WO2011154765A1 - Palier à roulement, palier de butée d'embrayage incorporant un tel palier à roulement et procédé d'assemblage d'un tel palier de butée d'embrayage - Google Patents

Palier à roulement, palier de butée d'embrayage incorporant un tel palier à roulement et procédé d'assemblage d'un tel palier de butée d'embrayage Download PDF

Info

Publication number
WO2011154765A1
WO2011154765A1 PCT/IB2010/001949 IB2010001949W WO2011154765A1 WO 2011154765 A1 WO2011154765 A1 WO 2011154765A1 IB 2010001949 W IB2010001949 W IB 2010001949W WO 2011154765 A1 WO2011154765 A1 WO 2011154765A1
Authority
WO
WIPO (PCT)
Prior art keywords
ring
rolling
rolling bearing
mounting member
force transmission
Prior art date
Application number
PCT/IB2010/001949
Other languages
English (en)
Inventor
Benoît Arnault
Original Assignee
Aktiebolaget Skf
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 Aktiebolaget Skf filed Critical Aktiebolaget Skf
Priority to DE112010005644.7T priority Critical patent/DE112010005644B4/de
Priority to PCT/IB2010/001949 priority patent/WO2011154765A1/fr
Publication of WO2011154765A1 publication Critical patent/WO2011154765A1/fr

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
    • 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
    • F16D23/142—Clutch-actuating sleeves or bearings; Actuating members directly connected to clutch-actuating sleeves or bearings with a resilient member acting radially between the bearing and its guide means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/06—Ball or roller bearings
    • F16C23/08—Ball or roller bearings self-adjusting
    • F16C23/082—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface
    • F16C23/084—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface sliding on a complementary spherical surface
    • 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
    • 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

Definitions

  • This invention relates to a rolling bearing adapted to transmit an axial thrust force relative to a central axis of the bearing.
  • a rolling bearing can be used in a clutch thrust bearing mounted on an automotive vehicle.
  • WO-A-2010/031756 teaches a way to solve this problem thanks to an internal travel track shaped in a section on a sphere on one of the rings of a ball bearing. A corresponding surface is provided on the other ring, in order to cooperate with a sealing gasket. Such an approach works satisfactorily and can be implemented in many cases. However, the overall radial dimensions of the ball bearing, in particular its outside diameter, are quite large, which can be an inconvenient in some circumstances.
  • the invention aims at solving this problem with a new rolling bearing which is compact in a radial direction, with respect to its central axis, and which can accommodate an alignment defect between the axis of the diaphragm mechanism and the axis of the output shaft of a gearbox in a clutch thrust bearing.
  • the invention concerns a rolling bearing adapted to transmit an axial thrust force and comprising an inner ring, an outer ring, a series of rolling bodies placed in a rolling chamber defined between respective facing surfaces of the inner ring and the outer ring and mounting means to mount the rolling bearing on a thrust force transmission part.
  • a first ring amongst the inner ring and the outer ring, has a first surface opposite the rolling chamber which is in the form of a section of a sphere centered on a first geometric point of a central axis of symmetry of the first ring
  • the mounting means include a mounting member provided with a second surface in the form of a section of a sphere centered on a second geometric point of a central axis of symmetry of the mounting member, while the respective radii of the first and second surfaces are identical and the first and second geometric points are superimposed.
  • a swivel-joint movement can occur between the first ring and the mounting member, which allows to accommodate an axes misalignment, as considered here-above.
  • the contact pressure between the rolling bodies and their respective raceways in the rolling chamber is regularly distributed, which ameliorates the lifetime period of the rolling bearing.
  • the rolling bodies of the rolling bearing can be balls, rollers or needles.
  • a rolling bearing according to the invention can be, for instance, a ball bearing, a roller bearing or a needle bearing
  • the words “axial”, “radial”, “axially”, “radially” and similar words relate, unless otherwise specified, to the axis of rotation of one ring of the rolling bearing with respect to the other ring.
  • a direction is “axial” when it is parallel to this axis and “radial” when it is perpendicular and secant to this axis.
  • a surface is “axial” when it is perpendicular to this axis and “radial” when it surrounds this axis and is perpendicular to a radial direction.
  • an axial effort is parallel to the axis of rotation and an axial surface is annular and perpendicular to this axis.
  • such a rolling bearing may incorporate one or more of the following features:
  • the first ring is the outer ring.
  • the first ring is the inner ring.
  • the mounting member is a metallic ring having a first cylindrical band, a second cylindrical band and an intermediate band joining the first and second cylindrical bands, the second surface being defined on a side of the intermediate band.
  • the mounting member is a ring with a metallic core and a synthetic fitting, the second surface being defined on a side of the fitting.
  • the fitting is overmoulded over the metallic core and the metallic core has a part which protrudes out of the fitting.
  • the first and second geometric points are offset axially, along the axis of symmetry of the first ring, relative to the series of rolling bodies.
  • the rolling bodies are balls arranged in a single series, and an angle defined between a plane perpendicular to the axis of symmetry of the first ring and a straight line joining the center of a ball to its contact point with one of the facing surfaces defining the rolling chambers is between 5° and 85°, preferably between 15° and 70°, most preferably about 60°.
  • the mounting means also include a wedging member adapted to wedge the mounting member on a thrust force transmission part.
  • this wedging member is a circlip.
  • the invention also concerns a clutch thrust bearing comprising a thrust force transmission part, such as a sleeve adapted to be connected to an output shaft or piston of a gearbox, and a rolling bearing as mentioned here-above.
  • a thrust force transmission part such as a sleeve adapted to be connected to an output shaft or piston of a gearbox, and a rolling bearing as mentioned here-above.
  • such a clutch thrust bearing can incorporate one or several of the following features:
  • the mounting member is mounted on the thrust force transmission part with a possibility of radial displacement with respect to a central axis of the rolling bearing.
  • the thrust force transmission part is provided with an external peripheral groove and the rolling bearing has a wedging element engaged within the groove.
  • the groove advantageously has a lateral wall which is inclined, with an angle between 5° and 90°, preferably between 20° and 70°, preferably of about 45°, with respect to a centra I axis of the thrust force transmission part and which diverges from an opposite lateral wall of the groove in a direction away from the bottom of the groove.
  • the invention also concerns a process for assembling a clutch thrust bearing as mentioned here-above, this process including at least the following steps:
  • figure 1 is an axial section of a clutch thrust bearing according to the invention incorporating a ball bearing according to the invention
  • figure 2 is a partly exploded axial section of the ball bearing belonging to the clutch thrust bearing of figure 1 ;
  • figure 3 in an enlarged view of detail III on figure 2 when the ball bearing is not exploded;
  • figure 4 is an enlarged view of detail IV on figure 1 ;
  • figure 5 is an axial section of the clutch thrust bearing of figure 1 in another configuration
  • figure 6 is an axial section similar to figure 1 for a clutch thrust bearing according to a second embodiment of the invention.
  • figure 7 is an enlarged view similar to figure 3 for the embodiment of figure 6 and figure 8 is en enlarged view of detail VIII on figure 6.
  • the clutch thrust bearing 2 represented on figures 1 , 4 and 5 includes a metallic sleeve 4 designed to be attached to a non-represented piston and centered on an input axis X4 which is a central axis of symmetry for sleeve 4.
  • Clutch thrust bearing 2 also includes a ball bearing 6 which is designed to be mounted onto sleeve 4.
  • Ball bearing 6 includes an inner ring 62, an outer ring 64 and one series of balls 66 held in position by a cage 70 within a rolling chamber 68 defined between an outer surface 622 of inner ring 62 and an inner surface 642 of outer ring 64.
  • X6 denotes the central axis of ball bearing 6 and is in an axis of symmetry for rings 62 and 64.
  • Outer ring 64 also has an outer surface 644 which is opposite rolling chamber 68. In other words, outer surface 644 faces a way from rolling chamber 68 with respect to outer ring 64.
  • a sealing gasket 72 is mounted on an edge 646 of outer ring 64.
  • a portion 648 of outer surface 644 is in the form of a section of sphere centered on a geometric point C1 which belongs to axis X6.
  • R1 denotes the radius of surface 648, that is the distance between surface 648 and geometric point C1.
  • a mounting ring 80 also belongs to ball bearing 6.
  • Ring 80 is made of a circular bended sheet of metal with a first or inner cylindrical band 82, a second or outer cylindrical band 84 and an intermediate band 86 which extends between bands 82 and 84.
  • Intermediate band 86 is inclined with respect to a central axis X8 of symmetry of mounting ring 80 with a mean angle a of about 60° .
  • Intermediate band 86 has a surface 8 62 oriented towards outer ring 64 which is also in the form of a section of a sphere.
  • Surface 862 is centered on a second geometric point C2 which belongs to axis X8.
  • R2 denotes the radius of surface 162, that is the distance between surface 862 and geometric point C2.
  • Radii R1 and R2 have the same value, so that surfaces 648 and 862 can be in sliding contact one against the other when geometric points C1 and C2 are superimposed at the intersection of axes X6 and X8, that is when ball bearing 6 is in a mounted configuration represented on figures 1 and 3 to 5.
  • P66 denotes a plane perpendicular to axis X6 and pressing through the centers C66 of balls 66.
  • d66 denotes the axial distance, along axis X6, between plane P66 and superimposed points C1 and C2. d66 is at least 3 times the diameter of the series of balls 66. This allows an efficient force transmission along axis X6 .
  • L66 denotes a straight line passing through the center C66 of a ball 66 and through its contact point A62 with surface 622. Line L66 also goes through the contact point A64 between ball 66 and surface 642.
  • ⁇ denotes the angle between line L66 and plane P66 in a radial plane with respect to axis X6. ⁇ is between 5° and 85°, preferably between 15° and 70°, most preferably about 60°.
  • Mounting ring 80 is used to mount ball bearing 6 onto sleeve 4.
  • sleeve 4 is provided with an outer peripheral groove 42 defined between a peripheral annular band 44 and a peripheral collar 46 of sleeve 4.
  • the side face 462 of collar 46 oriented towards band 44 is inclined with respect to axis X4 at an angle ⁇ of about 45°.
  • Side face 462 diverges from band 44 in a direction away from the bottom 422 of groove 42.
  • Angle ⁇ can have a value between 5° and 90°, preferably between 20° and 70°, 45° being most preferred.
  • a circlip 90 also belongs to ball bearing 6 and is used to wedge band 82 of mounting ring 80 with respect to sleeve 4. Actually, circlip 90 elastically engages within groove 42 so that it exerts an axial effort E90 with respect to axis X4 in a direction which blocks mounting ring 80 against the surface 442 of band 44 oriented towards collar 46.
  • circlip 90 to hold mounting ring 80 with respect to sleeve 4 is compatible with a radial displacement of mounting ring 80 with respect to axis X4, that is an adjustment of the relative positions of axes X4 and X8, these axes remaining parallel in all circumstances when ring 80 is wedged onto sleeve 4.
  • the mounting means 80 and 90 which belong to ball bearing 6, are such that a sub-assembly 100 including items 62 to 66 can have its position adjusted in order to accommodate an offset of axes X4 and X6 one with respect to the other, thanks to the adjustment possibility represented by arrow A80.
  • a misalignment of these axes can also be accommodated via a swivel-joint movement of ring 64 with respect to ring 80, thanks to sliding of surfaces 648 and 862 one against the other, as shown by arrow B80.
  • This swivel-joint movement takes place around superimposed geometric points C1 and C2.
  • This swivel-joint movement can be identified by comparing the two configurations of clutch thrust bearing 2 respectively represented on figures 1 and 5.
  • axes X4 and X6 are not aligned and not parallel.
  • these axes are superimposed, that is parallel and with more than one point belonging to both of them.
  • mounting ring 80 is first positioned around groove 42. Then, circlip 90 is positioned around groove 42, next to band 82 and, thanks to its elasticity, it partly engages within groove 42. Because of the orientation of surface 462 and of the value of angle ⁇ , this induces axial effort F90 which wedges mounting ring 80 on sleeve 4.
  • Sub-assembly 100 is formed with items 62, 64 and 66.
  • this subassembly also includes items 70 and 72.
  • This sub-assembly 100 can be pre-constituted, prior to the mounting of ring 80 onto sleeve 4, or built afterwards.
  • This sub-assembly 100 is mounted onto mounting ring 80 by engaging the edge part 649 of outer ring 64, which defines outer surface portion 648, against the intermediate band 86 of mounting ring 80.
  • sub-assembly 100 can pivot with respect to mounting ring 80 around geometric points C1 and C2 which are then superimposed. This is possible thanks to the geometry of surfaces 648 and 862, in particular their respective radii R1 and R2 which have the same value.
  • clutch thrust bearing 2 can function correctly in the configurations of figure 1 , where axes X4 and X200 are offset and inclined with respect to the other, or in the configuration of figure 5, where these axes are superimposed.
  • mounting ring 80 has a metallic core 83 which has substantially the same shape as mounting ring 80 in the first embodiment.
  • This metallic core is partly overmoulded into a fitting 85 of synthetic material, e.g. PA 4.6 or PA 6.6 or PTFE, with or without fibre glass reinforcement particles.
  • Fitting 85 defines a surface 852 in the form of a section of a sphere centered on a geometric point C2 similar to geometric point C2 in the first embodiment. Then, a swivel- joint movement occurs between the outer surface portion 648 of outer ring 64 and surface 852 of fitting 85 when points C1 and C2 are superimposed.
  • the material of fitting 85 can be chosen to improve the friction coefficient between surfaces 648 and 852.
  • Core 83 is only partly surrounded by fitting 85 so that the inner cylindrical band 82 of core 83 interacts with circlip 90 and band 44 as in the first embodiment. This also applies at the level of a terminal bended portion 842 of band 84 which lies directly against surface 442, as in the first embodiment.
  • clutch thrust bearing 2 and ball bearing 6 work as in the first embodiment, so that they can accommodate that the central axes X4 of thrust transfer sleeve 4 and X200 of diaphragm hooks are offset and/or not aligned.
  • outer ring 64 is provided with the first surface 648 in the form of a portion of a sphere.
  • first surface 648 in the form of a portion of a sphere.
  • such a surface could be provided on inner ring 62.
  • the invention is represented on the figures with a ball bearing.
  • other types of rolling bearings e.g. roller bearings or needle bearings, can be used with the invention.
  • adjustment of the radial position of mounting ring 80 with respect to sleeve 4 and of the angular position of outer ring 64 with respect to mounting ring 80 occurs on the first time that ball bearing 6 interacts with sleeve 4 and diaphragm hooks 200. Once it is correctly positioned with respect to sleeve 4, bearing 6 remains in its configuration with respect to items 4 and 200.

Landscapes

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

Abstract

L'invention concerne un palier à roulement (6) adapté pour transmettre une force de poussée axiale ; il comprend une bague interne (62), une bague externe (64), une série d'organes de roulement (66) placés dans une chambre de roulement (68) définie entre les surfaces opposées respectives de la bague interne et de la bague externe, et un moyen de montage (80, 90) destiné à monter le palier à roulement sur une partie de transmission de force de poussée. Une première bague (64), parmi la bague interne (62) et la bague externe (64), comporte une première surface (648) opposée à la chambre de roulement qui est sous la forme d'un segment d'une sphère centrée sur un premier point géométrique (C1) appartenant à un axe de symétrie (X6) de la première bague (64). Le moyen de montage inclut un élément de montage (80) doté d'une seconde surface (862) sous la forme d'un segment d'une sphère centrée sur un second point géométrique (C2) appartenant à un axe de symétrie (X8) de l'élément de montage. Les rayons respectifs (R1, R2) des première et seconde surfaces sont identiques et les points géométriques (C1, C2) sont superposés.
PCT/IB2010/001949 2010-06-11 2010-06-11 Palier à roulement, palier de butée d'embrayage incorporant un tel palier à roulement et procédé d'assemblage d'un tel palier de butée d'embrayage WO2011154765A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE112010005644.7T DE112010005644B4 (de) 2010-06-11 2010-06-11 Wälzlager, Kupplungsausrücklager mit einem derartigen Wälzlager und Verfahren zum Zusammenbauen eines derartigen Kupplungsausrücklagers
PCT/IB2010/001949 WO2011154765A1 (fr) 2010-06-11 2010-06-11 Palier à roulement, palier de butée d'embrayage incorporant un tel palier à roulement et procédé d'assemblage d'un tel palier de butée d'embrayage

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/IB2010/001949 WO2011154765A1 (fr) 2010-06-11 2010-06-11 Palier à roulement, palier de butée d'embrayage incorporant un tel palier à roulement et procédé d'assemblage d'un tel palier de butée d'embrayage

Publications (1)

Publication Number Publication Date
WO2011154765A1 true WO2011154765A1 (fr) 2011-12-15

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PCT/IB2010/001949 WO2011154765A1 (fr) 2010-06-11 2010-06-11 Palier à roulement, palier de butée d'embrayage incorporant un tel palier à roulement et procédé d'assemblage d'un tel palier de butée d'embrayage

Country Status (2)

Country Link
DE (1) DE112010005644B4 (fr)
WO (1) WO2011154765A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019021116A1 (fr) 2017-07-22 2019-01-31 Texspin Bearings Limited Palier de libération d'embrayage à auto-alignement

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0062535A1 (fr) * 1981-04-06 1982-10-13 Skf (U.K.) Limited Dispositif de débrayage auto-centreur
FR2504626A1 (fr) * 1981-04-23 1982-10-29 Skf Kugellagerfabriken Gmbh Butee d'embrayage, particulierement pour un embrayage de vehicule automobile
FR2540950A1 (fr) * 1983-02-12 1984-08-17 Nippon Seiko Kk Dispositif de debrayage du type auto-centreur
DE102006059300A1 (de) * 2006-12-15 2008-06-19 Schaeffler Kg Kupplungsausrücklagereinrichtung
WO2010031756A1 (fr) 2008-09-16 2010-03-25 Aktiebolaget Skf Roulement à billes, son utilisation et véhicule à moteur équipé d'un tel roulement

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2224710C3 (de) 1972-05-20 1980-11-20 Fichtel & Sachs Ag, 8720 Schweinfurt Zentral geführter Kupplungsausrücker
DE10124663A1 (de) 2001-05-18 2002-11-21 Ina Schaeffler Kg Selbsteinstellendes Kupplungsausrücklager
DE102008005028A1 (de) 2008-01-22 2009-07-23 Schaeffler Kg Kupplungsausrücklagereinrichtung

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0062535A1 (fr) * 1981-04-06 1982-10-13 Skf (U.K.) Limited Dispositif de débrayage auto-centreur
FR2504626A1 (fr) * 1981-04-23 1982-10-29 Skf Kugellagerfabriken Gmbh Butee d'embrayage, particulierement pour un embrayage de vehicule automobile
FR2540950A1 (fr) * 1983-02-12 1984-08-17 Nippon Seiko Kk Dispositif de debrayage du type auto-centreur
DE102006059300A1 (de) * 2006-12-15 2008-06-19 Schaeffler Kg Kupplungsausrücklagereinrichtung
WO2010031756A1 (fr) 2008-09-16 2010-03-25 Aktiebolaget Skf Roulement à billes, son utilisation et véhicule à moteur équipé d'un tel roulement

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019021116A1 (fr) 2017-07-22 2019-01-31 Texspin Bearings Limited Palier de libération d'embrayage à auto-alignement
JP2020527684A (ja) * 2017-07-22 2020-09-10 テックススピン・ベアリングス・リミテッド 自動調心型クラッチリリース軸受
EP3658792A4 (fr) * 2017-07-22 2020-12-16 Texspin Bearings Limited Palier de libération d'embrayage à auto-alignement

Also Published As

Publication number Publication date
DE112010005644T5 (de) 2013-03-28
DE112010005644B4 (de) 2024-05-08

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