WO2010130536A1 - Palier d'actionnement d'embrayage, notamment pour un système à double embrayage - Google Patents

Palier d'actionnement d'embrayage, notamment pour un système à double embrayage Download PDF

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Publication number
WO2010130536A1
WO2010130536A1 PCT/EP2010/055231 EP2010055231W WO2010130536A1 WO 2010130536 A1 WO2010130536 A1 WO 2010130536A1 EP 2010055231 W EP2010055231 W EP 2010055231W WO 2010130536 A1 WO2010130536 A1 WO 2010130536A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
ring
outer ring
clutch
clutch actuating
Prior art date
Application number
PCT/EP2010/055231
Other languages
German (de)
English (en)
Inventor
Norbert Radinger
Tomas Smetana
Original Assignee
Schaeffler Technologies Gmbh & Co. 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 Technologies Gmbh & Co. Kg filed Critical Schaeffler Technologies Gmbh & Co. Kg
Priority to EP10717097A priority Critical patent/EP2430326A1/fr
Priority to DE112010001978T priority patent/DE112010001978A5/de
Priority to CN201080020363.1A priority patent/CN102422038B/zh
Publication of WO2010130536A1 publication Critical patent/WO2010130536A1/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
    • F16C33/72—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
    • 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
    • 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
    • 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 actuation bearing as such serves to set the engagement state of the clutch system by adjusting its axial position relative to an associated clutch system.
  • the invention is directed to an engagement bearing as such serves to initiate a provided for bringing about a clutch engagement state axial force in a clutch system.
  • a clutch actuating bearing in the form of a release bearing which is arranged concentrically to a transmission main shaft and in the axial direction of the same displaced. With appropriate axial load of the clutch actuation bearing, the bearing can be spent in a disengaged position and thereby cancel the engaged state of an associated clutch system.
  • the clutch actuating bearing comprises a bearing inner ring and a bearing outer ring. On the bearing inner ring, a ring element is placed which forms a radially outwardly penetrating radial flange. Between this radial flange and the inner wall of the bearing outer ring a sealing gap is formed.
  • elastomer seals are also used in clutch actuation bearings. These elastomer seals are characterized by a high sealing effect. Due to the frictional contact of the sealing lips with the associated running surfaces, the result is opposite However, contactless seals typically result in a somewhat higher level of friction that leads to heating of the bearing.
  • the invention has for its object to provide a clutch actuation bearing which is relatively inexpensive to produce from a manufacturing point of view, and which is characterized in addition to a high Schmierstoff Weghaltewir- kung also by a low bearing friction.
  • a clutch actuating bearing with a bearing inner ring, a bearing outer ring, and rolling elements which are accommodated in a defined between the two bearing rings track space and support the two bearing rings against each other, wherein this clutch actuating bearing is characterized in that attached to the bearing inner ring, a first ring element is the one to the inner wall of the bearing outer ring cone-like penetrating skirt portion, and that in the bearing outer ring, a second ring member is inserted, which forms an inwardly penetrating annular jacket which extends leaving a sealing gap along a rolling body facing away from the outside of the conical surface portion.
  • Figure 1 is an axial sectional view illustrating the construction of a erfindunmultien clutch actuation bearing for a dual-clutch transmission
  • Figure 2 is a detailed view illustrating further constructive details of the clutch actuation bearing according to the invention, as well as the achieved here lubricant retention effect.
  • the inventive clutch actuating bearing shown in Figure 1 comprises a bearing inner ring 1, a bearing outer ring 2, and rolling elements 3 are taken in a defined between the two bearing rings 1, 2 track space and support the two bearing rings 1, 2 in the manner of an angular contact ball bearing against each other ,
  • the bearing outer ring 2 is provided in its coupling device (not shown) facing the end region with a ring flange 2a which serves as such the initiation of the bearing actuation forces in the bearing outer ring 2.
  • the clutch actuation bearing according to the invention is characterized in that a first ring element 4 is attached to the bearing inner ring 1 which has a protruding to the inner wall of the bearing outer ring 2 conical surface portion 4a, and that the bearing outer ring 2, a second ring element 5 is attached, which is an inwardly penetrating annular jacket 5a forms which extends while leaving a sealing gap S along a side facing away from the rolling elements 3 outside of the conical surface portion 4a.
  • the sealing gap S is designed in such a way that its gap width measured parallel to the bearing axis is somewhat smaller in the inner region than in the middle and in the outer region.
  • the mutually facing and the sealing gap space defining lateral surfaces of the two ring elements 4, 5 do not extend to each other so far equidistant.
  • the first ring element 4 further has a sleeve section 4b, which adjoins the outer edge region of the conical surface section 4a.
  • the sleeve portion 4b is designed such that it also forms a running gap together with the inner wall of the bearing outer ring 2.
  • the first ring element 4 furthermore has a press ring section 4d on which the geometry of a seat section provided by the bearing inner ring 1 is matched such that the first ring element 4 is anchored there under a relatively high load-bearing press fit. It is possible to realize in the joining region of these two components 1, 4 also other geometries by which, for example, a positive securing of the first ring member 4 is achieved on the bearing inner ring 1.
  • the bearing inner ring 1 is seated in an encompassed from the bearing outer ring 2 axial region.
  • the bearing inner ring 1 forms a Kalotten preparation in the region of its inner peripheral surface 1 a.
  • a compensation ring 9 is supported on this Kalotten scanning .
  • That compensation ring 9 in turn supports a pressure ring 10.
  • the pressure ring 10 serves to initiate the guided over the bearing actuation force in a not-shown here coupling system.
  • the Aufschub termee the first ring member 4 is fixed to the bearing inner ring 1 by a radially retracted ring land 4c.
  • the first ring element 4 is dimensioned such that this encompasses almost the entire between the front bearing ring end face 1 a and the rolling elements 3 extending axial region of the bearing inner ring 1.
  • the sleeve section 4b of the first ring element 4 forms a lubricant retention space R.sub.s which is largely sealed off from the adjoining wall region of the bearing outer ring 2.
  • lubricant would first have to advance to the rolling elements 3 and then into the circumferential ring gap between the sleeve section 4b of the first ring element 4 and the inner peripheral wall of the bearing outer ring 2 penetrate.
  • this circumferential annular gap prevails lubricant backpressure which builds up in the cone shell-like gap space S by lubricant shear stress, as well as by centrifugal force.
  • the second ring element 5 is axially secured to the bearing outer ring 2.
  • a securing groove 2b is formed in the bearing outer ring 2.
  • An outer annular jacket section 5b of the second annular element 5 is seated in this securing groove 2b.
  • a plurality of notches 5c are formed which, as such, subdivide the annular jacket section 5b into a plurality of segments. These segments can compress radially during assembly of the second ring element 5 and snap in Eich the desired position of the ring element in the securing groove 2b a.
  • the clear width ta, tb of the gap areas adjoining the conical surface section 4a and the sleeve section 4b is preferably in the range from 0.2 to 0.8 mm.
  • the ring elements 4, 5 shown here are made of a high-strength material, in particular steel. It is also possible to manufacture these components from high-strength plastic material, or in particular as metal Perform plastic composite components. Insofar as the bearing is designed essentially only for one direction of rotation, it is possible to provide additional lubricant-retaining structures such as spiral grooves in the region of the gaps.

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 d'actionnement d'embrayage. Selon l'invention, un premier élément annulaire est fixé sur une bague interne de palier et présente une section d'aire latérale de cône faisant saillie vers la paroi interne de la bague externe de palier. Un deuxième élément annulaire est fixé sur la bague externe de palier et forme une surface latérale annulaire en saillie vers l'intérieur, ladite surface latérale s'étendant, sous sollicitation d'une fente d'étanchéité, le long de la surface extérieure de la section surface latérale de cône, ladite surface extérieure étant opposée aux corps roulants.
PCT/EP2010/055231 2009-05-12 2010-04-21 Palier d'actionnement d'embrayage, notamment pour un système à double embrayage WO2010130536A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP10717097A EP2430326A1 (fr) 2009-05-12 2010-04-21 Palier d'actionnement d'embrayage, notamment pour un système à double embrayage
DE112010001978T DE112010001978A5 (de) 2009-05-12 2010-04-21 Kupplungsbetätigungslager, insbesondere für ein Doppelkupplungssystem
CN201080020363.1A CN102422038B (zh) 2009-05-12 2010-04-21 离合器操作轴承、尤其用于双离合器系统的离合器操作轴承

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009020861.5 2009-05-12
DE102009020861A DE102009020861A1 (de) 2009-05-12 2009-05-12 Kupplungsbetätigungslager, insbesondere für ein Doppelkupplungssystem

Publications (1)

Publication Number Publication Date
WO2010130536A1 true WO2010130536A1 (fr) 2010-11-18

Family

ID=42308368

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2010/055231 WO2010130536A1 (fr) 2009-05-12 2010-04-21 Palier d'actionnement d'embrayage, notamment pour un système à double embrayage

Country Status (4)

Country Link
EP (1) EP2430326A1 (fr)
CN (1) CN102422038B (fr)
DE (2) DE102009020861A1 (fr)
WO (1) WO2010130536A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20220144069A1 (en) * 2019-03-05 2022-05-12 Zf Friedrichshafen Ag Clutch Assembly, Motor Vehicle Powertrain, and Method for Operating a Powertrain

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10619674B1 (en) * 2019-01-14 2020-04-14 Aktiebolaget Skf Bearing assembly

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2190213A5 (fr) * 1972-06-24 1974-01-25 Fichtel & Sachs Ag
JPS5032451U (fr) * 1973-07-20 1975-04-09
DE19933634A1 (de) * 1999-07-17 2001-01-18 Schaeffler Waelzlager Ohg Dichtfederscheibe für ein Kupplungs-Ausrücklager
JP2001311437A (ja) * 2000-04-28 2001-11-09 Koyo Seiko Co Ltd クラッチレリーズ軸受
DE19912432B4 (de) 1998-03-20 2008-05-15 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Ausrücklager
JP2008232405A (ja) * 2007-03-23 2008-10-02 Jtekt Corp クラッチレリーズ軸受

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2190213A5 (fr) * 1972-06-24 1974-01-25 Fichtel & Sachs Ag
JPS5032451U (fr) * 1973-07-20 1975-04-09
DE19912432B4 (de) 1998-03-20 2008-05-15 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Ausrücklager
DE19933634A1 (de) * 1999-07-17 2001-01-18 Schaeffler Waelzlager Ohg Dichtfederscheibe für ein Kupplungs-Ausrücklager
JP2001311437A (ja) * 2000-04-28 2001-11-09 Koyo Seiko Co Ltd クラッチレリーズ軸受
JP2008232405A (ja) * 2007-03-23 2008-10-02 Jtekt Corp クラッチレリーズ軸受

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20220144069A1 (en) * 2019-03-05 2022-05-12 Zf Friedrichshafen Ag Clutch Assembly, Motor Vehicle Powertrain, and Method for Operating a Powertrain

Also Published As

Publication number Publication date
CN102422038A (zh) 2012-04-18
EP2430326A1 (fr) 2012-03-21
DE102009020861A1 (de) 2010-11-18
DE112010001978A5 (de) 2012-09-13
CN102422038B (zh) 2014-07-23

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