WO2010130535A1

WO2010130535A1 - Clutch actuation bearing device, in particular for a dual clutch system

Info

Publication number: WO2010130535A1
Application number: PCT/EP2010/055230
Authority: WO
Inventors: Norbert Radinger; Tomas Smetana
Original assignee: Schaeffler Technologies Gmbh & Co. Kg
Priority date: 2009-05-12
Filing date: 2010-04-21
Publication date: 2010-11-18
Also published as: DE102009020860A1

Abstract

The invention relates to a clutch actuation bearing which is actuated by a actuator ring. According to the invention, an annular flange which protrudes in a radially outward direction is formed on an end area of the bearing outer ring, said end area facing the clutch device in the mounted position. A surface section of an actuator ring rests on said annular flange. Said bearing outer ring is spring-loaded predominantly in the axial direction.

Description

Name of the invention

Clutch actuation bearing device, in particular for a double clutch system

description

Field of the invention

The invention relates to a clutch actuation bearing device as such serves to set the engagement state thereof by adjusting the axial position of a bearing relative to an associated clutch system. In particular, 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.

Background of the invention

From DE 10 2005 027 608 A1 a clutch actuating bearing is known, which is arranged concentrically to a transmission main shaft and the same in the axial direction of the same displaced. With appropriate positioning of the

Kupplungsbetätigungslagers relative to an associated clutch system, this can be spent in an engaged state in which a torque can be transmitted via the clutch system. The initiation of an axial force urging the clutch actuation bearing against the associated clutch device is effected by using an actuator ring which as such is placed on the clutch actuation bearing and forms a circumferential flange.

DE G 70 36 423.7 likewise discloses a clutch actuating bearing which is suitable for transmitting a condition which is relevant for the clutch engagement state. provided axial force is provided. This clutch actuating bearing comprises a bearing inner ring and a bearing outer ring. On the bearing outer ring an actuator ring is placed on the similar to the bearing system described above forms a peripheral flange which serves as sol- rather the axial force introduction.

The problem with common clutch systems is that typically only limited space is available for the clutch actuating bearing itself and the claw mechanism provided for displacing it.

Object of the invention

The invention has for its object to provide a Kupplungsbetätigungsla- gereinrichtung that is relatively inexpensive to produce under manufacturing aspects, and is characterized by an advantageous mechanical performance.

Inventive solution

This object is achieved by a Kupplungsbetäti- supply bearing device with a bearing inner ring, a bearing outer ring, rolling elements are housed in a defined between the two bearing rings track space and support the two bearing rings against each other, and an actuator ring as such surrounds the bearing outer ring and the initiation of a clutch actuation force is used in the bearing outer ring, wherein this clutch actuating bearing device is characterized in that on the bearing outer ring at an end facing in the installed position of a coupling device end, a radially outwardly hervororkragender annular flange is formed, and that the actuator ring comprises a seat portion which rests on this annular flange and thereby axially supported is. This advantageously makes it possible to "drag" the bearing outer ring through the actuator ring and transfer the forces acting on the actuator ring into the bearing outer ring in a structurally advantageous manner Within the actuator ring, a compensation chamber can be provided, which permits sufficient radial displacement of the bearing outer ring within the actuator ring to avoid radial strains.

According to a particularly preferred embodiment of the invention, the seat surface portion of the actuator ring is formed by a radially outwardly projecting annular flange. At the outer edge of this annular flange, a skirting ridge may be formed as such stiffen the annular flange.

According to a particularly preferred embodiment of the invention a plurality of projections, in particular in the form of flat, cap-like exhibitions are formed in the region of the annular flange of the Aktuatorringes as such form the seated on the annular flange of the bearing outer ring support surfaces. These displays are preferably formed as flat caps, or - viewed from the back of the annular flange as a flat pot or cup-like recesses with a flat bottom. These support cap portions are arranged under preferably uniform pitch on the annular flange of the actuator ring. This results in a particularly evenly distributed initiation of Kupplungsbe- actuating force in the bearing outer ring. The actuator ring can be designed as a relatively thin-walled component. Preferably, the actuator ring is stiffened by a plurality of bead structures. According to a particularly preferred embodiment of the invention, the bearing outer ring is manufactured as a deep-drawn part in particular from a preferably subsequently treated-treated steel material. The bearing inner ring and the bearing outer ring are preferably designed so that they form a Schrägkugeilager. Between the bearing inner ring and the bearing outer ring a sealing device is preferably provided which is preferably located as such in the encompassed by the annular flange axial region and seals the bearing interior. This sealing device is preferably formed by an elastomeric sealing ring element which is anchored to the bearing outer ring. this sealing ring element preferably forms a sealing lip which runs under low prestressing on an outer peripheral surface of the inner ring.

In the bearing inner ring, a pressure or so-called Z-ring is preferably supported via a ring calotte joint. The pressure ring and the annular flange of the bearing outer ring are preferably designed so that they have substantially the same outer diameter. The actuator ring can be designed so that it engages around the bearing outer ring to form a ring-bell-shaped housing.

Brief description of the figures

Further details and features of the invention will become apparent from the following description taken in conjunction with the drawings. It shows:

Figure 1 is an axial sectional view for illustrating the structure of a erfindungemäßen clutch actuation bearing device for a dual-clutch transmission;

Figure 2 is a perspective view of the Aktua- torring invention;

FIG. 3 a further perspective view of the actuator ring according to the invention, likewise with a view towards its rear side facing away from the bearing; ₃ 4a 4b, 4c is an illustration of the change in the series to illustrate Axiallastverteilung along the annular flange of the Aktuatorringes;

Figure 5 is a sketch illustrating the design of the exhibitions of the annular flange.

Detailed description of the figures

The inventive Kupplungsbetätigungsla- gereinrichtung shown in Figure 1 comprises a bearing inner ring 1, a bearing outer ring 2, and rolling elements 3 which are received 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 clutch actuation bearing device according to the invention furthermore comprises an actuator ring 4 which, as such, surrounds the bearing outer ring 2 and serves to introduce a clutch actuation force into the bearing outer ring 2.

The clutch actuation bearing device according to the invention is characterized in that a radially outwardly protruding annular flange 2 a is formed on the bearing outer ring 2 at an end region facing in the installed position of a coupling device or a pressure ring 10, and in that the actuator ring 4 forms a seat surface on this

Ring flange 2a is seated and thereby axially supported.

This makes it possible to realize the power flow path illustrated in the diagram. The bearing outer ring 2 is thus dragged over its annular flange 2a. This results in a particularly advantageous load on the bearing outer ring 2 and maintaining a favorable geometry of the Wälzkörperlaufbahn formed by the bearing outer ring. The actuator ring 4 and the bearing outer ring 2 are further coordinated in this embodiment, such that between these two rings 2, 4 remains a gap which allows a certain radial displacement of these two rings 2, 4 against each other. In that space, an elastomeric Vorzentrierungselement not shown here can be added that the actuator ring 4 and the bearing outer ring 2 centered to each other.

The actuator ring 4 is designed as a deep-drawn component and has a plurality of stiffening beads. The actuator ring 4 has a radially inwardly penetrating collar portion 4c. At this collar portion 4c, a guide ring 7 is anchored. The guide ring 7 supports the guidance of the actuator ring 4 on a central bushing 8.

The bearing inner ring 1 is seated in an axial region encompassed by the bearing outer ring 2. The bearing inner ring 1 forms in the region of its inner peripheral surface 1a a Kalottenfläche sitting on a balance ring 9. That compensation ring 9 in turn is supported on a pressure ring 10. The pressure ring 10 serves to initiate the guided over the bearing actuation force Fa in a not-shown here coupling system.

In one of the aforementioned pressure ring 10 and the bearing encompassed axial region is another clutch actuation bearing 1 1.

In Figure 2, the actuator ring 4 is shown in a perspective view with a view of the inside thereof. In addition to the annular flange 4a provided for the axial force transmission, the actuator ring 4 comprises a jacket section 4b which is adapted to the outside geometry of the bearing outer ring 2 (see FIG. 1) while leaving an annular space, as well as a rear region (ie, a side facing away from the Z-ring 10) the bearing outer ring 2 engages behind and thereby radially inwardly penetrating ring bottom 4c. The ring bottom 4c is provided with a bead structure 4d which stiffen the actuator ring 4, in particular the ring bottom 4c. The SI- The bridge structure 4d forms a plurality of stiffening walls which, for example, can have the "star-contour-like" course shown here, alternating between the inner edge and the outer edge of the annular base.

As can further be seen from this illustration, a plurality of flat cleats or displays 4e are formed in the region of the annular flange 4a. These exhibitions 4e each have top surfaces which as such in the installed state on the flange 2a of the bearing outer ring 2, or possibly an intermediate washer sit.

On the annular flange 4a two support ears 4f, 4g are further formed as such serve the Betätigungskraftabgriff from a Betätigungsklauensystem not shown here.

FIG. 3 shows the actuator ring 4 according to the invention with a view to the latter

Back further illustrated. In this representation, in particular, the annular web 4h can be seen which extends along the outer edge of the annular flange 4a. By means of this annular web 4h, a high structural rigidity of the actuator ring 4 is achieved, in particular in the region of the support tubes 4f, 4g.

The protrusions or displays 4e which can be seen in particular in the illustration according to FIG. 3 and which are formed on the annular flange 4a can be designed such that they come into play in dependence on the axial forces introduced into the ear sections 4g, 4f.

FIGS. 4a, 4b and 4c illustrate which of the displays 4e come into play under low load, under load and overload. In the exemplary embodiment shown here, the actuator ring is designed in such a way that at low load initially the exhibitions 4en1 or 4en2 which are visible here are seated on the radial flange of the bearing outer ring. As illustrated in FIG. 4b, when the operating load is reached, in addition to the exhibitions 4en1, 4en2, the exhibitions 4eb1, 4eb2, 4eb3 and 4eb4 also rest on the radial flange 2a of the bearing outer ring.

In case of overload or when the maximum allowable release bearing axial force is reached, the elastic deformation of the actuator ring 4 relieves the expositions 4en1 and 4en2. The Axialkraftübertragung then takes place through a symmetrical 4-point contact on the exhibitions 4eb1, 4eb2, 4eb3, 4eb4. In the case of a temporary maximum load overrun, a safety support can also be provided by the overload exposures 4em1 and 4em2 formed in the exhibitions via the sitting in addition to the aforementioned exhibitions and the ear sections 4f, 4g.

The above-described, specific carrying behavior of the actuator ring according to the invention is achieved taking into account the structural mechanical properties of the entire actuator ring. Typically, initially provided for the transmission of low axial forces expositions 4en1, 4en2 or studs sit on the radial flange 2a of the bearing outer ring. These exhibitions 4en1 and 4en2 are in the embodiment shown here on an axis Q, which is orthogonal to a the ear sections 4f, 4g passing through axis Q2. The galleries or exhibitions 4en1, 4en2, which already bear at low load, face each other with respect to the center axis X of the actuator ring. The above-described concept for substantially even axial force transmission from the actuator ring 4 into the radial flange 2a of the bearing outer ring can also be achieved by otherwise special design of the actuator ring 4 in substantially the same manner.

In particular, it is possible to provide other structures in the region of the annular flange 4 a instead of the exhibitions or lugs 4 e, or else a correspondingly non-uniform one in this annular flange 4 a itself Furthermore, it is also possible to achieve the special distribution of load distribution between the annular flange 4 a of the actuator ring 4 and the radial flange 2 a of the bearing outer ring by insert elements which as such have the inherent elasticity, ie their deformation behavior in the dimensioning-relevant force range of the actuator ring 4 map accordingly.

FIG. 5 once again exemplarily illustrates the relationship of the studs or displays 4en1, 4en2, 4eb1, 4eb2, 4em1 of the annular flange 4a of the actuator ring 4 relative to the annular flange 2a of the bearing outer ring 2. As can be seen, carry at low load essentially only the exhibitions 4en1 and 4en2. At operating load sitting in addition to the aforementioned exhibitions 4en1 or 4en2 or studs and the exhibitions or studs 4eb1, 4eb2 on the annular flange 2a. Finally, if an overload is exceeded, the stud 4em1 also sits on the

Ring flange 2a on. In the exemplary embodiment shown here, the exhibits or studs are designed in such a way that they have different distances Δ1 and Delta Δ2 relative to the footprint F defined by the annular flange 2a.

In the embodiment described above in connection with FIGS. 2 to 5, a so-called two-point contact prevails at low load, the introduction of force into the radial flange 2a of the bearing outer ring 2 taking place at a 90 degree offset to the connection axis Q2, below which the actuating force is introduced into the actuator ring 4. This results in a certain cardan suspension of the bearing race which has an advantageous effect on the smoothness of the bearing. At operating load there is a 6-point, in which there is a particularly uniform axial force distribution on the radial flange 2a of the bearing outer ring 2. In the event of overload, power is transmitted via a symmetrical 4-point contact.

Claims

claims

A clutch operating bearing device comprising:

a bearing inner ring (1),

a bearing outer ring (2),

- Rolling elements (3) which are received in a defined between the two bearing rings (1, 2) track space and the two bearing rings (1, 2) are supported against each other, and

- An actuator ring (4) as such, the bearing outer ring (2) engages and the initiation of a clutch actuating force in the bearing outer ring (2), - characterized in that on the bearing outer ring (2) at an in

Installation position of a coupling device facing end portion, a radially outwardly hervororkragender annular flange (2 a) is formed, and that the actuator ring (4) comprises a seat surface portion which is seated on this annular flange (2 a) and thereby axially supported.

2. clutch actuating bearing device according to claim 1, characterized in that the actuator ring (4) also has an annular flange (4a) which extends in the vicinity of the annular flange (2a) of the bearing outer ring (2), and that the seat surface portion of the Aktuatorrin- ges (4 ) is formed by the annular flange (2a) ..

3. clutch actuating bearing device according to claim 2, characterized in that the seat surface portion of the annular flange is divided into a plurality of support zones.

4. clutch actuating bearing device according to claim 2, characterized in that the support zones are formed as small elevations on the annular flange.

5. clutch operating bearing device according to one of claims 1 to

4, characterized in that the support zones are formed under the same circumferential distribution on the annular flange.

6. clutch actuating bearing device according to one of claims 1 to

5, characterized in that the actuator ring forms a ring-bell-like housing which surrounds the bearing outer ring (2).

7. clutch actuating bearing device according to one of claims 1 to 6, characterized in that on the actuator ring (4) on its the annular flange (2 a) facing away from a radially inwardly penetrating annular wall is formed.

8. clutch operating bearing device according to one of claims 1 to

6, characterized in that in the bearing inner ring, a pressure ring is supported via a Ringkalottengelenk, and that the pressure ring and the annular flange of the bearing outer ring are designed such that they have substantially the same outer diameter.

A clutch operating bearing device comprising: a bearing inner race (1),

a bearing outer ring (2),

- Rolling elements (3) which are received in a defined between the two bearing rings (1, 2) track space and the two bearing rings (1, 2) against each support, and - an actuator ring (4) as such surrounds the bearing outer ring (2) and the initiation of a clutch actuation force into the bearing outer ring (2),

- characterized in that on the bearing outer ring (2) a radially outwardly hervororkragender annular flange (2 a) is formed, and that the actuator ring (4) comprises a seat surface portion of the on this

Ring flange (2a) is seated, wherein the annular flange (2a) with respect to a rolling body track so axially to the power outlet side of the camp towards sets is that upon initiation of a clutch actuation force (Fa) in the annular flange (2 a) the bearing outer ring (2) in an intermediate region between the annular flange (2 a) and said rolling body raceway of the bearing outer ring (2) is loaded axially to train.