WO2009095101A2 - Système de butée de débrayage - Google Patents

Système de butée de débrayage Download PDF

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Publication number
WO2009095101A2
WO2009095101A2 PCT/EP2008/065206 EP2008065206W WO2009095101A2 WO 2009095101 A2 WO2009095101 A2 WO 2009095101A2 EP 2008065206 W EP2008065206 W EP 2008065206W WO 2009095101 A2 WO2009095101 A2 WO 2009095101A2
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
bearing race
race
clutch release
annular wall
Prior art date
Application number
PCT/EP2008/065206
Other languages
German (de)
English (en)
Other versions
WO2009095101A3 (fr
Inventor
Steffen Dittmer
Bernhard KLÖPFER
Ludwig Winkelmann
Original Assignee
Schaeffler Kg
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 Schaeffler Kg filed Critical Schaeffler Kg
Publication of WO2009095101A2 publication Critical patent/WO2009095101A2/fr
Publication of WO2009095101A3 publication Critical patent/WO2009095101A3/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
    • 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
    • F16C33/72—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
    • F16C33/7886—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted outside the gap between the inner and outer races, e.g. sealing rings mounted to an end face or outer surface of a race
    • 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
    • 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
    • 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
    • F16C33/761—Sealings of ball or roller bearings specifically for bearings with purely axial load
    • 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
    • F16D2300/06—Lubrication details not provided for in group F16D13/74
    • 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

Definitions

  • the invention relates to a clutch release bearing device having a first race, a second race, rolling elements which are received in a defined between the two raceways track space, and a cage device for guiding the rolling elements within said track space.
  • the invention relates to a clutch release bearing device which withstands high running loads even under unfavorable environmental conditions, especially in dusty environments.
  • the invention has for its object to provide solutions by which it is possible to create a clutch release bearing device which is inexpensive to produce, and is characterized by a high insensitivity to moisture and dust.
  • a second bearing race which represents the bearing race rotating about a bearing axis and which forms a second rolling body tread area
  • Rolling elements which are accommodated in a path space defined between the first bearing race and the second bearing race,
  • this coupling release bearing device is characterized in that the sealing device has a cover ring element which dips into a sealing zone, wherein the cover ring element in such a way in the clutch release bearing device it is integrated that this cut a potential particle passageway between the two annular walls is reduced and also rotates the second annular wall formed by the second bearing race relative to the Abdeckringelement.
  • the clutch release bearing device is designed such that the sealing zone extends between the cover ring element and the second annular wall.
  • Structures, in particular conveyor thread grooves, can be formed both on the cover ring element and on the second annular wall adjoining the cover ring element and, in the case of a designated direction of rotation of the second bearing race, tend to counteract the passage of any contaminants through the sealing zone.
  • the cover ring element is designed in such a way that it comprises a sheet-metal ring which acts as a highly rigid structure and is preferably manufactured by deep-drawing deformation.
  • This sheet metal ring can be designed so that it is brought so close to the annular wall of the second, circumferential bearing race that access of impurities is already at least largely prevented by the case realized here, extremely low running gap.
  • the cover ring element in such a way that it also comprises an elastomer structure.
  • This elastomeric structure may be designed so that it forms at least one sliding contact sealing lip, which rests, for example, on a tread portion, which optionally directly through the second annular wall of the second bearing race is formed. It is also possible to make the elastomeric structure with respect to its torus cross-section so that it forms a plurality of sliding contact sealing lips, which bear against radially slightly spaced-apart contact zones on the annular wall.
  • the Kupplungsaus Wegneck worn is designed such that the cooperating with the Abdeckringelement, in particular provided by this sealing lips tread portion is formed by a mecanicswandung- sabexcellent the second annular wall.
  • the cover ring element in particular the elastomer structure, in such a way that the running or sealing gap is formed in cooperation with an inner end face section of the second annular wall.
  • the cover ring element is connected to the first race. This makes it possible to ensure a particularly precise positioning of the opening into the sealing zone portions of the Abdeckringiatas with respect to the second annular wall and against, supported by the second bearing race structures.
  • the cover ring element or the elastomeric structure provided by it is preferably centered by the first raceway. This centering can be done in particular by the Abdeckringelement used in an inner opening region of the first race, in particular in a bounded by the first annular wall opening or bore, in particular is pressed.
  • the cover ring element As an alternative to the aforementioned approach of anchoring the cover ring element to the first race, according to another aspect of the present invention it is also possible to connect the cover ring element to a carrier bush carrying the first race.
  • This connection can be done in particular by using a first bearing race on the support bushing securing plate spring.
  • This diaphragm spring allows the cover Ring element are clamped against a provided by the first annular wall of the first bearing race face.
  • the cooperating with the second bearing race in particular by this provided second annular wall and in this case the sealing zone defining structures so that a minor , Radial displacement of the second annular wall relative to the Abdeckringelement is permitted.
  • This radial displaceability of the second annular wall relative to the cover ring element can be made possible, in particular, by designing the cover ring element or the elastomer structure provided by the latter in such a way that it bears against an inner end face, ie a surface of the second annular wall which is essentially normal to the bearing axis.
  • the sealing zone formed in the interaction of the second bearing race or the second annular wall provided by the second annular wall with the Abdeckringelement is designed so that one of any, from outside penetrating impurities to be overcome passageway from a radially outer level (large radius) to a radial further inside circumferential level (smaller radius) leads.
  • This makes it possible to provide in the region of this passageway relative movements between the sealing zone delimiting the moving surfaces, which counteract the passage of impurities.
  • the invention is based task is GE measure a further aspect of the invention also solved by a Kupplungsaussch- with the features specified in claim 15 and / or 22 features.
  • the cover ring element is preferably anchored to the second annular wall in a form-fitting manner. This anchoring can be accomplished, in particular, via a beading area, which engages behind the second annular wall on an end face facing away from the sealing zone.
  • the cover ring element can, as in the above-described exemplary embodiment, be designed such that it encompasses a sealing lip device made of an elastomer material. This sealing lip device can be designed such that it has a sealing lip which abuts against an end face defined by the first annular wall of the first bearing race.
  • the cover ring member is designed to include a sheet metal ring core having a torus cross section with an angle profile.
  • the incorporation of the sealing lip device into the cover ring element is preferably accomplished in such a way that the elastomer body carrying the sealing lip device sits in the inner corner region of this angle profile.
  • the angle profile can also be designed so that it comprises a ring leg which, while leaving a small clearance gap to the first
  • Ring wall of the first bearing race penetrates. This makes it possible, only by the relatively rigid structure of the Abdeckringettis potentially for the passage of any impurities available
  • FIG. 1 shows an axial sectional illustration for illustrating the structure of a first embodiment of a clutch release bearing according to the invention
  • FIG. 1b shows a detail sketch to illustrate a particularly advantageous design of a sealing zone defined in conjunction with the covering ring element according to the invention
  • FIG. 2 shows an axial sectional illustration for illustrating a second variant of a clutch release bearing device according to the invention
  • FIG. 3 shows an axial sectional illustration for illustrating a third variant of a clutch release bearing device according to the invention with a multi-part cover ring element centered on the stationary bearing race
  • FIG. 4 shows an axial sectional illustration for illustrating a fourth variant of a clutch release bearing device according to the invention with a cover ring element which is provided with an elastomeric sealing lip engaging in an inner opening of the second bearing race,
  • FIG. 5 shows an axial sectional illustration for illustrating a fifth variant of a clutch release bearing device according to the invention which is largely similar to the variant according to FIG.
  • FIG. 6a is an axial sectional view for illustrating a variant of a release bearing device according to the invention with a positioned by a bearing support sleeve DichtAbdeckringele- element
  • FIG. 6b shows a further axial sectional representation for illustrating a seventh variant of a clutch release bearing device according to the invention, likewise with a sealing ring device positioned by a carrier bush,
  • FIG. 7 shows an axial sectional illustration for illustrating an eighth variant of a clutch release bearing device according to the invention
  • FIG. 8 shows an axial sectional illustration for illustrating a ninth variant of a clutch release bearing device according to the invention
  • FIG. 9 shows an axial sectional illustration for illustrating a tenth variant of a clutch release bearing device according to the invention.
  • FIG. 10 is an axial sectional view illustrating an eleventh variant of a Kupplungsaus Wegnecklagerein- inventive device.
  • the clutch release bearing device illustrated in FIG. 1 a comprises a first bearing race 1 with a first rolling body running surface region B1, a second bearing race 2, which represents the bearing race rotating about a bearing axis X and which forms a second rolling body raceway region B2.
  • the first bearing race 1 and the second bearing race 2 are designed so that they overlap each other in the axial direction, wherein the second bearing race 2 in this case surrounds the first bearing race 1 on the outside.
  • Both on the first bearing race 1 and on the second bearing race 2 is in each case a radially inwardly below the radial level of the first WälzSystem- Running range B1 retracted ring wall 1 a, 2 a formed.
  • rolling elements W are added.
  • the Wälzköper W are designed as balls.
  • the provided by the two bearing races 1, 2 Wälz stresses Kunststoff Kunststoff Schemee B1 and B2 form in conjunction with the rolling elements W an angular contact ball bearings.
  • the rolling elements W are guided in the defined between the two bearing races 1, 2 track space B by a cage device 3, which is preferably made of a plastic material and can be designed, for example, as a ball snap cage.
  • the clutch release bearing device is further provided with a sealing device, which as such serves to suppress the entry of impurities to the track space B via a gap defined between the two annular walls 1a, 2a.
  • the clutch release bearing device shown here is characterized in that the sealing device has a Abdeckringelement 4, which dips into a sealing zone D, wherein the Abdeckringelement 4 is so incorporated into the Kupplungsaus Wegnecklager adopted that thereby the cross-section of a potential particle passageway between the two annular walls 1 a , 2a is reduced and also rotates the annular wall 2a formed by the second bearing race 2 relative to the Abdeckringelement 4.
  • the sealing zone D is formed directly between the Abdeckringelement and an outer peripheral surface of the second annular wall 2a.
  • the Abdeckringelement 4 is designed as a deep-drawn sheet metal ring and the same to the first race 1, in particular to the annular wall 1 a.
  • the cover ring element 4 is centered in this embodiment directly by the first race 1, in particular its annular wall 1 a.
  • the cover ring element 4 is preferably made of a heat-treated and / or coated steel material and formed so that it forms a seat surface 4a, which directly on a the Abdeckringelement 4 facing end face 1 b of the annular wall 1 a seated.
  • the cover ring element 4 is provided in its inner peripheral region with an annular web 4b, which engages under an inner peripheral surface formed by the annular wall 1 a 1 c. Through this annular web 4b, the cover ring element 4 is centered directly through the inner opening of the annular wall 1 a. Through the seat 1 b, the cover ring member 4 is positioned in the axial direction.
  • the cover ring element 4 may be designed so that it is anchored sufficiently resiliently under sufficient pressure fit on the first bearing race 1.
  • the first bearing race 1 is guided on a support bush 5 such that the first bearing race 1 relative to the support bush 5 by a certain amount in the radial direction is displaced.
  • the backup of the first bearing race 1 and thus the entire rolling bearing device on the support bushing 5 is achieved by a plate spring 6, which is supported on a provided by the support sleeve 5 ring edge 7, while the first bearing race 1 with the interposition of a hardened contact disk 8 to a through the Carrier socket 5 provided annular shoulder 9 spans.
  • the preceding explanations apply to a large extent analogously.
  • the provided by the first bearing race 1 and the second bearing race 2 ring walls 1 a, 2 a are designed so that the inner circumferential openings defined by these have substantially the same inner diameter.
  • the annular wall 2a is designed so that it forms a convex bulging, optionally kalottenringieri end face.
  • the sealing or foreclosure of the track space B against any, to the sealing zone D penetrating impurities is achieved according to the invention by a tethered to the annular wall 1 a of the first bearing race 1 Abdeckringelement 4.
  • the Abdeckringelement 4 is designed so that this one hand supports a supported and centered on the annular wall 1 a sheet metal ring 14 and secured by this plastic ring 10.
  • the plastic ring is secured to the sheet metal ring 4 via a crimping section 4e.
  • the plastic ring 10 is designed such that it forms an annular wall 2a penetrating annular web 10a, which engages as such the defined by the annular wall 2a inner peripheral wall 2b similar to the embodiment of Figure 1 below.
  • the plastic ring 10 is further configured such that it provides an inner end face 10b, which defines an annular space in which is provided for tensioning the first bearing race 1 and the annular wall 1 a provided against the support structure 5 plate spring 6.
  • the plastic ring 10 is equipped with a sealing lip ring structure preferably made of an elastomeric material, by means of which a further sealing of the between the plastic ring 10 and the inner ring is ensured. nenisation the second annular wall 2a remaining running gap is achieved.
  • FIG. 3 shows a third variant of a clutch release bearing device according to the invention, which largely corresponds in its construction to the variant according to FIG. Notwithstanding the embodiment described in conjunction with Figure 2, in this third variant, instead of the plastic ring 10 (see Figure 2), a cover ring element 10 'manufactured as a deep-drawn component is provided which, similar to the plastic ring 10 according to Figure 2, provides a seal - Donate! 10a ', which engages as such in an opening defined by the second annular wall 2a inner opening, leaving an extremely small clearance.
  • the ring 4 provided for positioning this cover ring element 10 'is furthermore designed with regard to its cross section so that it forms additional ring structures, by means of which an additional partitioning of the web space B with respect to the surroundings of the release bearing device is achieved.
  • the Abdeckringelement 10 ' the aforementioned Axialbuchsenabrough / sealing leg 10a', a radial annular web portion 10b, a bridging portion 10c, an inclined back to the Abdeckringelement 4 ring back 10d and an anchoring ring web 10e.
  • This anchoring ring web 10e is axially secured to the cover ring element / ring 4 by a passage 4e.
  • the shield ring or the cover ring element 10 ' is positioned by the ring 4 both in the axial direction and in the radial direction.
  • the ring 4 is supported and centered on the annular wall 1 a of the first bearing ring 1 as in the embodiments described above.
  • the covering ring element 4 is provided with a sealing lip device 40 made of an elastomer material.
  • This sealing lip device 40 is designed in the embodiment shown here so that it forms a first sealing lip 41 and a second sealing lip 42.
  • the first sealing lip 41 engages under one by the second Ring wall 2a of the second bearing race 2 provided mecanicals- wall.
  • the second sealing lip 42 provided by the sealing lip device 40 bears against an inner end face 2s of the annular wall 2a facing the web space B.
  • the sealing lip device 40 is made of an elastomer material and vulcanized onto a metal ring core 4 a of the cover ring element 4 designed as a deep-drawn component.
  • the metal ring core 4a is, as in the embodiments described above, designed so that it is seated on the one hand on a provided by the first annular wall 1 a end face and also centered by a defined by the annular wall 1 a inner peripheral opening.
  • the Abdeckringelement 4 is urged under action of the plate spring 6 against the provided by the first annular wall 1 a end face. Also in this embodiment, the first bearing race 1 relative to the support bush 5 in the radial direction is slightly displaced. The attached to the first annular wall 1 a Abdeckringelement 4 is positioned by the first bearing race 1 relative to the second bearing race 2 high precision.
  • the first bearing race 1 encompassing the second bearing race 2 forms on its side facing away from the annular wall 2a "clutch remote" side a second clearance with the first bearing race 1.
  • This second clearance is sealed by a sealing device HD, which secured via an annular cap RK on the second bearing race 2 is.
  • the sealing lip device 40 is designed in this embodiment so that it provides a first sealing lip 41 and a second sealing lip 42 which are positioned by the Abdeckring- element 4.
  • the Abdeckringelement 4 has, similar to the embodiment of Figure 4, an annular flange 4a, which is positioned both axially and radially through the annular wall 1 a of the first bearing race 1.
  • the cover ring element with the interposition of a cold-worked or heat-treated and or coated annular disc 44 by the plate spring 6 against the provided by the first annular wall 1 a end face stretched.
  • the plate spring 6 is thus not directly adjacent to the metal ring / annular flange 4 a of the Abdeckringiatas 4.
  • annular shoulder 9 is in the same manner as in the embodiment of Figure 8, made of a cold-worked or heat-treated and coated or steel material supporting disc 8 is arranged.
  • the support disk 8 is placed on the support structure 5 such that it is not displaceable in the radial direction substantially.
  • the cover ring element 4 provided for sealing the running gap is secured to the support structure 5.
  • the cover ring element 4 comprises a metal ring 4a produced as a deep-drawn forming part and a sealing lip device 40 made of an elastomer material.
  • the sealing lip device 40 forms a sealing lip 42 which rests against an inner surface provided by the annular wall 2a.
  • the elastomer structure / sealing lip device 40 is vulcanized onto the cover ring element 4.
  • the cover ring element 4 comprises a bushing section 4f, which as such engages under an inner opening formed by the support structure 5. This section 4f is axially secured to the carrier structure 5 via a crimping section 4e.
  • a sealing of the release bearing is accomplished, wherein the bore 71 of the outer ring 72 is locked in place.
  • Sealing lip 73 acts as a pre-seal with non-abrasive sealing lip for dirt repellency.
  • the task of the main seal takes over the axially acting against the outer ring 2 inner sealing lip 74.
  • a facing the inner ring sealing lip 78 is the fat retention. It can be designed in particular as a sliding seal or to minimize friction as a gap seal.
  • the sealing ring carrier 75 with its tuned length of the cylindrical portion ensures a tight tolerance of the inner biasing force of the plate spring 76 when crimping the retaining ring 77.
  • the seal carrier can be made of a standard material, such as DC 03.
  • FIG. 7 shows a further variant of a clutch release bearing device according to the invention, in which, in addition to a partitioning of the rolling element track space B from contamination, a shielding of the fixing or connecting mechanism for connecting the first bearing race 1 to the carrier structure 5 is achieved.
  • a seal of the release bearing is achieved by a radially acting and formed by the Abdeckringelement 4 labyrinth seal.
  • two deep-drawn angle rings 43, 44 are positively fixed to the circumferential outer ring 2.
  • the standing labyrinth ring cover 45 is fixed to the flanging plate 46.
  • Material for the sealing components is preferably C17 MV designed as a tempered and work hardened strip material. The dirt-repellent conveying effect can be improved by helical threads on the sealing surfaces of the labyrinth rings.
  • a double seal which has a radially-acting sealing lip in the outer ring bore as the actual main seal.
  • This main sealing lip protects the release bearing against the ingress of contaminants from the outside.
  • the second axially acting sealing lip prevents the lubricant from escaping from the release bearing.
  • the seal carrier is preferably made of tempered Band material produced, which has a minimum surface hardness of 400 HV and is fixed in the bore of the inner ring.
  • the sealing device is designed such that it has a cover ring element 80 which dips into an annular gap space between the two bearing races 1, 2, wherein the cover ring element 80 is connected to the second annular wall 2 a in that the cover ring element 80 engages or passes through an inner opening defined by the second annular wall 2a.
  • the cover ring element 80 is anchored to the second annular wall 2a in a form-fitting manner.
  • the cover ring element 80 is axially secured by a beading on the second annular wall 2a.
  • the covering ring element 80 comprises a sealing lip device 81 made of an elastomeric material, which has a sealing lip 82 which rests against an end face defined by the first annular wall 1a.
  • the cover ring element 80 comprises a sheet metal ring core, which has a torus cross section with an angle profile up.
  • the elastomer body forming the sealing lip device 81 sits in the inner corner region of this angle profile.
  • the elastomer seal shown can be connected as a pickled element or by vulcanizing material to the ring leg 83.
  • the angle profile comprises a ring leg 83 which on the one hand causes fat retention of the grease located in the region of the web space B by the sealing lip device and on the other hand also causes an additional narrowing of the potential passage region between the two bearing races 1, 2.
  • the cross-section of the cover ring element 80 is designed such that it forms, on the one hand, a bushing section extending through the inner circumferential opening 2a of the ring wall 2a and a fixing ring section 86 which is pressed back substantially by 90 degrees.
  • a release bearing is provided with an angle ring for sealing the clutch near side of the release bearing.
  • the angle ring is supported on a coupling-near plane surface of the inner ring flange and is centered over the inner ring bore in relation to the circumferential outer ring.
  • the Axialverlauf and the cylindrical shoulder on the angle ring are arranged taking into account the minimum required clearance with a narrow gap to the bore of the outer ring and form a seal for sealing a labyrinth seal.
  • To reduce wear in the contact region of the diaphragm spring for the inner preload of the release bearing is proposed to produce the sealing ring made of strip material deep-drawn and subjected to a heat treatment to achieve a surface hardness of at least 400 HV.
  • the angle ring can also be made of already tempered material, eg C45 A + H or C17 MV with at least 400 HV.
  • a conveying thread on the outer diameter of the cylindrical projection of the angle ring and / or in the bore of the outer ring in the area of the sealing gap.

Abstract

L'invention concerne un système de butée de débrayage comprenant une première bague de roulement, une seconde bague de roulement, des éléments roulants logés dans un espace formant un chemin de roulement, défini entre les deux bagues de roulement, ainsi qu'un système de cage destiné à guider les éléments roulants à l'intérieur de l'espace formant un chemin de roulement. L'objectif de l'invention est de fournir des solutions permettant de réaliser un système de butée de débrayage de fabrication économique et se distinguant par une grande insensibilité à l'humidité et aux poussières. Selon l'invention, cet objectif est atteint au moyen d'un système de butée de débrayage comprenant une première bague de roulement pourvue d'une première zone de surface de roulement pour les éléments roulants, une seconde bague de roulement, qui représente une bague de roulement s'étendant autour d'un axe de palier et forme une seconde zone de surface de roulement pour les éléments roulants, la seconde et la première bague de roulement se chevauchant dans le sens axial, la seconde bague de roulement s'engageant autour de la première bague de roulement sur la face extérieure et une paroi de bague, rentrée radialement en dedans sous le niveau radial de la première zone de surface de roulement, étant réalisée aussi bien sur la première que sur la seconde bague de roulement, des éléments roulants logés dans un espace formant un chemin de roulement, défini entre la première bague de roulement et la seconde bague de roulement, un système de cage destiné à guider les éléments roulants à l'intérieur dudit espace ainsi qu'un dispositif d'étanchéité destiné à empêcher que des impuretés ne pénètrent dans l'espace formant un chemin de roulement par une zone de passage potentielle définie entre les deux parois de bague. Le système de butée de débrayage se caractérise en ce que le dispositif d'étanchéité présente un élément annulaire de recouvrement s'enfonçant dans une zone étanche, ledit élément ann
PCT/EP2008/065206 2008-01-30 2008-11-10 Système de butée de débrayage WO2009095101A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008006656A DE102008006656A1 (de) 2008-01-30 2008-01-30 Kupplungsausrücklagereinrichtung
DE102008006656.7 2008-01-30

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EP3009702A1 (fr) 2014-10-13 2016-04-20 Aktiebolaget SKF Butée, dispositif de butée d'embrayage et véhicule automobile équipé d'un tel dispositif

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FR2944843B1 (fr) * 2009-04-27 2013-11-29 Skf Ab Roulement a billes, butee d'embrayage-debrayage comprenant un tel roulement et vehicule automobile equipe d'un tel roulement.
JP5768334B2 (ja) * 2010-07-05 2015-08-26 株式会社ジェイテクト クラッチレリーズ軸受装置
WO2012013236A1 (fr) * 2010-07-29 2012-02-02 Aktiebolaget Skf Roulement de débrayage comprenant un joint tournant
WO2015018383A1 (fr) * 2013-08-08 2015-02-12 Schaeffler Technologies AG & Co. KG Système de butée de débrayage
FR3033376B1 (fr) * 2015-03-04 2018-08-31 Ntn-Snr Roulements Butee d'embrayage de vehicule automobile equipee d'un insert d'appui sur le diaphragme
DE102017211785A1 (de) * 2016-08-08 2018-02-08 Aktiebolaget Skf Wälzlager mit Schutzflansch und Zusammenbauverfahren eines Laufrings mit einem derartigen Schutzflansch
CN108071708B (zh) * 2016-11-07 2021-02-02 舍弗勒技术股份两合公司 分离轴承

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FR2180305A5 (fr) * 1972-04-13 1973-11-23 Skf Ind Trading & Dev
DE4338261A1 (de) * 1992-11-14 1994-05-19 Fichtel & Sachs Ag Lager, insbesondere für Ausrücksysteme von Reibungskupplungen
EP0773384A1 (fr) * 1995-11-09 1997-05-14 Skf France Flasque de protection pour roulement, roulement associé et procédé de fabrication d'une bague de roulement équipée d'un flasque de protection
EP0859161A1 (fr) * 1997-02-13 1998-08-19 Skf France Dispositif de manoeuvrre d'embrayage à organe élastique d'autoalignement
EP1489327A1 (fr) * 2003-06-18 2004-12-22 Aktiebolaget SKF Butée de débrayage et procédé de montage
DE102004034439A1 (de) * 2004-07-16 2006-02-02 Ina-Schaeffler Kg Kupplungsausrücklager
DE102005053612A1 (de) * 2005-11-10 2007-05-16 Schaeffler Kg Ausrücklager für eine Betätigungseinrichtung einer Schaltkupplung
WO2009027184A2 (fr) * 2007-08-28 2009-03-05 Schaeffler Kg Dispositif de retenue
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FR2078793A5 (fr) * 1970-02-19 1971-11-05 Skf Kugellagerfabriken Gmbh
FR2180305A5 (fr) * 1972-04-13 1973-11-23 Skf Ind Trading & Dev
DE4338261A1 (de) * 1992-11-14 1994-05-19 Fichtel & Sachs Ag Lager, insbesondere für Ausrücksysteme von Reibungskupplungen
EP0773384A1 (fr) * 1995-11-09 1997-05-14 Skf France Flasque de protection pour roulement, roulement associé et procédé de fabrication d'une bague de roulement équipée d'un flasque de protection
EP0859161A1 (fr) * 1997-02-13 1998-08-19 Skf France Dispositif de manoeuvrre d'embrayage à organe élastique d'autoalignement
EP1489327A1 (fr) * 2003-06-18 2004-12-22 Aktiebolaget SKF Butée de débrayage et procédé de montage
DE102004034439A1 (de) * 2004-07-16 2006-02-02 Ina-Schaeffler Kg Kupplungsausrücklager
DE102005053612A1 (de) * 2005-11-10 2007-05-16 Schaeffler Kg Ausrücklager für eine Betätigungseinrichtung einer Schaltkupplung
WO2009027184A2 (fr) * 2007-08-28 2009-03-05 Schaeffler Kg Dispositif de retenue
WO2009074506A1 (fr) * 2007-12-12 2009-06-18 Schaeffler Kg Butée de débrayage

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3009702A1 (fr) 2014-10-13 2016-04-20 Aktiebolaget SKF Butée, dispositif de butée d'embrayage et véhicule automobile équipé d'un tel dispositif
US10030715B2 (en) 2014-10-13 2018-07-24 Aktiebolaget Skf Bearing, clutch bearing device and motor vehicle equipped with such a clutch bearing device

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