WO2008068122A1 - Embrayage de séparation pour une boîte de vitesses - Google Patents

Embrayage de séparation pour une boîte de vitesses Download PDF

Info

Publication number
WO2008068122A1
WO2008068122A1 PCT/EP2007/061967 EP2007061967W WO2008068122A1 WO 2008068122 A1 WO2008068122 A1 WO 2008068122A1 EP 2007061967 W EP2007061967 W EP 2007061967W WO 2008068122 A1 WO2008068122 A1 WO 2008068122A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
rolling elements
shift
clutch
hand
Prior art date
Application number
PCT/EP2007/061967
Other languages
German (de)
English (en)
Inventor
Ludwig Winkelmann
Steffen Dittmer
Rainer Eidloth
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 WO2008068122A1 publication Critical patent/WO2008068122A1/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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/34—Rollers; Needles
    • F16C33/36—Rollers; Needles with bearing-surfaces other than cylindrical, e.g. tapered; with grooves in the bearing surfaces
    • 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
    • F16C19/34—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 for both radial and axial load
    • F16C19/36—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 for both radial and axial load with a single row of rollers
    • 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
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • 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
    • F16D25/00—Fluid-actuated clutches
    • F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
    • F16D25/082—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation
    • F16D25/087—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation the clutch being actuated by the fluid-actuated member via a diaphragm spring or an equivalent array of levers
    • 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
    • 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
    • F16D2300/26—Cover or bell housings; Details or arrangements thereof

Definitions

  • the invention relates to a shift disconnect clutch for a manual transmission, comprising a circulating with the crankshaft of a drive motor, formed from a flywheel, a clutch cover, a pressure ring and a pressure spring loaded this assembly, further rotatably connected to a transmission input shaft, arranged between flywheel and thrust ring clutch disc , and to the transmission input shaft coaxial, axially displaceable actuator for lifting the pressure spring from the pressure ring, wherein between actuator and clutch cover on the one hand a support bearing and between the actuating element and pressure spring on the other hand, a release bearing is arranged, which are each designed as rolling bearings.
  • shift disconnect couplings are widely used in the automotive industry, wherein the actuator is, for example, mechanically via a foot pedal, hydraulically or electrically adjusted to open the clutch for a switching operation.
  • the support bearing forms the pivot bearing of the assembly described above with respect to the non-rotating actuator, while the release bearing is a connection between the non-rotating actuator and the generally formed as a diaphragm spring pressure spring.
  • Such a shift disconnect clutch is known for example from DE 101 38 722 A1.
  • Modern support bearings and release bearings are usually designed as constantly revolving ball bearings whose lubrication via a Greased warehouse arranged grease depot takes place. Since no lubrication possibility is provided for such bearings, thus the life of such bearings is mainly dependent on the size or the possible service life of the existing grease deposits within the camp.
  • the size of the grease deposit is determined by the free volume of the space between the bearing rings minus the occupied by the rolling elements and the bearing cage volume.
  • the available grease depot for the lubrication of the known bearings is therefore relatively small and can not be extended due to the already almost complete utilization of the available space without complex structural changes in the storage environment and / or the bearing dimensions. Also, an increase in the carrying capacity of the known bearings were set for the same reasons so far technical limits.
  • the invention has for its object to provide a shift disconnect coupling of the type mentioned in the preamble of the invention, which allows for the same load capacity smaller axial dimensions or at the same axial dimensions improved carrying capacity, and the grease depot can be increased compared to bearings of the same dimensions , whereby a longer life is achievable.
  • the invention is based on the finding that, in conventional ball bearings, the lateral spherical caps of the balls which do not support the ball treads touch, contribute to the bearing performance of the camp nothing, but rather restrict only the inner volume of the bearing and thus the size of the possible grease deposits, so that they can be omitted without affecting the bearing capacity of the camp.
  • the invention is therefore based on a gearshift clutch for a manual transmission, comprising a rotatable with the crankshaft of a drive motor, formed from a flywheel, a clutch cover, a pressure ring and a pressure spring loaded this assembly, further rotatably connected to a transmission input shaft, arranged between flywheel and thrust ring and clampable clutch disc, as well as a coaxial to the transmission input shaft, axially displaceable actuator for lifting the pressure spring from the pressure ring, between actuator and clutch cover on the one hand a support bearing and between the actuating element and pressure spring on the other hand, a release bearing is arranged, which are each designed as rolling bearings. It is provided according to the present invention that the rolling elements are formed at least of the support bearing as ball rollers with each symmetrically flattened from the spherical shape and arranged parallel to each other side surfaces.
  • the space obtained by the reduced width of the ball rollers is used for increasing the internal volume.
  • the inner volume of the bearing can be increased by the amount of volume of the falling ball caps, so that the bearing can accommodate a correspondingly larger amount of grease, whereby the life of the bearing is increased in a corresponding manner.
  • the space obtained by the reduced width of the ball rollers can also be used to reduce the bearing dimensions. This measure therefore allows a axial shortening of the bearing to the reduced compared to the spherical shape width of the rolling elements.
  • a further variant of the invention provides that the flattening of the rolling elements to ball rollers with the same axial width thereof can also be used to increase the ball roller diameter, i. a ball roller has a larger diameter at a diameter of a ball of the same width and thus a higher load capacity.
  • the support bearing is designed as an angular ball roller bearing so that it can absorb axial forces and radial forces.
  • the support bearing is designed as a double-row angular ball roller bearing, which can be realized because of the possibility of a shortened axial length an axially nevertheless compact bearing.
  • the rolling elements of the release bearing are formed as ball rollers with two symmetrically flattened from the spherical shape and arranged parallel to each other side surfaces.
  • the entire, consisting of support bearing and release bearing bearing group can be made very compact and thus adapt to the generally tight space conditions in switching disconnect couplings.
  • the release bearing is designed as an angular ball bearing, so that this, too, the axial reaction forces of the pressure spring and optionally radial forces, for example due to a radial axial offset between the clutch and the gearbox Be input shaft or because of not absolutely axial acting reaction forces of the pressure spring, can accommodate.
  • the rows of balls of a bearing are each guided in a window cage, wherein the voltage applied to the side surfaces longitudinal webs of the cage windows are formed spherically in a longitudinal section profile of the bearing.
  • a spherical profile cross-section contributes to the naturally occurring rolling movements of the rolling elements in the bearing operation is sufficient free space available and a function-disturbing forced operation of the rolling elements is avoided.
  • the voltage applied to the longitudinal webs of the cage window side surfaces of the ball rollers are formed spherically in a longitudinal section of the bearing, wherein the longitudinal webs of each cage window are then executed.
  • a compression spring can be clamped between the support bearing on the one hand and the release bearing, which biases the release bearing in the actuating direction.
  • FIG. 2a shows a partial longitudinal section through a shift disconnect clutch with a support bearing designed as a ball roller bearing
  • FIG. 2b shows a detail of the prior art shown in FIG. 1 in a scale which is the same as in FIG. 2a.
  • FIG. 3 shows a partial longitudinal section approximately corresponding to FIG. 2, each with a support bearing and release bearing constructed as a ball roller bearing,
  • Figure 4 shows an enlarged view of a partial longitudinal section approximately according to the figure 1 with a designed as a double-row ball roller bearing support bearings, and
  • Figure 5 in an enlarged view a partial longitudinal section approximately corresponding to Figure 4 with a designed as a double-row ball roller bearing support bearing and designed as a single-row ball roller bearing release bearing.
  • the shift disconnect clutch shown in Figure 1 essentially comprises a circulating with the crankshaft 2 of a drive motor, not shown, from a flywheel 4, a clutch cover 6, a pressure ring 8 and a burdening them, designed as a diaphragm spring pressure spring assembly 10, further comprising a transmission input shaft 12 rotationally connected, between flywheel 4 and pressure ring 8 arranged and clamped clutch disc 14, and a coaxial to the transmission input shaft 12, axially displaceable actuator 16 for lifting the An horrfe- 10 from the pressure ring 8, wherein between the non-rotating actuator 16 and the clutch cover 6 on the one hand Support bearing 18 and between the adjusting element 16 and the rotating pressure spring 10 on the other hand, a release bearing 20 is arranged.
  • the shift disconnect clutch is shown in the engaged state, in which the clutch linings 22 between the pressure ring 8 and flywheel 4 are clamped, so that a torque of the crankshaft 2 is transmitted to the transmission input shaft 12.
  • the actuator 16 is shifted in the figure 1 to the left, over the release bearing 20, the pressure spring 10 is lifted from the pressure ring 8, so that no torque is transmitted from the crankshaft 2 to the transmission input shaft 12 (see Figure 1, upper half) ,
  • the actuating element 16 is actuated hydraulically.
  • the supply of hydraulic fluid via a hydraulic connection 24th is actuated hydraulically.
  • the support bearing 18 and the release bearing 20 are each formed as conventional angular contact ball bearings with trained as solid balls rolling elements, which has the disadvantages described above in terms of axial length, the grease reservoir and the bearing capacity of the bearings.
  • Figure 2a shows a partial longitudinal section through a switching disconnect clutch approximately according to the figure 1, in which the present invention is realized.
  • the same components of Figure 1 are provided with the same reference numerals.
  • the shift disconnect clutch of Figure 2a differs from the shift disconnect clutch of Figure 1 substantially in the embodiment of the support bearing 26.
  • the rolling elements 28 are no longer formed as solid spheres det, but as spherical rollers with two symmetrically flattened from the spherical shape and parallel
  • the ball rollers preferably have an axial width b, which is about 15% to 20% less than a ball with the same diameter.
  • FIG. 2b shows, in an enlarged view, a conventional bearing arrangement according to FIG. 1, in which the rolling elements of the support bearing 18 are designed as solid balls.
  • the rolling bodies 28 of FIG. 2 a have a larger diameter compared to the balls of FIG. 2 b with essentially the same axial width b, so that they have a higher load capacity.
  • This compared to conventional balls of the same width enlarged diameter of the ball rollers can be up to 40% larger.
  • the inner volume of the support bearing 26 obtained by the omission of the ball caps is greater than that of the support bearing 18, so that a larger grease depot and thus a longer service life of the support bearing 26 is possible.
  • the space sealed off from the seals by the reduced width of the rolling elements 28 has been used on the one hand for increasing the internal volume, and on the other hand also for increasing the rolling element diameter. It can also be easily shown that with a design of the balls of the support bearing 18 as ball rollers with otherwise the same radius an axial shortening of the bearing is possible.
  • Figure 3 shows a partial longitudinal section approximately corresponding to Figure 2, but in addition to the support bearing 26 and the rolling elements 36 of the release bearing 38 are formed as ball rollers with two symmetrically flattened from the spherical shape and mutually parallel side surfaces. Also in this case, the space obtained by the reduced width of the rolling elements 36 space was used on the one hand for increasing the internal volume and on the other hand to increase the WälzMech devisr at substantially the same axial length of the bearing.
  • FIG. 4 shows a partial longitudinal section approximately according to FIG. 2a, but with the support bearing 42 being designed as a double-row angular ball roller bearing.
  • the rolling elements 44 and 46 are in turn formed as ball rollers with two symmetrically flattened from the spherical shape and arranged parallel to each other side surfaces and guided in window cages 48 and 50, respectively.
  • the support bearing 42 has a common for both rows of ball rollers outer ring 52 and two associated with the respective ball roller rows inner rings 54 and 56, which can be formed so that the two rows of ball rollers are biased axially against each other.
  • the larger axial width of the double-row bearing 42 compared to a single-row bearing can be at least partially compensated for by the fact that the rolling elements 44 and 46 have a smaller axial width at the same radius.
  • FIG. 5 shows an exemplary embodiment according to FIG. 4, in which, however, the rolling elements 58 of the release bearing 60 are designed as ball rollers with flattened side surfaces, so that here too the advantages described further above result.

Landscapes

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

Abstract

L'invention concerne un embrayage de séparation pour une boîte de vitesses, comprenant : une unité modulaire tournant avec le vilebrequin (2) d'un moteur d'entraînement et constituée d'un volant d'inertie (4), d'un couvercle d'embrayage (6), d'une bague de pression (8) et d'un ressort de pression (10) sollicitant cette bague ; un disque d'embrayage (14) disposé entre le volant d'inertie (4) et la bague de pression (8) et lié en rotation à un arbre d'entrée de boîte (12) ; et un élément d'actionnement (16) coaxial à l'arbre d'entrée de boîte et mobile en translation axiale, pour dégager le ressort de pression (10) de la bague de pression (8). Un palier porteur (18) est disposé entre l'élément d'actionnement (16) et le couvercle d'embrayage (6) d'une part, et un palier de débrayage (20) est disposé entre l'élément d'actionnement (16) et le ressort de pression (10) d'autre part, ces paliers étant respectivement réalisés sous forme de paliers à roulement. Les éléments roulants (28) au moins du palier porteur (18), mais éventuellement aussi du palier de débrayage (20), sont réalisés sous la forme de rouleaux sphériques pourvus chacun de deux faces latérales (30, 32) symétriquement aplaties par rapport à la forme sphérique et disposées parallèlement entre elles.
PCT/EP2007/061967 2006-12-06 2007-11-07 Embrayage de séparation pour une boîte de vitesses WO2008068122A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006057482.6 2006-12-06
DE102006057482A DE102006057482A1 (de) 2006-12-06 2006-12-06 Schalttrennkupplung für ein Schaltgetriebe

Publications (1)

Publication Number Publication Date
WO2008068122A1 true WO2008068122A1 (fr) 2008-06-12

Family

ID=38996761

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2007/061967 WO2008068122A1 (fr) 2006-12-06 2007-11-07 Embrayage de séparation pour une boîte de vitesses

Country Status (2)

Country Link
DE (1) DE102006057482A1 (fr)
WO (1) WO2008068122A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008141604A1 (fr) * 2007-05-18 2008-11-27 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Embrayage à friction
WO2013151800A1 (fr) * 2012-04-02 2013-10-10 Borgwarner Inc. Dispositif d'embrayage
US11333201B2 (en) * 2018-08-31 2022-05-17 Toyota Jidosha Kabushiki Kaisha Greasing device for clutch release mechanism

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009030972A1 (de) * 2008-07-14 2010-01-21 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Doppelkupplung
US8590685B2 (en) 2008-07-14 2013-11-26 Schaeffler Technologies AG & Co. KG Dual clutch
EP2310706B1 (fr) * 2008-07-14 2012-11-14 Schaeffler Technologies AG & Co. KG Embrayage double
FR3042465B1 (fr) * 2015-10-20 2018-08-10 Valeo Embrayages Kit d'assemblage d'un systeme d'embrayage, systeme d'embrayage et procede d'assemblage d'un systeme d'embrayage

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4334195A1 (de) * 1993-10-07 1994-03-24 Geuer Mann Ernst Radial-Wälzlager mit Kugelscheiben
GB2298682A (en) * 1995-03-10 1996-09-11 Torrington Co Ball bearing and bearing ball therefor
DE10138722A1 (de) * 2000-08-17 2002-02-28 Luk Lamellen & Kupplungsbau Antriebsstrang

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE431471C (de) * 1921-03-24 1926-07-07 Karl Oskar Leon Rollenlager
FR2082870A5 (fr) * 1970-03-31 1971-12-10 Ferodo Sa
JPH07317811A (ja) * 1994-05-23 1995-12-08 Hino Motors Ltd 自動クラッチ装置
DE102005014556A1 (de) * 2005-03-31 2006-10-05 Schaeffler Kg Radialwälzlager, insbesondere einreihiges Rillenkugellager

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4334195A1 (de) * 1993-10-07 1994-03-24 Geuer Mann Ernst Radial-Wälzlager mit Kugelscheiben
GB2298682A (en) * 1995-03-10 1996-09-11 Torrington Co Ball bearing and bearing ball therefor
DE10138722A1 (de) * 2000-08-17 2002-02-28 Luk Lamellen & Kupplungsbau Antriebsstrang

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008141604A1 (fr) * 2007-05-18 2008-11-27 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Embrayage à friction
DE112008001069B4 (de) * 2007-05-18 2018-01-25 Schaeffler Technologies AG & Co. KG Reibungskupplung
WO2013151800A1 (fr) * 2012-04-02 2013-10-10 Borgwarner Inc. Dispositif d'embrayage
US9670967B2 (en) 2012-04-02 2017-06-06 Borgwarner Inc. Clutch device for a drive train
US11333201B2 (en) * 2018-08-31 2022-05-17 Toyota Jidosha Kabushiki Kaisha Greasing device for clutch release mechanism

Also Published As

Publication number Publication date
DE102006057482A1 (de) 2008-06-12

Similar Documents

Publication Publication Date Title
DE102015201257B3 (de) Kugelgewindetrieb und zugehöriger elektromechanischer Aktuator
WO2008068122A1 (fr) Embrayage de séparation pour une boîte de vitesses
DE19580454C1 (de) Wälzlagereinheit mit einer Zentrierung und einem Flansch
DE19839481A1 (de) Verteilergetriebe für ein Kraftfahrzeug
EP2762285B1 (fr) Engrenage de bétonnière sur camion avec roulement asymétrique à rotule sur rouleaux supportant l'arbre de sortie
EP2513502A1 (fr) Système de paliers pour une chaîne cinématique d'une automobile
DE102007049982A1 (de) Wälzlager, insbesondere zur Lagerung eines Nutzfahrzeugrades
DE10150228B4 (de) Vorderachse eines Kraftfahrzeugs mit lenkbaren, angetriebenen oder nicht angetriebenen Rädern
DE102020131828B4 (de) Aktuator für eine Lenkeinrichtung eines Kraftfahrzeuges
WO2010049227A1 (fr) Palier à roulement, notamment palier de roue
DE102009014339A1 (de) Bremseinrichtung insbesondere für ein Kraftfahrzeug
WO2008071735A2 (fr) Palier de réglage
WO2004020856A1 (fr) Logement d'un arbre
WO2009059585A2 (fr) Montage d'une roue planétaire pour optimiser la répartition des charges
WO2020108684A1 (fr) Système de direction avec palier de pivotement
DE102020103422A1 (de) Planetenwälzgewindetrieb
EP1598574B1 (fr) Eléments d'appui
DE102015221556A1 (de) Planetenwälzgewindespindel (PWG) eines Aktors
WO2008068123A1 (fr) Palier de soutien d'une transmission à embrayage double
DE10311851B4 (de) Schwenklagerung
DE102006035163A1 (de) Schrägschulterlager, insbesondere Ausrücklager für eine in Kraftfahrzeugen eingesetzte Schalttrennkupplung
WO2021190685A1 (fr) Ensemble butée de débrayage
DE102020127289A1 (de) Wälzlageranordnung
DE10344804B4 (de) Schwenklagerung
WO2017067547A1 (fr) Palier de débrayage

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: 07822283

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 07822283

Country of ref document: EP

Kind code of ref document: A1