WO2012014069A1 - Roller bearing with seal integral with cage and camshaft apparatus having such a roller bearing - Google Patents

Roller bearing with seal integral with cage and camshaft apparatus having such a roller bearing Download PDF

Info

Publication number
WO2012014069A1
WO2012014069A1 PCT/IB2011/001975 IB2011001975W WO2012014069A1 WO 2012014069 A1 WO2012014069 A1 WO 2012014069A1 IB 2011001975 W IB2011001975 W IB 2011001975W WO 2012014069 A1 WO2012014069 A1 WO 2012014069A1
Authority
WO
WIPO (PCT)
Prior art keywords
cage
annular
roller bearing
oil
sealing body
Prior art date
Application number
PCT/IB2011/001975
Other languages
French (fr)
Inventor
Yoshitaka Waseda
Kenichi Nakaoka
Motoichi Murakami
Kenichi Harada
Original Assignee
Toyota Jidosha Kabushiki Kaisha
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Toyota Jidosha Kabushiki Kaisha filed Critical Toyota Jidosha Kabushiki Kaisha
Publication of WO2012014069A1 publication Critical patent/WO2012014069A1/en

Links

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
    • 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
    • F16C33/7893—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a cage or integral therewith
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L1/053—Camshafts overhead type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • 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
    • F16C19/44—Needle bearings
    • F16C19/46—Needle bearings with one row or needles
    • 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
    • F16C33/46—Cages for rollers or needles
    • F16C33/4605—Details of interaction of cage and race, e.g. retention or centring
    • 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
    • F16C33/46—Cages for rollers or needles
    • F16C33/4617—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages
    • F16C33/4623—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages
    • F16C33/4635—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages made from plastic, e.g. injection moulded window cages
    • 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
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
    • F16C33/6674—Details of supply of the liquid to the bearing, e.g. passages or nozzles related to the amount supplied, e.g. gaps to restrict flow of the liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L2001/0476—Camshaft bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2301/00—Using particular materials
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2810/00—Arrangements solving specific problems in relation with valve gears
    • F01L2810/02—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/18—Camshafts

Definitions

  • This invention relates to a roller bearing and a camshaft apparatus in which the roller bearing is used.
  • roller bearings are available to be used in the journal portions of camshafts instead of sliding bearings arranged between a cylinder head and cap member (see, for example, Japanese Patent Application Publication No. 2006-250268 (JP-A-2006-250268)). Namely, torque loss during rotation of the camshaft is reduced by using a roller bearing in the camshaft journal portion.
  • an oil hole continuous with a hydraulic pressure source is formed in the cap member to supply oil to the variable valve timing mechanism, and an oil path that guides the oil supplied through the oil hole to the variable valve timing mechanism is formed in the shaft.
  • bearing housings 504 and 508 be formed in a cap member 505 and a cylinder head 502 respectively so as not to interfere with an oil hole 507 of the cap member 505, and that a roller bearing 540, provided with inner and outer rings 550 and 560, a roller 570 and a cage 580, be arranged in the bearing housings 504 and 508.
  • the invention provides a roller bearing capable of inhibiting excessive inflow of oil into the roller bearing without increasing the number of components or the number of assembly steps, and a camshaft apparatus in which this roller bearing is used.
  • a first aspect of this invention relates to a roller bearing provided with an inner ring, an outer ring, a plurality of rollers rollably arranged in an annular space between the inner ring and the outer ring, and a cage that holds the rollers.
  • the cage is integrally provided with first and second annular portions separated from each other by a prescribed interval in an axial direction, and a plurality of post portions that connect the first and second annular portions and that demarcate pockets for holding the plurality of rollers, and the first annular portion of the cage is integrally formed with an annular sealing body that approachably and separatably opposes the inner and outer rings by extending across end surfaces thereof on one side and seals one end of the annular space by approaching or contacting the end surfaces of the inner and outer rings on the one side due to hydraulic pressure.
  • the cage may also be formed of a synthetic resin material.
  • First and second end cylindrical portions that protrude in the axial direction may be respectively formed on an inner peripheral portion of the end surface of the inner ring on the one side and an outer peripheral portion of the end surface of the outer ring on the one side, and minute gaps may be formed respectively between the inner peripheral surface of the sealing body and the end cylindrical portion of the inner ring, and between the outer peripheral surface of the sealing body and the end cylindrical portion of the outer ring.
  • An inner annular protrusion and an outer annular protrusion capable of respectively contacting the end surfaces of the inner and outer rings on the one side may be formed in the sealing body.
  • a locking piece that restricts movement of the cage in the axial direction by engaging with at least one of end surfaces of the inner and outer rings on the one side may be formed on the second annular porti6n of the cage.
  • a second aspect of this invention relates to a camshaft apparatus in which the above-mentioned roller bearing is arranged in bearing housings respectively formed in a cylinder head and a cap member in a journal portion of camshaft in which cams are arranged on an axis of a shaft.
  • a variable valve timing mechanism is provided in one end of the shaft, an oil hole continuous with a hydraulic pressure source is formed in the cap member to supply oil to the variable valve timing mechanism, an oil path that guides oil supplied through the oil hole to the variable valve timing mechanism is formed in the shaft, and a sealing body of a cage approaches or contacts end surfaces of inner and outer rings on the one side due to hydraulic pressure generated when oil is supplied to the variable valve timing mechanism through the oil hole and the oil path, to thereby seal one end of an annular space between the inner and outer rings.
  • FIG. 1 is a longitudinal cross-sectional view showing a camshaft apparatus in which a roller bearing according to a first embodiment of the invention is used;
  • FIGS. 2A and 2B are enlarged longitudinal cross-sectional views showing a first journal portion of the camshaft apparatus
  • FIG. 3 is a perspective view showing a cage of the roller bearing
  • FIG. 4 is a perspective view showing the arrengment of a roller and a cage in an annular space between inner and outer rings;
  • FIG. 5 is a longitudinal cross-sectional view showing an embodiment in which a locking piece is formed in either the inner or outer diameter of a second annular portion of a cage;
  • FIG. 6 is a longitudinal cross-sectional view showing an embodiment in which an annular protrusion is not formed in a sealing body of a cage;
  • FIG. 7 is a longitudinal cross-sectional view showing an embodiment in which a locking piece is not formed on a second annular portion of a cage.
  • FIG. 8 is a longitudinal cross-sectional view showing a camshaft apparatus of a comparative example.
  • a camshaft 1 1 having a plurality of cams 13 on the axis of a shaft 12 is rotatably supported by a cam journal (first journal portion 10 as well as other journals) composed between a cylinder head 2 and a cap member 5.
  • a circular indentation 3 is formed in a portion of the cylinder head 2 corresponding to each portion of the first journal portion 10 and the other journals, and the cap member 5, having circular indentations 6 corresponding to the circular indentations 3, is fastened to the cylinder head 2 with bolts and the like.
  • an oil hole 7 that is continuous with a hydraulic pressure source (pump) is formed in the cap member 5 corresponding to the first journal portion 10.
  • an oil channel 20, which guides oil supplied through the oil hole 7 to a variable valve timing mechanism 31, is formed in the shaft 12.
  • This oil path 20 has a vertical hole 21 formed in the radial direction of the shaft 12 and a horizontal hole 22 formed in the axial direction.
  • a knock pin 14 is driven into one end surface of the shaft 12, and a timing gear 33 and the variable valve timing mechanism 31 (indicating an example of provided components) are provided in one end of the shaft 12 while positioned by the knock pin 14.
  • the end of the horizontal hole 22 of the oil path 20 on the shaft 12 is continuous with and connected to the variable valve timing mechanism 31.
  • first journal portion 10 semicircular bearing housings 4 and 8 are respectively formed in the cap member 5 and the cylinder head 2 so that there is no interference with the oil hole 7 of the cap member 5.
  • a roller bearing (a needle roller bearing is shown in the drawings) 40 provided in the bearing housings 4 and 8 of the first journal portion 10 is provided with an inner ring 50, an outer ring 60, a plurality of rollers (needle rollers) 70 rollably arranged in an annular space between the inner and outer rings 50 and 60, and a cage 80 that holds the plurality of rollers 70.
  • the inner ring 50 is formed into a cylindrical shape and that is fixed by being press fit onto the outer peripheral surface of the shaft 12, and an inner ring raceway surface 51 that opposes the plurality of rollers 70 is formed in the outer peripheral surface thereof.
  • the outer ring 60 is fixed by being fit onto the bearing housings 4 and 8 on the outer peripheral surfaces thereof, and an outer ring raceway surface 61 is formed on the inner peripheral surface of the outer ring 60, on the other side of the annular space from the inner ring raceway surface 51 of the inner ring 50.
  • the plurality of rollers 70 held by the cage 80 are rollably provided between the inner ring raceway surface 51 and the outer ring raceway surface 61.
  • the cage 80 is integrally provided with first and second annular portions 81 and 82 separated from each other by a prescribed interval in the axial direction, and a plurality of post portions 84 that connect the first and second annular portions 81 and 82 and that demarcate pockets 83 for holding the plurality of rollers 70.
  • An annular sealing body 90 is integrally formed in the first annular portion 81 of the cage 80. The sealing body 90 extends across end surfaces of the inner and outer rings 50 and 60 on one side, and approachably and separatably opposes the inner and outer rings 50 and 60. In addition, the sealing body 90 seals one end of the annular space between the inner and outer rings 50 and 60 by approaching or contacting the end surfaces of the inner and outer rings 50 and 60 on the one side due to the hydraulic pressure.
  • end cylindrical portions 53 and 56 are respectively formed along the inner peripheral portions of both end surfaces of the inner ring 50
  • end cylindrical portions 63 and 66 are respectively formed along the outer peripheral portions of both end surfaces of the outer ring 60 as well.
  • Minute gaps S that compose labyrinths are set between the end cylindrical portion 53 of one end of the inner ring 50 (right side when viewed facing FIG. 2A) and the inner peripheral surface of the sealing body 90, and between the end cylindrical portion 63 of one end of the outer ring 60 and the outer peripheral surface of the sealing body 90.
  • an inner annular protrusion 91 and an outer annular protrusion 92 are respectively formed on the sealing surface of the sealing body 90 (surface opposing the end surfaces of the inner and outer rings 50 and 60 on the one side).
  • Each of the inner annular protrusion 91 and the outer annular protrusion 92 has an arc-shaped cross-section.
  • the inner annular protrusion 91 and the outer, annular, protrusion.92 make linear .contact with end aurfaces.of the inner and outer rings 50 and 60 on the one side.
  • an inner diameter locking piece 95 and an outer diameter locking piece 96 are formed on the inner peripheral surface and outer peripheral surface of the second annular portion 82 of the cage 80.
  • the inner diameter locking piece 95 and the outer diameter locking piece 96 restrict movement of the cage 80 in the axial direction by respectively engaging with the end surfaces of the inner and outer rings 50 and 60 on the other side.
  • the outer diameter locking piece 96 is not attached to the second annular portion 82 on the side where the inner diameter locking piece 95 is attached. Draining of oil is facilitated as a result of configuring in this manner.
  • the inner diameter locking piece 95 and the outer diameter locking piece 96 are elastically deformed and inserted. As indicated by the double-dashed dotted line in FIG. 4, when inserted to a prescribed position, the inner diameter locking piece 95 and the outer diameter locking piece 96 elastically return to their original shapes, and as a result thereof, respectively engage with the end surfaces of the inner and outer rings 50 and 60 on the other side.
  • oil supplied from a hydraulic pressure source flows through the oil path 20 of the shaft 12 by passing through the oil hole 7 of the cap member 5 of the first journal portion 10. Relative rotation of the timing gear 33 and the shaft 12 is then controlled (by lead angle control or delay angle control) by oil supplied to the variable valve timing mechanism 31 from the oil path 20.
  • the inner annular protrusion 91 and the outer annular protrusion 92 may also have a semicircular cross-section.
  • this invention is not limited to the first embodiment, but rather can be worked in various forms within a scope that does not deviate from the gist of the invention.
  • the first embodiment indicated an example of the case of the roller bearing 40 being provided in the first journal unit 10 of the camshaft apparatus
  • the roller bearing 40 of the embodiment can also be used in a power transmission apparatus other than a camshaft apparatus.
  • movement of the cage 80 in the axial direction can also be restricted in the case in which the inner diameter locking piece 95 (or outer diameter locking piece 96) is formed only on the inner peripheral surface (or outer peripheral surface) of the second annular portion 82 of the cage 80.
  • FIG. 1 shows an example of the case of the roller bearing 40 being provided in the first journal unit 10 of the camshaft apparatus
  • the roller bearing 40 of the embodiment can also be used in a power transmission apparatus other than a camshaft apparatus.
  • movement of the cage 80 in the axial direction can also be restricted in the case in which the inner diameter locking piece 95 (or outer diameter locking piece 96) is formed
  • a configuration may also be employed in which the sealing surface of the sealing body 90 seals by respectively making surface contact with end surfaces of the inner and outer rings 50 and 60 on the one side.
  • a configuration may be employed in which the sealing surface of the sealing body 90 seals by respectively making surface contact with the end surfaces of the inner and outer rings 50 and 60 on the one side, but locking pieces are not formed on the second annular portion 82 of the cage 80. In this case, end cylindrical portions on both ends of the inner ring 50 and end cylindrical portions on both ends of the outer ring 60 are not required.

Abstract

A roller bearing includes an inner ring (50), an outer ring (60), a plurality of rollers (70) and a cage (80). The cage (80) is formed of a synthetic resin material, and is integrally provided with first and second annular portions (81, 82) separated from each other by a prescribed interval in the axial direction, and a plurality of post portions (84) that connect the first and second annular portions (81, 82) and that demarcate pockets (83) for holding the plurality of rollers (70). The first annular portion (81) of the cage (80) is integrally formed with an annular sealing body (90) that approachably and separatably opposes the inner and outer rings (50, 60) by extending across end surfaces thereof on one side and seals one end of an annular space by approaching or contacting the end surfaces of the inner and outer rings (50, 60) on the one side due to hydraulic pressure.

Description

ROLLER BEARING WITH SEAL INTEGRAL WITH CAGE AND CAMSHAFT APPARATUS HAVING SUCH A ROLLER BEARING
BACKGROUND OF THE INVENTION 1. Field of the Invention
[0001] This invention relates to a roller bearing and a camshaft apparatus in which the roller bearing is used.
2. Description of Related Art
[0002] Roller bearings are available to be used in the journal portions of camshafts instead of sliding bearings arranged between a cylinder head and cap member (see, for example, Japanese Patent Application Publication No. 2006-250268 (JP-A-2006-250268)). Namely, torque loss during rotation of the camshaft is reduced by using a roller bearing in the camshaft journal portion. In addition, in the case of providing a variable valve timing mechanism in one end of the camshaft, an oil hole continuous with a hydraulic pressure source is formed in the cap member to supply oil to the variable valve timing mechanism, and an oil path that guides the oil supplied through the oil hole to the variable valve timing mechanism is formed in the shaft. In a camshaft apparatus having a structure as described above, it has been proposed that, as shown in FIG. 8, bearing housings 504 and 508 be formed in a cap member 505 and a cylinder head 502 respectively so as not to interfere with an oil hole 507 of the cap member 505, and that a roller bearing 540, provided with inner and outer rings 550 and 560, a roller 570 and a cage 580, be arranged in the bearing housings 504 and 508.
[0003] However, in the camshaft apparatus shown in FIG. 8, when oil supplied from a hydraulic pressure source is supplied to a variable valve timing mechanism 531 through the oil hole 507 in the cap member 505 and an oil path 520 of a shaft 512, a portion of the oil discharged from the discharge port of the oil hole 507 in the cap member 505 towards the entrance of the oil path 520 of the shaft 512 is likely to flow excessively towards the inside of the roller bearing 540. In this case, viscous resistance increases due to excess oil within the roller bearing 540 resulting in torque loss. Therefore, although it has been considered to inhibit excessive inflow of oil into the roller bearing 540 by providing a dedicated sealing member in one end of the annular space between the inner ring 550 and the outer ring 560 of the roller bearing 540, in this case, the number of components and the number of assembly steps are increased by the presence of the sealing member, thereby resulting in increased costs.
SUMMARY OF THE INVENTION
[0004] The invention provides a roller bearing capable of inhibiting excessive inflow of oil into the roller bearing without increasing the number of components or the number of assembly steps, and a camshaft apparatus in which this roller bearing is used.
[0005] A first aspect of this invention relates to a roller bearing provided with an inner ring, an outer ring, a plurality of rollers rollably arranged in an annular space between the inner ring and the outer ring, and a cage that holds the rollers. The cage is integrally provided with first and second annular portions separated from each other by a prescribed interval in an axial direction, and a plurality of post portions that connect the first and second annular portions and that demarcate pockets for holding the plurality of rollers, and the first annular portion of the cage is integrally formed with an annular sealing body that approachably and separatably opposes the inner and outer rings by extending across end surfaces thereof on one side and seals one end of the annular space by approaching or contacting the end surfaces of the inner and outer rings on the one side due to hydraulic pressure. The cage may also be formed of a synthetic resin material.
[0006] According to the above-mentioned configuration, when hydraulic pressure acts on the sealing body of the cage, the sealing body approaches or contacts end surfaces of the inner and outer rings on the one side due to that hydraulic pressure, and as a result thereof one end of the annular space between the inner and outer rings can be sealed. As a result, excessive inflow of oil into the roller bearing (into the annular space between the inner and outer rings) can be inhibited. In addition, since the sealing body is integrally formed in the first annular portion of the cage, the number of components and number of assembly steps can be decreased in comparison with the case of fabricating and providing a dedicated sealing member separate, from the cage, thereby making it possible to reduce costs.
[0007] First and second end cylindrical portions that protrude in the axial direction may be respectively formed on an inner peripheral portion of the end surface of the inner ring on the one side and an outer peripheral portion of the end surface of the outer ring on the one side, and minute gaps may be formed respectively between the inner peripheral surface of the sealing body and the end cylindrical portion of the inner ring, and between the outer peripheral surface of the sealing body and the end cylindrical portion of the outer ring.
[0008] According to the above-mentioned configuration, as a result of composing labyrinths (non-contact sealing portions) with minute gaps between the inner peripheral surface of the sealing body and the end cylindrical portion of the inner ring, and between the outer peripheral surface of the sealing body and the end cylindrical portion of the outer ring, excessive inflow of oil into the roller bearing can be more effectively inhibited.
[0009] An inner annular protrusion and an outer annular protrusion capable of respectively contacting the end surfaces of the inner and outer rings on the one side may be formed in the sealing body.
[0010] According to the above-mentioned configuration, as a result of the inner annular protrusion and outer annular protrusion of the sealing body respectively contacting the end surfaces of the inner and outer rings on the other side, sliding frictional force during bearing rotation can be reduced in comparison with the case of the one side of the sealing body respectively making surface contact with the end surfaces of the inner and outer rings on the other side.
[0011] A locking piece that restricts movement of the cage in the axial direction by engaging with at least one of end surfaces of the inner and outer rings on the one side may be formed on the second annular porti6n of the cage. [0012] According to the above-mentioned configuration, as a result of the locking piece formed on the second annular portion of the cage engaging with at least one of the end surfaces of the inner and outer rings on the other side, movement of the cage in the axial direction can be restricted. Consequently, the problem of the rollers inadvertently moving in the axial direction together with the cage and coming out of the inner and outer rings during, for example, storage, transport or assembly of the roller bearing can be prevented.
[0013] A second aspect of this invention relates to a camshaft apparatus in which the above-mentioned roller bearing is arranged in bearing housings respectively formed in a cylinder head and a cap member in a journal portion of camshaft in which cams are arranged on an axis of a shaft. A variable valve timing mechanism is provided in one end of the shaft, an oil hole continuous with a hydraulic pressure source is formed in the cap member to supply oil to the variable valve timing mechanism, an oil path that guides oil supplied through the oil hole to the variable valve timing mechanism is formed in the shaft, and a sealing body of a cage approaches or contacts end surfaces of inner and outer rings on the one side due to hydraulic pressure generated when oil is supplied to the variable valve timing mechanism through the oil hole and the oil path, to thereby seal one end of an annular space between the inner and outer rings.
[0014] According to the above-mentioned configuration, during operation of the variable valve timing mechanism, oil supplied from the hydraulic pressure source (such as a pump) is supplied to the variable valve timing mechanism through the oil hole of the cap member and the oil path of the shaft (camshaft). At this time, if a portion of the oil discharged from the discharge port of the oil hole of the cap member towards the entrance of the oil path of the shaft flows toward the roller bearing through the minute gap between the cap member and the shaft, the hydraulic pressure of the oil acts on the sealing body of the cage. Whereupon, the sealing body approaches or contacts end surfaces of the inner and outer rings on the one side, and one end of the annular space between the inner and outer rings is sealed. Consequently, excessive inflow of oil into the roller bearing (into the annular space between the inner and outer rings) can be inhibited, which together with reducing torque loss, also prevents a supply shortage of oil to the variable valve timing mechanism.
BRIEF DESCRIPTION OF THE DRAWINGS
[0015] Features, advantages, and technical and industrial significance of exemplary embodiments of the invention will be described below with reference to the accompanying drawings, in which like numerals denote like elements, and wherein:
FIG. 1 is a longitudinal cross-sectional view showing a camshaft apparatus in which a roller bearing according to a first embodiment of the invention is used;
FIGS. 2A and 2B are enlarged longitudinal cross-sectional views showing a first journal portion of the camshaft apparatus;
FIG. 3 is a perspective view showing a cage of the roller bearing;
FIG. 4 is a perspective view showing the arrengment of a roller and a cage in an annular space between inner and outer rings;
FIG. 5 is a longitudinal cross-sectional view showing an embodiment in which a locking piece is formed in either the inner or outer diameter of a second annular portion of a cage;
FIG. 6 is a longitudinal cross-sectional view showing an embodiment in which an annular protrusion is not formed in a sealing body of a cage;
FIG. 7 is a longitudinal cross-sectional view showing an embodiment in which a locking piece is not formed on a second annular portion of a cage; and
FIG. 8 is a longitudinal cross-sectional view showing a camshaft apparatus of a comparative example. DETAILED DESCRIPTION OF EMBODIMENTS
[First Embodiment]
[0016] The following provides an explanation of a first embodiment of this invention in accordance with FIGS. 1 to 4. As shown in FIG. 1, in a camshaft apparatus according to a first embodiment of this invention, a camshaft 1 1 having a plurality of cams 13 on the axis of a shaft 12 is rotatably supported by a cam journal (first journal portion 10 as well as other journals) composed between a cylinder head 2 and a cap member 5. In addition, a circular indentation 3 is formed in a portion of the cylinder head 2 corresponding to each portion of the first journal portion 10 and the other journals, and the cap member 5, having circular indentations 6 corresponding to the circular indentations 3, is fastened to the cylinder head 2 with bolts and the like.
[0017] As shown in FIGS. 1 and 2 A, an oil hole 7 that is continuous with a hydraulic pressure source (pump) is formed in the cap member 5 corresponding to the first journal portion 10. In addition, an oil channel 20, which guides oil supplied through the oil hole 7 to a variable valve timing mechanism 31, is formed in the shaft 12. This oil path 20 has a vertical hole 21 formed in the radial direction of the shaft 12 and a horizontal hole 22 formed in the axial direction.
[0018] In addition, as shown in FIGS. 1 and 2 A, a knock pin 14 is driven into one end surface of the shaft 12, and a timing gear 33 and the variable valve timing mechanism 31 (indicating an example of provided components) are provided in one end of the shaft 12 while positioned by the knock pin 14. The end of the horizontal hole 22 of the oil path 20 on the shaft 12 is continuous with and connected to the variable valve timing mechanism 31.
[0019] In the first journal portion 10, semicircular bearing housings 4 and 8 are respectively formed in the cap member 5 and the cylinder head 2 so that there is no interference with the oil hole 7 of the cap member 5. A roller bearing (a needle roller bearing is shown in the drawings) 40 provided in the bearing housings 4 and 8 of the first journal portion 10 is provided with an inner ring 50, an outer ring 60, a plurality of rollers (needle rollers) 70 rollably arranged in an annular space between the inner and outer rings 50 and 60, and a cage 80 that holds the plurality of rollers 70.
[0020] The inner ring 50 is formed into a cylindrical shape and that is fixed by being press fit onto the outer peripheral surface of the shaft 12, and an inner ring raceway surface 51 that opposes the plurality of rollers 70 is formed in the outer peripheral surface thereof. In addition, the outer ring 60 is fixed by being fit onto the bearing housings 4 and 8 on the outer peripheral surfaces thereof, and an outer ring raceway surface 61 is formed on the inner peripheral surface of the outer ring 60, on the other side of the annular space from the inner ring raceway surface 51 of the inner ring 50. The plurality of rollers 70 held by the cage 80 are rollably provided between the inner ring raceway surface 51 and the outer ring raceway surface 61.
[0021] In addition to being formed of a synthetic resin material having heat resistance and wear resistance, as shown in FIGS. 2A and 3, the cage 80 is integrally provided with first and second annular portions 81 and 82 separated from each other by a prescribed interval in the axial direction, and a plurality of post portions 84 that connect the first and second annular portions 81 and 82 and that demarcate pockets 83 for holding the plurality of rollers 70. An annular sealing body 90 is integrally formed in the first annular portion 81 of the cage 80. The sealing body 90 extends across end surfaces of the inner and outer rings 50 and 60 on one side, and approachably and separatably opposes the inner and outer rings 50 and 60. In addition, the sealing body 90 seals one end of the annular space between the inner and outer rings 50 and 60 by approaching or contacting the end surfaces of the inner and outer rings 50 and 60 on the one side due to the hydraulic pressure.
[0022] In addition, in this first embodiment, as shown in FIG. 2A, end cylindrical portions 53 and 56 are respectively formed along the inner peripheral portions of both end surfaces of the inner ring 50, and end cylindrical portions 63 and 66 are respectively formed along the outer peripheral portions of both end surfaces of the outer ring 60 as well. Minute gaps S that compose labyrinths are set between the end cylindrical portion 53 of one end of the inner ring 50 (right side when viewed facing FIG. 2A) and the inner peripheral surface of the sealing body 90, and between the end cylindrical portion 63 of one end of the outer ring 60 and the outer peripheral surface of the sealing body 90.
[0023] In addition, in this first embodiment, an inner annular protrusion 91 and an outer annular protrusion 92 are respectively formed on the sealing surface of the sealing body 90 (surface opposing the end surfaces of the inner and outer rings 50 and 60 on the one side). Each of the inner annular protrusion 91 and the outer annular protrusion 92 has an arc-shaped cross-section. The inner annular protrusion 91 and the outer, annular, protrusion.92 make linear .contact with end aurfaces.of the inner and outer rings 50 and 60 on the one side.
[0024] In addition, in this first embodiment, an inner diameter locking piece 95 and an outer diameter locking piece 96 are formed on the inner peripheral surface and outer peripheral surface of the second annular portion 82 of the cage 80. The inner diameter locking piece 95 and the outer diameter locking piece 96 restrict movement of the cage 80 in the axial direction by respectively engaging with the end surfaces of the inner and outer rings 50 and 60 on the other side. As shown in FIG. 3, the outer diameter locking piece 96 is not attached to the second annular portion 82 on the side where the inner diameter locking piece 95 is attached. Draining of oil is facilitated as a result of configuring in this manner. In addition, as shown in FIG. 4, when providing the rollers 70 together with the cage 80 by inserting through an opening in one side of the annular space between the inner and outer rings 50 and 60, the inner diameter locking piece 95 and the outer diameter locking piece 96 are elastically deformed and inserted. As indicated by the double-dashed dotted line in FIG. 4, when inserted to a prescribed position, the inner diameter locking piece 95 and the outer diameter locking piece 96 elastically return to their original shapes, and as a result thereof, respectively engage with the end surfaces of the inner and outer rings 50 and 60 on the other side.
[0025] In the camshaft apparatus according to this first embodiment configured in the manner described above, oil supplied from a hydraulic pressure source flows through the oil path 20 of the shaft 12 by passing through the oil hole 7 of the cap member 5 of the first journal portion 10. Relative rotation of the timing gear 33 and the shaft 12 is then controlled (by lead angle control or delay angle control) by oil supplied to the variable valve timing mechanism 31 from the oil path 20.
[0026] At this time, a portion of oil discharged from the discharge port of the oil hole 7 of the cap member 5 towards the entrance of the oil path 20 of the shaft 12 flows toward the roller bearing 40 by passing through the minute gap between the cap member 5 and the shaft 12, and the hydraulic pressure of this oil acts on the sealing body 90 of the cage 80. Whereupon, the inner annular protrusion 91 and the outer annular protrusion92 of the sealing body 90 contact end surfaces of the inner and outer rings 50 and 60 on the one side, and seal one end of the annular space between the inner and outer rings 50 and 60. As a result, excessive inflow of oil into the roller bearing 40 (into the annular space between the inner and outer rings 50 and 60) can be inhibited and torque loss can be reduced. Moreover, as a result of inhibiting excessive inflow of oil into the roller bearing 40, a supply shortage of oil to the variable valve timing mechanism 31 can be prevented. As a result, oil can be adequately supplied to the variable valve timing mechanism 31. In addition, in a state in which the hydraulic pressure acting on the sealing body 90 is low, a small amount of oil flows into the roller bearing 40 by passing between the end surfaces of the outer rings 50 and 60 on the one side and the sealing body 90, thereby acting as lubricating oil of the roller bearing 40.
[0027] In addition, in this first embodiment, excessive inflow of oil into the roller bearing 40 can be more effectively inhibited as a result of configuring labyrinths (non-contact sealing portions) by minute gaps formed respectively between the inner peripheral surface of the sealing body 90 and the end cylindrical portion 53 of the inner ring 50, and between the outer peripheral surface of the sealing body 90 and the end cylindrical portion 63 of the outer ring 60.
[0028] In addition, in this first embodiment, the inner annular protrusion 91 and the outer annular protrusion 92 formed on the sealing surface of the sealing body 90 so as to respectively contact end surfaces of the inner and outer rings 50 and 60 on the one side. Consequently, sliding frictional force during bearing rotation can be reduced in comparison with the case of the sealing surface of the sealing body 90 respectively making surface contact with the end surfaces of the inner and outer rings 50 and 60 on the one side. As shown in FIG. 2B, the inner annular protrusion 91 and the outer annular protrusion 92 may also have a semicircular cross-section. As a result of employing such a configuration, sliding resistance between the outer rings 50 and 60 and the inner annular protrusion 91 and the outer annular protrusion 92 can be reduced even if the sealing body 90 is pressed against the inner and outer rings 50 and 60 by hydraulic pressure.
[0029] In addition, in this first embodiment, .movement of the cage 80 in the axial direction can be restricted as a result of the inner diameter locking piece 95 and the outer diameter locking piece 96 of the second annular portion 82 of the cage 80 respectively engaging with the end surfaces of the inner and outer rings 50 and 60 on the other side. As a result, the problem of the rollers 70 inadvertently moving in the axial direction together with the cage 80 and coming out of the inner and outer rings 50 and 60 during, for example, storage, transport or assembly of the roller bearing 40 can be prevented.
[0030] Furthermore, this invention is not limited to the first embodiment, but rather can be worked in various forms within a scope that does not deviate from the gist of the invention. For example, although the first embodiment indicated an example of the case of the roller bearing 40 being provided in the first journal unit 10 of the camshaft apparatus, the roller bearing 40 of the embodiment can also be used in a power transmission apparatus other than a camshaft apparatus. In addition, as shown in FIG. 5, movement of the cage 80 in the axial direction can also be restricted in the case in which the inner diameter locking piece 95 (or outer diameter locking piece 96) is formed only on the inner peripheral surface (or outer peripheral surface) of the second annular portion 82 of the cage 80. In addition, as shown in FIG. 6, a configuration may also be employed in which the sealing surface of the sealing body 90 seals by respectively making surface contact with end surfaces of the inner and outer rings 50 and 60 on the one side. In addition, as shown in FIG. 7, a configuration may be employed in which the sealing surface of the sealing body 90 seals by respectively making surface contact with the end surfaces of the inner and outer rings 50 and 60 on the one side, but locking pieces are not formed on the second annular portion 82 of the cage 80. In this case, end cylindrical portions on both ends of the inner ring 50 and end cylindrical portions on both ends of the outer ring 60 are not required.

Claims

1. A roller, bearing, comprising: an inner ring; an outer ring; a plurality of rollers rollably arranged in an annular space between the inner ring and the outer ring; and a cage that holds the rollers, wherein
the cage is integrally provided with first and second annular portions separated from each other by a prescribed interval in an axial direction, and a plurality of post portions that connect the first and second annular portions and that demarcate pockets for holding the plurality of rollers, and
the first annular portion of the cage is integrally formed with an annular sealing body that approachably and separatably opposes the inner and outer rings by extending across end surfaces thereof on one side and seals one end of the annular space by approaching or contacting the end surfaces of the inner and outer rings on the one side due to hydraulic pressure.
2. The roller bearing according to claim 1 , wherein
end cylindrical portions protruding in the axial direction are respectively formed on an inner peripheral portion of the end surface of the inner ring on the one side and an outer peripheral portion of the end surface of the outer ring on the one side, and minute gaps are formed respectively between the inner peripheral surface of the sealing body and the first end cylindrical portion of the inner ring, and between the outer peripheral surface of the sealing body and the second end cylindrical portion of the outer ring.
3. The roller bearing according to claim 1 or 2, wherein
an inner annular protrusion and an outer annular protrusion capable of respectively contacting the end surfaces of the inner and outer rings on the one side are formed in the sealing body.
4. The roller bearing according to claim 3, wherein cross-sections of the inner annular protrusion and the outer annular protrusion are semicircular.
5. The roller bearing according to any one of claims 1 to 4, wherein
a locking piece that restricts movement of the cage in the axial direction by engaging with at least one of end surfaces of the inner and outer rings on the other side is formed on the second annular portion of the cage.
6. The roller bearing according to claim 5, wherein
the locking piece includes an inner diameter locking piece and an outer diameter locking piece respectively formed on an inner peripheral surface and an outer peripheral surface of the second annular portion, and
the outer diameter locking piece is not formed on the outer peripheral surface of the second annular portion where the inner diameter locking piece is formed.
7. The roller bearing according to any one of claims 1 to 6, wherein
the cage is formed of a synthetic resin material.
8. A camshaft apparatus, comprising: the roller bearing according to any one of claims 1 to 7 being arranged in bearing housings respectively formed in a cylinder head and a cap member in a journal portion of camshaft in which cams are arranged on an axis of a shaft, wherein
a variable valve timing mechanism is provided in one end of the shaft, an oil hole continuous with a hydraulic pressure source is formed in the cap member to supply oil to the variable valve timing mechanism, and an oil path that guides oil supplied through the oil hole to the variable valve timing mechanism is formed in the shaft, and
a sealing body of a cage approaches or contacts end surfaces of inner and outer rings on the one side due to hydraulic pressure generated when oil is supplied to the variable valve timing mechanism through the oil hole and the oil path, to thereby seal one end of an annular space between the inner and outer rings.
PCT/IB2011/001975 2010-07-26 2011-07-26 Roller bearing with seal integral with cage and camshaft apparatus having such a roller bearing WO2012014069A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2010166894A JP5488296B2 (en) 2010-07-26 2010-07-26 Rolling bearing and camshaft device
JP2010-166894 2010-07-26

Publications (1)

Publication Number Publication Date
WO2012014069A1 true WO2012014069A1 (en) 2012-02-02

Family

ID=44651875

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/IB2011/001975 WO2012014069A1 (en) 2010-07-26 2011-07-26 Roller bearing with seal integral with cage and camshaft apparatus having such a roller bearing

Country Status (2)

Country Link
JP (1) JP5488296B2 (en)
WO (1) WO2012014069A1 (en)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011121597A1 (en) * 2011-12-17 2013-06-20 Neumayer Tekfor Holding Gmbh Mounting for camshaft and camshaft
GB2504100A (en) * 2012-07-17 2014-01-22 Mechadyne Internat Ltd A concentric camshaft supported by roller bearings
WO2014128215A1 (en) * 2013-02-20 2014-08-28 Aktiebolaget Skf Rolling bearing cage with latching means, and needle bearing with an outer ring which is latched onto a cage
US20140284944A1 (en) * 2013-03-25 2014-09-25 Brose Schliesssysteme Gmbh & Co. Kg Motor vehicle lock
CN105829745A (en) * 2013-12-16 2016-08-03 日本精工株式会社 Cage and roller
DE102015218633A1 (en) 2015-09-28 2017-03-30 Aktiebolaget Skf Rolling bearings with bearing cage
CN107002761A (en) * 2014-09-17 2017-08-01 舍弗勒技术股份两合公司 Variable torque bearing
DE102019101257A1 (en) * 2019-01-18 2020-07-23 Bayerische Motoren Werke Aktiengesellschaft Valve train for an internal combustion engine with a variable camshaft control

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013200007A (en) * 2012-03-26 2013-10-03 Ntn Corp Ball bearing
JP6212862B2 (en) * 2012-12-27 2017-10-18 株式会社ジェイテクト Liquid lubricated bearing and vehicle pinion shaft support device
JP5783308B2 (en) * 2014-08-12 2015-09-24 スズキ株式会社 Camshaft support structure
JP5783309B2 (en) * 2014-08-12 2015-09-24 スズキ株式会社 Camshaft support structure
FR3045747B1 (en) * 2015-12-16 2018-02-02 Ntn-Snr Roulements BEARING BEARING

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1913905U (en) * 1965-02-17 1965-04-15 Duerkoppwerke Ag ROLLER BEARINGS, IN PARTICULAR GROOVE BALL BEARINGS.
DE1914884U (en) * 1965-03-03 1965-04-29 Duerkoppwerke Ag ROLLER BEARING WITH PLASTIC CAGE.
US3554621A (en) * 1967-08-23 1971-01-12 Federal Bearings Co Inc Combination cage and seal for antifriction bearings
DE19745410A1 (en) * 1997-10-15 1999-04-22 Schaeffler Waelzlager Ohg Roller bearing with a one-piece plastic cage
JP2006250268A (en) 2005-03-11 2006-09-21 Jtekt Corp Rolling bearing and cam shaft device
DE102007013039A1 (en) * 2007-03-19 2008-09-25 Schaeffler Kg Method of arranging an undivided rolling bearing on a shaft and rolling bearing therefor
JP2010077910A (en) * 2008-09-26 2010-04-08 Mazda Motor Corp Camshaft lubricating device
JP2010084531A (en) * 2008-09-29 2010-04-15 Mazda Motor Corp Oil feeder for camshaft

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1913905U (en) * 1965-02-17 1965-04-15 Duerkoppwerke Ag ROLLER BEARINGS, IN PARTICULAR GROOVE BALL BEARINGS.
DE1914884U (en) * 1965-03-03 1965-04-29 Duerkoppwerke Ag ROLLER BEARING WITH PLASTIC CAGE.
US3554621A (en) * 1967-08-23 1971-01-12 Federal Bearings Co Inc Combination cage and seal for antifriction bearings
DE19745410A1 (en) * 1997-10-15 1999-04-22 Schaeffler Waelzlager Ohg Roller bearing with a one-piece plastic cage
JP2006250268A (en) 2005-03-11 2006-09-21 Jtekt Corp Rolling bearing and cam shaft device
DE102007013039A1 (en) * 2007-03-19 2008-09-25 Schaeffler Kg Method of arranging an undivided rolling bearing on a shaft and rolling bearing therefor
JP2010077910A (en) * 2008-09-26 2010-04-08 Mazda Motor Corp Camshaft lubricating device
JP2010084531A (en) * 2008-09-29 2010-04-15 Mazda Motor Corp Oil feeder for camshaft

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011121597A1 (en) * 2011-12-17 2013-06-20 Neumayer Tekfor Holding Gmbh Mounting for camshaft and camshaft
WO2013087062A1 (en) * 2011-12-17 2013-06-20 Naumayer Tekfor Holding Gmbh Bearing for a camshaft, and a camshaft
DE102011121597B4 (en) 2011-12-17 2024-01-18 Aktiebolaget Skf Camshaft and camshaft bearings
US9322430B2 (en) 2011-12-17 2016-04-26 Aktiebolaget Skf Bearing for a camshaft, and a camshaft
GB2504100A (en) * 2012-07-17 2014-01-22 Mechadyne Internat Ltd A concentric camshaft supported by roller bearings
WO2014013409A2 (en) 2012-07-17 2014-01-23 Mechadyne International Limited A concentric camshaft arrangement
WO2014013409A3 (en) * 2012-07-17 2014-03-06 Mechadyne International Limited A concentric camshaft arrangement
CN104428497A (en) * 2012-07-17 2015-03-18 麦加戴恩国际有限公司 A concentric camshaft arrangement
WO2014128215A1 (en) * 2013-02-20 2014-08-28 Aktiebolaget Skf Rolling bearing cage with latching means, and needle bearing with an outer ring which is latched onto a cage
CN105074241A (en) * 2013-02-20 2015-11-18 斯凯孚公司 Rolling bearing cage with latching means, and needle bearing with an outer ring which is latched onto a cage
US9366063B2 (en) * 2013-03-25 2016-06-14 Brose Schliesssysteme Gmbh & Co. Kg Motor vehicle lock
US20140284944A1 (en) * 2013-03-25 2014-09-25 Brose Schliesssysteme Gmbh & Co. Kg Motor vehicle lock
CN105829745A (en) * 2013-12-16 2016-08-03 日本精工株式会社 Cage and roller
EP3085976A1 (en) * 2013-12-16 2016-10-26 NSK Ltd. Cage and roller
EP3085976A4 (en) * 2013-12-16 2017-03-29 NSK Ltd. Cage and roller
US10047795B2 (en) 2013-12-16 2018-08-14 Nsk Ltd. Cage and rollers
CN107002761A (en) * 2014-09-17 2017-08-01 舍弗勒技术股份两合公司 Variable torque bearing
CN107002761B (en) * 2014-09-17 2019-02-15 舍弗勒技术股份两合公司 Variable torque bearing
DE102015218633A1 (en) 2015-09-28 2017-03-30 Aktiebolaget Skf Rolling bearings with bearing cage
DE102015218633B4 (en) * 2015-09-28 2018-10-11 Aktiebolaget Skf Rolling bearings with bearing cage
DE102019101257A1 (en) * 2019-01-18 2020-07-23 Bayerische Motoren Werke Aktiengesellschaft Valve train for an internal combustion engine with a variable camshaft control

Also Published As

Publication number Publication date
JP5488296B2 (en) 2014-05-14
JP2012026526A (en) 2012-02-09

Similar Documents

Publication Publication Date Title
WO2012014069A1 (en) Roller bearing with seal integral with cage and camshaft apparatus having such a roller bearing
US8303191B2 (en) Multi-part axial cage for a large-diameter roller bearing
EP2386772B1 (en) Rolling bearing with internal lubrication
EP3006757B1 (en) Rolling bearing with an oil permeable sealing device
WO2014103694A1 (en) Rolling bearing
US8740470B2 (en) Retainer for radial roller bearing
JP2014084949A (en) Cylindrical roller bearing
EP2840269B1 (en) Rolling bearing
KR20150136494A (en) Shaft bearing with a shaft seal
EP2085666B1 (en) Sealing device and rolling bearing device
CN112969866A (en) Unit type wave gear device
EP3076038B1 (en) Rolling bearing with sealing arrangement
US9182029B2 (en) Mechanical system with one-way clutch and alternator comprising such a system
CN107269688B (en) Rolling bearing
US20190226535A1 (en) Clutch device
CN101971461B (en) Arrangement and process for mounting an axial bearing in a hermetic compressor
WO2011142217A1 (en) Ball bearing with both sides sealed
US10584743B2 (en) Needle roller thrust bearing
CN110307250B (en) Roller cage bearing
US8202006B2 (en) Sealing device, rolling bearing, and rolling bearing for wheel
JP2010096317A (en) Ball screw device
CN108150524B (en) Thrust bearing and retainer for thrust bearing
KR102417576B1 (en) Wave gear and bearing element for a wave gear
EP2202418B1 (en) Rolling bearing
CN111801504B (en) Radial oblique roller bearing

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 11757413

Country of ref document: EP

Kind code of ref document: A1

DPE1 Request for preliminary examination filed after expiration of 19th month from priority date (pct application filed from 20040101)
NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 11757413

Country of ref document: EP

Kind code of ref document: A1