DE102014209418A1 - Clutch release assembly for an oil bath clutch - Google Patents

Abstract

A release bearing 2 for a clutch release assembly 1 of an oil bath clutch is indicated. To improve the flow of oil within the annular space 6 between the two bearing rings 4, 5, a shoulder 14 is indicated, which is connected to a bearing flange 10.1 one of the two bearing rings 5, and forms a defined sealing gap 17 together with the other bearing ring 4.

Description

Technical area

The invention relates to Kupplungsausrückanordnungen, as used to separate or close the adhesion between an internal combustion engine and a downstream of this machine transmission of motor vehicles.

In addition to the actual shift disconnect clutch, clutch disengagement arrangements comprise a mechanism which at least temporarily removes the frictional connection of the shift disconnect clutch. For this purpose, it is customary to provide the Kupplungsausrückanordnungen of internal combustion engines with so-called release bearings, which are arranged around a housing. These release bearings are generally formed by a bearing inner ring and a bearing outer ring, wherein the bearing outer ring surrounds the bearing inner ring coaxially. Furthermore, rolling elements are provided which roll between the raceways provided by the bearing rings. The bearing outer ring of such a release bearing is in physical contact with the diaphragm springs of a shift disconnect clutch. It is customary to provide the bearing outer ring with a contact flange which extends in the direction of the axis of rotation of the release bearing and on which support the disengagement mechanism of the shaft-separating clutch. The bearing inner ring such release bearing is fixed axially and rotationally fixed to a housing shoulder of the housing. If the frictional connection between the internal combustion engine and the downstream transmission is interrupted by means of the shift disconnect clutch, a force acting on the housing is displaced axially against the action of the diaphragm springs by means of the housing, the bearing inner ring and the rolling elements of the bearing outer ring. Such an arrangement is out DE 10 2013 208 715 known.

For the sake of completeness, it should already be pointed out that under a disengagement mechanism in the context of this application membrane springs or pressure pots are understood which, when displaced axially by means of the abutment flange, with which they are in physical contact or are supported on them, disengage the Shift disconnect clutch or interrupting the power flow between the engine and transmission effect. Also, the invention is not limited to clutch release systems, in which the intermediary of the release bearing of the traction is interrupted, but can also be set in connection with release bearings of dual clutch transmissions, with which the adhesion between the transmission and the engine is made.

Shift disconnect couplings can be designed either as dry clutches or oil bath clutches. The fundamental difference between these two types of coupling is that the respective friction partners of the dry clutch are in direct contact, while in oil bath clutches the friction partners run in an oil bath. Since the coupling process inevitably waste heat and since the removal of waste heat in dry clutches is difficult, oil bath clutches are usually used at higher, pending on the clutch torques, since the oil flow is suitable to provide adequate cooling.

As already indicated, in the engaged state of the clutch by the concern of the diaphragm spring on the rotating bearing ring of this bearing ring is constantly exposed to the speed of the internal combustion engine. In order for the release bearing to permanently accelerate or to run on the speed of the engine, the release bearings are lubricated for dry clutches by a grease filling lifetime. In this case, the seals that are to encapsulate the grease filling in the release bearing, decisive importance, because a leakage of grease or contamination of the friction partners with lubricant inevitably leads to a clutch slippage.

Since in oil bath clutches the friction partners run anyway in an oil bath, the lubrication of the rolling elements between the bearing rings of the release bearing is worried by the already existing oil bath in these types of couplings. A disadvantage of this type of lubrication is considered, however, that the oil bath is contaminated with abrasion of the friction partners and that this abrasion is suitable to settle between the bearing rings of the release bearing, which can lead to damage to the release bearing.

The invention is therefore based on the object of specifying a clutch release arrangement and a method for producing bearing rings of such a disengagement arrangement whose release bearing is lubricated by the oil bath of a Ölbadkupplung and which excludes deposits of abrasion within the release bearing and in particular allows a targeted flow in the overall system.

This object is achieved with claims 1 to 5. A method for forming bearing rings is specified in claims 6 to 8.

The invention is based on the finding, a defined gap - in the context of this application referred to as a sealing gap to create - which flows during rotation of the bearing outer ring relative to the bearing inner ring for a release bearing and deposits between the Bearing rings excluding oil flow ensures. In detail, this is achieved in that the free end of the abutment flange has an angled relative to the radial extent of the abutment flange shoulder and that in the assembled state, the shoulder and the other bearing ring include a sealing gap between them. Essential for a good flow through the annular space between the two bearing rings is that the shoulder on the one bearing ring to the shoulder opposite surface on the other bearing ring in each operating condition of the release bearing maintains a constant distance, over the entire length in which the shoulder opposite surface to other Langering covered. If one waives the production advantages which are given for a sealing gap which is aligned parallel to the axis of rotation, the sealing gap can also enclose an angle to the rotational axis of the release bearing.

The shoulder on the one bearing ring, which forms the sealing gap together with the other bearing ring, can be provided by a sheet metal ring which is pressed into a bearing ring for this purpose.

It is far less complicated if the shoulder and the abutment flange of the respective bearing ring are integrally formed. In such a design, not only the preparation of the sheet metal ring and the insertion of the sheet metal ring is saved in the bearing ring, but also created a shoulder with very precise masses, which does not reach in a separate production about a to be used in the bearing ring metal ring because of the summation of tolerances can be.

The use of space through the shoulder can be neglected if the shaft has a reduced material thickness relative to the abutment flange.

In order to avoid conflicts with a rolling cage leading cage, it is advantageous if the one bearing ring engages in the radial distance between the shoulder and the wall of the bearing ring having the shoulder.

A particularly simple method for forming a, bearing a shoulder bearing ring is given if in one or more forming steps, the general geometry of the bearing ring is formed and if at the same time or after or forming steps to form the general geometry of the respective bearing ring in a further forming step the free end of the abutment flange of this bearing ring is angled to form a shoulder. In this case, a bearing ring with a general geometry is understood to mean one which has the raceway and an abutment flange, which is adjacent to the raceway and mostly angled relative to the raceway. Because of the circular ring shape of such bearing rings with general geometry, the free end of the abutment flange also surrounds a central bore. If a bearing ring of general geometry with the abutment shoulder placed on a counter-holder and a tool whose diameter is greater than the diameter of the bore in the abutment, provided and lowered onto the bearing ring or its abutment, the free end of the abutment flange to form an annular Shoulder put through.

If during the forming step, which leads to the bending of the shoulder relative to the abutment flange, at the same time the shoulder is stretched, not only the thickness of the shoulder to be formed is reduced by the flow of material, but also their length in the insertion direction of the tool.

A distortion of the bearing ring of general geometry must be feared if, during the bending and ironing of the shoulder acting on the free end of the abutment flange and the forming shoulder force is supported by a counter-holder on which rests the abutment flange and the forming Shoulder comes to the plant. Of particular importance in this case are the areas of the counter-holder which come into physical contact with the forming shoulder, because these areas not only promote an extraordinarily dimensionally stable shoulder, but also support ironing of the shoulder.

Brief description of the figures

Show it:

1 an embodiment of a Kupplungsausrückanordnung;

2 another embodiment of a Kupplungsausrückanordnung;

3a - 3c three process steps for forming a bearing ring of a Kupplungsausrückanordnung according to the embodiment according to 2 ,

Ways to carry out the invention

The invention will now be explained in more detail with reference to FIGS.

In 1 is from a clutch release assembly 1 only the release bearing 2 and a diaphragm spring not belonging to the clutch 3 shown. The release bearing 2 is from a Bearing inner ring 4 and a bearing outer ring 5 formed, with the bearing outer ring 5 the bearing inner ring 4 Coaxially surrounds. Between the two bearing rings 4 . 5 there is an annulus 6 in which rolling elements 7 are arranged on the two bearing rings 4 . 5 provided careers 8th roll. In this embodiment, the rolling elements 7 formed by balls leading to their leadership in a cage 9 are used. Even if the two in 1 shown bearing rings 4 . 5 formed largely identical and each having a substantially perpendicular to the axis of rotation DA abutment flange 10.1 . 10.2 as an integral part, is for the present invention, only one piece with the rotating bearing outer ring 5 connected abutment flange 10.1 significant.

For the function of the clutch release arrangement 1 Let it be briefly noted that when a force F on the abutment flange 10.2 of the bearing inner ring in this case 4 is exercised, shifts under mediation by the rolling elements 7 the bearing outer ring 5 in the direction of arrow P and causes with this axial displacement over the abutment flange 10.1 adjacent diaphragm springs 3 a disengagement of the clutch (not shown).

In the 1 shown Kupplungsausrückanordnung 1 is operated in conjunction with an oil bath or wet clutch. This is in 1 indicated that the annulus 6 with oil 11 is filled, which is the lubrication of the rolling elements 7 between the bearing rings 4 . 5 takes over. To the life of bearings and thus also release bearings 2 shortening contamination of the annulus 6 with in the oil 11 To exclude dispersed suspended particles (not shown), it is essential that a controlled flow of oil through the annulus 6 is guaranteed. This oil flow is intended to prevent the suspended particles absorbed by oil, in particular in the annulus 6 can settle.

To do this in accordance with the execution 1 to ensure is in the bearing outer ring 5 an L-shaped sheet metal ring 12 pressed in, with one leg 13.1 on the inside 15 of the abutment flange 10.1 of the rotating bearing outer ring 5 abuts and the other leg 13.2 of the metal ring 12 , which in connection with this application also as a shoulder 14 is substantially parallel to the axis of rotation DA and to the outside 16 of the stationary bearing inner ring 4 a radial distance A complies, in connection with this application as a sealing gap 17 is designated. For the circulation of the oil 11 in the annulus 6 is the radial distance A or the sealing gap 17 crucial. To ensure adequate circulation of oil 11 in the annulus 6 to effect or to oil 11 from outside the annulus 6 through the sealing gap 17 in the annulus 6 to promote, it is anxious to form the radial distance A rather small. This is contrary to the fact that the provision of such a small sealing gap 17 necessary components (bearing rings 4 . 5 , Metal rings 12 ) are subject to tolerances. This means that to avoid touching contact between the thigh 13.2 or the shoulder 14 and the bearing inner ring 4 These tolerance deviations must be taken into account so that then in practice the radial distance A is designed to be larger. However, even taking this into account, variations in the size of the radial distance A are unavoidable, resulting in fluctuating flow rates in practice.

In 2 is another embodiment of a clutch release assembly 1 shown which as well as the in 1 illustrated embodiment, a release bearing 2 includes, which of a bearing inner ring 4 , a bearing outer ring surrounding this coaxially 5 and between the bearing rings 4 . 5 Rolling Wälzköpern 7 is formed in the form of balls.

In contrast to the execution according to 1 is in accordance with the execution 2 the shoulder 14 leading to the bearing inner ring 4 maintains a radial distance A, integral with the abutment flange 10.1 connected. Also, in this embodiment, the disengaging mechanism is not of a diaphragm spring, but of a on the abutment flange 10.1 adjacent, only schematically shown pressure pot 18 educated.

Compared to the execution according to 1 is made by the integral connection of shoulder 14 and abutment flange 10.1 achieved that tolerance error in the execution according to 1 as a result of the metal ring used 12 must be considered, are eliminated and thus easily a narrower and no or negligible fluctuation width underlying radial distance A of the sealing gap 17 can be realized. It is clear from the illustration according to 2 removable, that is integral with the abutment flange 10.1 connected shoulder 14 has only a small thickness DS in the radial direction, so that despite their interposition between the axis of rotation DA and the bearing inner ring 4 only very little space for the shoulder 14 is consumed.

Together with the 3a to 3c Now, a method for forming a bearing outer ring 5 according to 2 described.

In 3a is a bearing outer ring 5 according to 2 shown in general geometry, which is made of a blank by corresponding forming steps. Under a general geometry, a bearing ring is understood whose career 8th and its abutment flange 10.1 already trained. Depending on the process, the general geometry of a bearing ring even already a central bore 19 belong. If she does not, it must be ensured that this hole 19 later - before executing the step according to 3b - in the abutment flange 10.1 is introduced.

3b shows a bearing outer ring 5 according to 3a , although in the room 20 a counterpart 21 is used. On this counter-holder 21 is the abutment flange 10.1 on. In addition, in this embodiment, the counter-holder 21 on its lateral lateral surface 22 the course of the wall 27 of the bearing outer ring 5 adapted, so that from him also the career 8th is supported. Centric within the counter-holder 21 is a circular opening 23 leave, whose diameter DÖ is greater than the diameter DB of the bore 19 , Above the bearing outer ring 5 is tool 24 arranged, which has a diameter DW, which lies between the diameter DÖ and DB.

Will now be the tool 24 on the on the counterhold 21 resting bearing outer ring 5 lowered in the direction of arrow PW, set up conditions that in 3c are shown.

Under the effect of the tool 24 that will be the hole 19 edging free end 25 ( 3b ) of the abutment flange 10.1 , inside in the opening 23 for the formation of the shoulder 14 retracted or put through. Since the difference between the half diameter DÖ and the half diameter DW is smaller than the thickness D of the abutment flange 10.1 will automatically with the feed of the tool 24 in the direction of arrow PW or pulling the material into the opening 23 one shoulder 14 formed, whose thickness DS relative to the thickness D of the abutment flange 10.1 is reduced.

Because of the counterpart 21 during the shaping of the shoulder 14 with the forming shoulder 14 comes into physical contact or this holds during their production, an extraordinary high dimensional stability of the shoulder 14 achieved, which is a reworking of the shoulder 14 before completing the release bearing 2 makes superfluous.

Only for the sake of completeness it should be noted that the tool 24 shown only schematically and in support of the insertion of the shoulder 14 or has corresponding edge rounding to support the flow of material. Also, for this purpose, the outer contour 26 of the tool 24 be slightly conical.

LIST OF REFERENCE NUMBERS

1

 Kupplungsausrückanordnung

2

 release bearing

3

 diaphragm spring

4

 Bearing inner ring

5

 Bearing outer ring

6

 annulus

7

 rolling elements

8th

career

9

Cage

10.1, 10.2

 abutment

11

 oil

12

sheet metal ring

13.1, 13.2

 leg

14

 shoulder

15

inside

16

 outside

17

sealing gap

18

pressure cooker

19

 drilling

20

room

21

backstop

22

 lateral surface

23

 opening

24

 Tool

25

 free end

26

outer contour

27

 wall

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102013208715 [0002]

Claims (8)

Clutch release arrangement for an oil bath clutch with a bearing inner ring 4 , with a bearing outer ring 5 who the bearing inner ring 4 Coaxially surrounds, with rolling elements 7 between the two bearing rings 4 . 5 are arranged and the on of the two bearing rings 4 . 5 provided careers 8th unroll, and with at least one abutment flange 10.1 , the integral part of one of the two bearing rings 4 . 5 is, which is substantially radially to the axis of rotation DA of the clutch release assembly 1 extends and at which the release mechanism 3 . 18 support a coupling, characterized in that the abutment flange 10.1 at its free end 25 one opposite the radial extent of the abutment flange 10.1 angled shoulder 14 and that in the assembled state, the shoulder 14 and the other bearing ring 4 or 5 a sealing gap 17 between them. Kupplungsausrücklageranordnung according to claim 1, characterized in that the shoulder 14 from a sheet metal ring 12 is formed, which is pressed into the respective bearing ring. Kupplungsausrücklageranordnung according to claim 1, characterized in that the shoulder 14 and the abutment flange 10.1 are integrally formed. Kupplungsausrückanordnung according to one of claims 1 to 3, characterized in that the shoulder 14 opposite the abutment flange 10.1 has a reduced material thickness. Kupplungsausrückanordnung according to one of claims 1 to 4, characterized in that the one bearing ring 4 in the radial distance A between the shoulder 14 and the walls 27 of the shoulder 14 bearing ring 5 intervenes. A method for producing a bearing ring according to claim 3, characterized in that in one or more forming steps, the general geometry of the bearing ring 5 is formed and that at the same time with or after the or the forming steps to form the general geometry of the respective storage 5 in a further forming step, the free end 25 of the abutment flange 10.1 this bearing ring 5 to form a shoulder 14 is angled. A method according to claim 6, characterized in that during the forming step, which for bending the shoulder 14 opposite the abutment flange 10.1 leads, at the same time the shoulder 14 is stripped. A method according to claim 7, characterized in that during the bending and ironing of the shoulder 14 the on the free end 25 of the abutment flange 10.1 and the forming shoulder 14 acting force of a counter-holder 21 supported on which the abutment flange 10.1 rests and to the forming shoulder 14 comes to the plant.

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