CN112013042B

CN112013042B - Clutch device

Info

Publication number: CN112013042B
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: 2024-07-26
Anticipated expiration: 2040-05-25
Also published as: CN112013042A; DE102019127221B3

Abstract

Clutch 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, wherein at least one annular sealing member (30, 32) is provided for reducing the gap width, which annular sealing member engages into or radially surrounds the radial gap in the first or second radial gap (27, 28).

Description

Clutch device

Technical Field

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

Background

Such clutch devices are used in a known manner for temporarily generating a force fit for transmitting torque between a drive shaft of an internal combustion engine or of an electric motor and an output shaft extending to a 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 inner friction plates axially movably engaged therebetween; and a handling element, typically in the form of a pressure tank, which is axially movable to axially squeeze the friction plate pack together. The outer friction plate carrier is connected, for example, with a drive shaft via which torque is introduced; and the inner friction plate carrier is connected to an output shaft leading to the transmission. By pressing the friction plate pack together, a force fit or friction fit is obtained, so that the torque introduced by the drive shaft via the outer friction plate carrier can be transferred via the friction plate pack 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 plate group, it is also known to design the clutch device as a double clutch. In this case, the clutch device comprises a first sub-clutch and a second sub-clutch, which each have: corresponding friction plate groups with outer and inner friction plates, and outer and inner friction plate carriers, wherein each friction plate group can be pressed together via a separate operating element, i.e. a separate pressure head. The two outer friction plate carriers are connected together, for example, with a torque-carrying drive shaft, while the two inner friction plate carriers are connected with separate output shafts which lead to separate transmission gears via which the individual sub-clutches can be shifted separately.

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

In the case of a single clutch, but also in the case of a double clutch, the outer friction plate carrier or one outer friction plate carrier is rotatably mounted on the housing cover, i.e. the clutch cover, via a rolling bearing, which has an outer ring, an inner ring and rolling bodies rolling between the outer ring and the inner ring, and is supported radially and axially. The housing cover is connected to the transmission housing and also serves as a wet chamber separating mechanism to separate the wet chamber from the external dry chamber, in which a normally wet-running clutch device is arranged and operated. Since the rolling bearings, which are mostly embodied as radial thrust ball bearings, absorb loads both axially and radially, are fastened to the housing cover by means of the inner ring of the rolling bearings, for this purpose the housing cover has an axial flange, to which the inner ring is attached by means of its inner ring circumference. The outer ring is connected to an outer friction plate carrier of the clutch, wherein the outer friction plate carrier is disposed on an outer circumference of the outer ring. As described, the outer friction plate carrier is connected to a drive shaft which engages into the housing cover from the motor side. In order to prevent the outflow of oil for clutch cooling in this region, a sealing element, typically a radial shaft sealing ring, is arranged between the housing cover and the output shaft. As with the lubrication of the rolling bearings, the lubrication of the sealing elements is also achieved by oil for clutch cooling, which in the known device is driven by centrifugal force radially out of the clutch and sprayed onto the transmission housing and is distributed in the wet space, wherein a sufficiently large amount of oil may enter the space between the clutch cover and the outer friction plate carrier. Depending on the operating state, the following may also occur: the oil is thrown radially outwards with respect to the upstanding housing cover by the pumping action of the rotating outer friction plate carrier and flows around the rolling bearings. 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 sealing element. Via a first radial gap which is present between the outer ring and the housing cover, oil is fed to the rolling bearing, and oil which enters via the first radial gap passes through the rolling bearing to a second radial gap between the inner ring and the outer friction plate carrier, from where it comes out into the sealing element region. At low rotational speeds or in an upright position, the oil reaching the region of the sealing element can flow back to some extent on the underside, i.e. below the drive shaft, i.e. into the second radial gap, through the rolling bearing and into the region between the outer friction disk carrier and the housing cover again via the first bearing gap.

Although a certain oil flow is required for lubricating the components, a problem associated with this is that hard dust particles that may accumulate with the oil reach the bearing area, which may lead to damage to the bearing, such as the sealing element, both at the running surface and at the rolling bodies.

Disclosure of Invention

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

In order to solve the problem, in a clutch device of the type mentioned at the beginning, 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 the second radial gap or radially surrounds the radial gap.

By means of the integrated annular sealing element, the clutch device according to the invention is provided with targeted measures for reducing the gap width or for masking the gap. This results in a strong reduction of the free volume or free flow cross section given at the gap side, which thus results in a reduction of the oil flow. A small oil flow is always possible despite the reduced free flow cross section or gap width, so that a 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 until 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, annular sealing elements are provided, which can be installed 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, in order to provide a measure for the reduction in both the first radial gap and the second radial gap. The or each sealing element is in this case either engaged in the respective radial gap, wherein the gap width has been reduced by said engagement, i.e. the arrangement of the sealing element in the radial gap. Alternatively or additionally, discussed further below, in view of overlapAfter the inflow to the respective radial gap has been reduced, i.e. after the flow cross section defining the inflow has been strongly reduced by bridging, a reduction in the gap width can also be achieved by the sealing element as a result of the radial envelope.

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

There are different possibilities in terms of the integration of such sealing components. According to a first embodiment of the invention, it is therefore 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 described inventive alternative, both the housing cover and the inner ring are fixed in position, the annular sealing element is mounted firmly between the housing cover and the inner ring and extends radially outwards 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 if, in addition, at the sealing part, an edge section of the radially overlapping (u bergreifen) outer ring extending towards the outer ring is provided at the outer ring circumference protruding from the first radial gap. This means that the outer edge of the sealing element is bent or folded when forming an axially extending annular flange, wherein the folded flange-like section extends axially on the outer ring and is slightly spaced apart from the outer ring with a corresponding axial gap. This means that a labyrinth seal type is additionally realized in the region, since the radial gap is additionally geometrically deflected on the outer ring via the flange overlap. This embodiment is advantageous for better protection against dust particles. That is, in this case, the seal member has not only a radial narrowing function or a shielding function but also an axial narrowing function or a shielding function.

Alternatively to the arrangement of the sealing element between the housing cover and the inner ring, it is also conceivable to arrange the sealing element at the axial end face of the outer ring or at the outer ring circumference. If the sealing element is fastened at the outer ring end side, the sealing element is positively engaged in the radial gap between the outer ring and the housing cover. This also applies in the following cases: the sealing element is arranged on the outer circumference of the outer ring and extends axially in the direction of the housing cover, in which case it extends in such a way that the first radial gap narrows. The fastening may be achieved, for example, by gluing the sealing element at the outer ring.

Instead of providing a 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 friction disk carrier such that the sealing element extends radially into the second radial gap between the inner ring and the outer friction disk carrier. The design seals against the sealing element on the other rolling bearing side. This ensures that the oil flowing through the rolling bearing and accumulating in the region of the sealing element flows into the second radial gap, although toward the lower drive shaft side, and can flow back into the wet chamber via the rolling bearing. At the same time, however, narrowing by the second radial gap prevents: the possible dust particles in the region of the sealing element are carried along here and can reach the rolling bearing region.

In this case, an edge section extending toward the inner ring and radially overlapping the inner ring can also be provided at the outer circumference of the sealing element protruding from the second radial gap. In other words, the corresponding axial flange is then formed by bending or bending the edge region at the inner ring circumference, which overlaps the inner ring at small intervals, so that a deflection of the second radial gap in the axial direction and thus a labyrinth seal type is also achieved there.

As in the case of the above-described embodiment with a sealing element arranged at the outer ring, it is also possible on the rolling bearing side to arrange, for example, adhesively bond, the sealing element at the axial end face or at the inner circumference of the inner ring. The sealing element can therefore be arranged directly at the axial end face and thus be arranged forcefully in the second radial gap in such a way that it narrows. Alternatively, the sealing element may also be arranged at the inner ring circumference and extend toward the outer friction disk carrier in such a way that the radial gap narrows.

The sealing part itself may be a plate part, preferably a simple deep drawn or stamped plate part, where the corresponding geometry can be easily shaped. However, it is also conceivable to produce the sealing part as a plastic part, where 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 sub-clutch and a preferably radially inner second sub-clutch, wherein the first sub-clutch has an outer friction plate carrier which is supported at the housing cover via a rolling bearing.

Drawings

The invention is described below with reference to the accompanying drawings according to embodiments. The drawings 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 view of a second embodiment of a clutch device according to the invention, and

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 clutch device 1 according to the invention, which is embodied here as a double clutch, comprising a first sub-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 axially movably disposed thereat. The friction plate group consisting of the outer and inner friction plates 4,6 can be pressed together by means of a pressure element 7, typically spring-loaded against a pressure head of a return element 8, under the influence of a first force K1 for obtaining a friction fit, whereby a torque introduced via the outer friction plate carrier 3 can be transmitted.

For this purpose, the outer friction plate carrier 3 is connected to the drive shaft 9, while the inner friction plate 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. operated, first sub-clutch 1.

A second sub-clutch 11 is provided, comprising: an outer friction plate carrier 12 having an outer friction plate 13 axially movable thereat; and an inner friction plate carrier 14 having an inner friction plate 15 that can be moved axially there, wherein, when a second pressure K2 is applied, the friction plate group consisting of the outer and inner friction plates 13, 15 is pressed together again via a further pressure element 16, again a pressure head, for obtaining a positive fit for transmitting torque, wherein the pressure element 16 can also be moved axially toward the return element 17.

The second outer friction plate carrier 12 is connected to the first outer friction plate carrier 3 in a rotationally fixed manner via an annular connecting element 18, so that when torque from the drive shaft 9 is introduced into the outer friction plate carrier 3, said torque is also automatically applied to the second outer friction plate carrier 12 which is forcibly rotated with the first outer friction plate carrier. The second inner friction plate carrier 14 is connected to a second output shaft 19 which extends into a second gear stage of the transmission, which is not shown 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 and rotatably supported at the housing cover 21 radially and axially via the rolling bearing 20. The rolling bearing 20 comprises an outer ring 22, and the outer friction plate carrier 3 is mounted on the outer ring 22 by means of corresponding bearing blocks 23.

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

As is shown in the enlarged illustration in particular in 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 disk carrier 3. As indicated by arrow P1 in fig. 1, the oil used 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 oil inflow is required in order to lubricate the rolling bearings 20, as is 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 carrier 24 and the drive shaft 9.

However, due to the width of the radial gap 27, there is a risk that: as 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 may lead to damage. In order to solve the problem, a sealing element 30 is provided, which is firmly mounted between the inner ring 24 and the housing cover 21, and which extends into the first radial gap and, seen radially, even slightly out of the first radial gap, see in particular fig. 2. At the outer circumference of the annular sealing element 30, a bent edge section 31 is provided, which in turn overlaps the outer ring 22 by a small distance, so that a labyrinth seal is approximately formed in this region.

By means of the annular or annular disk-shaped sealing element 30, which can be a plate element or a plastic element, it is evident that the radial gap 27 or its free flow cross section is significantly narrowed and reduced, so that, nevertheless, a smaller proportion of oil can always flow via the radial gap into the rolling bearing region and the sealing element region, which is required for lubrication, however, 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 the clutch device 1 according to the invention, wherein identical reference numerals are used for identical 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, wherein the two sub-clutches 2, 11 are also provided with the components described in relation to fig. 1, with reference to the description relating thereto.

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

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

As is evident from fig. 4, the purpose of this arrangement is to provide a sealing element 32 between the outer ring 22 and the outer friction plate carrier 3. As 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 flow back into the wet chamber via the rolling bearing 20, however, due to the narrowing of the free flow cross section of the second radial gap 28 and the labyrinth design, possible dust particles are blocked and therefore cannot reach the region.

It is preferably conceivable to provide sealing elements 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 carrier

4. External friction plate

5. Inner friction plate carrier

6. Inner friction plate

7. Pressure element

8. Reset element

9. Driving shaft

10. Output shaft

11. Sub-clutch

12. Outer friction plate carrier

13. External 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. Shell cover

22. Outer ring

23. Bearing pedestal

24. Inner ring

25. Bearing pedestal

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 clutch device, the clutch device comprising: an outer friction disc 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 disc 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 disc carrier, characterized in that at least one annular sealing element (30, 32) is provided for reducing the gap width, which annular sealing element is arranged in or radially shields the first radial gap or the second radial gap (27, 28).

2. Clutch device according to claim 1, characterized in that a 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, characterized in that at the sealing part one (30) at the outer circumference protruding from the first radial gap (27) there is provided an edge section (31) extending towards the outer ring (22) radially overlapping the outer ring (22).

4. Clutch device according to claim 1, characterized in that a sealing part one (30) is provided at the axial end side of the outer ring (22) or at the outer ring circumference.

5. Clutch device according to any of the preceding claims, characterized in that a sealing member two (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, characterised in that at the sealing part two (32) at the inner 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 one of claims 1 to 4, characterized in that a second sealing part is provided at the axial end side of the inner ring (24) or at the inner circumference.

8. Clutch device according to claim 1, characterized in that the sealing member (30, 32) is a sheet metal member or a plastic member.

9. Clutch device according to claim 1, characterized in that the clutch device is a double clutch or multiple clutch, comprising a first sub-clutch (2) and a radially inner second sub-clutch (11), wherein the first sub-clutch (2) has an outer friction plate carrier (3) supported at the housing cover (21) via the rolling bearing (20).