WO2012110123A1 - Ensemble palier destiné à actionner un embrayage - Google Patents

Ensemble palier destiné à actionner un embrayage Download PDF

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Publication number
WO2012110123A1
WO2012110123A1 PCT/EP2011/070336 EP2011070336W WO2012110123A1 WO 2012110123 A1 WO2012110123 A1 WO 2012110123A1 EP 2011070336 W EP2011070336 W EP 2011070336W WO 2012110123 A1 WO2012110123 A1 WO 2012110123A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
ratio
bearing arrangement
clutch
arrangement according
Prior art date
Application number
PCT/EP2011/070336
Other languages
German (de)
English (en)
Inventor
Ernst Masur
Etienne Rueff
Georg Von Petery
Original Assignee
Schaeffler Technologies AG & 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 AG & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Publication of WO2012110123A1 publication Critical patent/WO2012110123A1/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
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • 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
    • F16D2300/12—Mounting or assembling

Definitions

  • the invention relates to a bearing arrangement for actuating a clutch, comprising a release bearing axially movable for engagement and disengagement of the clutch, and an axially fixed support bearing comprising an inner or outer ring with rolling bodies running therebetween.
  • Bearing arrangements of the type described are used in the field of single or double clutches or corresponding hybrid systems.
  • the actually disengaging or retracting operation of the downstream clutch is obtained via the axially movable release bearing.
  • the inner ring of the axially movable release bearing with corresponding actuating levers of a diaphragm spring or the like which are pivotally mounted in the clutch housing connected.
  • To disengage the release bearing is moved against the actuating lever, so that they pivot about a pivot bearing, over which the force acting on a pressure plate of a clutch disc axial forces are reduced, so that the tension of the clutch disc reduced to a these opposing second clutch disc and consequently the clutch is disengaged.
  • the engagement process is carried out in the reverse manner, namely, when the release bearing is moved back in the opposite direction, so that the operating lever of the clutch disc are relieved and swing back due to their spring properties, so that the clutch disc again in solid, frictional engagement with the opposing second Clutch disc is brought.
  • the release bearing is arranged for this purpose in a conventional manner on a corresponding axially movable guided sleeve, which in turn is coupled with an actuating mechanism, via which the axial movement can be initiated.
  • the support bearing is usually a combined radial and thrust bearing, which is supported bearing arrangement with its inner ring, while it is radially held in the mounting position with its outer ring on a suitable housing member of the coupling and axially fixed by a suitable collar or circlips, etc., wherein the Arrangement can also be reversed.
  • this support bearing with its both radial and in particular also axia- len support, which is ultimately connected between the actual coupling device on the one hand and the associated actuator, namely the disengagement device with the bearing assembly according to the invention on the other hand, avoids that axial forces on the coupled shafts, in particular the Crankshaft, which is connected to the clutch, act, which can load their bearings.
  • the arrangement of the release bearing and the support bearing is usually such that both are arranged axially offset. This results in a considerable axial space, which requires the bearing assembly in the installation situation, but which is not always given due to the increasing compaction.
  • the invention is therefore based on the problem of specifying a bearing arrangement of the type mentioned, which is improved in terms of the required axial space.
  • a bearing assembly of the type described above that the release bearing and the support bearing are coaxially arranged one inside the other, wherein the pitch circle diameter Tk of the support bearing on which the rolling elements are, and the rolling element diameter dw are selected such that a ratio Tk / dw> 8 is given.
  • a coaxially nested construction in which the release bearing is arranged coaxially in the support bearing located radially further outward. This results in that the axial length can be considerably reduced, since in the end ultimately hardly an axial offset is given, but both are coaxial with each other.
  • the inner diameter of the inner ring of the angular contact ball bearing is to be chosen as small as possible, so that a radially as compact as possible coaxial arrangement relative to the inner release bearing results in the diameter of the component on which the inner ring is supported.
  • This is advantageous in that, in addition, the radial installation space can additionally be kept very small.
  • the invention proposes to optimize the dimensioning of the support bearing with respect to the ratio of the pitch diameter to Wälz analyses to Wälz analyses bemesser, namely to the effect that the Wälz phenomena bemesser is chosen as small as possible, so that a ratio of the pitch circle diameter to Wälz phenomena bemesser, ie Tk / dw> 8, preferably even Tk / dw> 10.
  • the ratio Tk / dw should be ⁇ 16.5. Due to the coaxial nesting arrangement of the two bearings, the pitch circle diameter of the support bearing inevitably increases, it is, based on conventional dimensions of the release bearing arranged in the support bearing> 72.5 mm.
  • Too large a radial structure is now counteracted according to the invention by a reduction of the WälzMechix devises, wherein the WälzSystem bemesser is chosen so that adjusts a value corresponding to the above-described ratio. This means that due to the reduction of the rolling body diameter, compared to conventional bearing designs, can achieve a radial space reduction.
  • the width b of the outer ring of the support bearing is selected such that a ratio between the width b and the rolling element diameter dw to b / dw ⁇ 2 , 5, preferably with b / dw ⁇ 2.3.
  • the width of the outer ring ie its axial dimension, is also reduced or adapted to the rolling element diameter, so that the ratio described above results. This leads to a very narrow structure.
  • the ratio b / dw should be> 1.5.
  • the pitch circle diameter Tk, the rolling body diameter dw and the width b to be selected such that the overall result is a design ratio Tk » dw / b> 35, preferably> 37.
  • This design ratio is a measure of the radial and axial structure of a bearing.
  • a generally suitable size ratio for a suitable bearing arrangement structure can be specified overall.
  • the design ratio Tk » dw / b should be ⁇ 65.
  • the support bearing has a total of a relatively small volume, equivalent to a small volume to Ingestion of lubricant needed to provide good lubrication.
  • the support bearing is sealed on both sides via a respective sealing ring.
  • an expedient development of the invention provides for a lubricant groove to be provided on the inner ring and / or outer ring of the support bearing adjacent to the respective rolling body running surface, ie that the volume is structurally enlarged via the one or the two lubricant grooves, so that despite an extremely narrow bearing a sufficient Lubricant volume for receiving the lubricant is available.
  • the bearing in which the rolling elements are preferably accommodated in a plastic cage, which is guided on the rolling body or on board depending on the load requirement, is sealed off via the sealing rings.
  • the seals are designed to be friction-optimized. h., That both the sealing ring geometry and the material used is chosen to cause the lowest possible friction.
  • one or more vent grooves are provided on the respective sealing ring or in the outer or inner ring. These are used for venting and thus for pressure equalization, so that the contact pressure of the sealing lips is almost constant under all operating conditions.
  • Figure 1 is a schematic representation in section of a bearing assembly according to the invention
  • Figure 2 is a sectional view of a usable for a bearing assembly according to the invention bearing support of a first embodiment;
  • Figure 3 is an enlarged detail sectional view of the support bearing of Figure 2;
  • Figure 4 is a sectional view of a usable for a bearing assembly according to the invention bearing support of a second embodiment
  • Figure 5 is an enlarged detail sectional view of the support bearing of Figure 4.
  • Figure 6 is a sectional view of a usable for a bearing assembly according to the invention bearing support of a third embodiment
  • Figure 7 is an enlarged detail sectional view of the support bearing of Figure 6;
  • Figure 1 shows a schematic diagram of a bearing assembly 1 according to the invention in the assembly position, ie in the Verbausituation in the region of a coupling 2, which is shown here only partially.
  • the coupling can be a single or double disc clutch or a hybrid system.
  • the bearing arrangement comprises on the one hand a release bearing 3, which is designed as an angular contact ball bearing and is arranged on a release sleeve 4, which is axially movable in a conventional manner, when a corresponding, not shown here closer actuator is actuated.
  • a release bearing 3 which is designed as an angular contact ball bearing and is arranged on a release sleeve 4, which is axially movable in a conventional manner, when a corresponding, not shown here closer actuator is actuated.
  • the clutch is disengaged and engaged.
  • the release bearing 3 has in known manner an inner ring 5 and an outer ring 6, between which rolling elements, here balls 7, run.
  • the inner ring 5 is mounted via an annular flange 8 in a conventional manner against actuating lever 9 of a diaphragm spring or the like of the clutch 2, which actuating lever 9 for disengaging the clutch, so if the release bearing 5 is moved to the left according to Figure 1, so that the actuating levers 9 associated clutch disc that the actuating levers 9 associated clutch disc is axially relieved and thus the clutch is opened.
  • the engagement or closing of the clutch takes place.
  • the bearing assembly 1 further comprises an annular support member 10 to which a support bearing 1 1, here in the form of a ball bearing, is arranged with its inner ring 12.
  • the support bearing 1 1 further comprises in known manner an outer ring 13 and between the rings rolling elements in the form of balls 14.
  • the outer ring 13 is supported on a housing member 15 of the coupling 2, both axially and radially.
  • the support bearing 1 1 with respect to the parameters pitch circle diameter Tk and rolling element diameter dw designed such that preferably results in a ratio of Tk / dw of> 10 and preferably ⁇ 16.5. Because due to the coaxial nesting of the two bearings 3 and 1 1 inevitably results in that the pitch circle diameter Tk of the support bearing 1 1, compared with previous axially offset bearing assemblies, increases. The counteracting the reduction of the Wälz stresses, thus the use of relatively small balls 13, wherein the diameter of the balls is chosen so that the ratio Tk / dw> 10 and ⁇ 16.5.
  • the outer ring is preferably chosen in its thickness so that it is as thin as possible, of course, taking into account the required strength properties. Furthermore, it is provided in the bearing assembly 1 according to the invention, to choose the width b of the outer ring 13 as small as possible, so that the support bearing 1 1 is as narrow as possible and is axially gar reckond.
  • the width b of the outer ring is chosen in relation to the rolling element diameter dw, in such a way that there is a ratio between the width b and the rolling element diameter dw, which is ⁇ 2.5, preferably ⁇ 2.3, and preferably> 1.5.
  • the parameters pitch circle diameter Tk, rolling body diameter dw and width b are to be selected such that they give a design ratio Tk » dw / b of preferably> 37 and preferably ⁇ 65.
  • FIGS. 2 and 3 show a first exemplary embodiment of a support bearing 1 according to the invention.
  • This comprises an inner ring 12 which is internally toothed, balls 14 fixed in a cage 16 and an outer ring 13.
  • the inner race is adjacent to the raceway 17 there on which roll the balls 14, a circumferential lubricant groove 18 is provided.
  • the outer ring 14 has a further lubricant groove 20 adjacent to the raceway 19 there, on which the balls 14 roll.
  • This is the volume, which is sealed by two sealing rings 21 which are fixed in the example shown in corresponding retaining grooves 22 or the like on the outer ring, slightly increased, so that despite the small width of the support bearing 1 1 results in a sufficiently large lubricant space.
  • the seals 21 extend to the inner ring 12.
  • the support bearing 1 1 is positioned in an arrangement shown in Figure 1 relative to the release bearing 3, d. h., it surrounds this radially.
  • the pitch circle diameter Tk is exemplarily 72.5 mm in the exemplary embodiment shown.
  • the width b is exemplary 14 mm.
  • the diameter of the balls 14 is exemplary 7, 144 mm. This results in the following relationships:
  • FIGS. 4 and 5 show a further embodiment of a usable and inventively dimensioned support bearing 1.
  • This in turn consists of an inner ring 12 and an outer ring 13, between which in turn run in a cage 16 guided rolling elements in the form of balls 14.
  • two sealing rings 21 are provided, which are fixed on the outside ring side in corresponding receptacles 22.
  • the pitch circle diameter Tk is in this support bearing 1 1, for example, 79 mm, the width b is z. B. 13, 1 mm, the rolling element diameter dw is, for example, 6.35 mm.
  • FIGS. 6 and 7 show a third variant according to the invention of a support bearing 11, in turn comprising an inner ring 12 and an outer ring 13, between which balls 17 guided in a cage 16 run.
  • the volume located therebetween is in turn sealed by two sealing rings 21, which are also fixed here in corresponding receptacles 22 on the outer ring.
  • no lubricant grooves have is here only on the outer ring 13th a lubricant groove 20 is formed.
  • the inner ring is designed very narrow in this embodiment, as far as its radial width.
  • the pitch circle diameter Tk in this embodiment is, for example, 91 mm
  • the width b is, for example, 16.7 mm
  • the rolling body diameter is, for example, 7.938 mm.
  • the various embodiments of the support bearing all of which are to be installed in the release bearing radially encompassing arrangement, has in common that they all defined so that the respective relevant conditions arise.
  • the ratio Tk / dw> 10 the ratio b / dw ⁇ 2.3, and the design ratio Tk » dw / b> 37, also the ratios are in each case initially defined interval.

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

Abstract

L'invention concerne un ensemble palier destiné à actionner un embrayage, comprenant une butée de débrayage axialement pouvant être déplacée pour l'enclenchement et le désenclenchement de l'embrayage, ainsi qu'un palier support axialement fixe comprenant une bague intérieure et une bague extérieure et des corps de roulement entre ces dernières. La butée de débrayage (3) et le palier support (11) sont agencés coaxialement l'un dans l'autre, le diamètre primitif de référence Tk du palier support (11) sur lequel reposent les corps de roulement (14) et le diamètre des corps de roulement dw étant choisis de manière à obtenir un rapport tel que Tk/dw > 8.
PCT/EP2011/070336 2011-02-16 2011-11-17 Ensemble palier destiné à actionner un embrayage WO2012110123A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011004193.1 2011-02-16
DE102011004193A DE102011004193A1 (de) 2011-02-16 2011-02-16 Lageranordnung zur Betätigung einer Kupplung

Publications (1)

Publication Number Publication Date
WO2012110123A1 true WO2012110123A1 (fr) 2012-08-23

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Application Number Title Priority Date Filing Date
PCT/EP2011/070336 WO2012110123A1 (fr) 2011-02-16 2011-11-17 Ensemble palier destiné à actionner un embrayage

Country Status (2)

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DE (1) DE102011004193A1 (fr)
WO (1) WO2012110123A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015204435A1 (de) * 2015-03-12 2016-09-15 Aktiebolaget Skf Lagerringe mit abgestimmter axialer Steifigkeit

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10116705A1 (de) * 2000-04-10 2001-10-11 Luk Lamellen & Kupplungsbau Kupplungsaggregat
US20050220382A1 (en) * 2004-03-23 2005-10-06 Tomohiko Katou Fixing structure for rolling bearing
EP1595084A1 (fr) * 2003-02-20 2005-11-16 Valeo Embrayages Dispositif comportant un module d'embrayage/de debrayage centre
EP1688634A1 (fr) * 2005-01-31 2006-08-09 Valeo Embrayages Dispositif de montage d'un palier sur un élément de transmission
EP1916435A2 (fr) * 2006-07-08 2008-04-30 ZF Friedrichshafen AG Système de couplage

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10116705A1 (de) * 2000-04-10 2001-10-11 Luk Lamellen & Kupplungsbau Kupplungsaggregat
EP1595084A1 (fr) * 2003-02-20 2005-11-16 Valeo Embrayages Dispositif comportant un module d'embrayage/de debrayage centre
US20050220382A1 (en) * 2004-03-23 2005-10-06 Tomohiko Katou Fixing structure for rolling bearing
EP1688634A1 (fr) * 2005-01-31 2006-08-09 Valeo Embrayages Dispositif de montage d'un palier sur un élément de transmission
EP1916435A2 (fr) * 2006-07-08 2008-04-30 ZF Friedrichshafen AG Système de couplage

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015204435A1 (de) * 2015-03-12 2016-09-15 Aktiebolaget Skf Lagerringe mit abgestimmter axialer Steifigkeit

Also Published As

Publication number Publication date
DE102011004193A1 (de) 2012-08-16

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