WO1996023984A1 - Ensemble butee de debrayage - Google Patents

Ensemble butee de debrayage Download PDF

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Publication number
WO1996023984A1
WO1996023984A1 PCT/EP1996/000311 EP9600311W WO9623984A1 WO 1996023984 A1 WO1996023984 A1 WO 1996023984A1 EP 9600311 W EP9600311 W EP 9600311W WO 9623984 A1 WO9623984 A1 WO 9623984A1
Authority
WO
WIPO (PCT)
Prior art keywords
release bearing
bearing according
ring
angle
plate spring
Prior art date
Application number
PCT/EP1996/000311
Other languages
German (de)
English (en)
Inventor
Bernhard KLÖPFER
Ludwig Winkelmann
Original Assignee
Ina Wälzlager 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 Ina Wälzlager Schaeffler Kg filed Critical Ina Wälzlager Schaeffler Kg
Priority to DE19680050D priority Critical patent/DE19680050D2/de
Priority to DE19680050A priority patent/DE19680050C1/de
Priority to BR9607006A priority patent/BR9607006A/pt
Publication of WO1996023984A1 publication Critical patent/WO1996023984A1/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
    • 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
    • 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
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/43—Clutches, e.g. disengaging bearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/06—Lubrication details not provided for in group F16D13/74

Definitions

  • the invention relates to a release bearing with an actuating device for disengaging a separating clutch, which is used in particular in vehicles and can be actuated hydraulically or mechanically, consisting, among other things, of a housing in which an actuating sleeve is guided in an axially displaceable manner and has a radially outwardly directed annular flange, which with its side facing the separating clutch serves to support the release bearing, the release bearing having a rotationally fixed outer ring and a rotatable inner ring, between which rolling elements are guided, and the outer ring being supported by a radially aligned shoulder, supported by a telier spring Ring flange abuts, while the inner ring bears directly or indirectly against the separating clutch via a radially aligned section.
  • a generic release bearing can be found in DE-A 43 27 879.
  • An insert plate which is largely overmolded with plastic, serves as reinforcement, with the exception of the contact area of the outer ring of the release bearing.
  • the angle disk used here is provided with a large number of recesses and projections in order to achieve a form-fitting connection with the plastic, which increases the manufacturing costs of the angle disk.
  • the known actuating sleeve requires a fixation of the angle plate during the plastic injection process of the actuating sleeve, which also affects the manufacturing costs adversely.
  • a release bearing is known in which an actuating sleeve is connected to a separate component, referred to as a board, on which a release bearing is supported.
  • a separate component referred to as a board
  • an angled disc spring is arranged between the actuating sleeve and the inner ring.
  • the object of the invention is to develop a release bearing using an alternative design, which:
  • Another object of the invention is:
  • the invention according to claim 1 provides an angle disk which has a radially outer bend which partially encompasses the ring flange of the actuating sleeve, as a result of which the angle disk is held in a form-fitting manner on the ring flange.
  • This training enables a simplified, inexpensive installation.
  • the design of the angle disk provides that it connects the entire contact area of the with the outer ring of the release bearing NEN approach in the area of the ring flange.
  • the angular disc fixed on the ring flange also has a radially inner section with an almost U-shaped cross-sectional profile, which has a free rim in the form of a ring flange which, in the installed state, engages around an inner end of the shoulder of the outer ring and which also supports the tel ⁇ spring used.
  • the design of the angle disk according to the invention enables a captive component assignment of the components joined together by the force of the plate spring and thus simplifies assembly.
  • the release bearing is supported indirectly via the shoulder of the outer ring on the sheet metal, in particular non-cutting, angled disc on the ring flange, the actuating sleeve made of plastic.
  • the inventive concept also represents a reduction in the number of components, due to the rim of the angled washer, which also serves to support the plate spring. Associated with this is also a reduction in the installation tolerances, which have an advantageous effect on the function and the service life of the release bearing.
  • the inventive concept according to claim 2 provides that after joining the components, the angle washer, the outer ring and the plate spring, the annular shoulder can be formed on the angle plate, which partially surrounds the plate spring and the shoulder of the outer ring.
  • the ring shoulder on the angle disk which is carried out without cutting, preferably by flanging, there is at the same time a desired prestressing of the telescopic spring with which it rests on the attachment of the outer ring.
  • the dimension of the axial spacing from the free board to the angle plate is greater than a sum of the wall thicknesses of the plate spring and the shoulder of the outer ring.
  • the plate spring is centered on the annular shoulder of the angle disk. This centering, for example formed by a circumferential projection, ensures a radially equally spaced contact point of the plate spring on the leg of the outer ring.
  • the release bearing including the plate spring and the angle disk, be designed as a pre-assemblable unit. This measure advantageously favors the cycle times of a complete release bearing unit and thus offers a cost advantage.
  • a closed plate spring is provided, the outer diameter of which corresponds to the pitch circle diameter of the rolling bodies in the installed state, ie. H. the outside diameter corresponds to the center of the rolling elements.
  • a geometrical assignment of the rolling bearing rings to the rolling elements is provided, which results in an osculation of> 53%.
  • the osculation which can also be referred to as the radius ratio, defines the curvature ratio between the outer ring and the rolling elements or between the inner ring and the rolling elements.
  • the osculation has a strong influence on the performance of the rolling bearing, in particular with regard to the static and dynamic basic load rating, the formation of the lubricating film, and the friction and wear.
  • the rolling bearing geometry of the release bearing according to the invention also claims a contact angle of ⁇ 45 °.
  • the contact angle also called the contact angle, is the angle that results between the connecting line through the contact points of a rolling bearing with the raceways and a radial direction.
  • a contact angle of> 45 ° is claimed, which occurs under a load and the associated deformation of the rolling bearing. The angle value thus corresponds to the actual contact angle.
  • the constructive configurations claimed in claims 13 and 14 also relate to measures which have an adverse dust or Reduce contamination in the rolling bearing raceway and thus have a positive effect on the service life of the rolling bearing.
  • the rotating inner ring is provided at the end with a radially inwardly directed tear-off edge, as a result of which contaminations reaching the inner ring cannot be conveyed further due to the protruding tear-off edge which forms a zone of lower peripheral speed.
  • a circumferential groove is arranged on the inner ring at the radially outward end, which prevents or reduces a loss of lubricant which can occur when the release bearing is heated at a standstill.
  • the features claimed in claims 13 and 14 are jointly attached to an inner ring.
  • the inventive concept according to claim 15 provides for the arrangement of a sealing ring for effectively sealing an annular gap between the actuating sleeve and the rotating inner ring.
  • a sealing ring fixed to the actuating sleeve is provided, the sealing lip of which bears against the inner ring under a prestress.
  • a lubricant reservoir is provided in the roller bearing according to claim 16, from which a specific lubrication is ensured which is sufficient over the service life of the roller bearing and which, for. B. is adapted to the life of the vehicle in which the release bearing is installed.
  • lubricant from the lubricant reservoir which is preferably arranged on the non-rotating roller bearing ring, reaches the roller bodies or the roller bearing raceway via a metering agent.
  • a dosing agent is, for example, a wick or, alternatively, any other agent which exerts a capillary action and which supplies the lubricant bearings with an amount of lubricant which is tailored to the requirements.
  • a high-strength, dimensionally stable and temperature-resistant plastic is provided as the material for the actuating sleeve, in particular PA 66 GF, which can also be provided with reinforcement to achieve improved strength.
  • the embodiment of the invention according to claim 18 provides ventilation bores arranged circumferentially distributed in the ring flange of the actuating sleeve, which allow an air flow to escape, which is triggered by the bearing ring configuration of the release bearing and which has a suction effect.
  • the advantageous derivation of the air flow occurring through the ring flange prevents disadvantageous entry of dirt particles into the rolling bearing.
  • Figure 1 in a half section an inventive release bearing in connection with an actuating sleeve
  • Figure 2 shows a plate spring according to the invention in a longitudinal section
  • FIG. 1 force-displacement diagram of the plate spring according to the invention.
  • FIG 1 shows an actuating device in half section, which comprises an actuating sleeve 2 and a release bearing 3.
  • the actuating device 1 is part of a mechanically or hydraulically actuatable device of a separating clutch, which is not shown in more detail, and which is inserted between an internal combustion engine and a manual transmission in vehicles.
  • the annular piston 2 is axially displaceably guided on a drive shaft, which is not shown in FIG. 1, and is connected indirectly or directly via an end face 4 to a component that can be acted upon mechanically or hydraulically.
  • the actuating sleeve 2 is connected in one piece to an annular flange 5 which is arranged offset to the center of the actuating sleeve 2 and directed towards the end face 4.
  • the release bearing 3 is axially supported on the ring flange 5 via an outer ring 6, the right-angled radial projection of the leg 7 abuts the entire surface of an angle disk 8 which is inserted between the ring flange 5 and the leg 6.
  • the outer ring 6 is supported by a plate spring 12 on the shoulder 7 non-positively on the angle plate 8. Inside the plate spring 12 is supported on a board 13 which is axially spaced from the longer board of the angle plate 8.
  • the formation of the rim 13 is carried out after a pre-assembly, in which the components, the angle plate 8, the leg 7 and the plate spring 12 are first joined together by a flange which surrounds the plate spring 12 in a radially outward direction.
  • the shaping results in a deliberate preloaded installation of the plate spring 12.
  • the axial spacing of the two legs of the angle plate 8 is greater than the addition of the wall thicknesses of the plate spring 12 and the shoulder 7.
  • a right-angled bend 14 which preferably partially locks into corresponding recesses on the ring flange 5.
  • a snapping between the angle plate 8 and the ring flange 5 is also possible.
  • the annular flange 5 is furthermore provided with circumferentially distributed, axially introduced ventilation bores 15 which open into a circumferential groove 29 made in the annular flange 5, and which correspond or interact with bores 16 or openings 17 in the angle disk 8 and which ensure the discharge of an air flow that arises due to the configuration of the release bearing 3.
  • This air flow which disadvantageously carries dirt particles, is thus effectively discharged and does not get into the release bearing 3.
  • the inner ring 10 is brought to the plate spring 12 while maintaining a limited gap dimension 18 .
  • the inner ring 10 is also provided at the end with a radially inwardly directed tear-off edge 19 which defines a zone of low circumferential Forms initial speed and prevents further conveyance of dirt particles that abut the inner ring 10 on the inside.
  • the inner ring 10 On the radially outward side, the inner ring 10 has a circumferential groove 20 which prevents lubricant outflow when the release bearing 3 is stationary and at rest.
  • a sealing ring 23 is provided on the end face 22 of the actuating sleeve 2, which effectively seals the annular gap 21 via a sealing lip 24 which is biased against the leg 11 of the inner ring 10.
  • Another seal 25 is attached to the outer ring 6, the sealing lip 26 abuts the inner ring 10. Also attached to the seal 25 on the outer ring 6, a lubricant reservoir 27 is provided, from which a precisely metered amount of lubricant is fed to the rolling element 9 and / or the rolling element raceway via a dosing means 28, for example a wick.
  • a dosing means 28 for example a wick.
  • the release bearing 3 is designed so that a pressure angle of a ⁇ 45 ° is established under load.
  • osculation i.e. H. a radius ratio is provided in which the radii between the outer ring 6 and the rolling elements 9 or the inner ring 10 and the rolling elements 9 of> 53%.
  • FIG. 2 shows the disc spring 12 designed according to the invention in a half section, which is designed taking into account the following dimensioning ranges:
  • the diaphragm spring 12 can be designed taking into account one of these previously specified relationships or by a combination of the two dimensional ranges according to the invention in order to achieve a desired characteristic curve of spring force / spring travel, such as that of characteristic "B" corresponds to Figure 3.
  • FIG. 3 the course of the characteristic curve of previous leaf springs of release bearings is compared with a plate spring according to the invention in a diagram.
  • the spring force "F” is plotted on the ordinate and the spring travel “f” on the abscissa.
  • the characteristic curve “A” shows the force-spring curve of previous cup springs and illustrates a relatively small spring travel “f A " between the spring forces "Fmin” and “Fmax”.
  • the characteristic curve “B” of the disc spring according to the invention shows a clear increase in the spring travel "f B " (see identification).
  • the disc spring 12 according to the invention then has a significantly higher value, which is particularly necessary for effective tolerance compensation and secure non-positive contact of the outer ring 6 on the angle disk 8 or the ring flange 5.

Landscapes

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

Abstract

La présente invention concerne une butée de débrayage, pourvue d'un dispositif d'actionnement servant à désengager un embrayage, en particulier utilisé dans des véhicules et à commande mécanique ou hydraulique. Elle est constituée notamment par un carter dans lequel un manchon d'actionnement (2), qui peut être déplacé axialement, présente une bride annulaire (5) sur laquelle une butée de débrayage (3) s'appuie indirectement. Cette dernière possède une bague extérieure (6) fixe en rotation et une bague intérieure (10) pouvant tourner, entre lesquelles se trouvent des corps de roulement (9), et la bague extérieure (6) s'appuie avec transmission des forces par friction, par une collerette (7), sur un disque en équerre (8) dont la position est fixe sur la bride annulaire (5). Selon l'invention, le disque en équerre (8) présente un rebord (14) extérieur chanfreiné radialement, qui entoure partiellement la bride annulaire (5) en la serrant, et une partie radialement intérieure, en forme de U, et cette partie intérieure forme, à son extrémité libre, une bordure (13) qui entoure une extrémité intérieure de la collerette (7) en la serrant et sur laquelle s'appuie une rondelle élastique (12).
PCT/EP1996/000311 1995-02-02 1996-01-26 Ensemble butee de debrayage WO1996023984A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE19680050D DE19680050D2 (de) 1995-02-02 1996-01-26 Kupplungsausrücklagereinheit
DE19680050A DE19680050C1 (de) 1995-02-02 1996-01-26 Kupplungsausrücklagereinheit
BR9607006A BR9607006A (pt) 1995-02-02 1996-01-26 Mancal de desengatar para um dispositívo de acionamento hidráulico de uma embreagem de separação

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19503218A DE19503218A1 (de) 1995-02-02 1995-02-02 Ausrücklager für eine hydraulische Betätigungsvorrichtung einer Trennkupplung
DE19503218.7 1995-02-02

Publications (1)

Publication Number Publication Date
WO1996023984A1 true WO1996023984A1 (fr) 1996-08-08

Family

ID=7752889

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1996/000311 WO1996023984A1 (fr) 1995-02-02 1996-01-26 Ensemble butee de debrayage

Country Status (4)

Country Link
KR (1) KR100357424B1 (fr)
BR (1) BR9607006A (fr)
DE (3) DE19503218A1 (fr)
WO (1) WO1996023984A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011050709A1 (de) 2011-05-30 2012-12-06 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Ausrückeinrichtung zum Betätigen einer Trennkupplung

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2748536B1 (fr) * 1996-05-09 1998-07-03 Skf France Dispositif de butee d'embrayage a rondelle elastique
DE19709056B4 (de) * 1997-03-06 2006-01-26 Ina-Schaeffler Kg Abdichtung für ein Kupplungsausrücklager
DE10118095B4 (de) * 2001-04-11 2009-10-01 Schaeffler Kg Abdichtung für ein Ausrücklager
DE10118365B4 (de) * 2001-04-12 2009-11-12 Schaeffler Kg Ausrücklager
DE102014226299B3 (de) * 2014-12-17 2015-10-15 Schaeffler Technologies AG & Co. KG Nehmerzylinder mit Transportsicherung sowie Verfahren zur Fixierung eines Kolbens an einem Ausrücklager
KR102245174B1 (ko) * 2019-05-31 2021-04-26 주식회사평화발레오 클러치의 릴리즈 베어링 조립체

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2514447A3 (fr) * 1981-10-09 1983-04-15 Riv Officine Di Villar Perosa Manchon d'auto-centrage pour la commande d'un embrayage a friction
US4561788A (en) * 1984-10-04 1985-12-31 Nippon Seiko Kabushiki Kaisha Clutch release bearing device
DE4327879A1 (de) * 1993-08-19 1995-02-23 Schaeffler Waelzlager Kg Schiebehülse für ein Kupplungsausrücklager

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2347571A1 (de) * 1973-09-21 1975-04-10 Herbert Hess Verbundelement fuer den hochbau
IT1084610B (it) * 1976-04-10 1985-05-25 Skf Kugellagerfabriken Gmbh Dispositivo distacco frizione.
DE3446328A1 (de) * 1984-12-19 1986-07-10 Anschuetz & Co Gmbh Mit einer umlaufschmierung ausgeruestetes lager
JPS6366629U (fr) * 1986-10-21 1988-05-06
FR2669980B1 (fr) * 1990-11-30 1993-01-22 Valeo Butee de debrayage a rondelle elastique externe, notamment pour vehicules automobiles.
DE9313557U1 (de) * 1993-09-08 1993-10-28 INA Wälzlager Schaeffler KG, 91074 Herzogenaurach Ausrückvorrichtung für eine Reibungsklupplung

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2514447A3 (fr) * 1981-10-09 1983-04-15 Riv Officine Di Villar Perosa Manchon d'auto-centrage pour la commande d'un embrayage a friction
US4561788A (en) * 1984-10-04 1985-12-31 Nippon Seiko Kabushiki Kaisha Clutch release bearing device
DE4327879A1 (de) * 1993-08-19 1995-02-23 Schaeffler Waelzlager Kg Schiebehülse für ein Kupplungsausrücklager

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011050709A1 (de) 2011-05-30 2012-12-06 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Ausrückeinrichtung zum Betätigen einer Trennkupplung

Also Published As

Publication number Publication date
BR9607006A (pt) 1997-10-28
DE19503218A1 (de) 1996-08-08
KR100357424B1 (ko) 2003-08-21
DE19680050D2 (de) 1998-04-16
DE19680050C1 (de) 2002-10-10
KR19980701783A (ko) 1998-06-25

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