WO2009084355A1 - Butée de débrayage et ensemble de palier de débrayage doté de celle-ci - Google Patents

Butée de débrayage et ensemble de palier de débrayage doté de celle-ci Download PDF

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Publication number
WO2009084355A1
WO2009084355A1 PCT/JP2008/071715 JP2008071715W WO2009084355A1 WO 2009084355 A1 WO2009084355 A1 WO 2009084355A1 JP 2008071715 W JP2008071715 W JP 2008071715W WO 2009084355 A1 WO2009084355 A1 WO 2009084355A1
Authority
WO
WIPO (PCT)
Prior art keywords
clutch release
release bearing
outer ring
seal member
seal
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2008/071715
Other languages
English (en)
Japanese (ja)
Inventor
Yasumitsu Ishikawa
Yasuyuki Katayama
Seiya Inoue
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NTN Corp
Original Assignee
NTN Corp
NTN Toyo Bearing Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2007338631A external-priority patent/JP2009156451A/ja
Priority claimed from JP2008010629A external-priority patent/JP2009174552A/ja
Priority claimed from JP2008017582A external-priority patent/JP2009180244A/ja
Application filed by NTN Corp, NTN Toyo Bearing Co Ltd filed Critical NTN Corp
Publication of WO2009084355A1 publication Critical patent/WO2009084355A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F16C19/16—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 a single row of balls
    • F16C19/163—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 a single row of balls with angular contact
    • 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
    • F16C33/58—Raceways; Race rings
    • F16C33/588—Races of sheet metal
    • 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
    • F16C33/58—Raceways; Race rings
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • 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
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7816—Details of the sealing or parts thereof, e.g. geometry, material
    • F16C33/783—Details of the sealing or parts thereof, e.g. geometry, material of the mounting region
    • 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
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7869—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward
    • 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
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/80—Labyrinth sealings
    • F16C33/805—Labyrinth sealings in addition to other sealings, e.g. dirt guards to protect sealings with sealing lips
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
    • F16D23/14—Clutch-actuating sleeves or bearings; Actuating members directly connected to clutch-actuating sleeves or 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
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/43—Clutches, e.g. disengaging bearing
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/08—Details or arrangements of sealings not provided for in group F16D3/84
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
    • F16D25/082—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation
    • F16D25/083—Actuators therefor

Definitions

  • the present invention relates to a clutch release bearing incorporated in a clutch device of a vehicle such as an automobile, and a clutch release bearing device including the same.
  • the clutch release bearing device is disposed between the engine and the transmission of the manual transmission vehicle, and moves in the axial direction in accordance with the operation of the clutch pedal to switch the clutch ON / OFF.
  • the clutch release bearing incorporated in the clutch release bearing device includes an inner ring 301 and an outer ring 302 that are rotatably provided via rolling elements (balls) 305.
  • a flange 304 is provided that contacts a rotating member (diaphragm spring) of the clutch device that does not.
  • the annular space formed between the inner ring 301 and the outer ring 302 is filled with a lubricant (for example, grease), and both wheels are used to prevent external leakage of the filled grease and entry of foreign matter into the annular space. Seal members 306 and 306 are disposed between them.
  • the outer diameter end portion of the seal member 306 is press-fitted and fixed to the inner diameter surface 303 of the outer ring 302 formed in a cylindrical surface extending in the axial direction.
  • 13 is a so-called contact type in which the inner diameter end portion (seal lip) contacts the inner ring 301 over the entire circumference in a state where the outer diameter end portion is fixed to the outer ring 302.
  • Patent Document 1 For example, see Patent Document 1).
  • the seal member assembled to the outer ring 302 in the above-described mode is not limited to the contact type described above, and the outer diameter end portion is fixed to the inner diameter surface of the outer ring.
  • the contact-type seal member includes a cored bar 307 and a rubber covering portion 308 that covers the surface of the cored bar.
  • the contact-type seal member includes a cored bar 307 and a rubber covering portion 308 that covers the surface of the cored bar.
  • a first problem of the present invention is to provide a clutch release bearing that can prevent the sealing member from being pulled out of the opening between both wheels without complicating the outer ring shape, and boasts high sealing performance. It is to provide.
  • a second object of the present invention is to provide a clutch release bearing with further improved sealing performance without increasing bearing torque.
  • a clutch release bearing having a contact portion with a rotating member of a clutch device is provided so as to be relatively rotatable through a rolling element.
  • the inner ring and the outer ring, and a seal member that seals the opening of the annular space formed between the inner ring and the outer ring, and the outer diameter end of the seal member is press-fitted and fixed to the inner diameter of the opening of the outer ring.
  • a clutch release bearing is provided in which an outer ring is fitted with a retaining member for restricting movement of the outer diameter end portion of the seal member to the outside in the axial direction.
  • the sealing member can be accompanied with an increase in internal pressure without complicating the outer ring shape. It is possible to prevent the seal member from being pulled out of the opening as much as possible.
  • the tightening margin (diameter tightening margin in the radial direction) of the seal member with respect to the inner diameter of the opening of the outer ring can be reduced, deformation of the seal member can be suppressed or prevented, and a stable sealing function can be ensured.
  • the axial movement of the seal member is restricted by the retaining member, it is possible to shorten the axial length of the region of the outer ring where the seal member is fixed, that is, to reduce the size of the bearing. it can.
  • the retaining member can include a cylindrical portion fitted to the outer diameter surface of the outer ring, and a flange portion extending from one end of the cylindrical portion and bent inward in the radial direction.
  • the inner diameter end portion of the flange portion of the retaining member can be arranged so that the tip thereof is in contact with the outer diameter end portion of the seal member. It can also arrange
  • the flange portion of the retaining member may be provided over the entire circumference (formed in a ring shape) or intermittently in the circumferential direction.
  • the latter configuration is suitable because the bearing can be reduced in weight and size.
  • the present invention is particularly suitable for a clutch release bearing that employs a so-called contact-type seal member in which an inner diameter end is brought into contact with the inner ring over the entire circumference. This is because the contact-type seal member can ensure high sealing performance as compared with the so-called non-contact type seal member, but the internal pressure is likely to rise due to the high sealability, and the outer ring is likely to be removed. .
  • a clutch release bearing having an abutting portion with a rotating member of the clutch device, which is relatively rotatable via a rolling element.
  • An inner ring and an outer ring provided, and a seal member that seals an opening of an annular space formed between the inner ring and the outer ring, and the outer diameter end of the seal member is press-fitted into the inner diameter surface of the outer ring extending in the axial direction
  • the fixed member is composed of a cored bar and a rubber coated part covering the surface thereof, and the outer diameter end of the sealing member is a part of the outer peripheral surface of which the cored bar is exposed on the inner diameter surface of the outer ring.
  • a clutch release bearing is provided in which a covering portion provided in a different axial direction from a part of the outer peripheral surface is pressed against the inner diameter surface of the outer ring.
  • the fixing member By pressing the metal core constituting the seal member against the inner surface of the outer ring as described above, the fixing member can be fixed to the outer ring without increasing the shape of the outer ring, and the seal member can be increased as the internal pressure increases. Can be prevented as much as possible from moving in the axial direction. However, it is not easy to bring the metals into close contact with each other without any gaps, and therefore there remains a risk that defects such as grease leakage may occur from the gaps formed between them.
  • the core provided as a part of the outer diameter end portion of the seal member and the covering portion provided in a different axial position are in pressure contact with the inner diameter surface of the outer ring.
  • the coating portion is closely attached to the inner diameter surface of the outer ring by its elastic restoring force.
  • the outer diameter end portion of the seal member is in contact with the inner diameter surface of the outer ring on the opening side of the annular space, and the core metal is disposed on the inner diameter surface of the outer ring on the opposite side of the annular space. It is desirable to press contact with. This is because the outer ring has a better adhesion to the inner surface of the outer ring than the core, and the sealing performance against entry of foreign matter from the outside is preferably the above-described mode.
  • the inner ring surface of the outer ring can be provided with a concave annular groove that is retracted to the outer diameter side from other places, and the annular groove and the covering portion can be fitted.
  • the covering portion of the sealing member is a known rubber material suitable for forming this type of sealing member, such as nitrile rubber (NBR), hydrogenated nitrile rubber (H-NBR), heat-resistant nitrile rubber, polyacrylic rubber, ethylene
  • NBR nitrile rubber
  • H-NBR hydrogenated nitrile rubber
  • EPDM propylene rubber
  • FKM fluorine rubber
  • the second configuration according to the present invention is particularly suitable for a clutch release bearing that employs a so-called contact seal in which an inner diameter end portion of a seal member is brought into contact with an outer diameter surface of an inner ring.
  • a so-called contact seal in which an inner diameter end portion of a seal member is brought into contact with an outer diameter surface of an inner ring.
  • the present invention is suitable for a clutch release bearing in which an outer ring on which an outer diameter end portion of a seal member is press-fitted and fixed is press-molded. This is because press molding is advantageous for lowering the manufacturing cost, but it is disadvantageous in forming each part with high precision, and a gap is easily formed between the seal member (the core metal) and the inner ring surface of the outer ring. .
  • a clutch release bearing having an abutting portion with a rotating member of a clutch device, and an inner ring and an outer ring provided so as to be relatively rotatable via rolling elements. And a seal member that seals the opening of the annular space formed between the inner ring and the outer ring, and a cover member that extends in the radial direction and faces the seal member in the axial direction at one end of the inner ring.
  • a clutch release bearing is provided in which a labyrinth seal extending in a radial direction is formed between the cover member and the seal member.
  • a labyrinth seal that is a non-contact seal is additionally provided on the outer side of the bearing with respect to the seal portion formed in cooperation with the seal member and the inner ring (or outer ring). Therefore, the sealing performance can be improved without increasing the bearing torque.
  • the member on one side forming the labyrinth seal is a cover material (separate from the inner ring) fixed to one end of the inner ring, and the cover material has a strength that can prevent the sealing member from being pulled out. It is sufficient if it is provided with the strength required for the main part of the inner ring. Therefore, the cover material can be formed of, for example, a thin steel plate or resin having a high degree of freedom in shape (easily processed), and thus this type of labyrinth seal can be simplified while reducing the weight of the bearing. Can be formed.
  • the labyrinth seal can be extended linearly in the radial direction.
  • an annular ridge is provided on at least one of the cover member or the seal member, and at this ridge (between the ridge and the ridge provided on the counterpart member or the counterpart member, the ridge is provided. ) Can be formed.
  • the labyrinth seal can be extended linearly in the radial direction, or in a meandering manner in the radial direction. In this case, since the entire length of the labyrinth seal can be increased as compared with the above-described configuration, the sealing performance can be further improved.
  • the labyrinth seal having such a configuration is provided with one or a plurality of annular protrusions on the cover material, and the seal member is provided with one or a plurality of annular protrusions with different radial positions from the annular protrusion of the cover material. It can be formed by the protrusion and the annular protrusion of the seal member.
  • the form of the annular protrusion is arbitrary as long as the labyrinth seal can be formed, and the required sealing performance and bearing type (outer ring rotation type, inner ring rotation type) It can be set accordingly.
  • the labyrinth seal extending in a meandering manner in the radial direction is not limited to one in which concave arcs and convex arcs are alternately continued.
  • the clutch release bearing according to the present invention described above includes, for example, a fixed body, and a movable body provided so as to be movable in the axial direction along the fixed body due to a volume variation of a variable volume chamber formed between the fixed body and the fixed body.
  • the movable body is provided with a clutch release bearing. In short, it can be suitably used by being incorporated in a hydraulically driven clutch release bearing device.
  • FIG. 1 is a clutch release bearing device incorporating a clutch release bearing to which the first configuration of the present invention is applied, and more specifically, a cross-sectional view showing an example of a hydraulically driven clutch release bearing device driven by hydraulic pressure. It is. The figure shows a state in which the clutch is engaged.
  • a clutch release bearing device 1 shown in FIG. 1 is provided with a fixed body 30 attached to a casing 50 of a gear box, and is provided so as to be movable in the axial direction with respect to the fixed body 30.
  • the main part is composed of the movable body 20 forming 40.
  • a control hydraulic pressure generator (not shown) is connected to the variable volume chamber 40, and the chamber 40 is filled with oil as a control fluid.
  • the left side in the figure is referred to as the front side
  • the right side in the figure is referred to as the rear side.
  • the fixed body 30 has a guide tube 33 provided with a radial edge 34 constituting the bottom of the variable volume chamber 40 at one end on the rear side, and an outer diameter side end of the radial edge 34 fitted in a groove 32 provided on the inner diameter surface.
  • a main portion is constituted by the cylindrical outer body 31.
  • the movable body 20 is disposed on the piston 22 that is externally fitted to the guide tube 33 via the piston support tube 21 and the front end of the piston 22, and is a rotary member of a clutch device (not shown) (hereinafter referred to as a diaphragm spring). And a clutch release bearing 10 having a contact portion with the main component.
  • the piston 22 projects outwardly from the outer cylindrical portion 22a and the inner cylindrical portion 22b extending in the axial direction, an annular portion 22c that connects the two cylindrical portions at one end on the front side, and a base end of the outer cylindrical portion 22a. And a protrusion 22d.
  • the inner cylindrical portion 22 b is inserted into the inner periphery of the outer body 31 to form a variable volume chamber 40 with the fixed body 30, and the protrusion 22 d is disposed on the outer periphery of the outer cylindrical portion 22 a. It plays a role of locking one end on the front side of the preload spring 24.
  • One end on the front side of the piston support tube 21 extends slightly beyond the annular portion 22c of the piston 22, and a centering ring (disc spring) 23 is fitted into an annular groove 21a formed on the outer diameter surface of the extended portion. Is done.
  • the aligning ring 23 has a spring force for elastically supporting the clutch release bearing 10 (the inner ring 11 thereof) in cooperation with the annular portion 22c of the piston 22, and the clutch release bearing 10 Alignment is allowed by being pressed toward the piston 22 by the spring force of the ring 23.
  • the clutch release bearing 10 which is the gist of the present invention will be described in detail.
  • the clutch release bearing 10 in the illustrated example is a so-called angular ball bearing, and as shown in an enlarged view in FIG. 2, an inner ring 11 and an outer ring 12 provided so as to be relatively rotatable via a plurality of rolling elements (balls) 13. , A cage 14 that is incorporated between the two wheels and holds the balls 13 at predetermined intervals in the circumferential direction, and first and second openings respectively disposed in the rear side and front side openings of the annular space formed between the two wheels.
  • the illustrated clutch release bearing 10 is an outer ring rotating type bearing in which an inner ring 11 is a stationary side and an outer ring 12 is a rotating side.
  • the inner ring 11 is a press-formed product of a steel plate, has a substantially cylindrical shape extending in the axial direction, a cylindrical portion 11a in which a rolling surface of the ball 13 is formed on the outer diameter surface, and one end on the front side of the cylindrical portion 11a. From the rear end of the cylindrical portion 11a to the outer diameter side, the first flange portion 11b extending between the annular portion 22c of the piston 22 and the aligning ring 23. Is integrally formed with a second flange portion 11c facing the rear end surface of the first seal member 15 via an axial gap.
  • the rear side end surface of the first flange portion 11b is formed in a flat surface in a direction perpendicular to the axis, corresponding to the end surface shape of the annular portion 22c of the piston 22 with which the first flange portion 11b abuts.
  • the 2nd collar part 11c can also be comprised by fixing another member of substantially the same shape to the rear side one end of the cylindrical part 11a among the components of the inner ring
  • the outer ring 12 is a press-formed product of a steel plate like the inner ring 11, has a substantially cylindrical shape extending in the axial direction, and a cylindrical portion 12a in which the rolling surface of the ball 13 is formed on the inner diameter surface 12a1, and the cylindrical portion 12a. It has a flange 12b that extends from one end of the front side to the inner diameter side and serves as a contact portion with a diaphragm spring (not shown). Of the inner diameter surface 12a1 of the cylindrical portion 12a, a region where both the seal members 15 and 16 are fixed is formed on a cylindrical surface parallel to the axis.
  • the flange portion 12b is always in contact with the diaphragm spring by a preload spring 24 acting between the outer body 31 and the flange portion 22d of the piston 22, and its cross-sectional shape is in line contact with the diaphragm spring (point contact in the sectional view). ), A convex arc shape protruding to the front side.
  • a carburized steel plate can be used as the steel plate for forming the inner ring 11 and the outer ring 12.
  • the carburized steel that can be used include nickel chrome steel (SNC), nickel chrome molybdenum steel (SNCM), chrome steel (SCr), and chrome molybdenum steel (SCM).
  • SNC nickel chrome steel
  • SNCM nickel chrome molybdenum steel
  • SCr chrome steel
  • SCM chrome molybdenum steel
  • either one or both of the inner ring 11 and the outer ring 12 may be a press-formed product of a steel plate as described above, a forged product, or a machined product such as cutting.
  • the second seal member 16 is composed of a core bar 17 having a substantially L-shaped cross section and a rubber cover 18 vulcanized and bonded to cover the surface of the core bar 17.
  • the second seal member 16 has an inner diameter of the outer ring 12 by pressing the covering portion 18 constituting the outer diameter end portion 16a against the inner diameter surface 12a1 (strictly speaking, the inner diameter surface on the front side) of the outer ring cylindrical portion 12a. It is press-fitted and fixed to the surface 12a1.
  • the inner diameter end portion 16b (lip) contacts the outer diameter surface of the inner ring 11 over the entire circumference, and a seal portion S formed of a so-called contact seal. Is formed. Thereby, the front side opening part of the annular space formed between both the wheels 11 and 12 is sealed.
  • the first seal member 15 is composed of a core bar 17 having a substantially L-shaped cross section, and a rubber cover 18 that is vulcanized and bonded to cover the surface of the core bar 17.
  • the covering portion 18 constituting the outer diameter end portion 15a is press-fitted to the inner diameter surface 12a1 of the outer ring 12 by being brought into pressure contact with the inner diameter surface 12a1 (strictly speaking, the inner diameter surface on the rear side) of the outer ring cylindrical portion 12a. Is done.
  • the inner diameter end portion 15b (lip) contacts the outer diameter surface of the inner ring 11 over the entire circumference, and a seal portion S formed of a so-called contact seal. Form. Thereby, the rear side opening part of the annular space formed between the two wheels 11 and 12 is sealed.
  • a known rubber material having excellent wear resistance for example, nitrile rubber (NBR), hydrogenated nitrile rubber (H-NBR), heat resistance Nitrile rubber, polyacrylic rubber, ethylene propylene rubber (EPDM), fluorine rubber (FKM), etc.
  • NBR nitrile rubber
  • H-NBR hydrogenated nitrile rubber
  • EPDM ethylene propylene rubber
  • FKM fluorine rubber
  • hydrogenated nitrile rubber or heat-resistant nitrile rubber exhibiting excellent water resistance (weather resistance) characteristics. Is particularly preferred.
  • the retaining member 19 has a substantially cylindrical shape extending in the axial direction, and includes a cylindrical portion 19a fitted to the outer diameter surface 12a2 of the outer ring 12 (cylindrical portion 12a), and one end (rear side end) of the cylindrical portion 19a. Part) and a flange part 19b extending radially inward.
  • the flange portion 19 b has a ring shape as shown in FIG. 3A, and the inner diameter end portion 19 b 1 is located on the outer side in the axial direction of the outer diameter end portion 15 a of the first seal member 15.
  • An inner diameter end portion 19b1 of the flange portion 19b is bent to the front side, and a tip thereof is in contact with an outer diameter end portion 15a of the first seal member 15 (strictly speaking, an outer peripheral corner portion of the outer diameter end portion 15a). Yes.
  • the retaining member 19 is fixed to the outer ring 12 by fitting a steel plate material press-molded in the above-described manner to the outer diameter surface 12a2 of the outer ring 12.
  • a stepped portion 12a3 having a tapered surface that is gradually reduced in diameter toward the front side is formed on the outer diameter surface 12a2 of the tubular portion 12a of the outer ring 12, and the cylinder of the retaining member 19 is formed on the stepped portion 12a3.
  • the steel plate material is bent along the shape of the outer ring 12, thereby preventing the retaining member 19. Formation and assembly to the outer ring 12 can also be performed.
  • an adhesive may be interposed therebetween.
  • the outer ring 12 It is possible to prevent the first seal member 15 from moving in the axial direction as the internal pressure rises without complicating the shape, and thus to prevent the first seal member 15 from being pulled out of the opening between the two wheels as much as possible. be able to.
  • both the sealing members 15 and 16 are so-called contact types that can ensure a relatively good sealing performance, the internal pressure is reduced by the rolling resistance of the balls 13 during the bearing operation. It is easy to rise, and therefore there is a high risk of the seal member (particularly the first seal member 15) being pulled out.
  • the configuration of the present invention it is possible to reliably prevent the outer ring 12 from being pulled out.
  • the outer diameter end portion of the first seal member 15 can be prevented as much as possible by adopting the above-described configuration.
  • the axial length of 15a that is, the length of the fixed portion of the first seal member 15 with respect to the outer ring 12, and the axial length of the rear-side inner diameter surface 12a1 of the outer ring 12 can be shortened. As a result, the bearing can be made compact.
  • the radial interference between the first seal member 15 and the outer ring 12 can be made smaller than before. Thereby, the deformation
  • the extension dimension of the retaining member 19 to the inner diameter side of the flange portion 19b is arbitrary as long as the axial movement of the first seal member 15 (the outer diameter end portion 15a thereof) can be restricted. As the length increases, the retaining member 19 and thus the clutch release bearing 10 become heavier.
  • the flange portion 19 is extended to the inner diameter side so that the inner diameter end portion 19b1 is positioned on the outer side in the axial direction of the outer diameter end portion 15a of the first seal member 15, so that the first seal While preventing the removal of the member 15 as much as possible, the weight of the clutch release bearing 10 due to the provision of the retaining member 19 can be suppressed as much as possible.
  • the flange portion 19b of the retaining member 19 is formed in a ring shape (formed over the entire circumference)
  • the flange portion 19b can be formed intermittently in the circumferential direction as shown in FIG. 3B. With this configuration, it is possible to reduce the weight of the retaining member 19 and thus the clutch release bearing 10 as compared to the above-described embodiment.
  • the retaining member 19 is formed of a metal material such as a steel plate.
  • the configuration of the present invention is not limited to this. That is, the retaining member 19 can be formed of a resin material or ceramics as long as the first seal member 15 can be prevented from moving in the axial direction (withdrawal).
  • the inner ring rotation type bearing structure as described in Patent Document 2 above is described. More specifically, in the case where a bearing structure is formed in which a flange portion that is a contact portion with a diaphragm spring is formed at one end on the front side of the inner ring 11 and a flange portion is not provided on one end on the front side of the outer ring 12.
  • the flange portion 19b fits the retaining member 19 provided at one end on the front side of the cylindrical portion 19a to the outer diameter surface of the outer ring 12, whereby the front side opening is sealed with the flange portion 19b. It is also possible to prevent the second seal member 16 from being removed.
  • FIG. 4 is a clutch release bearing device incorporating a clutch release bearing to which the second configuration of the present invention is applied.
  • FIG. 4 is a sectional view showing an example of a hydraulically driven clutch release bearing device driven by hydraulic pressure. is there. This figure shows a state in which the clutch is engaged.
  • a clutch release bearing device 101 shown in the figure is provided with a fixed body 130 attached to a casing 150 of a gear box, and is provided so as to be movable in the axial direction with respect to the fixed body 130.
  • the movable body 120 forming 140 forms a main part.
  • a control hydraulic pressure generator (not shown) is connected to the variable volume chamber 140, and the chamber 140 is filled with oil as a control fluid.
  • the left side in the figure is referred to as the front side
  • the right side in the figure is referred to as the rear side.
  • the fixed body 130 has a guide tube 133 provided with a radial edge 134 constituting the bottom of the variable volume chamber 140 at one end on the rear side, and an outer diameter side end of the radial edge 134 fitted in a groove 132 provided on the inner diameter surface.
  • a main part is constituted by the cylindrical outer body 131.
  • the movable body 120 is disposed at the front end of the piston 122 that is externally fitted to the guide tube 133 via the piston support tube 121, and is in contact with a rotating member (diaphragm spring) of a clutch device (not shown).
  • a clutch release bearing 110 having a portion is provided as a main constituent member.
  • the piston 122 includes an outer cylindrical portion 122a and an inner cylindrical portion 122b that extend in the axial direction, an annular portion 122c that connects both cylindrical portions at one end on the front side, and an outer diameter side that extends from the base end portion of the outer cylindrical portion 122a. And an existing flange portion 122d.
  • the inner cylindrical portion 122b is inserted into the inner periphery of the outer main body 131 to form a variable volume chamber 140 between the fixed body 130 and the flange portion 122d is an outer periphery of the outer cylindrical portion 122a (piston 122). It plays the role which latches the front side one end of the preload spring 124 arrange
  • One end on the front side of the piston support tube 121 extends slightly beyond the annular portion 122c of the piston 122, and a centering ring (disc spring) 123 is fitted into an annular groove 121a formed on the outer diameter surface of the extended portion. Is done.
  • the alignment ring 123 has a spring force for elastically supporting the clutch release bearing 110 (the inner ring 111 thereof) in cooperation with the annular portion 122c of the piston 122.
  • the clutch release bearing 110 Alignment is allowed by being pressed toward the piston 122 by the spring force of the ring 123.
  • the clutch release bearing 110 in the illustrated example is a so-called angular ball bearing, and as shown in an enlarged view in FIG. 5, an inner ring 111 and an outer ring 112 provided so as to be relatively rotatable via a plurality of rolling elements (balls) 113.
  • a cage 114 that is incorporated between the two wheels and holds the balls 113 at predetermined intervals in the circumferential direction, and first and second seal members 115 disposed at both ends of an annular space formed between the two wheels. 116, and an annular space formed between the two wheels is filled with grease as a lubricant.
  • the illustrated clutch release bearing 110 is an outer ring rotation type bearing in which the inner ring 111 constitutes a stationary side and the outer ring 112 constitutes a rotation side.
  • the inner ring 111 is a press-molded product obtained by subjecting a molded product obtained by pressing a steel plate to a heat treatment from the viewpoint of suppressing manufacturing costs.
  • the inner ring 111 has an inner diameter side from a front-side end of a substantially cylindrical portion extending in the axial direction.
  • a first flange 111a having a distal end portion interposed between the annular portion 122c of the piston 122 and the aligning ring 123; a cylindrical portion extending from the rear side end to the outer diameter side;
  • the rear end of the seal member 115 and the second flange 111b facing each other with a gap in the axial direction are integrally provided.
  • the rear side end surface of the first flange portion 111a is formed in a flat surface in a direction perpendicular to the axis line, corresponding to the shape of the end surface of the annular portion 122c of the piston 122 with which the first flange portion 111a contacts.
  • the 2nd collar part 111b can also be comprised by fixing another member to the rear side end of a cylindrical part.
  • the outer ring 112 is a press-formed product of a steel plate like the inner ring 111, and extends from the one end on the front side of the substantially cylindrical portion extending in the axial direction to the inner diameter side, and a flange portion 112a serving as a contact portion with a diaphragm spring (not shown).
  • a region where both the seal members 115 and 116 are fixed is formed in a cylindrical surface extending in the axial direction.
  • the flange portion 112a of the outer ring 112 is always in contact with the diaphragm spring by a preload spring 124 acting between the outer main body 131 and the flange portion 122d of the piston 122, and its cross-sectional shape is in line contact with the diaphragm spring (cross-sectional view).
  • a convex arc shape projecting to the front side is formed so as to make point contact.
  • a carburized steel plate can be used as a steel plate for forming the inner ring 111 and the outer ring 112 as a steel plate for forming the inner ring 111 and the outer ring 112.
  • the carburized steel that can be used include nickel chrome steel (SNC), nickel chrome molybdenum steel (SNCM), chrome steel (SCr), and chrome molybdenum steel (SCM).
  • SNC nickel chrome steel
  • SNCM nickel chrome molybdenum steel
  • SCr chrome steel
  • SCM chrome molybdenum steel
  • either or both of the inner ring 111 and the outer ring 112 can be a press-formed product of a steel plate as described above, a forged product, or a machined product such as cutting.
  • the second seal member 116 includes a core metal 117 having a substantially L-shaped cross section, and a rubber covering portion 118 vulcanized and bonded to cover the surface of the core metal 117.
  • the outer diameter end portion 119 is press-fitted and fixed to the inner diameter surface 112b (strictly speaking, the inner diameter surface on the front side) of the outer ring 112 extending in the axial direction.
  • the outer diameter end portion 119 of the second seal member 116 is covered with the covering portion 118 on the entire surface of the core metal 117, and the outer ring 112 is brought into pressure contact with the inner diameter surface 112 b of the outer ring 112.
  • the inner surface 112b is press-fitted and fixed.
  • the first seal member 115 includes a core metal 117 having a substantially L-shaped cross section, and a rubber covering portion 118 that is vulcanized and bonded to cover the surface of the core metal 117.
  • the outer diameter end portion 119 is press-fitted and fixed to the inner diameter surface 112b (strictly speaking, the inner diameter surface on the rear side) of the outer ring 112 extending in the axial direction.
  • the outer diameter end portion 19 of the first seal member 115 has a covering portion 118 formed so as to cover a part of the outer peripheral surface of the core metal 117 on the opening side (rear side).
  • the press-fitting and fixing of the first seal member 115 to the inner diameter surface 112b of the outer ring 112 is performed by using the covering portion 118 formed in a predetermined region on the opening side (rear side) and in a predetermined region on the opposite opening side (front side).
  • the exposed core metal 117 is pressed against the inner diameter surface 112b of the outer ring 112, respectively.
  • the outer diameter end portion 119 is press-fitted and fixed to the outer ring inner diameter surface 112b, the lip provided at the inner diameter end portion comes into contact with the outer diameter surface of the inner ring 111 over the entire circumference, and a seal composed of a so-called contact seal. Part S1 is formed. Thereby, the rear side opening of the annular space formed between the two wheels 111 and 112 is sealed.
  • the rubber material used for forming the covering portion 118 may be a known rubber material suitable for forming this type of seal member, for example, nitrile rubber (NBR), hydrogenated nitrile rubber (H-NBR), heat resistant Nitrile rubber, polyacrylic rubber, ethylene propylene rubber (EPDM), fluorine rubber (FKM), etc. can be used, but hydrogenated nitrile rubber or heat-resistant nitrile rubber with excellent water resistance (weather resistance) and wear resistance Is particularly preferable, and is formed using hydrogenated nitrile rubber in this embodiment.
  • NBR nitrile rubber
  • H-NBR hydrogenated nitrile rubber
  • EPDM ethylene propylene rubber
  • FKM fluorine rubber
  • the fixing strength of the outer diameter end portion 119 of the first seal member 115 with respect to the outer ring 112 is set so that only the covering portion 118 is pressed against the inner diameter surface 112b of the outer ring 112. Compared to the conventional configuration, it can be increased.
  • the outer ring 112 and the metal core 117 both of which are made of a metal material, adhere to each other without any gaps.
  • the outer ring 112 is a press-molded product, in particular, between the two. A gap is likely to occur.
  • the rubber cover 118 provided at a different axial position from the core metal 117 constituting a part of the outer diameter end 119 of the first seal member 115 is provided with the inner diameter surface 112 b of the outer ring 112. In this pressure contact portion, the covering portion 118 is in close contact with the inner diameter surface 112b of the outer ring 112 in an excellent manner by its elastic restoring force.
  • the covering portion 118 is pressed against the inner diameter surface 112 b of the outer ring 112 on the opening (rear opening) side of the annular space formed between the inner ring 111 and the outer ring 112. This is effective against the entry of foreign matter from the outside, and is suitable for satisfying the high muddy water resistance demanded in recent years.
  • the above-described operational effects can be obtained simply by appropriately setting the formation position, thickness, and the like of the covering portion 118 that is vulcanized and bonded to the core metal 117, and it is not necessary to complicate the shape of the outer ring 112.
  • With a simple structure it is possible to reliably prevent the deterioration of the sealing performance due to the poor adhesion of the outer diameter end portion 119 of the member 115, that is, the occurrence of unexpected problems such as grease leakage and foreign substance intrusion.
  • FIG. As shown in the figure, a concave annular groove 112c that is retracted to the outer diameter side from the other part is provided in the vicinity of the rear side opening portion in the inner diameter surface 112b of the outer ring 112, and the first seal member 115 is provided in the annular groove 112c. It is also possible to fit the covering portion 118 constituting the outer diameter end portion 119. With such a configuration, since the annular groove 112c and the covering portion 118 are engaged in the axial direction, the axial movement of the first seal member 115 is more effectively prevented, and a predetermined sealing performance can be obtained more stably. It is done.
  • the second seal member 116 has a part of one end face (front side end face) in contact with the flange 112a of the outer ring 112, and therefore, the second seal member accompanying an increase in internal pressure or the like.
  • the movement of 116 toward the opening (front opening) is prevented.
  • the outer diameter end portion 119 of the second seal member 116 has the same configuration as the conventional one, but this type of backup function cannot be obtained due to the shape of the outer ring 112 and the like, and the same shaft as the first seal member 115 is used.
  • the outer diameter end portion 119 of the second seal member 116 can be configured similarly to the outer diameter end portion 119 of the first seal member 115.
  • the clutch release bearing in which the outer ring 112 is provided with the flange that is in contact with the diaphragm spring has been described.
  • the flange extending to the outer diameter side is provided at one end (one end on the front side) of the inner ring 111.
  • FIG. 7 is a cross-sectional view showing an example of a clutch release bearing device incorporating a clutch release bearing to which the third configuration of the present invention is applied, and more specifically, an example of a hydraulically driven clutch release bearing device driven by hydraulic pressure.
  • a clutch release bearing device 201 shown in FIG. 1 is provided with a fixed body 230 attached to a casing 250 of a gear box, and is provided so as to be movable in the axial direction with respect to the fixed body 230.
  • the main part is composed of the movable body 220 forming 240.
  • a control hydraulic pressure generator (not shown) is connected to the variable volume chamber 240, and the chamber 240 is filled with oil as a control fluid.
  • the left side in the figure is referred to as the front side
  • the right side in the figure is referred to as the rear side.
  • the fixed body 230 has a guide tube 233 provided with a radial edge 234 constituting the bottom of the variable volume chamber 240 at one end on the rear side, and an outer diameter side end of the radial edge 234 fitted in a groove 232 provided on the inner diameter surface.
  • the main part is composed of the cylindrical outer body 231.
  • the movable body 220 is disposed on the piston 222 that is externally fitted to the guide tube 233 via the piston support tube 221 and a front end of the piston 222, and is a rotary member of a clutch device (not shown) (hereinafter referred to as a diaphragm spring). And a clutch release bearing 210 having a contact portion with the main component.
  • the piston 222 protrudes from the base end of the outer cylindrical portion 222a to the outer diameter side, the outer cylindrical portion 222a and the inner cylindrical portion 222b extending in the axial direction, the annular portion 222c connecting the two cylindrical portions at one end on the front side. And a protrusion 222d.
  • the inner cylindrical portion 222b is inserted into the inner periphery of the outer body 231 to form a variable volume chamber 240 with the fixed body 230, and the protrusion 222d is disposed on the outer periphery of the outer cylindrical portion 222a. It plays a role of locking one end on the front side of the preload spring 224.
  • One end on the front side of the piston support tube 221 extends slightly beyond the annular portion 222c of the piston 222, and a centering ring (disc spring) 223 is fitted into an annular groove 221a formed on the outer diameter surface of the extended portion. Is done.
  • the aligning ring 223 has a spring force for elastically supporting the clutch release bearing 210 (the inner ring 211 thereof) in cooperation with the annular portion 222c of the piston 222. Alignment is allowed by being pressed toward the piston 222 by the spring force of the ring 223.
  • the clutch release bearing 210 of the illustrated example is a so-called angular ball bearing, and as shown in an enlarged view in FIG. 8, an inner ring 211 and an outer ring 212 provided so as to be relatively rotatable via a plurality of rolling elements (balls) 213.
  • a cage 214 which is incorporated between the two wheels and holds the balls 213 at predetermined intervals in the circumferential direction, and first and second openings respectively disposed in the rear side and front side openings of the annular space formed between the two wheels.
  • Seal members 215 and 216 and a cover member 219 fixed to one end on the rear side of the inner ring 211 are provided.
  • the clutch release bearing 210 is an outer ring rotation type bearing in which the inner ring 211 is stationary and the outer ring 212 is rotating.
  • the inner ring 211 is, for example, a press-formed product of a steel plate, has a substantially cylindrical shape extending in the axial direction, a cylindrical portion 211a in which a rolling surface 211a1 of the ball 213 is formed on the outer diameter surface, and a front surface of the cylindrical portion 211a.
  • a flange portion 211b that extends radially inward from one end of the side and has a tip portion interposed between the annular portion 222c of the piston 222 and the aligning ring 223 is integrally provided.
  • the rear side end surface of the flange portion 211b is formed in a flat surface in a direction perpendicular to the axis line, corresponding to the end surface shape of the annular portion 222c of the piston 222 with which the flange portion 211b abuts.
  • the outer ring 212 is a press-formed product of a steel plate like the inner ring 211, has a substantially cylindrical shape extending in the axial direction, and a cylindrical portion 212a in which a rolling surface 212a1 of the ball 213 is formed on the inner diameter surface, and the cylindrical portion 212a.
  • a flange portion 212b that extends from one end of the front side to the inner diameter side and serves as a contact portion with a diaphragm spring (not shown) is integrally provided.
  • the region where the seal members 215 and 216 are fixed is formed on the cylindrical surface 212a2 parallel to the axis.
  • the flange portion 212b is always in contact with the diaphragm spring by a preload spring 224 that acts between the outer body 231 and the flange portion 222d of the piston 222, and its cross-sectional shape is in line contact with the diaphragm spring (point contact in the cross-sectional view). ), A convex arc shape protruding to the front side.
  • a carburized steel plate can be used as the steel plate for forming the inner ring 211 and the outer ring 212.
  • the carburized steel that can be used include nickel chrome steel (SNC), nickel chrome molybdenum steel (SNCM), chrome steel (SCr), and chrome molybdenum steel (SCM).
  • SNC nickel chrome steel
  • SNCM nickel chrome molybdenum steel
  • SCr chrome steel
  • SCM chrome molybdenum steel
  • one or both of the inner ring 211 and the outer ring 212 can be a press-formed product of a steel plate as described above, a forged product, or a machined product such as cutting.
  • the second seal member 216 includes a core bar 217 having a substantially L-shaped cross section and a rubber cover 218 that is vulcanized and bonded so as to cover the surface of the core bar 217, and the rear side is opened as a whole. It has a substantially U-shaped cross section.
  • the outer diameter end portion 216a is press-fitted and fixed to the cylindrical surface 212a2 of the outer ring 212 (strictly speaking, the front cylindrical surface 212a2), and in this state, the inner diameter end portion 216b (lip) has the entire circumference. It contacts the outer diameter surface of the inner ring 211 over the entire area.
  • a seal portion S10 made of a so-called contact seal is formed, and the front side opening of the annular space formed between the two wheels 211 and 212 is sealed.
  • the first seal member 215 is composed of a core metal 217 having a substantially L-shaped cross section, and a rubber covering portion 218 vulcanized and bonded to cover the surface of the core metal 217. As a whole, it has a substantially U-shaped cross section with the front side opened.
  • the outer diameter end 215a is press-fitted and fixed to the cylindrical surface 212a2 of the outer ring 212 (strictly speaking, the rear cylindrical surface 212a2), and in this state, the inner diameter end 215b (lip) has the entire circumference.
  • a seal portion S10 made of a so-called contact seal is formed.
  • nitrile rubber NBR
  • H-NBR hydrogenated nitrile rubber
  • EPDM ethylene propylene rubber
  • FKM fluorine rubber
  • the cover material 219 has a substantially disk shape extending in the radial direction as a whole, and is fixed to the rear side end of the inner ring 211 by fitting an inner diameter end portion 219b bent to the front side to the inner diameter surface of the inner ring 211.
  • the cover member 219 has an annular portion 219a facing the rear side end face of the first seal member 215 via a predetermined axial gap, and a predetermined area on the outer diameter side of the annular portion 219a on the front side. And a raised portion 219c formed by raising a predetermined amount.
  • the raised portion 219c is closer to the first seal member 215 than the annular portion 219a, and the labyrinth seal S2 whose front side end surface extends linearly in the radial direction between the front side end surface and the rear side end surface of the first seal member 215.
  • the cover material 219 is a press-formed product obtained by press-forming a thin steel plate material from at least each part of the inner ring 211.
  • the cover material 219 can be formed of a thin steel plate because the first seal member 215 is formed from the rear side opening of the annular space in accordance with an increase in internal pressure during bearing operation. This is because it is sufficient if the strength is sufficient to prevent removal, and the strength required for the inner ring 211 (the cylindrical portion 211a and the flange portion 211b) is not necessary.
  • an adhesive may be interposed between the inner diameter end 219b of the cover member 219 and the inner ring 211.
  • the two wheels 211 and 212 are composed of a seal portion S10 formed by the cooperation of the first seal member 215 and the inner ring 211, and a labyrinth seal S2 formed by the cooperation of the cover member 219 and the first seal member 215. The rear side opening of the annular space formed therebetween is sealed (sealed).
  • a labyrinth seal S2 that is a non-contact seal is additionally provided on the outer side of the bearing. Therefore, it is possible to improve the sealing performance at the rear side opening portion of both the opening portions of the annular space formed between the two wheels 211 and 212 without increasing the bearing torque.
  • the member on one side forming the labyrinth seal S2 is formed of a steel plate material that is thinner than the inner ring 211.
  • Such a thin steel plate has a high degree of freedom in shape and is lightweight. Therefore, it is possible to easily form the labyrinth seal S2 while reducing the weight of the clutch release bearing 210. From the above, according to the present invention, it is possible to simply provide the clutch release bearing 210 that has higher sealing performance while being light weight and low torque.
  • the raised portion 219c is provided in the cover material 219, and the labyrinth seal that extends linearly in the radial direction between the end surface of the raised portion 219c and the end surface of the first seal member 215 opposite to the raised portion 219c.
  • S2 is formed, the means for forming the labyrinth seal S2 of this aspect is not limited to this.
  • the covering portion 218 constituting the first seal member 215 is provided with a protruding portion that protrudes more to the rear side than the other portion, and the gap between the end surface of the protruding portion and the end surface of the cover material 219 opposite to this (
  • the covering portion 218 of the first seal member 215 is vulcanized and bonded, and the form of the covering portion 218 can be easily changed simply by changing the shape of the molding die. Therefore, this type of labyrinth seal S2 can be easily formed without causing a particular increase in cost.
  • FIG. 9 shows a second embodiment of the clutch release bearing 210 to which the third configuration of the present invention is applied.
  • the main difference of the clutch release bearing 210 shown in FIG. 8 from that shown in FIG. 8 is that the annular protrusions 219d and 219d are provided at two locations separated in the radial direction of the cover member 219 and the first seal member 215 is formed.
  • An annular protrusion 215c is provided on the covering portion 218 so as to have a radial position different from the annular protrusion 219d provided on the cover material 219 (strictly, between the annular protrusions 219d and 219d).
  • the annular protrusions 215c and 219d form a labyrinth seal S2 extending in a meandering manner in the radial direction.
  • the overall length of the labyrinth seal S2 can be increased as compared with the first embodiment in which the labyrinth seal S2 extending linearly in the radial direction is formed, so that the sealing performance can be further improved. Since the covering portion 218 constituting the first seal member 215 is vulcanized and bonded (molded) to the surface of the cored bar 217, a special increase in cost due to the formation of the annular protrusion 215c on the covering portion 218 is Does not occur.
  • FIGS. 10 to 12 show third to fifth embodiments of the clutch release bearing 210 to which the third configuration of the present invention is applied, respectively, and are modifications of the clutch release bearing 210 shown in FIG.
  • the main difference between the embodiment shown in FIG. 10 and that shown in FIG. 9 is that the annular protrusion 219d provided on the outer side in the radial direction is omitted from the two annular protrusions 219d provided on the cover member 219 shown in FIG. It is in the point. 11 is different from that shown in FIG. 9 in that the cover member 219 is provided with one annular projection 219d and the annular projection 219d is sandwiched between the first seal member 215 and the first seal member 215.
  • the portion 218 is provided with two annular protrusions 215c and 215c. 12 is different from the embodiment shown in FIG. 9 in that the annular projection 219d provided on the radially inner side of the two annular projections 219d and 219d provided on the cover member 219 shown in FIG. It is in the point that is omitted.
  • the present invention is applied to the clutch release bearing 210 in which the inner ring 211 is the stationary side and the outer ring 212 is the rotating side has been described.
  • the inner ring 211 is the rotating side and the outer ring.
  • the configuration of the present invention to the clutch release bearing 210 having 212 as a stationary side.
  • the abutting portion with the diaphragm spring is a flange provided to extend radially outward at one end on the front side of the inner ring 211 (not shown).
  • the collar provided at the front end of the outer ring 212 is not necessary.
  • a serpentine labyrinth seal S2 in which concave arcs and convex arcs are alternately formed is formed. It is also possible to form a labyrinth seal S2 meandering in a rectangular wave shape. Such a configuration can be easily obtained, for example, by forming the annular protrusions 219d and 215c provided on the cover member 219 and the first seal member 215 in a rectangular cross section (not shown).
  • each embodiment mentioned above is an illustration to the last, and the position of the annular protrusions 219d and 215c provided on the cover material 219 and the first seal member 215, the number, the cross-sectional shape, etc. are appropriately changed according to the required sealing performance and the like. Is possible.
  • the cover material 219 is formed of a thin steel plate material
  • the material for forming the cover material 219 is not particularly limited, and can be formed of a resin material or ceramics.
  • the clutch release bearing can be further reduced in weight.
  • the third configuration of the present invention described above can be applied to the clutch release bearing 10 shown in FIG. 2 and the clutch release bearing 110 shown in FIG. That is, in the clutch release bearing shown in FIGS. 2 and 5, a labyrinth seal can be formed between the rear side end face of the first seal member and the inner ring collar portion facing the rear end face.
  • the flange provided on the rear side of the inner ring has a separate structure as shown in FIG. 8, that is, the rear side flange of the inner ring is omitted, as shown in FIG.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

L'invention concerne une butée de débrayage dans laquelle, sans reproduire la forme d'un complexe de bagues externes, on empêche autant que possible un élément d'étanchéité de sortir d'une ouverture entre les deux bagues. La butée de débrayage (10) possède comme éléments structurels principaux les bagues interne et externe (11, 12) et des premier et second éléments d'étanchéité (15, 16). Les bagues interne et externe (11, 12) sont disposées de façon à pouvoir tourner l'une par rapport à l'autre, des billes (13) étant retenues entre les bagues interne et externe. Les premier et second éléments d'étanchéité (15, 16) possèdent des extrémités de diamètre externe adaptées par pression et fixées à une surface de diamètre interne (12a1) de la bague externe (12) et scellent le côté arrière et le côté frontal, respectivement, d'un espace annulaire formé entre les bagues interne et externe (11, 12). Un élément de retenue (19) destiné à restreindre le déplacement axial vers l'extérieur d'une extrémité de diamètre externe (15a) du premier élément d'étanchéité (15) est adapté sur la surface de diamètre externe (12a2) de la bague externe (12).
PCT/JP2008/071715 2007-12-28 2008-11-28 Butée de débrayage et ensemble de palier de débrayage doté de celle-ci Ceased WO2009084355A1 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
JP2007338631A JP2009156451A (ja) 2007-12-28 2007-12-28 クラッチレリーズ軸受およびこれを備えるクラッチレリーズ軸受装置
JP2007-338631 2007-12-28
JP2008010629A JP2009174552A (ja) 2008-01-21 2008-01-21 クラッチレリーズ軸受およびこれを備えるクラッチレリーズ軸受装置
JP2008-010629 2008-01-21
JP2008017582A JP2009180244A (ja) 2008-01-29 2008-01-29 クラッチレリーズ軸受およびこれを備えるクラッチレリーズ軸受装置
JP2008-017582 2008-01-29

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WO2009084355A1 true WO2009084355A1 (fr) 2009-07-09

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2955367A1 (fr) * 2010-01-20 2011-07-22 Snr Roulements Sa Butee d'embrayage de vehicule automobile equipee d'un dispositif d'etancheite
EP2980432A4 (fr) * 2013-03-27 2016-11-02 Ntn Toyo Bearing Co Ltd Dispositif de roulement de roue
CN111981056A (zh) * 2019-05-24 2020-11-24 斯凯孚公司 密封的离合器推力轴承装置及包括这样的装置的传动系统

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4514963Y1 (fr) * 1965-12-10 1970-06-24
JPS59197624A (ja) * 1983-04-15 1984-11-09 ヴァレオ 自動車用クラッチスラスト軸受の組立て方法
JP2004176782A (ja) * 2002-11-26 2004-06-24 Nsk Ltd シール及びクラッチレリーズ軸受装置
JP2006009932A (ja) * 2004-06-25 2006-01-12 Koyo Seiko Co Ltd クラッチレリーズ軸受
JP2006189086A (ja) * 2005-01-06 2006-07-20 Ntn Corp クラッチレリーズ軸受

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4514963Y1 (fr) * 1965-12-10 1970-06-24
JPS59197624A (ja) * 1983-04-15 1984-11-09 ヴァレオ 自動車用クラッチスラスト軸受の組立て方法
JP2004176782A (ja) * 2002-11-26 2004-06-24 Nsk Ltd シール及びクラッチレリーズ軸受装置
JP2006009932A (ja) * 2004-06-25 2006-01-12 Koyo Seiko Co Ltd クラッチレリーズ軸受
JP2006189086A (ja) * 2005-01-06 2006-07-20 Ntn Corp クラッチレリーズ軸受

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2955367A1 (fr) * 2010-01-20 2011-07-22 Snr Roulements Sa Butee d'embrayage de vehicule automobile equipee d'un dispositif d'etancheite
WO2011089335A1 (fr) * 2010-01-20 2011-07-28 Ntn-Snr Roulements Butee d'embrayage de vehicule automobile equipee d'un dispositif d'etancheite
CN102792044A (zh) * 2010-01-20 2012-11-21 Ntn-Snr轴承股份有限公司 配有密封装置的机动车的离合器分离轴承
CN102792044B (zh) * 2010-01-20 2015-05-13 Ntn-Snr轴承股份有限公司 配有密封装置的机动车的离合器分离轴承
EP2980432A4 (fr) * 2013-03-27 2016-11-02 Ntn Toyo Bearing Co Ltd Dispositif de roulement de roue
US10081218B2 (en) 2013-03-27 2018-09-25 Ntn Corporation Wheel bearing apparatus
CN111981056A (zh) * 2019-05-24 2020-11-24 斯凯孚公司 密封的离合器推力轴承装置及包括这样的装置的传动系统
CN111981056B (zh) * 2019-05-24 2024-10-29 斯凯孚公司 密封的离合器推力轴承装置及包括这样的装置的传动系统

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