CN112013042A

CN112013042A - Clutch device

Info

Publication number: CN112013042A
Application number: CN202010447876.6A
Authority: CN
Inventors: 弗兰克·比尔曼; 蒂埃里·格拉塞尔
Original assignee: Schaeffler Technologies AG and Co KG
Current assignee: Schaeffler Technologies AG and Co KG
Priority date: 2019-05-28
Filing date: 2020-05-25
Publication date: 2020-12-01
Also published as: DE102019127221B3

Abstract

A clutch device comprises an outer friction disk carrier (3) coupled to a drive shaft (9), and a rolling bearing (20) having an outer ring (22) and an inner ring (24), wherein the inner ring (24) is fastened to a housing cover (21) and the outer friction disk carrier (3) is fastened to the outer ring (22), wherein a first radial gap (27) is present between the outer ring (22) and the housing cover (21) and a second radial gap (28) is present between the inner ring (24) and the outer friction disk carrier, wherein at least one annular sealing element (30, 32) is provided for reducing a gap width, which engages into the first or second radial gap (27, 28) or radially surrounds the radial gap.

Description

Clutch device

Technical Field

The invention relates to a clutch device, comprising: an outer friction lining carrier coupled to the drive shaft and a rolling bearing having an outer ring and an inner ring, wherein the inner ring is fastened to the housing cover and the outer friction lining carrier is fastened to the outer ring, wherein a first radial gap is present between the outer ring and the housing cover and a second radial gap is present between the inner ring and the outer friction lining carrier.

Background

Such a clutch device is used in a known manner for temporarily producing a force fit of the transmission torque between the drive shaft of the internal combustion engine or of the electric motor and the output shaft extending to the transmission. If the clutch device is embodied as a single clutch, the clutch device generally comprises: an outer friction plate carrier having an outer friction plate axially movable thereat; an inner friction plate carrier having an inner friction plate axially movable thereat engaged between outer friction plates; and an operating element, usually in the form of a pressure tank, which is axially movable in order to press the friction plate pack together axially. The outer friction lining carrier is connected, for example, to a drive shaft via which torque is introduced; while the inner friction lining carrier is connected to an output shaft leading to the transmission. By pressing the friction plate packs together, a force fit or friction fit is obtained, so that a torque introduced by the drive shaft via the outer friction plate carrier can be transmitted via the friction plate packs to the inner friction plate carrier and via said inner friction plate carrier to the output shaft of the transmission.

In addition to the design as a single clutch with only one friction disk stack, it is also known to design the clutch device as a dual clutch. In this case, the clutch device includes a first sub-clutch and a second sub-clutch, each of the first sub-clutch and the second sub-clutch having: a corresponding set of friction plates with outer and inner friction plates, and an outer and inner friction plate carrier, wherein each set of friction plates can be pressed together via a separate actuating element, i.e. a separate pressure head. The two outer friction disk carriers are connected for example jointly with the drive shaft, which introduces the torque, while the two inner friction disk carriers are connected with the individual output shafts, which lead to individual transmission gears via which the individual partial clutches can be shifted individually.

The construction of the above-described single clutch or double clutch is sufficiently known.

In the case of a single clutch, but also in the case of a dual clutch, the outer friction plate carrier or one of the outer friction plate carriers is/are rotatably mounted at the housing cover, i.e. the clutch cover, via a rolling bearing which has an outer ring, an inner ring and rolling bodies which roll between the outer ring and the inner ring, and is/are supported radially and axially. The housing cover is connected to the transmission housing and also serves as a wet chamber release mechanism for releasing the wet chamber from the external dry chamber, in which the normally wet-running clutch device is arranged and operated. The rolling bearings, which are usually designed as radial thrust ball bearings because of the absorption of both axial and radial loads, are fastened to the housing cover by means of their inner ring, for which purpose the housing cover has an axial flange on which the inner ring rests by means of its inner ring circumference. The outer ring is connected to an outer disk carrier of the clutch, wherein the outer disk carrier is arranged on the outer circumference of the outer ring. As described, the outer disk carrier is connected to a drive shaft which engages into the housing cover from the motor side. In order to prevent the oil used for clutch cooling in this region from flowing out, a sealing element, typically a radial shaft sealing ring, is arranged between the housing cover and the output shaft. As well as the lubrication of the rolling bearing, the lubrication of the sealing elements is effected via oil for clutch cooling, which in the known device is driven radially out of the clutch by centrifugal force and is sprayed towards the transmission cover and is distributed there in the wet space, wherein a sufficiently large amount of oil can enter the space between the clutch cover and the outer friction lining carrier. Depending on the operating state, the following may also occur: the oil is thrown radially outward relative to the upright housing cover by the pumping action of the rotating outer disk carrier and flows around the rolling bearing. However, depending on the rotational speed, the following is also possible: in this case, the oil flows through the rolling bearing and is then used for bearing lubrication, wherein the oil then also reaches the region of the sealing element and lubricates the latter. The oil is supplied to the rolling bearing via a first radial gap which is present between the outer ring and the housing cover, the oil which enters via the first radial gap passing through the rolling bearing to a second radial gap between the inner ring and the outer friction lining carrier, and from there out the oil to the region of the sealing element. At low rotational speeds or in the upright position, the oil reaching the sealing element region can flow back again to some extent at the underside, i.e. below the drive shaft, i.e. into the second radial gap, flow through the rolling bearing and, via the first bearing gap, again into the region between the outer disk carrier and the housing cover.

Although a certain oil flow is required for lubricating the components, a problem associated with this is that hard dust particles which may accumulate reach the bearing region with the oil, which can lead to damage of the bearing both at the running surface and at the rolling elements, such as sealing elements, which can also be damaged.

Disclosure of Invention

The problem on which the invention is based is therefore that of providing a clutch device which is improved with respect to this.

In order to solve this problem, in a clutch device of the type mentioned at the outset, at least one annular sealing element is provided according to the invention for reducing the gap width, which annular sealing element engages into the first radial gap or into the second radial gap or radially surrounds the radial gap.

By means of the integrated annular sealing part, the clutch device according to the invention is provided with targeted measures for reducing the gap width or for covering the gap. This leads to a strong reduction in the free volume or free flow cross section available on the gap side, which therefore leads to a reduction in the oil flow. Despite the reduced free flow cross section or gap width, a small oil flow is always possible, so that the lubricating effect is maintained. At the same time, however, by reducing the oil flow, the possible ingress of harmful, hard dust particles is strongly reduced to almost eliminated, which extends the service life of the rolling bearing and possibly also of the sealing element.

In order to reduce the gap width, an annular sealing part is provided, which can be mounted at different points and can be used to reduce the gap width of the first radial gap or the second radial gap, wherein of course two such annular sealing elements can also be provided, so that a reduction measure is provided not only in the first radial gap but also in the second radial gap. The or each sealing part is either engaged in the respective radial gap, wherein the gap width is already reduced by the engagement, i.e. the arrangement of the sealing element in the radial gap. Alternatively or additionally, it is also discussed below that the overlap is caused

After the inflow to the respective radial gap has been reduced, i.e. after the flow cross section delimiting the inflow has been strongly reduced by overlapping, a reduction of the gap width can also be achieved by the radial enclosure via the sealing element.

The integration of one or more sealing elements is a simple, yet extremely effective measure for extending the service life, which prevents the intrusion of dust particles, but at the same time also enables the lubrication of important components.

There are different possibilities in the integration of such sealing components. Thus, according to the first inventive embodiment, it is possible for the sealing element to be mounted between the inner ring and the housing cover and to extend radially into a first radial gap between the outer ring and the housing cover. In the alternative of the invention, in which both the housing cover and the inner ring are stationary, the annular sealing element is mounted firmly between the housing cover and the inner ring and extends radially outward into the adjoining radial gap between the housing cover and the outer ring. In combination with the above advantages, the width of the radial gap is significantly reduced by the engagement.

It is expedient here for a rim section of the radially overlapping outer ring to be provided, which extends towards the outer ring, additionally at the sealing part at the outer ring circumference which projects from the first radial gap. This means that the outer edge of the sealing element is bent or bent when forming an axially extending annular flange, wherein the bent flanged section extends axially on the outer ring and is spaced slightly from the outer ring with a corresponding axial gap. This means that a labyrinth seal type is additionally realized in this region, since the radial gap is bridged via the flange and additionally geometrically deflected on the outer ring. The design is advantageous for better protection against the ingress of dust particles. That is, in this case, the seal member has not only a narrowing function or a shielding function in the radial direction but also a narrowing function or a shielding function in the axial direction.

Alternatively to the provision of the sealing element between the housing cover and the inner ring, it is also conceivable to provide the sealing element on the axial end side of the outer ring or on the outer ring circumference. If the sealing element is fastened at the outer ring end side, the sealing element is forcibly engaged into the radial gap between the outer ring and the housing cover. This also applies in the following cases: the sealing part is arranged on the outer circumference of the outer ring and extends axially in the direction of the housing cover, wherein the sealing part extends in such a way that the first radial gap is narrowed. The fastening can be achieved, for example, by gluing the sealing element at the outer ring.

Alternatively to providing the sealing element between the housing cover and the inner ring or at the outer ring itself, it is conceivable to provide the sealing element between the outer ring and the outer disk carrier such that the sealing element extends radially into a second radial gap between the inner ring and the outer disk carrier. The design is sealed off on the other rolling bearing side against the sealing element. This ensures that the oil which flows through the rolling bearing and accumulates in the region of the sealing element flows back into the second radial gap, albeit to the lower drive shaft side, and can flow back into the wet chamber via the rolling bearing. At the same time, however, the narrowing of the second radial gap prevents: possible dust particles in the region of the sealing element are carried along here and can reach the region of the rolling bearing.

In this case, it is also possible to additionally provide an edge section extending toward the inner ring at the outer ring circumference protruding from the second radial gap at the sealing part, said edge section radially overlapping the inner ring. In other words, here too, but then, at the inner circumference, a corresponding axial flange is formed by bending or bending of the edge region, which axial flange overlaps the inner ring at a small distance at the inner circumference, so that a deflection of the second radial gap in the axial direction and thus a labyrinth seal type is also achieved there.

As is also the case in the above-described embodiment with the provision of the sealing element at the outer ring, it is also possible at the rolling bearing side to provide, for example, glue, the sealing element at the axial end face or at the inner circumference of the inner ring. The sealing part can therefore be arranged directly at the axial end side and, in turn, be arranged in the second radial gap in a forced manner in such a way that it narrows. Alternatively, the sealing element can also be arranged on the inner circumference and extend toward the outer disk carrier in such a way that the radial gap is narrowed.

The sealing part itself can be a plate part, preferably a simple deep drawn or stamped plate part, at which the corresponding geometry can be easily shaped. However, it is also conceivable to produce the sealing part as a plastic part, in which case the desired geometry can likewise be easily formed within the scope of a shape-based plastic injection molding method.

Finally, the clutch device, which may preferably be a double clutch or a multiple clutch, comprises a first partial clutch and a preferably radially inner second partial clutch, wherein the first partial clutch has an outer friction disk carrier which is mounted on the housing cover via a rolling bearing.

Drawings

The invention is elucidated below with reference to the drawings according to embodiments. The figures are schematic and show:

figure 1 is a schematic view of a clutch device according to a first embodiment of the invention,

figure 2 shows a modified partial view of the region of the rolling bearing device in figure 1,

fig. 3 shows a schematic representation of a second embodiment of a coupling device according to the invention, an

Fig. 4 shows an enlarged detail view of the rolling bearing device of the clutch device in fig. 3.

Detailed Description

Fig. 1 shows a coupling device 1 according to the invention, which is embodied here as a dual clutch, comprising a first partial clutch 2 having: an outer friction plate carrier 3 having an outer friction plate 4 axially movable thereat; and an inner friction plate carrier 5 having an inner friction plate 6 arranged axially displaceably thereon. Under the action of the first force K1, the set of outer and inner friction disks 4, 6 can be pressed together via a pressure element 7, usually spring-loaded against a pressure head of a restoring element 8, in order to obtain a friction fit, whereby a torque introduced via the outer friction disk carrier 3 can be transmitted.

For this purpose, the outer disk carrier 3 is connected to the drive shaft 9, while the inner disk carrier 5 is connected to the first output shaft 10, so that the torque introduced via the drive shaft 9 can be transmitted to the first output shaft 10 via the pressed-together, i.e. actuated, first partial clutch 1.

There is a second sub-clutch 11, which comprises: an outer friction plate carrier 12 having an outer friction plate 13 axially movable thereat; and an inner disk carrier 14 with an inner disk 15 which is axially displaceable at it, wherein, when a second pressure force K2 is applied, the disk set consisting of outer and

inner disks

13, 15 is pressed together again via a further pressure element 16, again a pressure head, for obtaining a form fit for transmitting torque, wherein here the pressure element 16 can also be moved axially toward the restoring element 17.

The second outer friction lining carrier 12 is connected in a rotationally fixed manner to the first outer friction lining carrier 3 via an annular connecting element 18, so that when a torque is introduced from the drive shaft 9 into the outer friction lining carrier 3, said torque is also automatically applied to the second outer friction lining carrier 12, which is rotated in a forced manner with respect to the first outer friction lining carrier. The second inner friction plate carrier 14 is connected to a second output shaft 19, which extends into a second gear position of the transmission, which is not illustrated in detail.

The basic structure of such a double clutch is sufficiently known.

As shown in fig. 1, the outer friction plate carrier 3 is supported rotatably and radially at a housing cover 21 via a rolling bearing 20. The rolling bearing 20 comprises an outer ring 22, on which outer ring 22 the outer friction plate carrier 3 is seated by means of a corresponding bearing seat 23.

As shown in fig. 1 and 2, the rolling bearing 20 also comprises an inner ring 24 which rests on a corresponding bearing seat 25 of the housing cover 21. Rolling elements 26 in the form of balls roll between the outer ring 22 and the inner ring 24, the rolling bearing 20 being a radial thrust ball bearing.

As can be seen in the enlarged illustration, in particular from fig. 2, a first radial gap 27 is present between the housing cover 21 and the outer ring 22, and a second radial gap 28 is present between the inner ring 24 and the outer friction lining carrier 3. As indicated by the arrow P1 in fig. 1, oil for cooling the clutch device 1 in the region between the housing cover 21 and the outer friction plate carrier 3 can flow into the region of the first radial gap 27. A certain inflow of oil is required in order to lubricate the rolling bearing 20, as is the case with a sealing element 29, for example in the form of a radial shaft sealing ring, which is arranged between the housing cover 21 or the bearing block 24 and the drive shaft 9.

However, due to the width of the radial gap 27, there is a risk that: with the oil, hard dust particles also reach the region of the rolling bearing 20 or also the region of the sealing element 29, which dust particles can lead to damage. In order to solve this problem, a sealing part 30 is provided which is mounted firmly between the inner ring 24 and the housing cover 21 and which, as seen in particular in fig. 2, extends into the first radial gap and, viewed radially, even slightly therefrom. At the outer circumference of the annular sealing part 30, a bent edge section 31 is provided, which in turn overlaps the outer ring 22 by a small amount at a slight distance, so that a labyrinth seal is formed approximately in this region.

By means of the annular or ring-disk-shaped sealing part 30, which may be a plate part or a plastic part, it is clear that the radial gap 27 or its free-flow cross section is significantly narrowed and reduced, so that, nevertheless, a smaller proportion of the oil can always flow via the radial gap into the rolling bearing region and the sealing element region, which is required for lubrication, but larger dust particles can no longer enter the rolling bearing region or the sealing element region.

Fig. 3 and 4 show a further embodiment of a coupling device 1 according to the invention, wherein the same reference numerals are used for the same components. The basic structure of the clutch device 1 in fig. 3 is identical to the basic structure of the clutch device 1 in fig. 1, and the two

partial clutches

2, 11 are also provided with the components described in relation to fig. 1, with reference to the description relating thereto.

Here too, a rolling bearing 20 is provided, via which the outer disk carrier 3 is axially and radially supported or rotatably mounted at the housing cover 21. Likewise, a sealing element 29 is provided between the housing cover 21 and the drive shaft 9.

In the variant of the invention, however, a sealing element 32 is provided, which is arranged between the outer ring 22 and the outer disk carrier 3 in the region of the bearing seat 23 and thus rotates together with the outer ring and the outer disk carrier. In this case, the sealing element 32, which is again embodied in the form of a ring or a ring disk and is produced as a simple plate or plastic part, extends into the second radial gap 28 between the inner ring 24 and the outer friction lining carrier 3, so that in this variant the second radial gap 28 or its free-flow cross section narrows and decreases. Here, the sealing part 32 also has a bent-over edge section 33 which extends axially in the direction of the inner ring in such a way as to form an axial flange and overlaps the inner ring slightly, however, at a small distance, so that an axial deflection of the second radial gap 28 is also achieved there. That is, a labyrinth seal type is also configured here.

The purpose of this arrangement with the sealing element 32 arranged between the outer ring 22 and the outer friction lining carrier 3 is evident from fig. 4. Since it is thereby avoided that dust particles which have accumulated with the oil before the sealing element 29 can flow back into the rolling bearing 20. Nevertheless, the oil itself can flow into the second radial gap 28 and back into the wet chamber via the rolling bearing 20, however, possible dust particles are blocked and therefore cannot reach this region due to the narrowing of the free flow cross section of the second radial gap 28 and the labyrinth design.

It is preferably conceivable to provide sealing

parts

30, 32 on both sides of the rolling bearing 20 in order to obtain a corresponding shielding with respect to both flow directions.

Reference numerals

1 Clutch device

2 sub-clutch

3 outer friction plate bearing piece

4 outer friction plate

5 inner friction plate bearing piece

6 inner friction plate

7 pressure element

8 reset element

9 drive shaft

10 output shaft

11 sub-clutch

12 outer friction plate carrier

13 outer friction plate

14 inner friction plate carrier

15 inner friction plate

16 pressure element

17 reset element

18 connecting element

19 output shaft

20 rolling bearing

21 casing cover

22 outer ring

23 bearing seat

24 inner ring

25 bearing seat

26 rolling element

27 first radial gap

28 second radial gap

29 sealing element

30 sealing member

31 edge section

32 sealing member

33 edge section

Claims

1. A clutched device, the clutched device comprising: an outer friction plate carrier (3) coupled to a drive shaft (9), and a rolling bearing (20) having an outer ring (22) and an inner ring (24), wherein the inner ring (24) is fastened to a housing cover (21) and the outer friction plate carrier (3) is fastened to the outer ring (22), wherein a first radial gap (27) is present between the outer ring (22) and the housing cover (21) and a second radial gap (28) is present between the inner ring (24) and the outer friction plate carrier, characterized in that at least one annular sealing element (30, 32) is provided for reducing a gap width, which engages into or radially surrounds the first or second radial gap (27, 28).

2. Clutch device according to claim 1, wherein the sealing member (30) is mounted between the inner ring (24) and the housing cover (21) and extends radially into the first radial gap (27) between the outer ring (22) and the housing cover (21).

3. Clutch device according to claim 2, wherein an edge section (31) extending towards the outer ring (22) radially overlapping the outer ring (22) is provided at the sealing member (30) at the outer ring circumference protruding from the first radial gap (27).

4. Clutch device according to claim 1, wherein the sealing member is provided at an axial end side or at an outer ring circumference of the outer ring (22).

5. Clutch device according to any one of the preceding claims, wherein the sealing member (32) is mounted between the outer ring (22) and the outer friction plate carrier (3) and extends radially into the second radial gap (28) between the inner ring (24) and the outer friction plate carrier (3).

6. Clutch device according to claim 5, wherein at the sealing member (32) at an inner ring circumference protruding from the second radial gap (28) there is provided an edge section extending towards the inner ring (24) radially overlapping the inner ring (24).

7. Clutch device according to any of claims 1 to 4, wherein the sealing member is provided at an axial end side or at an inner circumference of the inner ring (24).

8. Clutch device according to any of the preceding claims, wherein the sealing member (30, 32) is a sheet metal member or a plastic member.

9. Clutch device according to one of the preceding claims, wherein the clutch device is a double clutch or a multiple clutch, comprising a first partial clutch (2) and a preferably radially inner second partial clutch (11), wherein the first partial clutch (2) has an outer friction plate carrier (3) which is supported at the housing cover (21) via the rolling bearing (20).