US20210277950A1 - Hybrid bearing assembly with rolling elements and plain bearing - Google Patents
Hybrid bearing assembly with rolling elements and plain bearing Download PDFInfo
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- US20210277950A1 US20210277950A1 US17/186,521 US202117186521A US2021277950A1 US 20210277950 A1 US20210277950 A1 US 20210277950A1 US 202117186521 A US202117186521 A US 202117186521A US 2021277950 A1 US2021277950 A1 US 2021277950A1
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- liner
- bearing assembly
- race
- inner race
- bore
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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
- F16C21/00—Combinations of sliding-contact bearings with ball or roller bearings, for exclusively rotary movement
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B64—AIRCRAFT; AVIATION; COSMONAUTICS
- B64C—AEROPLANES; HELICOPTERS
- B64C9/00—Adjustable control surfaces or members, e.g. rudders
- B64C9/02—Mounting or supporting thereof
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B64—AIRCRAFT; AVIATION; COSMONAUTICS
- B64C—AEROPLANES; HELICOPTERS
- B64C9/00—Adjustable control surfaces or members, e.g. rudders
- B64C9/14—Adjustable control surfaces or members, e.g. rudders forming slots
- B64C9/16—Adjustable control surfaces or members, e.g. rudders forming slots at the rear of the wing
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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
- F16C11/00—Pivots; Pivotal connections
- F16C11/04—Pivotal connections
- F16C11/06—Ball-joints; Other joints having more than one degree of angular freedom, i.e. universal joints
- F16C11/0614—Ball-joints; Other joints having more than one degree of angular freedom, i.e. universal joints the female part of the joint being open on two sides
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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
- F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
- F16C23/06—Ball or roller bearings
- F16C23/08—Ball or roller bearings self-adjusting
- F16C23/082—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface
- F16C23/086—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface forming a track for rolling elements
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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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/20—Sliding surface consisting mainly of plastics
- F16C33/201—Composition of the plastic
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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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/66—Special parts or details in view of lubrication
- F16C33/6696—Special parts or details in view of lubrication with solids as lubricant, e.g. dry coatings, powder
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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
- F16C39/00—Relieving load on bearings
- F16C39/02—Relieving load on bearings using mechanical means
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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
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
- F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
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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
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
- F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
- F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
- F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
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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
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/24—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly
- F16C19/26—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly with a single row of rollers
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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
- F16C2208/00—Plastics; Synthetic resins, e.g. rubbers
- F16C2208/20—Thermoplastic resins
- F16C2208/30—Fluoropolymers
- F16C2208/32—Polytetrafluorethylene [PTFE]
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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
- F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
- F16C2240/12—Force, load, stress, pressure
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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
- F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
- F16C23/02—Sliding-contact bearings
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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
- F16C2326/00—Articles relating to transporting
- F16C2326/43—Aeroplanes; Helicopters
Definitions
- the present invention is directed to bearings and, more particularly, to hybrid bearings for use in fixed wing aircraft flap hinge arms.
- the wings of a fixed wing aircraft typically employ ailerons and flaps that are mounted on hinges longitudinally along the wings.
- Ailerons are flight control surfaces that are hinged to the trailing edges of the wing and are independently movable up and down to deflect airflow away from the wing, thereby altering the lift on the wing and controlling the roll moment of the aircraft as well as allowing the plane to bank.
- Flaps are flight control surfaces that are also hinged to the trailing edges of the wings but are movable in tandem up or down. Angling the flaps down to deflect airflow down and away from the wing reduces the flight speed and allows the angle of descent to be increased without increasing air speed. In larger aircraft, the flaps are also generally extendable outward from the trailing edges.
- the curvature of the wing is increased. Because the flaps are mounted along the wings in the directions in which the wings extend, increasing the curvature of a wing causes stress at the points at which the flaps are coupled to the wing. Bearings are used at these points in conjunction with linkages to enable the flaps to be extended and angled in response to pilot control. Placing stresses on the points at which the flaps are coupled to the wings may compromise the operation of the bearings, which in turn may affect the positioning of the flaps and operation of the aircraft.
- U.S. Patent Application Publication No. 2011/0220762 discloses an aircraft wing that includes a wing structure, a slat panel mounted on a track, and an actuator mechanism on the wing structure coupled to the track for moving the slat panel between a deployed position and a retracted position.
- Track roller bearings on the wing structure rotatably contact the track
- side roller bearings on the wing structure rotatably contact at least one side of the track.
- the actuator mechanism includes a shaft rotatably mounted on the wing structure, an actuator arm coupled to the track by a bearing linkage, and an actuator lever coupled to the shaft by a bearing linkage and to the actuator arm by a bearing linkage.
- At least one bearing linkage includes a spherical plain bearing.
- U.S. Patent Publication No. 2011/067509 German Patent Application No. 197 50 113, U.S. Pat. No. 1,457,584, U.S. Patent Publication No. 2012/058923, European Patent Application No. 0 843 106 and International Patent Application Publication No. WO 2012/080983 are also relevant to the present application.
- the present invention resides in a bearing assembly comprising: an outer race having an inner surface defining a concave contour; an inner race positioned in the outer race, the inner race having an inner surface defining a bore therethrough and an outer surface defining at least one groove circumscribing the outer surface; a plurality of rolling elements rollably located in the at least one groove and in rolling contact with the inner surface of the outer race; and a lubricious liner having an inner liner-surface and an exterior liner-surface, the exterior liner-surface being disposed on the inner surface defining the bore, the lubricious liner having a modulus of compression of a magnitude sufficient to allow misalignment of the inner liner-surface relative to the exterior liner-surface in response to a force applied thereto.
- the present invention resides in a bearing assembly comprising: an outer race having an inner surface defining a concave contour; an inner race positioned in the outer race, the inner race having an inner surface defining a bore therethrough and an outer surface defining at least one groove circumscribing the outer surface; a plurality of rolling elements rollably located in the at least one groove and in rolling contact with the inner surface of the outer race; and a lubricious liner having a coefficient of friction of a magnitude sufficient to prevent relative motion between the inner race and a shaft extending through the bore of the inner race during a first operating condition and to allow relative motion between the inner race and the shaft during a second operating condition.
- the present invention resides in a flap hinge arm of a fixed wing aircraft, comprising: an arm; a connecting rod pivotally connected to the arm and pivotally connectable to a flap; and a bearing assembly positioned on the arm and connectable to a wing of the fixed wing aircraft, the bearing assembly comprising, an outer race having an inner surface defining a concave contour; an inner race positioned in the outer race, the inner race having an inner surface defining a bore therethrough and an outer surface defining at least one groove circumscribing the outer surface; a plurality of rolling elements rollably located in the at least one groove and in rolling contact with the inner surface of the outer race; and a lubricious liner having an inner liner-surface and an exterior liner-surface, the exterior liner-surface being disposed on the inner surface defining the bore, the lubricious liner having a modulus of compression of a magnitude sufficient to allow misalignment of the inner liner-surface relative to the exterior liner-surface in response to a
- FIG. 1 is a side sectional view of a bearing assembly, of the present invention.
- FIG. 2A presents one embodiment of the bearing assembly of FIG. 1 in a first operating condition.
- FIG. 2B presents the bearing assembly of FIG. 2A in a second operating condition.
- FIG. 3A presents another embodiment of the bearing assembly of FIG. 1 in a first operating condition.
- FIG. 3B presents the bearing assembly of FIG. 3A in a second operating condition.
- FIG. 4A presents another embodiment of the bearing assembly of FIG. 1 in a first operating condition.
- FIG. 4B presents the bearing assembly of FIG. 4A in a second operating condition.
- FIG. 5 is a side sectional view of another embodiment of a bearing assembly of the present invention.
- FIG. 6 is a side sectional view of yet another alternate embodiment of a bearing assembly of the present invention.
- FIG. 7 is a side sectional view of yet another alternate embodiment of a bearing assembly of the present invention.
- FIG. 8 is a side sectional view of yet another alternate embodiment of a bearing assembly of the present invention.
- FIG. 9 is a side view of a flap hinge arm of a fixed wing aircraft in which the bearing assembly of FIG. 1 or FIGS. 5-8 is installed.
- FIG. 10 is a front sectional view of the arm and bearing assembly of the flap hinge arm of FIG. 9 .
- FIG. 11 is a side sectional view of a wing of a fixed wing aircraft incorporating the flap hinge arm of FIG. 9 in an extended position.
- FIG. 12 is a side sectional view of a wing of a fixed wing aircraft incorporating the flap hinge arm of FIG. 9 in a retracted position.
- bearing assembly 10 is a hybrid bearing that combines the misalignment (swivel action) capabilities of a plain spherical bearing and the rolling element aspect of an airframe control bearing, with a third degree of freedom which includes axial sliding of the bearing on a self-lubricated surface thus allowing for the accommodation of a greater degree of misalignment (e.g., rotational, tilt or cocking, and axial sliding) as compared to conventional bearings used in flap hinge arms.
- the range of motion of oscillation can be up to about 45 degrees.
- the present invention is not limited to an oscillation range of motion of about 45 degrees, however, as the oscillation of the bearing assembly may be greater than about 45 degrees.
- the bearing assembly 10 comprises an inner race 12 concentrically positioned in an outer race 14 .
- a plurality of rolling elements or balls 16 are located between and rollingly engage the inner and outer races, 12 and 14 respectively.
- the present invention is not limited to the use of balls 16 , however, as any suitable rolling element may be employed.
- the inner race 12 is defined by an inner surface 18 and an outer surface 20 .
- the outer surface 20 includes two grooves 17 that circumscribe the outer surface 20 . At least a portion of the balls 16 rollingly engage each of the grooves 17 .
- the balls 16 are arranged in two staggered rows such that each ball is staggered relative to the next adjacent ball.
- the inner surface 18 defines a bore 22 extending through the inner race 12 , the bore being located substantially concentrically about an axis A.
- the outer race 14 is a ring that is defined by an inner surface 26 having a spherically concave contour and an outer surface 28 .
- the concave contour of the outer race inner surface 26 allows for the inner race 12 to be misaligned relative to the outer race 14 by up to about 45 degrees to accommodate the oscillation range of motion of bearing assembly 10 as described above.
- the balls 16 rollingly engage the inner surface 26 .
- the outer surface 28 is suitably configured to facilitate the mounting of the bearing assembly 10 in a flap hinge arm. Upon incorporation of the bearing assembly 10 into the flap hinge arm, the outer race 14 and the inner race 12 rotate independently of each other.
- outer race 14 has been shown and described as being a ring, the present invention is not limited in this regard as the outer race can assume any practical shape or be integral with the flap hinge arm into which the bearing assembly 10 is installed without departing from the broader aspects of the present invention.
- the bearing assembly 10 includes a seal 30 positioned across the interface of the inner race 12 and the outer race 14 to inhibit the ingress of debris and contaminants into the bearing assembly. Retaining rings 32 are employed on the outer race 14 on opposing sides of the seals 30 to secure the seals in place.
- the bearing assembly 10 may include two seals 30 positioned generally opposite one another on opposing sides of the bearing assembly.
- the balls 16 may be made from a steel or an alloy steel.
- the balls 16 may be made from a stainless steel such as 440C (AMS 5880 or 5618), 52100 (AMS 6440), or Corrosion Resistant Nitrogen (“CREN”) Steel (e.g., Cronidur 30® (available from Progressive Alloy Steels Unlimited of Las Vegas, Nev.), AMS 5898, or other suitable CREN when available), or the like. It is also contemplated that the balls 16 may be made from other materials that are sufficiently hard or can be sufficiently hardened through heat treatment.
- CREN Corrosion Resistant Nitrogen
- Both the inner race 12 and the outer race 14 may be made from a steel or an alloy steel, including, but not limited to, a stainless steel such as 440C (AMS 5880 or 5618), AMS 5655 solution nitride (CREN), 52100 (AMS 6440), Cronidur 30® (AMS 5898), or Aubert and Duvall XD15NW®, or another suitable material.
- a stainless steel such as 440C (AMS 5880 or 5618), AMS 5655 solution nitride (CREN), 52100 (AMS 6440), Cronidur 30® (AMS 5898), or Aubert and Duvall XD15NW®, or another suitable material.
- the bearing assembly 10 also includes a self-lubricating coating composition bonded to the inner surface 18 defining the bore 22 to form a lubricious liner 36 having an inner liner-surface 36 B and an exterior liner-surface 36 A.
- the bearing assembly 10 is mounted on a shaft 23 which extends through the bore 22 .
- the shaft 23 is substantially cylindrical and defines an exterior surface 25 .
- the lubricious liner 36 is disposed between the shaft 23 and the bore 22 .
- the lubricious liner inner liner-surface 36 B engages the exterior surface 25 of the shaft 23 ; and the lubricious liner exterior liner-surface 36 A engages the inner surface 18 defining the bore 22 .
- the shaft 23 is press fit into the bore 22 so that during normal operation of the bearing assembly 10 the shaft 23 is fixed relative to the inner race 12 and there is essentially no slippage between the lubricious liner 36 and the exterior surface 25 .
- the lubricious liner 36 has a continuous annular shape.
- the lubricious liner 36 has an axial length L.
- the interior liner-surface 36 B engages the exterior surface 25 of the shaft 23 , continuously and entirely circumferentially around the shaft 23 (e.g., uninterrupted), along the axial length L of the lubricious liner 36 .
- the exterior liner-surface 36 A engages the inner surface 18 , continuously and entirely circumferentially around the inner surface 18 (e.g., uninterrupted), along the axial length L of the lubricious liner 36 .
- the coefficient of friction of the lubricious liner 36 is of a magnitude sufficient to prevent relative motion between the inner race 12 and the shaft 23 extending through the bore 22 during a first operating condition and to allow relative motion between the inner race 12 and the shaft 23 during a second operating condition, both in a radial direction and in an axial direction.
- a first operating torque t 1 is transmitted to the outer race 14 which rotates in relation to inner race 12 by action of the balls 16 .
- a second operating torque t 2 is transmitted to the lubricious liner 36 and correspondingly to the shaft 23 .
- the lubricious liner 36 has a static coefficient of friction of a sufficient magnitude to maintain the shaft 23 in a substantially fixed relation to the inner race 12 and the lubricious liner 36 during normal operation when the first operating torque is in the range up to torque t 1 and the second operating torque is in the range up to torque t 2 .
- an indicator I 1 indicates a first position of bearing 10 during normal operation wherein the indicator I 1 of the shaft 23 , lubricious liner 36 , inner race 12 , and outer race 14 align.
- the outer race rotates as indicated by an indicator I 2 while the indicator I 1 of the shaft 23 , lubricious liner 36 and inner race 12 remains stationary.
- a third operating torque, or an anomalous operation torque t 3 in excess of normal operating torque t 1 is transmitted to the outer race 14 which rotates in relation to inner race 12 by action of the balls 16 .
- a fourth operating torque, or an anomalous operation torque t 4 in excess of normal operating torque t 2 is transmitted to the inner race 12 , lubricious liner 36 and correspondingly to the shaft 23 .
- the coefficient of friction of the lubricious liner 36 is of a sufficient magnitude to enable rotational sliding engagement between the exterior surface 25 of shaft 23 and the lubricious liner 36 when friction between the inner race 12 and the outer race 14 exceeds a predetermined magnitude thereby causing anomalous operation.
- an indicator I 3 indicates a first position of bearing 10 during anomalous operation wherein the indicator I 3 of the shaft 23 , lubricious liner 36 , inner race 12 , and outer race 14 align.
- the outer race rotates as indicated by an indicator 15
- the shaft 23 also rotates in relation to the lubricious liner 36 and inner race 12 as indicated by an indicator I 4 .
- outer race 14 may rotate less than rotation under normal operation (i.e., the outer race 14 is rotating under anomalous operation), or the outer race 14 may remain stationary in relation to the inner race 12 . If rotation of the outer race 14 relative to the inner race 12 is impeded by seizure of the balls 16 , the inner race 12 and lubricious liner 36 will move relative to the shaft 23 and the exterior surface 25 slides relative to the lubricious liner 36 .
- the lubricious liner 36 is operable to engage a mating surface and to enable sliding engagement with the mating surface when torque required to rotate the outer race 14 relative to the inner race 12 , exceeds a predetermined value.
- an axial force defined as equal to or less than an axial holding force is transmitted to the interface of the lubricious liner 36 and the shaft 23 wherein lubricious liner 36 is operable to engage and retain shaft 23 .
- an axial force greater than the axial holding force is transmitted to the interface of the lubricious liner 36 and the shaft 23 wherein lubricious liner 36 is operable to permit axial sliding or shifting of shaft 23 .
- the predetermined value of a torque applied to bearing 10 is normal operating torque t 1
- anomalous operation torque t 3 is in a range of magnitude of about 1.5 normal operating torque t 1 .
- the predetermined value of a torque applied to bearing 10 is normal operating torque t 1
- anomalous operation torque t 3 is in a range of magnitude of about 1.25 normal operating torque t 1
- the predetermined value of a torque applied to bearing 10 is normal operating torque t 1
- anomalous operation torque t 3 is in a range of magnitude of about 1.1 normal operating torque t 1
- the lubricious liner 36 also functions as a fail-safe mechanism by allowing the shaft to rotational slip in the bore 22 if the bearing were to seize.
- the bearing assembly 10 is mounted on the shaft 23 which is a least partially disposed in the bore 22 and exterior surface 25 of shaft 23 engages the lubricious liner 36 .
- the lubricious liner 36 reduces friction between exterior surface 25 of shaft 23 received in or through the bore 22 and the inner surface 18 defining the bore particularly when forces (for example, as a result of wing bending or thermal differentials) act on the shaft in directions indicated by the arrow R and parallel to an axis B.
- the bearing assembly 10 may also translate along the shaft to some degree with reduced friction because of the presence of the lubricious liner 36 .
- the coefficient of friction of the lubricious liner 36 is of a magnitude sufficient to prevent relative motion between the inner race 12 and the shaft 23 extending through the bore 22 during a first operating condition and to allow relative motion between the inner race 12 and the shaft 23 during a second operating condition.
- exterior surface 25 of shaft 23 engages the lubricious liner 36 and moves in the direction R a distance Y in relation to inner surface 18 of bore 22 .
- Distance Y can be represented in relation to an outer diameter D of shaft 23 . In one embodiment, distance Y is in the range of about 0.25 D. In one embodiment, distance Y is in the range of about 0.5 D.
- distance Y is in the range of about D. In one embodiment, distance Y is in the range of about 2 D.
- the lubricious liner 36 also removes the need for the incorporation of a galvanic barrier on the bearing assembly 10 or the shaft in the event that the surface defining the bore 22 is a different material than the material of the shaft.
- the lubricious liner 36 has a modulus of compression of a magnitude sufficient to allow misalignment (e.g., axial angular misalignment) of the lubricious liner inner liner-surface 36 B disposed on the exterior surface 25 of the shaft 23 relative to the lubricious liner exterior liner-surface 36 A disposed on the inner surface 18 defining the bore 22 in the inner race 12 in the directions generally indicated by the arrow N in response to a force applied thereto.
- misalignment e.g., axial angular misalignment
- the bearing assembly 10 is mounted on the shaft 23 which is a least partially disposed in the bore 22 and exterior surface 25 of shaft 23 engages the lubricious liner 36 .
- the lubricious liner 36 has a modulus of compression of a magnitude sufficient to maintain the lubricious liner inner liner-surface 36 B in a substantially fixed relation to the lubricious liner exterior liner-surface 36 A during normal operation such shaft 23 , lubricious liner 36 and inner race 12 are substantially concentric about a central axis B.
- the lubricious liner 36 Upon application of a force or load in the direction N, the lubricious liner 36 has a modulus of compression of a magnitude sufficient to allow angular misalignment (i.e., an angular misalignment feature) of the inner race 12 relative to the shaft 23 such that a central axis C of shaft 23 is displaced or misaligned from the axis B of bore 22 by a misalignment angle ⁇ .
- the misalignment angle ⁇ is from about one degree to about two degrees. In another embodiment, the misalignment angle ⁇ is from about one degree to about ten degrees.
- the misalignment angle ⁇ is up to about 15 degrees.
- the lubricious liner 36 surrounds the shaft 23 and has a substantially equal thickness W 1 , W 1 ′ a full 360° around exterior surface 25 between first end 36 C and second end 36 D.
- Lubricious liner 36 has a modulus of compression of a magnitude sufficient to allow sufficient compression of a width W 1 of the liner and correspondingly allow sufficient expansion of width W 1 ′ such that lubricious liner inner liner-surface 36 B remains disposed on exterior surface 25 of shaft 23 and lubricious liner exterior liner-surface 36 A remains disposed on inner surface 18 of bore 22 of inner race 12 .
- lubricious liner inner liner-surface 36 B remains in full contact with exterior surface 25 of shaft 23 and lubricious liner exterior liner-surface 36 A remains in full contact with inner surface 18 of bore 22 of inner race 12 .
- a portion of width W 1 is compressible at the first end 36 C to a width W 2 and another portion of width W 1 ′ is correspondingly expandable to a width W 3 .
- a portion of the width W 1 is compressible to width W 2 and another portion of the width W 1 ′ is expandable to width W 3 .
- a portion of width W 1 is compressible to width W 2 and another portion of width W 1 ′ is expandable to width W 3 up to a range of about 10% of width W 1 . In one embodiment, a portion of width W 1 is compressible to width W 2 and another portion of width W 1 ′ is expandable to width W 3 up to a range of about 25% of width W 1 . In one embodiment, a portion of width W 1 is compressible to width W 2 and another portion of width W 1 ′ is expandable to width W 3 up to a range of about 50% of width W 1 .
- the lubricious liner 36 includes polytetrafluoroethylene (PTFE).
- PTFE polytetrafluoroethylene
- the PTFE may be in fiber form and woven with fabrics, such as, but not limited to, cotton, polyester, glass fiber, carbon fiber, nylon, aramid materials such as NOMEX® and KEVLAR® manufactured by DuPont, and combinations of the foregoing.
- the fabric may be set in a thermosetting resin or thermoplastic resin.
- thermosetting resins include, but are not limited to, phenolic resins, polyester resins, epoxy resins, urethane resins, polyurethane resins, polyimide resins, and the like.
- the lubricious liner 36 includes the woven PTFE fiber and chopped PTFE fibers in addition to the other fibers and resins listed above. In yet another embodiment, the lubricious liner 36 includes chopped PTFE fibers in addition to the other fibers and resins listed above and does not include the woven PTFE fiber.
- the lubricious liner 36 could be molded to or injected and adhered onto the inner surface 18 defining the bore 22 .
- the lubricious liner 36 includes a thermosetting resin, such as a phenolic resin, a polyester resin, an epoxy resin, a urethane resin, a polyurethane resin, a polyimide resin, or the like, which is mixed with any one or a combination of fibers such as PTFE, cotton, polyester, glass fiber, carbon fiber, nylon, and aramid fibers such as NOMEX® and KEVLAR®.
- a thermosetting resin such as a phenolic resin, a polyester resin, an epoxy resin, a urethane resin, a polyurethane resin, a polyimide resin, or the like, which is mixed with any one or a combination of fibers such as PTFE, cotton, polyester, glass fiber, carbon fiber, nylon, and aramid fibers such as NOMEX® and KEVLAR®.
- the present invention is not limited to a bearing assembly comprising two rows of balls, as indicated above.
- the bearing assembly may include rolling elements generally know as rollers of any shape including spherical rollers or balls, convex rollers or barrel rollers, concave rollers or hourglass rollers, cylindrical rollers, tapered rollers, etc.
- the rolling element bearings may have one or two rows of rolling elements.
- a bearing assembly 110 may comprise an inner race 112 located in an outer race 114 with a plurality of rolling elements or balls 116 located therebetween in a single row.
- the inner race 112 is a ring defined by inner and outer surfaces, the inner surface defining a bore 122 extending therethrough, the bore being located substantially concentrically about an axis F.
- a lubricious liner 136 is disposed on the inner surface defining the bore 122 .
- bearing assembly 110 includes a seal 130 positioned across the interface of the inner race 112 and the outer race 114 to inhibit the ingress of debris and contaminants into the bearing assembly.
- the bearing assembly 110 may include two seals 130 positioned generally opposite one another on opposing sides of the bearing assembly. Retaining rings 132 are employed on the outer race 114 on one side of the seals 130 to secure the seal in place.
- a bearing assembly 210 includes an inner race 212 located in an outer race 214 with a plurality of rolling elements or barrel rollers 216 (i.e., convex rollers) located therebetween in a single row.
- the inner race 212 is a ring defined by inner and outer surfaces, the inner surface defining a bore 222 extending therethrough, the bore being located substantially concentrically about an axis G.
- the outer race 214 is integrally formed with a linkage assembly 240 , such as for example a flap hinge arm 40 as further described below with reference FIG. 9 .
- bearing assembly 210 includes a seal 230 positioned across the interface of the inner race 212 and the outer race 214 to inhibit the ingress of debris and contaminants into the bearing assembly.
- the bearing assembly 210 may include two seals 230 positioned generally opposite one another on opposing sides of the bearing assembly. Retaining rings 232 are employed on the outer race 214 on opposing sides of the seals 230 to secure the seals in place.
- a bearing assembly 310 includes an inner race 312 located in an outer race 314 with a plurality of rolling elements or hourglass rollers 316 (i.e. concave curvature which means the outer raceways correspondingly are convex) located therebetween in a single row.
- the inner race 312 is a ring defined by inner and outer surfaces, the inner surface defining a bore 322 extending therethrough.
- the outer race 314 is integrally formed with a linkage assembly 340 , such as for example flap hinge arm 40 as further described below with reference FIG. 9 .
- bearing assembly 310 includes a seal 330 positioned across the interface of the inner race 312 and the outer race 314 to inhibit the ingress of debris and contaminants into the bearing assembly.
- the bearing assembly 310 may include two seals 330 positioned generally opposite one another on opposing sides of the bearing assembly. Retaining rings 332 are employed on the outer race 314 to secure the seals in place.
- a bearing assembly 410 includes an inner race 412 located in an outer race 414 with a plurality of rolling elements or cylindrical rollers 416 located therebetween in a single row.
- the inner race 412 is a ring defined by inner and outer surfaces, the inner surface defining a bore 422 extending therethrough.
- the outer race 414 is integrally formed with a linkage assembly 440 , such as for example flap hinge arm 40 as further described below with reference FIG. 9 .
- a lubricious liner 436 is disposed on the inner surface defining the bore 222 .
- bearing assembly 410 includes a seal 430 positioned across the interface of the inner race 412 and the outer race 414 to inhibit the ingress of debris and contaminants into the bearing assembly.
- the bearing assembly 210 may include two seals 230 positioned generally opposite one another on opposing sides of the bearing assembly. Retaining rings 432 are employed on the outer race 414 on opposing sides of the seals 430 to secure the seals in place.
- the lubricious liners 136 , 236 , 336 and/or 436 may be PTFE in fiber form and woven with fabrics, such as, but not limited to, cotton, polyester, glass fiber, carbon fiber, nylon, or aramid materials with or without thermosetting resin or thermoplastic resin. Also, the PTFE fiber may be woven or chopped. Furthermore, the material of the lubricious liners 136 , 236 , 336 and/or 436 may be molded or injected as desired for the application at hand.
- flap hinge arm 40 As shown in FIG. 9 , one exemplary embodiment of a flap hinge arm for a fixed wing aircraft is designated generally by the reference number 40 and is hereinafter referred to as “flap hinge arm 40 .”
- the flap hinge arm 40 is defined by an arm 42 having the bearing assembly 10 mounted on one end 42 A thereof and a connecting rod 44 pivotally coupled to an opposing end 42 B of the arm.
- the connecting rod 44 includes a link apparatus 46 having a spherical plain bearing 47 mounted therein.
- the present invention is not limited to the connecting rod 44 having the link apparatus 46 and the spherical plain bearing 47 , however, as any suitable bearing assembly may be associated with the connecting rod.
- the present invention is also not limited to the bearing assembly 10 being mounted in the flap hinge arm 40 , however, as the bearing assembly 110 may also be mounted therein.
- a rod end is typically mounted. This rod end can be attached to the connecting rod by a threaded or welded connection, or any other suitable means.
- An outer race can be mounted in the rod end eye with a Grumman groove, a press fit, or other suitable means. Instead of an outer race, the inner surface of the rod end eye can be used as the outer raceway (i.e. no separable outer race) by suitable heat treatment and machining (hard turning, grinding, or the like).
- the inner race 12 of the bearing assembly 10 may be integral with the arm 42 and elongated in a direction transverse to a major axis G through the arm.
- the bore 22 with the lubricious liner 36 extends transverse to the major axis H for receiving a shaft, for example shaft 23 having exterior surface 25 which engages the lubricious liner 36 .
- the two outer races 14 are positioned proximate the ends of the elongated inner race 12 , each outer race 14 being mountable as desired to rotatably support the arm 42 in a fixed wing aircraft.
- the flap hinge arm 40 is mounted aft of a spar 48 in a wing 50 of a fixed wing aircraft.
- the bearing assembly 10 of the flap hinge arm 40 is mounted in ribbing 49 or the like aft of the spar 48 .
- the flap hinge arm 40 is in an extended position that allows a flap 54 to which the flap hinge arm is coupled to extend out of an opening 56 at the rearward-facing surface of the wing 50 .
- the flap 54 is defined by a leading portion 54 a and a trailing portion 54 b linkably coupled to each other via a connecting linkage 58 .
- the connecting linkage 58 is pivotally connected to an extension arm 60 pivotally mounted at a pivot point 62 in the wing 50 and pivotally mounted at a pivot point 64 on the leading portion 54 a.
- the leading portion 54 a is coupled to a hinged extension lever 66 comprising a rearward arm 66 a coupled to a forward arm 66 b at a pivot point 67 .
- the forward arm 66 b is pivotally coupled to the wing 50 proximate the ribbing 49 at a pivot point 69 .
- a support link 70 is also coupled to the forward arm 66 b at a pivot point 71 and to the wing at a pivot point 72 .
- the connecting rod 44 of the flap hinge arm 40 is also pivotally connected to the forward arm 66 b.
- the hinged extension lever 66 is pivoted at pivot point 69 and pulled forward, thereby causing the forward arm 66 b and the rearward arm 66 a to fold at pivot point 67 . In doing so, the flap 54 is pulled into the opening 56 in the rearward-facing surface of the wing 50 .
Abstract
A bearing assembly includes an outer race having an inner surface defining a concave contour and an inner race positioned in the outer race. The inner race has an inner surface defining a bore therethrough and an outer surface defining at least one groove circumscribing the outer surface. A plurality of rolling elements is rollably located in the groove and is in rolling contact with the inner surface of the outer race. A lubricious liner has an inner liner-surface and an exterior liner-surface, the exterior liner-surface being disposed on the inner surface defining the bore. The lubricious liner has a modulus of compression of a magnitude sufficient to allow misalignment of the inner liner-surface relative to the exterior liner-surface in response to a force applied thereto.
Description
- The instant application is a continuation application of and claims priority benefit to U.S. application Ser. No. 14/438,785, entitled “HYBRID BEARING ASSEMBLY WITH ROLLING ELEMENTS AND PLAIN BEARING,” filed on Apr. 27, 2015, which is a national stage application of, and claims priority benefit to PCT Application No. PCT/US13/38626, entitled “HYBRID ROLLING ELEMENT AND PLAIN BEARING,” filed on Apr. 29, 2013, which is a PCT application of and claims priority to U.S. Provisional Patent Application No. 61/640,302, entitled “HYBRID ROLLING ELEMENT AND PLAIN BEARING,” filed on Apr. 30, 2012, the entirety of each of which is incorporated by reference herein.
- The present invention is directed to bearings and, more particularly, to hybrid bearings for use in fixed wing aircraft flap hinge arms.
- The wings of a fixed wing aircraft typically employ ailerons and flaps that are mounted on hinges longitudinally along the wings. Ailerons are flight control surfaces that are hinged to the trailing edges of the wing and are independently movable up and down to deflect airflow away from the wing, thereby altering the lift on the wing and controlling the roll moment of the aircraft as well as allowing the plane to bank. Flaps are flight control surfaces that are also hinged to the trailing edges of the wings but are movable in tandem up or down. Angling the flaps down to deflect airflow down and away from the wing reduces the flight speed and allows the angle of descent to be increased without increasing air speed. In larger aircraft, the flaps are also generally extendable outward from the trailing edges.
- In using the flaps, however, the curvature of the wing is increased. Because the flaps are mounted along the wings in the directions in which the wings extend, increasing the curvature of a wing causes stress at the points at which the flaps are coupled to the wing. Bearings are used at these points in conjunction with linkages to enable the flaps to be extended and angled in response to pilot control. Placing stresses on the points at which the flaps are coupled to the wings may compromise the operation of the bearings, which in turn may affect the positioning of the flaps and operation of the aircraft.
- U.S. Patent Application Publication No. 2011/0220762 discloses an aircraft wing that includes a wing structure, a slat panel mounted on a track, and an actuator mechanism on the wing structure coupled to the track for moving the slat panel between a deployed position and a retracted position. Track roller bearings on the wing structure rotatably contact the track, and side roller bearings on the wing structure rotatably contact at least one side of the track. In another configuration, the actuator mechanism includes a shaft rotatably mounted on the wing structure, an actuator arm coupled to the track by a bearing linkage, and an actuator lever coupled to the shaft by a bearing linkage and to the actuator arm by a bearing linkage. At least one bearing linkage includes a spherical plain bearing. In addition, U.S. Patent Publication No. 2011/067509, German Patent Application No. 197 50 113, U.S. Pat. No. 1,457,584, U.S. Patent Publication No. 2012/058923, European Patent Application No. 0 843 106 and International Patent Application Publication No. WO 2012/080983 are also relevant to the present application.
- In one aspect, the present invention resides in a bearing assembly comprising: an outer race having an inner surface defining a concave contour; an inner race positioned in the outer race, the inner race having an inner surface defining a bore therethrough and an outer surface defining at least one groove circumscribing the outer surface; a plurality of rolling elements rollably located in the at least one groove and in rolling contact with the inner surface of the outer race; and a lubricious liner having an inner liner-surface and an exterior liner-surface, the exterior liner-surface being disposed on the inner surface defining the bore, the lubricious liner having a modulus of compression of a magnitude sufficient to allow misalignment of the inner liner-surface relative to the exterior liner-surface in response to a force applied thereto.
- In another aspect, the present invention resides in a bearing assembly comprising: an outer race having an inner surface defining a concave contour; an inner race positioned in the outer race, the inner race having an inner surface defining a bore therethrough and an outer surface defining at least one groove circumscribing the outer surface; a plurality of rolling elements rollably located in the at least one groove and in rolling contact with the inner surface of the outer race; and a lubricious liner having a coefficient of friction of a magnitude sufficient to prevent relative motion between the inner race and a shaft extending through the bore of the inner race during a first operating condition and to allow relative motion between the inner race and the shaft during a second operating condition.
- In another aspect, the present invention resides in a flap hinge arm of a fixed wing aircraft, comprising: an arm; a connecting rod pivotally connected to the arm and pivotally connectable to a flap; and a bearing assembly positioned on the arm and connectable to a wing of the fixed wing aircraft, the bearing assembly comprising, an outer race having an inner surface defining a concave contour; an inner race positioned in the outer race, the inner race having an inner surface defining a bore therethrough and an outer surface defining at least one groove circumscribing the outer surface; a plurality of rolling elements rollably located in the at least one groove and in rolling contact with the inner surface of the outer race; and a lubricious liner having an inner liner-surface and an exterior liner-surface, the exterior liner-surface being disposed on the inner surface defining the bore, the lubricious liner having a modulus of compression of a magnitude sufficient to allow misalignment of the inner liner-surface relative to the exterior liner-surface in response to a force applied thereto, and a coefficient of friction of a magnitude sufficient to prevent relative motion between the inner race and a shaft extending through the bore of the inner race during a first operating condition and to allow relative motion between the inner race and the shaft during a second operating condition.
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FIG. 1 is a side sectional view of a bearing assembly, of the present invention. -
FIG. 2A presents one embodiment of the bearing assembly ofFIG. 1 in a first operating condition. -
FIG. 2B presents the bearing assembly ofFIG. 2A in a second operating condition. -
FIG. 3A presents another embodiment of the bearing assembly ofFIG. 1 in a first operating condition. -
FIG. 3B presents the bearing assembly ofFIG. 3A in a second operating condition. -
FIG. 4A presents another embodiment of the bearing assembly ofFIG. 1 in a first operating condition. -
FIG. 4B presents the bearing assembly ofFIG. 4A in a second operating condition. -
FIG. 5 is a side sectional view of another embodiment of a bearing assembly of the present invention. -
FIG. 6 is a side sectional view of yet another alternate embodiment of a bearing assembly of the present invention. -
FIG. 7 is a side sectional view of yet another alternate embodiment of a bearing assembly of the present invention. -
FIG. 8 is a side sectional view of yet another alternate embodiment of a bearing assembly of the present invention. -
FIG. 9 is a side view of a flap hinge arm of a fixed wing aircraft in which the bearing assembly ofFIG. 1 orFIGS. 5-8 is installed. -
FIG. 10 is a front sectional view of the arm and bearing assembly of the flap hinge arm ofFIG. 9 . -
FIG. 11 is a side sectional view of a wing of a fixed wing aircraft incorporating the flap hinge arm ofFIG. 9 in an extended position. -
FIG. 12 is a side sectional view of a wing of a fixed wing aircraft incorporating the flap hinge arm ofFIG. 9 in a retracted position. - As shown in
FIG. 1 , an airframe control bearing assembly for use with an aircraft flap hinge arm is designated generally by thenumber 10 and is hereinafter referred to as “bearingassembly 10.”Bearing assembly 10 is a hybrid bearing that combines the misalignment (swivel action) capabilities of a plain spherical bearing and the rolling element aspect of an airframe control bearing, with a third degree of freedom which includes axial sliding of the bearing on a self-lubricated surface thus allowing for the accommodation of a greater degree of misalignment (e.g., rotational, tilt or cocking, and axial sliding) as compared to conventional bearings used in flap hinge arms. In particular, the range of motion of oscillation can be up to about 45 degrees. The present invention is not limited to an oscillation range of motion of about 45 degrees, however, as the oscillation of the bearing assembly may be greater than about 45 degrees. - In the illustrated embodiment, the
bearing assembly 10 comprises aninner race 12 concentrically positioned in anouter race 14. A plurality of rolling elements orballs 16 are located between and rollingly engage the inner and outer races, 12 and 14 respectively. The present invention is not limited to the use ofballs 16, however, as any suitable rolling element may be employed. Theinner race 12 is defined by aninner surface 18 and anouter surface 20. Theouter surface 20 includes twogrooves 17 that circumscribe theouter surface 20. At least a portion of theballs 16 rollingly engage each of thegrooves 17. As illustrated, theballs 16 are arranged in two staggered rows such that each ball is staggered relative to the next adjacent ball. Theinner surface 18 defines abore 22 extending through theinner race 12, the bore being located substantially concentrically about an axis A. - In the illustrated embodiment, the
outer race 14 is a ring that is defined by aninner surface 26 having a spherically concave contour and anouter surface 28. The concave contour of the outer raceinner surface 26 allows for theinner race 12 to be misaligned relative to theouter race 14 by up to about 45 degrees to accommodate the oscillation range of motion of bearingassembly 10 as described above. Theballs 16 rollingly engage theinner surface 26. Theouter surface 28 is suitably configured to facilitate the mounting of the bearingassembly 10 in a flap hinge arm. Upon incorporation of the bearingassembly 10 into the flap hinge arm, theouter race 14 and theinner race 12 rotate independently of each other. While theouter race 14 has been shown and described as being a ring, the present invention is not limited in this regard as the outer race can assume any practical shape or be integral with the flap hinge arm into which the bearingassembly 10 is installed without departing from the broader aspects of the present invention. - The bearing
assembly 10 includes aseal 30 positioned across the interface of theinner race 12 and theouter race 14 to inhibit the ingress of debris and contaminants into the bearing assembly. Retaining rings 32 are employed on theouter race 14 on opposing sides of theseals 30 to secure the seals in place. The bearingassembly 10 may include twoseals 30 positioned generally opposite one another on opposing sides of the bearing assembly. - The
balls 16 may be made from a steel or an alloy steel. For example, theballs 16 may be made from a stainless steel such as 440C (AMS 5880 or 5618), 52100 (AMS 6440), or Corrosion Resistant Nitrogen (“CREN”) Steel (e.g.,Cronidur 30® (available from Progressive Alloy Steels Unlimited of Las Vegas, Nev.), AMS 5898, or other suitable CREN when available), or the like. It is also contemplated that theballs 16 may be made from other materials that are sufficiently hard or can be sufficiently hardened through heat treatment. - Both the
inner race 12 and theouter race 14 may be made from a steel or an alloy steel, including, but not limited to, a stainless steel such as 440C (AMS 5880 or 5618), AMS 5655 solution nitride (CREN), 52100 (AMS 6440),Cronidur 30® (AMS 5898), or Aubert and Duvall XD15NW®, or another suitable material. - The bearing
assembly 10 also includes a self-lubricating coating composition bonded to theinner surface 18 defining thebore 22 to form alubricious liner 36 having an inner liner-surface 36B and an exterior liner-surface 36A. As illustrated inFIG. 1 , the bearingassembly 10 is mounted on ashaft 23 which extends through thebore 22. Theshaft 23 is substantially cylindrical and defines anexterior surface 25. Thelubricious liner 36 is disposed between theshaft 23 and thebore 22. The lubricious liner inner liner-surface 36B engages theexterior surface 25 of theshaft 23; and the lubricious liner exterior liner-surface 36A engages theinner surface 18 defining thebore 22. Theshaft 23 is press fit into thebore 22 so that during normal operation of the bearingassembly 10 theshaft 23 is fixed relative to theinner race 12 and there is essentially no slippage between thelubricious liner 36 and theexterior surface 25. As shown inFIGS. 2A and 2B , thelubricious liner 36 has a continuous annular shape. As shown inFIGS. 3A and 3B thelubricious liner 36 has an axial length L. The interior liner-surface 36B engages theexterior surface 25 of theshaft 23, continuously and entirely circumferentially around the shaft 23 (e.g., uninterrupted), along the axial length L of thelubricious liner 36. The exterior liner-surface 36A engages theinner surface 18, continuously and entirely circumferentially around the inner surface 18 (e.g., uninterrupted), along the axial length L of thelubricious liner 36. - The coefficient of friction of the
lubricious liner 36 is of a magnitude sufficient to prevent relative motion between theinner race 12 and theshaft 23 extending through thebore 22 during a first operating condition and to allow relative motion between theinner race 12 and theshaft 23 during a second operating condition, both in a radial direction and in an axial direction. For example, during a first operating condition, referred to herein as “normal operation,” as shown inFIG. 2A , a first operating torque t1 is transmitted to theouter race 14 which rotates in relation toinner race 12 by action of theballs 16. A second operating torque t2 is transmitted to thelubricious liner 36 and correspondingly to theshaft 23. Thelubricious liner 36 has a static coefficient of friction of a sufficient magnitude to maintain theshaft 23 in a substantially fixed relation to theinner race 12 and thelubricious liner 36 during normal operation when the first operating torque is in the range up to torque t1 and the second operating torque is in the range up to torque t2. For illustrative purposes, an indicator I1 indicates a first position of bearing 10 during normal operation wherein the indicator I1 of theshaft 23,lubricious liner 36,inner race 12, andouter race 14 align. Upon torque t1 being transmitted to bearing 10, the outer race rotates as indicated by an indicator I2 while the indicator I1 of theshaft 23,lubricious liner 36 andinner race 12 remains stationary. - In contrast, during a second operating condition, referred to herein as “anomalous operation,” as shown in
FIG. 2B , a third operating torque, or an anomalous operation torque t3 in excess of normal operating torque t1, is transmitted to theouter race 14 which rotates in relation toinner race 12 by action of theballs 16. A fourth operating torque, or an anomalous operation torque t4 in excess of normal operating torque t2, is transmitted to theinner race 12,lubricious liner 36 and correspondingly to theshaft 23. The coefficient of friction of thelubricious liner 36 is of a sufficient magnitude to enable rotational sliding engagement between theexterior surface 25 ofshaft 23 and thelubricious liner 36 when friction between theinner race 12 and theouter race 14 exceeds a predetermined magnitude thereby causing anomalous operation. For illustrative purposes, an indicator I3 indicates a first position of bearing 10 during anomalous operation wherein the indicator I3 of theshaft 23,lubricious liner 36,inner race 12, andouter race 14 align. Upon torque t3 being transmitted to bearing 10, the outer race rotates as indicated by anindicator 15, and theshaft 23 also rotates in relation to thelubricious liner 36 andinner race 12 as indicated by an indicator I4. In such a case,outer race 14 may rotate less than rotation under normal operation (i.e., theouter race 14 is rotating under anomalous operation), or theouter race 14 may remain stationary in relation to theinner race 12. If rotation of theouter race 14 relative to theinner race 12 is impeded by seizure of theballs 16, theinner race 12 andlubricious liner 36 will move relative to theshaft 23 and theexterior surface 25 slides relative to thelubricious liner 36. Thelubricious liner 36 is operable to engage a mating surface and to enable sliding engagement with the mating surface when torque required to rotate theouter race 14 relative to theinner race 12, exceeds a predetermined value. - Under normal operation, an axial force defined as equal to or less than an axial holding force is transmitted to the interface of the
lubricious liner 36 and theshaft 23 whereinlubricious liner 36 is operable to engage and retainshaft 23. Under anomalous operation, an axial force greater than the axial holding force, defined as an axial break-away force, is transmitted to the interface of thelubricious liner 36 and theshaft 23 whereinlubricious liner 36 is operable to permit axial sliding or shifting ofshaft 23. In one embodiment, the predetermined value of a torque applied to bearing 10 is normal operating torque t1, and anomalous operation torque t3 is in a range of magnitude of about 1.5 normal operating torque t1. In another embodiment, the predetermined value of a torque applied to bearing 10 is normal operating torque t1, and anomalous operation torque t3 is in a range of magnitude of about 1.25 normal operating torque t1. In another embodiment, the predetermined value of a torque applied to bearing 10 is normal operating torque t1, and anomalous operation torque t3 is in a range of magnitude of about 1.1 normal operating torque t1. Furthermore, thelubricious liner 36 also functions as a fail-safe mechanism by allowing the shaft to rotational slip in thebore 22 if the bearing were to seize. - As also shown in
FIG. 3A , the bearingassembly 10 is mounted on theshaft 23 which is a least partially disposed in thebore 22 andexterior surface 25 ofshaft 23 engages thelubricious liner 36. Thelubricious liner 36 reduces friction betweenexterior surface 25 ofshaft 23 received in or through thebore 22 and theinner surface 18 defining the bore particularly when forces (for example, as a result of wing bending or thermal differentials) act on the shaft in directions indicated by the arrow R and parallel to an axis B. The bearingassembly 10 may also translate along the shaft to some degree with reduced friction because of the presence of thelubricious liner 36. As described above, the coefficient of friction of thelubricious liner 36 is of a magnitude sufficient to prevent relative motion between theinner race 12 and theshaft 23 extending through thebore 22 during a first operating condition and to allow relative motion between theinner race 12 and theshaft 23 during a second operating condition. As shown inFIG. 3B , when forces act onshaft 23 in directions R parallel to axis B during a second operating condition,exterior surface 25 ofshaft 23 engages thelubricious liner 36 and moves in the direction R a distance Y in relation toinner surface 18 ofbore 22. Distance Y can be represented in relation to an outer diameter D ofshaft 23. In one embodiment, distance Y is in the range of about 0.25 D. In one embodiment, distance Y is in the range of about 0.5 D. In one embodiment, distance Y is in the range of about D. In one embodiment, distance Y is in the range of about 2 D. Thelubricious liner 36 also removes the need for the incorporation of a galvanic barrier on the bearingassembly 10 or the shaft in the event that the surface defining thebore 22 is a different material than the material of the shaft. - As shown in
FIGS. 4A and 4B , thelubricious liner 36 has a modulus of compression of a magnitude sufficient to allow misalignment (e.g., axial angular misalignment) of the lubricious liner inner liner-surface 36B disposed on theexterior surface 25 of theshaft 23 relative to the lubricious liner exterior liner-surface 36A disposed on theinner surface 18 defining thebore 22 in theinner race 12 in the directions generally indicated by the arrow N in response to a force applied thereto. As such,lubricious liner 36 provides for an axial angular misalignment of theshaft 23 in relation to theinner race 12. The bearingassembly 10 is mounted on theshaft 23 which is a least partially disposed in thebore 22 andexterior surface 25 ofshaft 23 engages thelubricious liner 36. Thelubricious liner 36 has a modulus of compression of a magnitude sufficient to maintain the lubricious liner inner liner-surface 36B in a substantially fixed relation to the lubricious liner exterior liner-surface 36A during normal operationsuch shaft 23,lubricious liner 36 andinner race 12 are substantially concentric about a central axis B. - Upon application of a force or load in the direction N, the
lubricious liner 36 has a modulus of compression of a magnitude sufficient to allow angular misalignment (i.e., an angular misalignment feature) of theinner race 12 relative to theshaft 23 such that a central axis C ofshaft 23 is displaced or misaligned from the axis B ofbore 22 by a misalignment angle α. As a result,shaft 23,lubricious liner 36 andinner race 12 are no longer concentric. In one embodiment, the misalignment angle α is from about one degree to about two degrees. In another embodiment, the misalignment angle α is from about one degree to about ten degrees. In one embodiment, the misalignment angle α is up to about 15 degrees. Referring toFIG. 4A , thelubricious liner 36 surrounds theshaft 23 and has a substantially equal thickness W1, W1′ a full 360° aroundexterior surface 25 betweenfirst end 36C andsecond end 36D.Lubricious liner 36 has a modulus of compression of a magnitude sufficient to allow sufficient compression of a width W1 of the liner and correspondingly allow sufficient expansion of width W1′ such that lubricious liner inner liner-surface 36B remains disposed onexterior surface 25 ofshaft 23 and lubricious liner exterior liner-surface 36A remains disposed oninner surface 18 ofbore 22 ofinner race 12. As such, lubricious liner inner liner-surface 36B remains in full contact withexterior surface 25 ofshaft 23 and lubricious liner exterior liner-surface 36A remains in full contact withinner surface 18 ofbore 22 ofinner race 12. As shown inFIG. 4B , in one embodiment, a portion of width W1 is compressible at thefirst end 36C to a width W2 and another portion of width W1′ is correspondingly expandable to a width W3. At thesecond end 36D, a portion of the width W1 is compressible to width W2 and another portion of the width W1′ is expandable to width W3. In one embodiment, a portion of width W1 is compressible to width W2 and another portion of width W1′ is expandable to width W3 up to a range of about 10% of width W1. In one embodiment, a portion of width W1 is compressible to width W2 and another portion of width W1′ is expandable to width W3 up to a range of about 25% of width W1. In one embodiment, a portion of width W1 is compressible to width W2 and another portion of width W1′ is expandable to width W3 up to a range of about 50% of width W1. - The
lubricious liner 36 includes polytetrafluoroethylene (PTFE). The PTFE may be in fiber form and woven with fabrics, such as, but not limited to, cotton, polyester, glass fiber, carbon fiber, nylon, aramid materials such as NOMEX® and KEVLAR® manufactured by DuPont, and combinations of the foregoing. When the PTFE is woven with fabric, the fabric may be set in a thermosetting resin or thermoplastic resin. Examples of thermosetting resins include, but are not limited to, phenolic resins, polyester resins, epoxy resins, urethane resins, polyurethane resins, polyimide resins, and the like. In an alternative embodiment, thelubricious liner 36 includes the woven PTFE fiber and chopped PTFE fibers in addition to the other fibers and resins listed above. In yet another embodiment, thelubricious liner 36 includes chopped PTFE fibers in addition to the other fibers and resins listed above and does not include the woven PTFE fiber. - In another embodiment, the
lubricious liner 36 could be molded to or injected and adhered onto theinner surface 18 defining thebore 22. In such an embodiment, thelubricious liner 36 includes a thermosetting resin, such as a phenolic resin, a polyester resin, an epoxy resin, a urethane resin, a polyurethane resin, a polyimide resin, or the like, which is mixed with any one or a combination of fibers such as PTFE, cotton, polyester, glass fiber, carbon fiber, nylon, and aramid fibers such as NOMEX® and KEVLAR®. - The present invention is not limited to a bearing assembly comprising two rows of balls, as indicated above. As shown in
FIGS. 5-7 , the bearing assembly may include rolling elements generally know as rollers of any shape including spherical rollers or balls, convex rollers or barrel rollers, concave rollers or hourglass rollers, cylindrical rollers, tapered rollers, etc. In each type of bearing assembly, the rolling element bearings may have one or two rows of rolling elements. - As shown in
FIG. 5 , a bearingassembly 110 may comprise aninner race 112 located in anouter race 114 with a plurality of rolling elements orballs 116 located therebetween in a single row. As with the bearing assembly ofFIG. 1 , theinner race 112 is a ring defined by inner and outer surfaces, the inner surface defining abore 122 extending therethrough, the bore being located substantially concentrically about an axis F. Alubricious liner 136 is disposed on the inner surface defining thebore 122. In one embodiment, bearingassembly 110 includes aseal 130 positioned across the interface of theinner race 112 and theouter race 114 to inhibit the ingress of debris and contaminants into the bearing assembly. The bearingassembly 110 may include twoseals 130 positioned generally opposite one another on opposing sides of the bearing assembly. Retaining rings 132 are employed on theouter race 114 on one side of theseals 130 to secure the seal in place. - As shown in
FIG. 6 , in one embodiment a bearingassembly 210 includes aninner race 212 located in anouter race 214 with a plurality of rolling elements or barrel rollers 216 (i.e., convex rollers) located therebetween in a single row. As with the bearing assembly ofFIG. 1 , theinner race 212 is a ring defined by inner and outer surfaces, the inner surface defining abore 222 extending therethrough, the bore being located substantially concentrically about an axis G. In one embodiment and as shown inFIG. 6 , theouter race 214 is integrally formed with alinkage assembly 240, such as for example aflap hinge arm 40 as further described below with referenceFIG. 9 . Alubricious liner 236 is disposed on the inner surface defining thebore 222. In one embodiment, bearingassembly 210 includes aseal 230 positioned across the interface of theinner race 212 and theouter race 214 to inhibit the ingress of debris and contaminants into the bearing assembly. The bearingassembly 210 may include twoseals 230 positioned generally opposite one another on opposing sides of the bearing assembly. Retaining rings 232 are employed on theouter race 214 on opposing sides of theseals 230 to secure the seals in place. - As shown in
FIG. 7 , in one embodiment a bearingassembly 310 includes aninner race 312 located in anouter race 314 with a plurality of rolling elements or hourglass rollers 316 (i.e. concave curvature which means the outer raceways correspondingly are convex) located therebetween in a single row. As with the bearing assembly ofFIG. 1 , theinner race 312 is a ring defined by inner and outer surfaces, the inner surface defining abore 322 extending therethrough. In one embodiment and as shown inFIG. 7 , theouter race 314 is integrally formed with alinkage assembly 340, such as for exampleflap hinge arm 40 as further described below with referenceFIG. 9 . Alubricious liner 336 is disposed on the inner surface defining thebore 322. In one embodiment, bearingassembly 310 includes aseal 330 positioned across the interface of theinner race 312 and theouter race 314 to inhibit the ingress of debris and contaminants into the bearing assembly. The bearingassembly 310 may include twoseals 330 positioned generally opposite one another on opposing sides of the bearing assembly. Retaining rings 332 are employed on theouter race 314 to secure the seals in place. - As shown in
FIG. 8 , in one embodiment a bearingassembly 410 includes aninner race 412 located in anouter race 414 with a plurality of rolling elements or cylindrical rollers 416 located therebetween in a single row. As with the bearing assembly ofFIG. 1 , theinner race 412 is a ring defined by inner and outer surfaces, the inner surface defining abore 422 extending therethrough. In one embodiment and as shown inFIG. 8 , theouter race 414 is integrally formed with alinkage assembly 440, such as for exampleflap hinge arm 40 as further described below with referenceFIG. 9 . Alubricious liner 436 is disposed on the inner surface defining thebore 222. In one embodiment, bearingassembly 410 includes aseal 430 positioned across the interface of theinner race 412 and theouter race 414 to inhibit the ingress of debris and contaminants into the bearing assembly. The bearingassembly 210 may include twoseals 230 positioned generally opposite one another on opposing sides of the bearing assembly. Retaining rings 432 are employed on theouter race 414 on opposing sides of theseals 430 to secure the seals in place. - As with the
lubricious liner 36 described above with reference to the bearingassembly 10, thelubricious liners lubricious liners - As shown in
FIG. 9 , one exemplary embodiment of a flap hinge arm for a fixed wing aircraft is designated generally by thereference number 40 and is hereinafter referred to as “flap hinge arm 40.” Theflap hinge arm 40 is defined by anarm 42 having the bearingassembly 10 mounted on oneend 42A thereof and a connectingrod 44 pivotally coupled to anopposing end 42B of the arm. As illustrated, the connectingrod 44 includes alink apparatus 46 having a spherical plain bearing 47 mounted therein. The present invention is not limited to the connectingrod 44 having thelink apparatus 46 and the spherical plain bearing 47, however, as any suitable bearing assembly may be associated with the connecting rod. The present invention is also not limited to the bearingassembly 10 being mounted in theflap hinge arm 40, however, as the bearingassembly 110 may also be mounted therein. At the end of a connecting rod, a rod end is typically mounted. This rod end can be attached to the connecting rod by a threaded or welded connection, or any other suitable means. An outer race can be mounted in the rod end eye with a Grumman groove, a press fit, or other suitable means. Instead of an outer race, the inner surface of the rod end eye can be used as the outer raceway (i.e. no separable outer race) by suitable heat treatment and machining (hard turning, grinding, or the like). - As shown in
FIG. 10 , theinner race 12 of the bearingassembly 10 may be integral with thearm 42 and elongated in a direction transverse to a major axis G through the arm. In such an embodiment, thebore 22 with thelubricious liner 36 extends transverse to the major axis H for receiving a shaft, forexample shaft 23 havingexterior surface 25 which engages thelubricious liner 36. The twoouter races 14 are positioned proximate the ends of the elongatedinner race 12, eachouter race 14 being mountable as desired to rotatably support thearm 42 in a fixed wing aircraft. - As shown in
FIGS. 11 and 12 , theflap hinge arm 40 is mounted aft of aspar 48 in a wing 50 of a fixed wing aircraft. The bearingassembly 10 of theflap hinge arm 40 is mounted in ribbing 49 or the like aft of thespar 48. Referring toFIG. 11 , theflap hinge arm 40 is in an extended position that allows a flap 54 to which the flap hinge arm is coupled to extend out of an opening 56 at the rearward-facing surface of the wing 50. The flap 54 is defined by a leading portion 54 a and a trailing portion 54 b linkably coupled to each other via a connecting linkage 58. The connecting linkage 58 is pivotally connected to an extension arm 60 pivotally mounted at apivot point 62 in the wing 50 and pivotally mounted at apivot point 64 on the leading portion 54 a. The leading portion 54 a is coupled to a hingedextension lever 66 comprising a rearward arm 66 a coupled to aforward arm 66 b at apivot point 67. Theforward arm 66 b is pivotally coupled to the wing 50 proximate theribbing 49 at a pivot point 69. Asupport link 70 is also coupled to theforward arm 66 b at apivot point 71 and to the wing at apivot point 72. The connectingrod 44 of theflap hinge arm 40 is also pivotally connected to theforward arm 66 b. - Referring now to
FIG. 12 , when theflap hinge arm 40 is retracted (thearm 42 is moved in the direction as indicated byarrow 76 inFIG. 11 ), the hingedextension lever 66 is pivoted at pivot point 69 and pulled forward, thereby causing theforward arm 66 b and the rearward arm 66 a to fold atpivot point 67. In doing so, the flap 54 is pulled into the opening 56 in the rearward-facing surface of the wing 50. - Although this invention has been shown and described with respect to the detailed embodiments thereof, it will be understood by those of skill in the art that various changes may be made and equivalents may be substituted for elements thereof without departing from the scope of the invention. In addition, modifications may be made to adapt a particular situation or material to the teachings of the invention without departing from the essential scope thereof. Therefore, it is intended that the invention not be limited to the particular embodiments disclosed in the above detailed description, but that the invention will include all embodiments falling within the scope of the foregoing description.
Claims (19)
1. A bearing assembly (10, 110, 210, 310, 410) comprising:
an outer race (14, 114, 214, 314, 414) having an inner surface (26) defining a concave contour;
an inner race (12, 112, 212, 312, 412) positioned in the outer race (14, 114, 214, 314, 414), the inner race (12, 112, 212, 312, 412) having an inner surface (18) defining a bore (22) therethrough and an outer surface (20) defining at least one groove (17) circumscribing the outer surface (20);
a plurality of rolling elements (16, 116, 216, 316, 416) rollably located in the at least one groove (17) and in rolling contact with the inner surface (26) of the outer race (14, 114, 214, 314, 414); and characterized by:
a lubricious liner (36, 136, 236, 336, 436) having an inner liner-surface (36A) and an exterior liner-surface (36B), the exterior liner-surface (36B) being disposed on the inner surface (18) defining the bore (22), the lubricious liner (36, 136, 236, 336, 436) having at least one of:
a modulus of compression of a magnitude sufficient to allow misalignment of the inner liner-surface (36A) relative to the exterior liner-surface (36B) in response to a force applied thereto; and
a coefficient of friction of a magnitude sufficient to prevent relative motion between the inner race (12, 112, 212, 312, 412) and a shaft (23) extending through the bore (22) of the inner race (12, 112, 212, 312, 412) during a first operating condition and to allow relative motion between the inner race (12, 112, 212, 312, 412) and the shaft (23) during a second operating condition.
2. The bearing assembly (10, 110, 210, 310, 410) of claim 1 , wherein the outer surface (20) of the inner race (12, 112, 212, 312, 412) comprises a plurality of grooves (17) in which the plurality of rolling elements (16, 116, 216, 316, 416) is located.
3. The bearing assembly (10, 110, 210, 310, 410) of claim 2 , wherein the plurality of rolling elements (16, 116, 216, 316, 416) is selected from a group consisting of spherical rollers, convex rollers, concave rollers and cylindrical rollers.
4. The bearing assembly (10, 110, 210, 310, 410) of claim 1 , further comprising a seal (30, 130, 230, 330, 430) secured to the outer race (14, 114, 214, 314, 414) and positioned across the plurality of rolling elements (16, 116, 216, 316, 416) to engage a surface of the inner race (12, 112, 212, 312, 412).
5. The bearing assembly (10, 110, 210, 310, 410) of claim 1 , wherein the plurality of rolling elements (16, 116, 216, 316, 416) are made from a material selected from the group consisting of stainless steel and corrosion resistant nitrided steel.
6. The bearing assembly (10, 110, 210, 310, 410) of claim 1 , wherein the outer race (14, 114, 214, 314, 414) and the inner race (12, 112, 212, 312, 412) are made from a material selected from the group consisting of stainless steel, tungsten steel, and corrosion resistant nitrided steel.
7. The bearing assembly (10, 110, 210, 310, 410) of claim 1 , wherein the lubricious liner (36, 136, 236, 336, 436) comprises PTFE.
8. The bearing assembly (10, 110, 210, 310, 410) of claim 7 , wherein the PTFE is in fiber form and woven with a fabric selected from the group consisting of cotton, polyester, glass fiber, carbon fiber, nylon, aramid material, and combinations of the foregoing materials.
9. The bearing assembly (10, 110, 210, 310, 410) of claim 8 , wherein the fabric is set in a thermosetting resin or thermoplastic resin.
10. The bearing assembly (10, 110, 210, 310, 410) of claim 1 wherein the concave contour of the inner surface (26) of the outer race (14, 114, 214, 314, 414) allows for the inner race (12, 112, 212, 312, 412) to be misaligned relative to the outer race (14, 114, 214, 314, 414) by up to about 45 degrees.
11. The bearing assembly (10, 110, 210, 310, 410) of claim 1 wherein a shaft is disposed in the bore of the inner race (12, 112, 212, 312, 412) and the shaft is misaligned relative to the inner race (12, 112, 212, 312, 412) by up to about 15 degrees.
12. A flap hinge arm (40) of a fixed wing aircraft, comprising:
an arm (42);
a connecting rod (44) pivotally connected to the arm (42) and pivotally connectable to a flap (54); and
a bearing assembly (10, 110, 210, 310, 410) positioned on the arm and connectable to a wing of the fixed wing aircraft, the bearing assembly comprising,
an outer race (14, 114, 214, 314, 414) having an inner surface (26) defining a concave contour;
an inner race (12, 112, 212, 312, 412) positioned in the outer race (14, 114, 214, 314, 414), the inner race (12, 112, 212, 312, 412) having an inner surface (18) defining a bore (22) therethrough and an outer surface (28) defining at least one groove (17) circumscribing the outer surface (28);
a plurality of rolling elements (16, 116, 216, 316, 416) rollably located in the at least one groove and in rolling contact with the inner surface (26) of the outer race (14, 114, 214, 314, 414); and characterized by
a lubricious liner (36, 136, 236, 336, 436) having an inner liner-surface (36A) and an exterior liner-surface (36B), the exterior liner-surface (36B) being disposed on the inner surface (18) defining the bore (22), the lubricious liner (36, 136, 236, 336, 436) having at least one of:
a modulus of compression of a magnitude sufficient to allow misalignment of the inner liner-surface (36A) relative to the exterior liner-surface (36B) in response to a force applied thereto, and
a coefficient of friction of a magnitude sufficient to prevent relative motion between the inner race (12, 112, 212, 312, 412) and a shaft extending through the bore of the inner race (12, 112, 212, 312, 412) during a first operating condition and to allow relative motion between the inner race (12, 112, 212, 312, 412) and the shaft during a second operating condition.
13. The flap hinge arm (40) of a fixed wing aircraft of claim 12 , further comprising a seal secured to the outer race (14, 114, 214, 314, 414) and positioned across the plurality of rolling elements (16, 116, 216, 316, 416) to engage a surface of the inner race (12, 112, 212, 312, 412).
14. The flap hinge arm (40) of a fixed wing aircraft of claim 12 , wherein the plurality of rolling elements (16, 116, 216, 316, 416) are made from a material selected from the group consisting of stainless steel and corrosion resistant nitrided steel.
15. The flap hinge arm (40) of a fixed wing aircraft of claim 12 , wherein the outer race (14, 114, 214, 314, 414) and the inner race (12, 112, 212, 312, 412) are made from a material selected from the group consisting of stainless steel, tungsten steel, and corrosion resistant nitrided steel.
16. The flap hinge arm (40) of a fixed wing aircraft of claim 12 , wherein the lubricious liner (36, 136, 236, 336, 436) comprises PTFE.
17. The flap hinge arm (40) of a fixed wing aircraft of claim 16 , wherein the PTFE is in fiber form and woven with a fabric selected from the group consisting of cotton, polyester, glass fiber, carbon fiber, nylon, aramid material, and combinations of the foregoing materials.
18. The flap hinge arm (40) of a fixed wing aircraft of claim 17 , wherein the fabric is set in a thermosetting resin or thermoplastic resin.
19. The flap hinge arm (40) of a fixed wing aircraft of claim 17 , wherein the plurality of rolling elements (16, 116, 216, 316, 416) is selected from a group consisting of spherical rollers, convex rollers, concave rollers and cylindrical rollers.
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US17/186,521 US20210277950A1 (en) | 2012-04-30 | 2021-02-26 | Hybrid bearing assembly with rolling elements and plain bearing |
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US201514438785A | 2015-04-27 | 2015-04-27 | |
US17/186,521 US20210277950A1 (en) | 2012-04-30 | 2021-02-26 | Hybrid bearing assembly with rolling elements and plain bearing |
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US14/438,785 Continuation US11149788B2 (en) | 2012-04-30 | 2013-04-29 | Hybrid bearing assembly with rolling elements and plain bearing |
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US17/186,521 Abandoned US20210277950A1 (en) | 2012-04-30 | 2021-02-26 | Hybrid bearing assembly with rolling elements and plain bearing |
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-
2013
- 2013-04-29 US US14/438,785 patent/US11149788B2/en active Active
- 2013-04-29 WO PCT/US2013/038626 patent/WO2014021958A1/en active Application Filing
- 2013-04-29 EP EP13795887.2A patent/EP2844886B1/en active Active
-
2021
- 2021-02-26 US US17/186,521 patent/US20210277950A1/en not_active Abandoned
Also Published As
Publication number | Publication date |
---|---|
EP2844886B1 (en) | 2018-11-07 |
US11149788B2 (en) | 2021-10-19 |
US20150292561A1 (en) | 2015-10-15 |
EP2844886A1 (en) | 2015-03-11 |
WO2014021958A1 (en) | 2014-02-06 |
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