generally T-shaped retainers.
  • FIG. 1 is an end view of the compliant foil fluid film radial bearing of the present invention
  • FIG. 2 is an enlarged sectional view of a portion of the compliant foil fluid film radial bearing of FIG. 1 ;
  • FIG. 3 is an exploded perspective view of the compliant foil fluid radial bearing of FIGS. 1 and 2 ;
  • FIG. 4 is an enlarged sectional view of a portion of an alternate compliant foil fluid film radial bearing of the present invention.
  • This multi-segment radial bearing 10 generally comprises a bushing 12 , a shaft or rotor 14 , a plurality of compliant foils 16 (shown as three), and a like plurality of foil undersprings 18 .
  • the interior bore 20 of the bushing 12 includes a plurality of anti-rotation devices or retainers 22 (shown as three, generally T-shaped retainers) which are equally spaced and extend the axial length of the interior bore 20 .
  • the retainers 22 divide the interior bore 20 of the bushing 12 into a like plurality of lobes 24 .
  • the compliant foils 16 and the foil undersprings 18 are disposed in each lobe 24 between adjacent generally T-shaped retainers 22 .
  • the interior bore 20 of the bushing 12 may or may not be cylindrical. If the interior bore 20 is not cylindrical, the generally T-shaped retainers 22 will divide the interior bore 20 into a plurality of shaped or contoured lobes 24 .
  • the generally T-shaped retainers will divide the interior bore 20 ′ into a plurality of equally spaced arc segments of a cylinder and the converging wedges will be formed via the compliant foil 16 ′ and/or the foil undersprings 18 ′ as generally shown in FIG. 4 .
  • the height of the foil undersprings 18 ′ may increase from the leading edge of the compliant foil 16 ′ to the trailing edge of the compliant foil 16 ′ in order to form the converging wedge.
  • the stiffness of the foil underspring can vary from the leading edge to the trailing edge to produce the same result, or shims of varying height can be positioned underneath the foil underspring.
  • the generally T-shaped retainers 22 may be symmetrical or conform to the leading edge and trailing edge of the contoured lobes 24 .
  • Non-symmetrical T-shaped retainers 22 will retain the foils 16 at different radii from the geometric center with the leading edge of the foils retained at a greater geometric radius than the trailing edge.
  • the generally T-shaped retainers 22 are formed as part of the contoured interior bore 20 of the bushing 12 with the base 26 thereof extending radially inwards from the interior bore 20 .
  • the cross piece of the generally T-shaped retainers 22 has a leading edge 30 and a trailing edge 28 , with the leading edge 30 having a greater thickness or width than the trailing edge 28 as best shown in FIG. 2 . Since the inner diameter of the cross piece is the same at both the leading edge 30 and the trailing edge 28 , this provides a greater diameter or depth for the trailing edge of the contoured lobe 24 which is under the thicker leading edge 30 of the generally T-shaped retainers 22 .
  • the contoured surface of the lobes 24 can be derived from one or a series of radii of a defined profile.
  • the contour of the lobes 24 in which the compliant foils 16 and underspring foils 18 rest upon can be a multiple of, or a fraction of, a specific number.
  • an appropriate contour can be constructed from vertices of an equilateral triangle of specific length side with circles formed from these vertices intersecting to give the contoured surface which may be machined, ground, EDM'ed or broached.
  • compliant foil fluid film radial bearing 10 While a preferred embodiment of the compliant foil fluid film radial bearing 10 is shown with three (3) compliant foil segments 16 and three (3) foil undersprings 18 , a greater number of compliant foils segments 16 and foil undersprings 18 can be utilized. For example, five (5) or more segments may be equally appropriate for the compliant foil fluid film radial bearing 10 .
  • the compliant foils 16 and foil undersprings 18 are trapped and held between adjacent T-shaped retainers 22 .
  • the compliant foils 16 would normally have a preformed arcuate shape as shown in FIG. 3 .
  • the foil undersprings 18 may have a preferred radius or simply be a rectangular sheet. In either case, the compliant foils 16 and foil undersprings 18 are axially inserted, either separately or together, into the interior bore 20 of bushing 12 between adjacent T-shaped retainers 22 .
  • the foil undersprings 18 are illustrated as a wavy springform, any conventional bearing underspring can be utilized, including the spring described in U.S. Pat. No. 5,427,455.
  • the underspring 18 may have variable spring rates or tapered heights from the leading edge to the trailing edge as shown in FIG. 4 .
  • the compliant foils 16 When trapped between adjacent T-shaped retainers 22 , the compliant foils 16 would be pre-loaded in compression between the adjacent T-shaped retainers 22 . In some instances, however, the compliant foils 16 may be merely retained in position between adjacent T-shaped retainers 22 without preloading.
  • the foil undersprings 18 would, however, normally be pre-loaded in compression between adjacent T-shaped retainers 22 .
  • the foil underspring 18 may contribute to the contoured shape of the compliant foils 16 . In most instances, the compliant foils 16 and foil underspring 18 would be separate and would be capable of sliding movement therebetween. There may, however, be instances where the compliant foils 16 and foil underspring 18 will be joined together into a single assembly.
  • the greater thickness of the leading edge 30 of the T-shaped retainer crosspiece produces a greater depth at the trailing edge of the compliant foils 16 to serve as a means to pull the compliant foils 16 away from the trailing edge of the converging wedge.
  • the trailing edge 28 of the T-shaped retainers 22 has less thickness thereby allowing the leading edge of the foils to rest closer to the shaft, which will facilitate development of the fluid film wedges.
  • the compliant foil fluid film radial bearing 10 can function hydrodynamically, by providing an external source of fluid under pressure, a hydrostatic aspect can be realized.
  • the external pressurized fluid may be introduced axially at the ends of the bushing or through radial holes 40 in the bushing 40 axially along and through the T-shaped retainers 22 .
  • the hydrostatic aspect will provide cooling fluid to the interior bore 20 of the bushing 12 , which will increase bearing life especially in a gas turbine application. Hydrostatic operation will also increase the load capacity of the bearing.
  • the radial bearing 10 of the present invention allows for automation by mass production and the components can easily be assembled by hand.
  • the compliant foils 16 may be stamped or fine blanked and there is no requirement for spot welding or chemical etching.
  • the large clearances between the compliant foils 16 and the shaft 14 at the T-shaped retainers 22 allow improved cooling of the shaft 14 and compliant foils 16 .
  • the design can accommodate a variety of underspring types and the T-shaped retainers 22 permit more design flexibility with respect to the shaft, foil and spring interaction.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Support Of The Bearing (AREA)
  • Sliding-Contact Bearings (AREA)

Abstract

A multi-segment radial bearing including a bushing with an interior bore having a plurality of anti-rotation retainers which are equally spaced and extend the axial length of the interior bore. The generally T-shaped retainers divide the interior bore of the bushing into a like plurality of lobes, with each lobe having a compliant foil and a foil underspring disposed between adjacent generally T-shaped retainers.

Description

TECHNICAL FIELD
This invention relates to the general field of compliant foil fluid film bearings and more particularly to an improved multi segment compliant foil fluid film radial bearing.
BACKGROUND OF THE INVENTION
Compliant foil fluid film radial bearings are currently being utilized in a variety of high speed rotor applications. These bearings are generally comprised of a bushing, a rotating element such as a rotor or shaft adapted to rotate within the bushing, non-rotating compliant fluid foil members mounted within the bushing and enclosing the rotating element, and non-rotating compliant spring foil members mounted within the bushing underneath the non-rotating compliant fluid foil members. The space between the rotating element and the bushing is filled with fluid (usually air) which envelops the foils. Conventionally, the compliant fluid foil elements are divided into a plurality of individual compliant foils to form a plurality of wedge shaped channels which converge in thickness in the direction of the rotation of the rotor.
The motion of the rotating element applies viscous drag forces to the fluid in the converging wedge channels. This results in increases in fluid pressure, especially near the trailing end of the wedge channels. If the rotating element moves toward the non-rotating element, the convergence angle of the wedge channel increases, causing the fluid pressure rise along the channel to increase. Conversely, if the rotating element moves away, the pressure rise along the wedge channel decreases. Thus, the fluid in the wedge channels exerts restoring forces on the rotating element that vary with and stabilize running clearances and prevent contact between the rotating and non-rotating elements of the bearing. Flexing and sliding of the foils causes coulomb damping of any axial or overturning motion of the rotating element of the bearing.
Owing to preload spring forces or gravity forces, the rotating element of the bearing is typically in physical contact with the fluid foil members of the bearing at low rotational speeds. This physical contact results in bearing wear. It is only when the rotor speed is above what is termed the lift-off/touch-down speed that the fluid dynamic forces generated in the wedge channels assure a running gap between the rotating and non-rotating elements.
Compliant foil fluid film radial bearings typically rely on backing springs to preload the fluid foils against the relatively movable rotating element so as to control foil position/nesting and to establish foil dynamic stability. The bearing starting torque (which should ideally be zero) is directly proportional to these preload forces. These preload forces also significantly increase the rotor speed at which the hydrodynamic effects in the wedge channels are strong enough to lift the rotating element of the bearing out of physical contact with the non-rotating members of the bearing. These preload forces and the high lift-off/touchdown speeds result in significant bearing wear each time the rotor is started or stopped.
Conventional compliant foil fluid film radial bearings operate with extremely small running clearances and moderate, as opposed to low, drag and power consumption. The clearances between the non-rotating fluid foil's converging channel ramp trailing ends and the rotating element are typically less than 100 micro-inches at operating conditions.
While most prior compliant foil fluid film radial bearings utilize a plurality of individual compliant foils and individual spring foils with a cylindrically bored bushing, there are instances where a single compliant foil and a single spring foil have been proposed with a cam shaped or lobed bushing. An example of this type of radial bearing can be found in U.S. Pat. No. 5,427,455 issued Jun. 27, 1995 to Robert W. Bosley, entitled “Compliant Foil Hydrodynamic Fluid Film Radial Bearing”.
SUMMARY OF THE INVENTION
The present invention is directed to a multi-segment radial bearing generally comprising a bushing, a shaft or rotor, a plurality of compliant foils, and a like plurality of foil undersprings.
The interior bore of the bushing includes a plurality of anti-rotation retainers that are equally spaced and extend the axial length of the interior bore, which may be either cylindrical or contoured. These generally T-shaped retainers divide the interior bore of the bushing into a like plurality of lobes, with each lobe having a compliant foil and foil underspring disposed therein between adjacent generally T-shaped retainers.
BRIEF DESCRIPTION OF THE DRAWINGS
Having thus described the present invention in general terms, reference will now be made to the accompanying drawings in which:
FIG. 1 is an end view of the compliant foil fluid film radial bearing of the present invention;
FIG. 2 is an enlarged sectional view of a portion of the compliant foil fluid film radial bearing of FIG. 1;
FIG. 3 is an exploded perspective view of the compliant foil fluid radial bearing of FIGS. 1 and 2; and
FIG. 4 is an enlarged sectional view of a portion of an alternate compliant foil fluid film radial bearing of the present invention.
 DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
Illustrated in FIGS. 1-3 is the compliant foil fluid film radial bearing 10 of the present invention. This multi-segment radial bearing 10 generally comprises a bushing 12, a shaft or rotor 14, a plurality of compliant foils 16 (shown as three), and a like plurality of foil undersprings 18.
The interior bore 20 of the bushing 12 includes a plurality of anti-rotation devices or retainers 22 (shown as three, generally T-shaped retainers) which are equally spaced and extend the axial length of the interior bore 20. The retainers 22 divide the interior bore 20 of the bushing 12 into a like plurality of lobes 24. The compliant foils 16 and the foil undersprings 18 are disposed in each lobe 24 between adjacent generally T-shaped retainers 22.
While the shaft or rotor 14 is cylindrical, the interior bore 20 of the bushing 12 may or may not be cylindrical. If the interior bore 20 is not cylindrical, the generally T-shaped retainers 22 will divide the interior bore 20 into a plurality of shaped or contoured lobes 24.
On the other hand, if the interior bore 20′ of the bushing 12′ is cylindrical, the generally T-shaped retainers will divide the interior bore 20′ into a plurality of equally spaced arc segments of a cylinder and the converging wedges will be formed via the compliant foil 16′ and/or the foil undersprings 18′ as generally shown in FIG. 4. The height of the foil undersprings 18′ may increase from the leading edge of the compliant foil 16′ to the trailing edge of the compliant foil 16′ in order to form the converging wedge. Alternately, the stiffness of the foil underspring can vary from the leading edge to the trailing edge to produce the same result, or shims of varying height can be positioned underneath the foil underspring.
The generally T-shaped retainers 22 may be symmetrical or conform to the leading edge and trailing edge of the contoured lobes 24. Non-symmetrical T-shaped retainers 22 will retain the foils 16 at different radii from the geometric center with the leading edge of the foils retained at a greater geometric radius than the trailing edge.
The generally T-shaped retainers 22 are formed as part of the contoured interior bore 20 of the bushing 12 with the base 26 thereof extending radially inwards from the interior bore 20. The cross piece of the generally T-shaped retainers 22 has a leading edge 30 and a trailing edge 28, with the leading edge 30 having a greater thickness or width than the trailing edge 28 as best shown in FIG. 2. Since the inner diameter of the cross piece is the same at both the leading edge 30 and the trailing edge 28, this provides a greater diameter or depth for the trailing edge of the contoured lobe 24 which is under the thicker leading edge 30 of the generally T-shaped retainers 22.
The contoured surface of the lobes 24 can be derived from one or a series of radii of a defined profile. For example, in the case of three (3) foil segments, the contour of the lobes 24 in which the compliant foils 16 and underspring foils 18 rest upon can be a multiple of, or a fraction of, a specific number. Also, an appropriate contour can be constructed from vertices of an equilateral triangle of specific length side with circles formed from these vertices intersecting to give the contoured surface which may be machined, ground, EDM'ed or broached.
While a preferred embodiment of the compliant foil fluid film radial bearing 10 is shown with three (3) compliant foil segments 16 and three (3) foil undersprings 18, a greater number of compliant foils segments 16 and foil undersprings 18 can be utilized. For example, five (5) or more segments may be equally appropriate for the compliant foil fluid film radial bearing 10.
The compliant foils 16 and foil undersprings 18 are trapped and held between adjacent T-shaped retainers 22. The compliant foils 16 would normally have a preformed arcuate shape as shown in FIG. 3. The foil undersprings 18 may have a preferred radius or simply be a rectangular sheet. In either case, the compliant foils 16 and foil undersprings 18 are axially inserted, either separately or together, into the interior bore 20 of bushing 12 between adjacent T-shaped retainers 22. Also, while the foil undersprings 18 are illustrated as a wavy springform, any conventional bearing underspring can be utilized, including the spring described in U.S. Pat. No. 5,427,455. The underspring 18 may have variable spring rates or tapered heights from the leading edge to the trailing edge as shown in FIG. 4.
When trapped between adjacent T-shaped retainers 22, the compliant foils 16 would be pre-loaded in compression between the adjacent T-shaped retainers 22. In some instances, however, the compliant foils 16 may be merely retained in position between adjacent T-shaped retainers 22 without preloading. The foil undersprings 18 would, however, normally be pre-loaded in compression between adjacent T-shaped retainers 22. The foil underspring 18 may contribute to the contoured shape of the compliant foils 16. In most instances, the compliant foils 16 and foil underspring 18 would be separate and would be capable of sliding movement therebetween. There may, however, be instances where the compliant foils 16 and foil underspring 18 will be joined together into a single assembly.
The greater thickness of the leading edge 30 of the T-shaped retainer crosspiece produces a greater depth at the trailing edge of the compliant foils 16 to serve as a means to pull the compliant foils 16 away from the trailing edge of the converging wedge. The trailing edge 28 of the T-shaped retainers 22 has less thickness thereby allowing the leading edge of the foils to rest closer to the shaft, which will facilitate development of the fluid film wedges.
Also, while the compliant foil fluid film radial bearing 10 can function hydrodynamically, by providing an external source of fluid under pressure, a hydrostatic aspect can be realized. The external pressurized fluid may be introduced axially at the ends of the bushing or through radial holes 40 in the bushing 40 axially along and through the T-shaped retainers 22. The hydrostatic aspect will provide cooling fluid to the interior bore 20 of the bushing 12, which will increase bearing life especially in a gas turbine application. Hydrostatic operation will also increase the load capacity of the bearing.
The radial bearing 10 of the present invention allows for automation by mass production and the components can easily be assembled by hand. The compliant foils 16 may be stamped or fine blanked and there is no requirement for spot welding or chemical etching. The large clearances between the compliant foils 16 and the shaft 14 at the T-shaped retainers 22 allow improved cooling of the shaft 14 and compliant foils 16. The design can accommodate a variety of underspring types and the T-shaped retainers 22 permit more design flexibility with respect to the shaft, foil and spring interaction.
While specific embodiments of the invention have been illustrated and described, it is to be understood that there are provided by way of example only and that the invention is not to be construed as being limited thereto but only by the proper scope of the following claims.

Claims (56)

1. A compliant foil fluid film radial bearing comprising:
a bushing having an interior bore including a plurality of equally spaced generally T-shaped retainers axially extending in said interior bore and a like plurality of lobes between adjacent generally T-shaped retainers;
a shaft rotatably supported within said interior bore of said bushing;
a plurality of compliant foils, with an individual compliant foil disposed in said interior bore of said bushing between adjacent generally T-shaped retainers; and
a plurality of foil undersprings, with an underspring disposed beneath each of said compliant foils between adjacent generally T-shaped retainers.
2. The compliant foil fluid film radial bearing of claim 1 wherein said interior bore is cylindrical and said individual compliant foils and said individual foil undersprings beneath said individual complaint foils establish a converging wedge between adjacent generally T-shaped retainers.
3. The compliant foil fluid film radial bearing of claim 1 wherein said interior bore is non-cylindrical, generally contoured lobes are formed between adjacent generally T-shaped retainers, and said individual compliant foils and said individual foil undersprings generally conform to the shape of said contoured lobes to establish a converging wedge.
4. A compliant foil fluid film radial bearing comprising:
a bushing having a cylindrical interior bore including a plurality of equally spaced retainers axially extending into said interior bore and a like plurality of arc segments between adjacent retainers;
a shaft rotatably supported within said interior bore of said bushing;
a plurality of compliant foils, with an individual compliant foil disposed in said interior bore of said bushing in each arc segment between adjacent retainers; and
a plurality of foil undersprings, with an underspring disposed beneath each of said compliant foils in each arc segment between adjacent retainers, the radial height of said foil undersprings increasing form its leading edge to its trailing edge to establish a converging wedge on the surface of said compliant foil facing said shaft.
5. The compliant foil fluid film radial bearing of claim 4 wherein said retainers are generally T-shaped.
6. The compliant foil fluid film radial bearing of claim 5 wherein said generally T-shaped retainers are symmetrical.
7. The compliant foil fluid film radial bearing of claim 5 wherein said generally T-shaped retainers are asymmetrical.
8. The compliant foil fluid film radial bearing of claim 7 wherein said generally T-shaped asymmetrical retainers have a crosspiece with a leading edge and a trailing edge, with the leading edge thicker than the trailing edge.
9. The compliant foil fluid film radial bearing of claim 4 wherein the radial stiffness of said foil undersprings increases form its leading edge to its trailing edge.
10. The compliant foil fluid film radial bearing of claim 9 wherein said bearing is hydrodynamic.
11. The compliant foil fluid film radial bearing of claim 9 wherein said retainers are generally T-shaped.
12. The compliant foil fluid film radial bearing of claim 9 wherein said bearing is hydrostatic.
13. A compliant foil fluid film radial bearing comprising:
a bushing having a non-cylindrical interior bore including a plurality of equally spaced retainers axially extending into said interior bore and a like plurality of contoured lobes between adjacent retainers;
a shaft rotatably supported within said interior bore of said bushing;
a plurality of compliant foils, with an individual compliant foil disposed in said interior bore of said bushing in each contoured lobe between adjacent retainers; and
a plurality of foil undersprings, with an underspring disposed beneath each of said compliant foils in each contoured lobe between adjacent retainers, the contour of each lobe between adjacent retainers establishing a converging wedge on the surface of said compliant foil facing said shaft.
14. The compliant foil fluid film radial bearing of claim 13 56 wherein said generally T-shaped retainers are symmetrical.
15. The compliant foil fluid film radial bearing of claim 14 16 wherein said generally T-shaped asymmetrical retainers have a crosspiece with a leading edge and a trailing edge, with the leading edge thicker than the trailing edge.
16. The compliant foil fluid film radial bearing of claim 13 56 wherein said generally T-shaped retainers are symmetrical asymmetrical.
17. The compliant foil fluid film radial bearing of claim 13 56 wherein said generally T-shaped retainers include radial openings to provide cooling flow to said interior bore of said bushing.
18. The compliant foil fluid film radial bearing of claim 13 and in addition means to provide cooling flow axially into said interior bore of said bushing.
19. A compliant foil fluid film radial bearing comprising:
a bushing having an interior bore including a plurality of generally T-shaped retainers axially extending in said interior bore;
a plurality of compliant foils, with an individual compliant foil disposed in said interior bore of said bushing between adjacent generally T-shaped retainers; and
a plurality of foil undersprings, with an underspring disposed beneath each of said compliant foils between adjacent generally T-shaped retainers.
20. The compliant foil fluid film radial bearing of claim 19 wherein said interior bore is cylindrical and said individual compliant foils and said individual foil undersprings beneath said individual compliant foils establish a converging wedge between adjacent generally T-shaped retainers.
21. The compliant foil fluid film radial bearing of claim 19 wherein said interior bore is non-cylindrical, generally contoured lobes are formed between adjacent generally T-shaped retainers, and said individual compliant foils and said individual foil undersprings generally conform to the shape of said contoured lobes to establish a converging wedge.
22. The compliant foil fluid film radial bearing of claim 19 wherein said bearing is hydrodynamic.
23. The compliant foil fluid film radial bearing of claim 19 wherein said bearing is hydrostatic.
24. The compliant foil fluid film radial bearing of claim 19 wherein said generally T-shaped retainers include radial openings to provide cooling flow to said interior bore of said bushing.
25. The compliant foil fluid film radial bearing of claim 19 further comprising:
means to provide cooling flow axially into said interior bore of said bushing.
26. The compliant foil fluid film radial bearing of claim 13 wherein said retainers are generally T-shaped retainers.
27. A compliant foil fluid film radial bearing comprising:
a bushing having a cylindrical interior bore including a plurality of retainers axially extending into said interior bore;
a plurality of compliant foils, with an individual compliant foil disposed in said interior bore of said bushing between adjacent retainers; and
a plurality of foil undersprings, with an underspring disposed beneath each of said compliant foils between adjacent retainers, the radial height of said foil undersprings increasing from its leading edge to its trailing edge to establish a converging wedge of said compliant foil.
28. The compliant foil fluid film radial bearing of claim 27 wherein said retainers are generally T-shaped.
29. The compliant foil fluid film radial bearing of claim 28 wherein said generally T-shaped retainers are asymmetrical.
30. The compliant foil fluid film radial bearing of claim 29 wherein said generally T-shaped asymmetrical retainers have a crosspiece with a leading edge and a trailing edge, with the leading edge thicker than the trailing edge.
31. The compliant foil fluid film radial bearing of claim 28 wherein said generally T-shaped retainers are symmetrical.
32. The compliant foil fluid film radial bearing of claim 28 wherein said generally T-shaped retainers include radial openings to provide cooling flow to said interior bore of said bushing.
33. The compliant foil fluid film radial bearing of claim 27 wherein the radial stiffness of said foil undersprings increases from its leading edge to its trailing edge.
34. The compliant foil fluid film radial bearing of claim 33 wherein said bearing is hydrodynamic.
35. The compliant foil fluid film radial bearing of claim 33 wherein said bearing is hydrostatic.
36. The compliant foil fluid film radial bearing of claim 27 further comprising:
means to provide cooling flow axially into said interior bore of said bushing.
37. A compliant foil fluid radial bearing comprising:
a bushing having a non-cylindrical interior bore including a plurality of retainers axially extending into said interior bore;
a plurality of compliant foils, with an individual compliant foil disposed in said interior bore of said bushing between adjacent retainers; and
a plurality of foil undersprings, with an underspring disposed beneath each of said compliant foils between adjacent retainers, the contour of the interior bore between adjacent retainers establishing a converging wedge on the surface of said compliant foil.
38. The compliant foil fluid radial bearing of claim 37 wherein said retainers are generally T-shaped.
39. The compliant foil fluid film radial bearing of claim 38 wherein said generally T-shaped retainers are asymmetrical.
40. The compliant foil fluid film radial bearing of claim 39 wherein said generally T-shaped asymmetrical retainers have a crosspiece with a leading edge and a trailing edge, with the leading edge thicker than the trailing edge.
41. The compliant foil fluid film radial bearing of claim 38 wherein said generally T-shaped retainers are symmetrical.
42. The compliant foil fluid film radial bearing of claim 38 wherein said bearing is hydrostatic.
43. The compliant foil fluid film radial bearing of claim 38 wherein said generally T-shaped retainers include radial openings to provide cooling flow to said interior bore of said bushing.
44. The compliant foil fluid film radial bearing of claim 38 wherein said bearing is hydrodynamic.
45. The compliant foil fluid film radial bearing of claim 37 further comprising:
means to provide cooling flow axially into said interior bore of said bushing.
46. A radial bearing bushing comprising:
a bushing having an interior bore;
one or more retainer bases axially extending into the interior bore;
one or more leading edges attached to each of the one or more retainer bases for retaining a compliant foil; and
one or more trailing edges attached to each of the one or more retainer bases for retaining a compliant foil.
47. The radial bearing of claim 46 wherein the interior bore is cylindrical.
48. The radial bearing of claim 46 wherein the interior bore is non-cylindrical.
49. The radial bearing of claim 46 wherein one or more of the one or more retainer bases include radial openings to provide cooling flow to said interior bore of said bushing.
50. A compliant foil radial bearing comprising:
a bushing having an interior bore including one or more retainer bases axially extending into the interior bore;
one or more compliant foils;
one or more leading edges attached to each of the one or more retainer bases for retaining a compliant foil trailing edge;
one or more tailing edges attached to each of the one or more retainer bases for retaining a compliant foil leading edge; and
one or more foil undersprings, each underspring disposed beneath a compliant foil.
51. The compliant foil radial bearing of claim 50 wherein the interior bore in non-cylindrical, generally contoured lobes are formed between adjacent retainer bases, and an individual compliant foil and underspring beneath the individual compliant foil generally conform to the shape of a contoured lobe to establish a converging wedge.
52. The compliant foil radial bearing of claim 50 wherein said bearing is hydrodynamic.
53. The compliant foil radial bearing of claim 50 wherein said bearing is hydrostatic.
54. The compliant foil radial bearing of claim 50 wherein the one or more retainer bases include radial openings to provide cooling flow to the interior bore of said bushing.
55. The compliant foil radial bearing of claim 50 further comprising:
means to provide cooling flow axially into the interior bore of the bushing.
56. The compliant foil radial bearing of claim 50 wherein the interior bore is cylindrical and an individual compliant foil and underspring beneath the individual compliant foil form a converging wedge.
US09/895,568 1998-01-05 2001-06-29 Compliant foil fluid film radial bearing Expired - Lifetime USRE39190E1 (en)

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Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080267543A1 (en) * 2007-04-26 2008-10-30 Capstone Turbine Corporation Compliant Foil Fluid Film Radial Bearing Or Seal
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US20100278469A1 (en) * 2009-05-04 2010-11-04 Pratt & Whitney Canada Corp. Bearing support
US20120260775A1 (en) * 2011-04-15 2012-10-18 Apex Brands, Inc. Flex-head wrench
US8337090B2 (en) 2009-09-10 2012-12-25 Pratt & Whitney Canada Corp. Bearing support flexible ring
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Families Citing this family (50)

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US6489692B1 (en) * 1999-12-13 2002-12-03 Capstone Turbine Corporation Method and apparatus for controlling rotation of magnetic rotor
US20020054718A1 (en) * 2000-11-03 2002-05-09 Weissert Dennis H. Bidirectional radial foil bearing
US6469411B2 (en) * 2000-12-15 2002-10-22 Magnetal Ab Compliant foil fluid film bearing with eddy current damper
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US6964522B2 (en) * 2004-01-22 2005-11-15 Honeywell International Inc. Hydrodynamic journal foil bearing system
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KR100760626B1 (en) 2006-05-03 2007-09-20 한국기계연구원 Lobe bearing with the bump foil
US20080309019A1 (en) * 2007-06-13 2008-12-18 General Electric Company Sealing assembly for rotary machines
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JP6136135B2 (en) 2012-07-18 2017-05-31 株式会社Ihi Radial foil bearing
US9587746B2 (en) 2012-07-31 2017-03-07 General Electric Company Film riding seals for rotary machines
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EP2937584B1 (en) * 2012-12-19 2018-10-10 NTN Corporation Foil bearing
US9989085B2 (en) 2013-01-19 2018-06-05 Honeywell International Inc. High strength foil journal bearing retainer
US9057401B2 (en) * 2013-01-19 2015-06-16 Honeywell International Inc. High strength foil journal bearing retainer
US9556899B2 (en) 2013-01-19 2017-01-31 Honeywell International Inc. High strength foil journal bearing retainer
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US10190431B2 (en) 2015-02-11 2019-01-29 General Electric Company Seal assembly for rotary machine
GB201512494D0 (en) * 2015-07-17 2015-08-19 Rolls Royce Plc And Rolls Royce Deutschland Ltd & Co Kg Gas turbine engine
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JP7027968B2 (en) * 2018-03-07 2022-03-02 株式会社Ihi Radial foil bearing
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DE102018222603A1 (en) 2018-12-20 2020-06-25 Robert Bosch Gmbh Foil storage
US11306726B2 (en) 2019-03-11 2022-04-19 Emerson Climate Technologies, Inc. Foil bearing assembly and compressor including same
DE102019210456A1 (en) 2019-07-16 2021-01-21 Robert Bosch Gmbh Foil storage
DE102019212922A1 (en) 2019-08-28 2021-03-04 Robert Bosch Gmbh Foil for a foil store
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DE102019212915A1 (en) 2019-08-28 2021-03-04 Robert Bosch Gmbh Storage support for a film store and film store
US11686341B2 (en) 2021-02-04 2023-06-27 Emerson Climate Technologies, Inc. Foil bearing assembly including segmented inner foil assembly and compressor including same
DE102021108882B3 (en) * 2021-04-09 2022-09-15 Schaeffler Technologies AG & Co. KG Radial foil bearing with stop edge in the outer ring for foil positioning

Citations (61)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3366427A (en) 1965-11-01 1968-01-30 Garrett Corp Selectively pressurized foil bearing arrangements
US3382014A (en) 1966-02-18 1968-05-07 Garrett Corp Self-acting foil bearings
US3615121A (en) 1969-04-01 1971-10-26 Garrett Corp Bearing foil anchoring arrangements
US3635534A (en) 1969-08-06 1972-01-18 Garrett Corp Self-pressurizing bearings with resilient elements
US3747997A (en) 1971-07-22 1973-07-24 Mechanical Tech Inc Hydrodynamic foil bearings
US3795427A (en) 1972-11-24 1974-03-05 Ampex Anti-whirl fluid bearing
US3809443A (en) 1971-08-05 1974-05-07 Mechanical Tech Inc Hydrodynamic foil bearings
US3957317A (en) 1975-05-21 1976-05-18 The Garrett Corporation Shaped foil bearing
US4118079A (en) 1976-06-12 1978-10-03 Rolls-Royce Limited Fluid bearings with conforming shells
US4133585A (en) 1977-08-04 1979-01-09 United Technologies Corporation Resilient foil journal bearing
US4153315A (en) 1976-05-24 1979-05-08 The Garrett Corporation Foil bearing stiffener
US4170389A (en) 1977-09-21 1979-10-09 Ampex Corporation Foil bearing
US4178046A (en) 1976-05-24 1979-12-11 The Garrett Corporation Foil bearing
US4195395A (en) 1976-05-24 1980-04-01 The Garrett Corporation Method of rotatably supporting two members with a foil bearing having a stiffener
US4208076A (en) 1978-12-29 1980-06-17 Mechanical Technology Incorporated Compliant hydrodynamic bearing with improved support element
US4213657A (en) 1978-12-29 1980-07-22 Mechanical Technology Incorporated Compliant hydrodynamic bearing with tubular support element
US4223958A (en) 1978-12-29 1980-09-23 Mechanical Technology Incorporated Modular compliant hydrodynamic bearing with overlapping bearing sheet
US4229054A (en) 1978-12-29 1980-10-21 Mechanical Technology Incorporated Multi-pad compliant hydrodynamic journal bearing
US4247155A (en) 1979-06-13 1981-01-27 United Technologies Corporation Resilient foil bearings
US4262975A (en) 1979-10-01 1981-04-21 Mechanical Technology Incorporated Compliant journal bearing with angular stiffness gradient
US4295689A (en) 1979-08-30 1981-10-20 United Technologies Corporation Adjustable clearance foil journal bearing and method of manufacturing foil element therefor
US4300806A (en) 1980-04-03 1981-11-17 Mechanical Technology Incorporated Multi-stage support element for compliant hydrodynamic bearings
US4315660A (en) 1979-03-14 1982-02-16 Tmaschinen Forschungsvereinigung Verbrennungskra Maschinen Aerodynamic multiple-wedge resilient bearing
US4371216A (en) 1978-07-03 1983-02-01 Toyoda Koki Kabushiki Kaisha Fluid bearing
US4415280A (en) 1981-11-23 1983-11-15 United Technologies Corporation Hydrodynamic fluid film bearing
US4415281A (en) 1981-11-23 1983-11-15 United Technologies Corporation Hydrodynamic fluid film bearing
US4435839A (en) 1982-09-21 1984-03-06 The Garrett Corporation Foil bearing rubbing surface coating application methods
US4445792A (en) 1982-11-22 1984-05-01 General Motors Corporation Variable preload foil bearing
US4451163A (en) * 1982-07-01 1984-05-29 The Garrett Corporation Foil bearing mounting carrier
US4475824A (en) 1982-07-01 1984-10-09 The Garrett Corporation Bearing foil stiffener
US4502795A (en) 1982-09-30 1985-03-05 The Garrett Corporation Foil bearing alignment
US4552466A (en) 1984-04-24 1985-11-12 The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration Compliant hydrodynamic fluid journal bearing
US4555187A (en) 1982-09-30 1985-11-26 The Garrett Corporation Foil bearing alignment
US4616388A (en) 1982-05-27 1986-10-14 Abg Semca Process for producing a hydrodynamic bearing having internal foil cartridge
US4795274A (en) 1987-08-10 1989-01-03 Allied-Signal Inc. Foil bearing
US4808070A (en) 1987-08-17 1989-02-28 Fonda Bonardi G Fluid bearing
US4818123A (en) 1986-07-24 1989-04-04 Allied-Signal Inc. Foil journal bearing cooling
US4896975A (en) 1988-12-13 1990-01-30 Allied-Signal Inc. Ceramic air bearing shaft
US4950089A (en) 1988-05-12 1990-08-21 Williams International Corporation Compliant foil bearing
US4961122A (en) 1987-05-11 1990-10-02 Hitachi, Ltd. Hydrodynamic grooved bearing device
US5017022A (en) 1988-11-09 1991-05-21 Allied-Signal, Inc. High temperature bearing
US5116143A (en) 1990-12-20 1992-05-26 Allied-Signal Inc. High load capacity journal foil bearing
US5129739A (en) 1989-08-09 1992-07-14 Nippon Seiko Kabushiki Kaisha Bearing with dynamic pressure grooves and method for manufacturing the same
US5228785A (en) 1990-12-20 1993-07-20 Allied-Signal, Inc. Stepped foil journal foil bearing
US5248205A (en) 1992-08-24 1993-09-28 Alliedsignal Inc. Foil thrust bearing with varying radial and circumferential stiffness
US5322371A (en) 1988-12-23 1994-06-21 Abg Semca Sa Fluid film bearing
US5427455A (en) * 1994-04-18 1995-06-27 Bosley; Robert W. Compliant foil hydrodynamic fluid film radial bearing
US5450719A (en) 1993-11-17 1995-09-19 Alliedsignal, Inc. Gas turbine engine rear magnetic or foil bearing cooling using exhaust eductor
US5498083A (en) 1994-12-15 1996-03-12 Air Products And Chemicals, Inc. Shimmed three lobe compliant foil gas bearing
US5519274A (en) 1994-09-07 1996-05-21 Rotodynamics-Seal Research, Inc. Magnetically active foil bearing
US5518320A (en) 1994-08-18 1996-05-21 The Texas A&M University System Foil bearing
US5549392A (en) * 1995-05-02 1996-08-27 Nastec, Inc. Resilient mount pad journal bearing
US5584582A (en) 1994-12-15 1996-12-17 Air Products And Chemicals, Inc. Bump foil design for improved damping and load capacity from compliant foil gas bearings
US5634723A (en) 1995-06-15 1997-06-03 R & D Dynamics Corporation Hydrodynamic fluid film bearing
US5658079A (en) 1995-06-05 1997-08-19 United Technologies Corporation Hydrodynamic fluid film journal bearing
US5885004A (en) 1997-11-12 1999-03-23 Boeing North America, Inc. Hydrostatically supported foil bearing
US5902049A (en) 1997-03-28 1999-05-11 Mohawk Innovative Technology, Inc. High load capacity compliant foil hydrodynamic journal bearing
US5911511A (en) 1997-09-26 1999-06-15 Alliedsignal Inc. Tilting pad foil thrust and journal bearings
US5911510A (en) 1997-10-15 1999-06-15 Alliedsignal Inc. Bi-directional foil bearings
US5915841A (en) 1998-01-05 1999-06-29 Capstone Turbine Corporation Compliant foil fluid film radial bearing
US6024491A (en) 1998-09-25 2000-02-15 Williams International Company, L.L.C. Air bearing

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3215480A (en) * 1963-08-29 1965-11-02 David J Marley Hydrodynamic foil bearings with bearing foil retaining means
DE2838768C3 (en) * 1978-09-06 1981-02-19 Dornier System Gmbh, 7990 Friedrichshafen Multi-surface plain bearings
JPS59217011A (en) * 1983-05-23 1984-12-07 Nippon Seiko Kk Foil bearing and its manufacturing method
WO1992011469A1 (en) * 1990-12-20 1992-07-09 Allied-Signal Inc. Stepped foil journal foil bearing

Patent Citations (62)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3366427A (en) 1965-11-01 1968-01-30 Garrett Corp Selectively pressurized foil bearing arrangements
US3382014A (en) 1966-02-18 1968-05-07 Garrett Corp Self-acting foil bearings
US3615121A (en) 1969-04-01 1971-10-26 Garrett Corp Bearing foil anchoring arrangements
US3635534A (en) 1969-08-06 1972-01-18 Garrett Corp Self-pressurizing bearings with resilient elements
US3747997A (en) 1971-07-22 1973-07-24 Mechanical Tech Inc Hydrodynamic foil bearings
US3809443A (en) 1971-08-05 1974-05-07 Mechanical Tech Inc Hydrodynamic foil bearings
US3795427A (en) 1972-11-24 1974-03-05 Ampex Anti-whirl fluid bearing
US3957317A (en) 1975-05-21 1976-05-18 The Garrett Corporation Shaped foil bearing
US4153315A (en) 1976-05-24 1979-05-08 The Garrett Corporation Foil bearing stiffener
US4178046A (en) 1976-05-24 1979-12-11 The Garrett Corporation Foil bearing
US4195395A (en) 1976-05-24 1980-04-01 The Garrett Corporation Method of rotatably supporting two members with a foil bearing having a stiffener
US4118079A (en) 1976-06-12 1978-10-03 Rolls-Royce Limited Fluid bearings with conforming shells
US4133585A (en) 1977-08-04 1979-01-09 United Technologies Corporation Resilient foil journal bearing
US4170389A (en) 1977-09-21 1979-10-09 Ampex Corporation Foil bearing
US4371216A (en) 1978-07-03 1983-02-01 Toyoda Koki Kabushiki Kaisha Fluid bearing
US4208076A (en) 1978-12-29 1980-06-17 Mechanical Technology Incorporated Compliant hydrodynamic bearing with improved support element
US4229054A (en) 1978-12-29 1980-10-21 Mechanical Technology Incorporated Multi-pad compliant hydrodynamic journal bearing
US4223958A (en) 1978-12-29 1980-09-23 Mechanical Technology Incorporated Modular compliant hydrodynamic bearing with overlapping bearing sheet
US4213657A (en) 1978-12-29 1980-07-22 Mechanical Technology Incorporated Compliant hydrodynamic bearing with tubular support element
US4315660A (en) 1979-03-14 1982-02-16 Tmaschinen Forschungsvereinigung Verbrennungskra Maschinen Aerodynamic multiple-wedge resilient bearing
US4247155A (en) 1979-06-13 1981-01-27 United Technologies Corporation Resilient foil bearings
US4295689A (en) 1979-08-30 1981-10-20 United Technologies Corporation Adjustable clearance foil journal bearing and method of manufacturing foil element therefor
US4262975A (en) 1979-10-01 1981-04-21 Mechanical Technology Incorporated Compliant journal bearing with angular stiffness gradient
US4300806A (en) 1980-04-03 1981-11-17 Mechanical Technology Incorporated Multi-stage support element for compliant hydrodynamic bearings
US4415280A (en) 1981-11-23 1983-11-15 United Technologies Corporation Hydrodynamic fluid film bearing
US4415281A (en) 1981-11-23 1983-11-15 United Technologies Corporation Hydrodynamic fluid film bearing
US4743126A (en) 1982-05-24 1988-05-10 Abg Semca Hydrodynamic bearings, and secondary assemblies for producing said bearings
US4616388A (en) 1982-05-27 1986-10-14 Abg Semca Process for producing a hydrodynamic bearing having internal foil cartridge
US4451163A (en) * 1982-07-01 1984-05-29 The Garrett Corporation Foil bearing mounting carrier
US4475824A (en) 1982-07-01 1984-10-09 The Garrett Corporation Bearing foil stiffener
US4435839A (en) 1982-09-21 1984-03-06 The Garrett Corporation Foil bearing rubbing surface coating application methods
US4502795A (en) 1982-09-30 1985-03-05 The Garrett Corporation Foil bearing alignment
US4555187A (en) 1982-09-30 1985-11-26 The Garrett Corporation Foil bearing alignment
US4445792A (en) 1982-11-22 1984-05-01 General Motors Corporation Variable preload foil bearing
US4552466A (en) 1984-04-24 1985-11-12 The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration Compliant hydrodynamic fluid journal bearing
US4818123A (en) 1986-07-24 1989-04-04 Allied-Signal Inc. Foil journal bearing cooling
US4961122A (en) 1987-05-11 1990-10-02 Hitachi, Ltd. Hydrodynamic grooved bearing device
US4795274A (en) 1987-08-10 1989-01-03 Allied-Signal Inc. Foil bearing
US4808070A (en) 1987-08-17 1989-02-28 Fonda Bonardi G Fluid bearing
US4950089A (en) 1988-05-12 1990-08-21 Williams International Corporation Compliant foil bearing
US5017022A (en) 1988-11-09 1991-05-21 Allied-Signal, Inc. High temperature bearing
US4896975A (en) 1988-12-13 1990-01-30 Allied-Signal Inc. Ceramic air bearing shaft
US5322371A (en) 1988-12-23 1994-06-21 Abg Semca Sa Fluid film bearing
US5129739A (en) 1989-08-09 1992-07-14 Nippon Seiko Kabushiki Kaisha Bearing with dynamic pressure grooves and method for manufacturing the same
US5228785A (en) 1990-12-20 1993-07-20 Allied-Signal, Inc. Stepped foil journal foil bearing
US5116143A (en) 1990-12-20 1992-05-26 Allied-Signal Inc. High load capacity journal foil bearing
US5248205A (en) 1992-08-24 1993-09-28 Alliedsignal Inc. Foil thrust bearing with varying radial and circumferential stiffness
US5450719A (en) 1993-11-17 1995-09-19 Alliedsignal, Inc. Gas turbine engine rear magnetic or foil bearing cooling using exhaust eductor
US5427455A (en) * 1994-04-18 1995-06-27 Bosley; Robert W. Compliant foil hydrodynamic fluid film radial bearing
US5518320A (en) 1994-08-18 1996-05-21 The Texas A&M University System Foil bearing
US5519274A (en) 1994-09-07 1996-05-21 Rotodynamics-Seal Research, Inc. Magnetically active foil bearing
US5498083A (en) 1994-12-15 1996-03-12 Air Products And Chemicals, Inc. Shimmed three lobe compliant foil gas bearing
US5584582A (en) 1994-12-15 1996-12-17 Air Products And Chemicals, Inc. Bump foil design for improved damping and load capacity from compliant foil gas bearings
US5549392A (en) * 1995-05-02 1996-08-27 Nastec, Inc. Resilient mount pad journal bearing
US5658079A (en) 1995-06-05 1997-08-19 United Technologies Corporation Hydrodynamic fluid film journal bearing
US5634723A (en) 1995-06-15 1997-06-03 R & D Dynamics Corporation Hydrodynamic fluid film bearing
US5902049A (en) 1997-03-28 1999-05-11 Mohawk Innovative Technology, Inc. High load capacity compliant foil hydrodynamic journal bearing
US5911511A (en) 1997-09-26 1999-06-15 Alliedsignal Inc. Tilting pad foil thrust and journal bearings
US5911510A (en) 1997-10-15 1999-06-15 Alliedsignal Inc. Bi-directional foil bearings
US5885004A (en) 1997-11-12 1999-03-23 Boeing North America, Inc. Hydrostatically supported foil bearing
US5915841A (en) 1998-01-05 1999-06-29 Capstone Turbine Corporation Compliant foil fluid film radial bearing
US6024491A (en) 1998-09-25 2000-02-15 Williams International Company, L.L.C. Air bearing

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
"Foil Air/Gas Bearing Technology-An Overview," Giri Agrawal, The American Society of Mechanical Engineers, Jun. 1997, pp. 1-11.
"Foil Gas Bearings for Turbomachinery," Giri Agrawal, The Engineering Society for Advancing Mobility Land Sear Air and Space, SAE Technical Paper Series, Jul. 1990.

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CA2254034A1 (en) 1999-07-05
DE69832579D1 (en) 2006-01-05
US5915841A (en) 1999-06-29
JPH11247844A (en) 1999-09-14
DE69832579T2 (en) 2006-08-03
JP4271757B2 (en) 2009-06-03
IL127021A (en) 2002-02-10
EP0927831A1 (en) 1999-07-07
EP0927831B1 (en) 2005-11-30
CA2254034C (en) 2007-06-05
IL127021A0 (en) 1999-09-22

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