CN109790875B

CN109790875B - Double clutch device

Info

Publication number: CN109790875B
Application number: CN201780062095.1A
Authority: CN
Inventors: A·西蒙诺夫; M·奥托
Original assignee: Schaeffler Technologies AG and Co KG
Current assignee: Schaeffler Technologies AG and Co KG
Priority date: 2016-10-06
Filing date: 2017-09-28
Publication date: 2021-03-23
Anticipated expiration: 2037-09-28
Also published as: DE112017005073A5; CN109790875A; WO2018065009A9; WO2018065009A1; DE102016219326A1

Abstract

The invention relates to a dual clutch device comprising a first clutch device (2) comprising a first outer disk carrier (3) having an associated first outer disk (4) and comprising a first inner disk carrier (5) having an associated first inner disk (6), and comprising a first outer disk carrier (3) having an associated first outer disk (4), wherein the first outer disk (4) and the first inner disk (6) form a first disk set (9), and a second clutch device (11) comprising a second outer disk carrier (12) having an associated second outer disk (13) and comprising a second inner disk carrier (14) having an associated second inner disk (15), wherein the second outer disk (13) and the second inner disk (15) form a second disk set (18), wherein the first inner disk carrier (5) is connected to a first output hub (8) in a rotationally fixed manner, the second inner plate carrier (14) is connected in a rotationally fixed manner to a second output hub (17), wherein a first lubricant duct (20) leading to the first plate package (9) and a second lubricant duct (21) leading to the second plate package (18) are provided, wherein the two lubricant ducts (20,21) are separated from one another, and each lubricant duct (20,21) can be supplied with lubricant individually via at least one lubricant supply opening (22,23) provided in each of the first and second output hubs (8, 17).

Description

Double clutch device

Technical Field

The invention relates to a dual clutch device comprising a first clutch device and a second clutch device arranged radially within the first clutch device, the first clutch device comprising a first outer disk carrier with an associated first outer disk and comprising a first inner disk carrier with an associated first inner disk, wherein the first outer disk and the first inner disk form a first disk set, and the second clutch device comprising a second outer disk carrier with an associated second outer disk and comprising a second inner disk carrier with an associated second inner disk, wherein the second outer disk and the second inner disk form a second disk set, wherein the first inner disk carrier is connected in a rotationally fixed manner to a first output hub and the second inner disk carrier is connected in a rotationally fixed manner to a second output hub.

Background

Such a double clutch device is used in a known manner for coupling a drive unit, for example an output of an internal combustion engine, to a transmission. This is achieved by two separate clutch devices each having a sheet pack. Each sheet pack comprises an outer sheet, which is usually arranged axially movably, on the outer sheet carrier and an inner sheet, which is likewise arranged axially movably, on the inner sheet carrier. The outer or inner sheet usually has a friction layer, so that a friction lock is formed when the respective sheet packs are pressed together by an annular actuating element, for example a press can. The torque transmitted via the drive shaft to the outer disk carrier can thereby be transmitted via the inner disk carrier to the corresponding output hub to the clutch. The two clutch devices can be actuated separately, i.e. one clutch device can be closed while the other clutch device is open, and vice versa. In the embodiment of the dual clutch device referred to here, the two clutch devices are arranged radially, i.e. the first clutch is radially further outside than the second clutch located inside the first clutch. The structure and function of such a double clutch device has long been known.

One embodiment of such a dual clutch device is a wet dual clutch. In the wet double clutch, in order to conduct away heat from the plate packets which become hot as a result of the frictional engagement being formed when closed, an oil flow is guided through the plate packets. Since a radial clutch configuration is currently described, the oil which is usually supplied via one of the two output hubs flows through the two plate sets from the radially inner to the radially outer side, i.e. the oil first flows through the plate set which is radially inner and then continues to the plate set which is radially outer. This achieves cooling of the individual plate groups or of the clutch device. In this connection, however, the respectively open clutch is also always flooded with oil, so that oil flows through the open clutch. This results in a drag torque after a certain coupling of the outer disk rotated by the oil with the inner disk which is not rotated in the open state of the clutch device.

Disclosure of Invention

The problem on which the invention is based is that of specifying an improved clutch device in comparison therewith.

In order to solve this problem, according to the invention, a first lubricant duct leading to the first plate set and a second lubricant duct leading to the second plate set are provided in the case of a dual clutch device of the type mentioned at the outset, wherein the two lubricant ducts are separated from one another and each lubricant duct can be supplied with lubricant individually via in each case at least one lubricant supply opening provided in the first and second output hubs.

In the dual clutch device according to the invention, the lubricant is supplied separately to the respective clutch device, i.e. to the respective partial clutch. This is achieved by the individual lubricant ducts being separated as far as possible from one another, so that the lubricant can flow in a defined manner into one clutch device and into the other clutch device.

The individual lubricant ducts, which are in the form of annular ducts extending radially from the inside to the outside, are realized here by corresponding output hubs to which the corresponding inner plate carriers of the first and second clutch devices are attached. For this purpose, at least one lubricant supply opening is provided in each of the first and second output hubs. Thus, lubricant is guided via the respective output hub into the respective lubricant channel and via said lubricant channel to the respective sheet pack.

In this way, a constant lubricant flow can be supplied in a targeted manner only to the one or the other clutch device via the individual lubricant ducts and their individual lubricant supply. This offers the following possibilities: by means of the respective temperature and lubricant management, only the clutch devices to be supplied are supplied with lubricant, i.e. oil, i.e. the respective clutch device or the respective disk stack can be supplied with lubricant or oil optimally in accordance with its load. By targeted control of the lubricant supply to the output hub-side lubricant supply bore, the lubricant supply to the individual lubricant channels can be controlled accordingly.

As mentioned, the two lubricant ducts are separated from each other. In this respect, this is not to be understood as a complete physical separation. Rather, the two clutch devices are of course fluidly coupled to each other in some manner, since the lubricant passages may communicate with each other. The lubricant passages are not hermetically separated from each other. However, due to the functional manner of such a double clutch and due to the fact that the lubricant initially flows in the radial direction as a result of a given component rotation, a considerable separation of the lubricant channels can be achieved after each channel is assigned a separate lubricant supply opening on the respective output hub and thus lubricant is introduced into the respective channel at a defined point. The lubricant supply opening opens into the respective sheet pack in a respective channel with a radial preferential direction, so that the sheet pack is also only supplied with lubricant.

In order to be able to separate the lubricant ducts as far as possible from one another, according to an expedient further development, at least one circumferential shielding plate is arranged radially between the second outer sheet carrier and the first inner sheet carrier, which shielding plate prevents the lubricant flowing through the second sheet pack and the second outer sheet carrier provided with the through-openings from flowing to the first sheet pack. Thus, according to this embodiment of the invention, a closed shielding plate is arranged between the two partial clutches, which shielding plate separates the two clutch devices or the plate packs from one another, as viewed in the radial direction. The lubricant flow through the second plate package situated radially inside usually flows out through the second outer plate carrier provided with corresponding through-openings. By means of the shielding plate connected behind the second sheet carrier, the lubricant flow is then deflected to some extent and guided away laterally, so that it cannot continue to the first sheet set.

The shielding plate is preferably stretched radially inward in the region of the edge, so that this edge is arranged directly adjacent to the second outer sheet support. This prevents lubricant, i.e. oil, from flowing laterally between the second outer plate carrier and the shielding plate after flowing through the first disk set into the first lubricant duct leading to the first clutch device.

The shielding plate itself is preferably connected to the second outer sheet support or to a connecting member connecting the first and second outer sheet supports. Thus, the shield plate is coupled with the outer sheet holder such that the shield plate rotates with the outer sheet holder.

Alternatively or in addition to the integration of the shielding plates, which prevent the lubricant flow from the second inner plate set to the first outer plate set, it is conceivable for the second outer plate carrier to be provided with passages only in the carrier sections axially offset relative to the first plate set. As mentioned, the outer sheet holder is usually provided with a through-opening in order to lead out the lubricant flowing through the sheet pack. In the known dual clutch or clutch device, the passages are embodied as longitudinal slots extending over almost the entire length of the outer plate carrier, whereas in this embodiment according to the invention the passages are embodied only relatively short and are located in the carrier sections axially offset with respect to the first plate package. Therefore, the lubricant guided out through the through portions that are offset from each other is guided out at a position where the lubricant can no longer flow to the first sheet group located radially outward. Thus, according to this embodiment of the invention, the second outer sheet metal carrier itself is shielded, since it is closed in the region of its radial vicinity to the first sheet metal set lying radially outside, i.e. has no radial through-openings.

Of course, it is also conceivable to provide both the shielding plate and the outer sheet holder having the offset through-holes.

The through-openings which are offset in the axial direction in the outer sheet metal carrier are preferably arranged in the region which, viewed in the radial direction, is located behind the connecting element which connects the first and second outer sheet metal carriers. The leading-out therefore takes place in the region in which the radially outer first sheet metal carrier is shielded in the axial direction by the connecting element, which is usually annular or disc-shaped. The first sheet pack is located axially in front of the connecting element, while the lubricant is led out axially behind the element.

Drawings

The invention is elucidated below on the basis of embodiments with reference to the drawing. These figures are schematic and show:

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

figure 2 is a schematic view of the second outer plate carrier of the double clutch device of figure 1 in a side view,

fig. 3 is a schematic diagram of a dual clutch device according to a second embodiment of the present invention.

Detailed Description

Fig. 1 shows a dual clutch device 1 according to the invention, comprising a first clutch device 2, which comprises a first outer plate carrier 3 with an assigned first outer plate 4 and comprises a first inner plate carrier 5 with an assigned first inner plate 6. The outer plate 4 is, for example, a steel plate, while the inner plate is a friction plate with friction linings. The first outer sheet carrier 3 is connected to a drive shaft 7 which is driven by an internal combustion engine or the like. The first inner disk carrier is connected to an output hub 8, which is coupled to an output shaft leading to a transmission, not shown in detail here.

The first outer and inner plates 4,6 form a first plate group 9, wherein the individual plates are arranged on the outer and

inner plate carriers

3,5 so as to be axially movable. The first outer plate and the first inner plate are pressed together axially by the actuating element 10, in this case, for example, by pressing on the can, so that a frictional connection is obtained and the first clutch device 2 can be closed if required.

Furthermore, a second clutch device 11 is provided, which comprises a second outer plate carrier 12 with an associated second outer plate 13, which is also a steel plate. Furthermore, a second inner plate carrier 14 is provided, which has an inner plate 15 arranged thereon, which is also a friction plate with friction linings.

The second outer plate holder 12 is coupled with the first outer plate holder 3 by means of a connecting member 16 such that rotation of the first outer plate holder 3 automatically results in rotation of the second outer plate holder 12. The second inner disk carrier 14 is coupled to a second output hub 17, which also leads to a transmission, not shown in detail.

The second outer and

inner plates

13,15 also form a second plate set 18, which can be pressed together, if necessary, by the actuating element 9, here in the exemplary case also a pressure pot, in the axial direction, as a result of the axially movable mounting of the outer and

inner plates

13,15 on the outer and

inner plate carriers

12,14, so that here too a frictional engagement occurs and the clutch device 11 is closed.

Depending on the open state and the closed state, the torque introduced via the drive shaft 7 can be transmitted either via the clutch device 2 to the first output hub 8 or via the second clutch device 11 to the second output hub 17. The basic structure and function of such a double clutch device 1 are known.

For the separate supply of lubricant either to the first clutch device 2 or the second clutch device 11 or to the first plate set 9 or the second plate set 18, two

separate lubricant ducts

20,21 are provided, which are largely separated from one another. Lubricant, i.e. oil, can be supplied in a targeted manner to the first clutch device 2 via the first lubricant duct 20, and lubricant can be correspondingly supplied to the second clutch device 11 via the second lubricant duct 21.

In order to feed each of these channels individually with lubricant, the two

output hubs

8,17 have separate lubricant supply bores 22,23, respectively. Preferably, a plurality of such lubricant supply holes 22,23 are distributed around the circumference of the

output hubs

8,17, so that lubricant can be guided as circumferentially as possible into the

respective lubricant channel

20,21, which is a circumferential annular channel.

The lubricant supply is shown by respective arrows a, B. The lubricant supply preferably takes place via a respective output shaft to the transmission, which output shaft has a respective supply bore.

The corresponding lubricant flow is shown either by the flow line C in the first lubricant duct 20 or by the flow line D in the second lubricant duct 21. It can be seen that the lubricant supplied via the lubricant supply opening 22 flows first in an intermediate chamber in the radial direction between the first inner sheet holder 5 and a support plate 24 arranged on the second inner sheet holder 14. The lubricant then flows laterally past the radially further inner second clutch device 11, i.e. past the second plate package 18. Since the rotating parts, in particular the continuously rotating

outer disk carriers

3,12 and the corresponding inner disk carriers of the closed clutch device, are present in the clutch system, an initially radially directed flow direction is necessarily obtained. This results in the lubricant flowing laterally along the second clutch device 11 to the first clutch device 2. The lubricant flowing radially from below onto the first inner sheet holder 5 flows through the radial through-openings 25 on the first inner sheet holder 5 and reaches the first sheet package 9 and there between the sheets 4,6 in order to cool these. The lubricant can then leave the first clutch device 2 again via the respective through-openings 26 in the outer plate carrier 3, which are radially and in the form of oblong holes.

The lubricant supply in the direction of the first clutch device is effected only when the clutch device 2 is closed, so that the clutch device is actively cooled when there is a friction process and thus heat is generated. However, if the clutch device 2 is open, no active lubricant supply takes place, so that the drag torque between the ventilated inner and outer plates 4,6 separated from one another is reduced, since there is only a small amount of coupled lubricant which can lead to drag torques.

The lubricant then flows onto the second inner sheet holder 14 and through it to the second sheet pack 18 via the respective through-openings 27. The lubricant then flows to the second outer sheet support 12. In contrast to the first outer sheet holder 3, which has a plurality of through openings 26 distributed in the axial direction and in the circumferential direction or a plurality of through openings 26 in the form of elongated holes, the second outer sheet holder 12 has corresponding through openings 29 only in holder sections 28 which are offset axially with respect to the first sheet pack 9, as is shown by way of example in fig. 2. The remaining region of the second plate carrier 12 is closed, i.e. the region adjacent to the first clutch device 2 or the first plate package 9, in particular when viewed radially, is closed. This results in that, after the outer disk carrier 12 is closed on one side, the lubricant from the second disk stack 18 flows axially on the inside of the second outer friction surface carrier 12 to the other side. The lubricant reaches the through-openings 29 and flows out of the plate package region via these through-openings. However, as shown in fig. 1, these through portions 29 are axially displaced from the first sheet set 9. These through-openings are arranged in the region "behind" the ring-shaped or disc-shaped connecting member 9, i.e. the region separated from the actual plate package region by the connecting member 16. In this way it is ensured that lubricant flowing through the second sheet pack 18 does not reach the first sheet pack 9.

This configuration also makes it possible to supply the second disk set 18 with lubricant in a targeted manner, if required, when the second clutch device 11 and thus the second disk set 18 are closed. If the second sheet pack is open, no active lubricant supply takes place. The possible drag torque between the separate, ventilated

sheets

13,15 is significantly reduced, since only a small amount of lubricant is present in the area of the sheets.

The supply of lubricant via the

lubricant openings

22,23 into the first or

second lubricant duct

20,21 can be effected by the respective valve unit connected upstream, which regulates the lubricant supply to the respective output hub, as a function of the desired or given closing state of the

clutch device

2, 11.

Fig. 3 shows an alternative embodiment of the double clutch device according to the invention, wherein the same reference numerals are used for the same components whenever necessary. The structure is the same as the structure according to fig. 1. That is, the dual clutch device 1 in fig. 3 also has the first clutch device 2 and the second clutch device 11. The first clutch device 2 has an outer plate carrier 3 with axially movable outer plates 4 and an inner plate carrier 5 with axially movable inner plates 6. The second clutch device also has an outer plate carrier 12 with an outer plate 13 axially movable thereon and an inner plate carrier 14 with an inner plate 15 axially movable thereon. Again, two separate

lubricant supply channels

20,21 are provided, which are supplied with lubricant via separate lubricant supply bores 22,23 formed on the

output hubs

8, 17.

The basic structure and function corresponds to the exemplary embodiment according to fig. 1, as described. Since here the two plate groups 9,18 can also be supplied with lubricant actively when required, individually via the

respective lubricant ducts

20, 21.

In contrast to the embodiment according to fig. 1, in order to separate or shield the first clutch device 2 from the second clutch device 11 in the radial direction, an axially extending circumferential shielding plate 30 is provided, which is arranged between the second outer plate carrier 12 and the first inner plate carrier 5, as viewed in the radial direction. The shielding plate 30, which is fastened with its other end to the connecting element 16 in the example described, i.e. the shielding plate 30 rotates with the

outer sheet holders

3,12, is bent or bent radially inward with its free edge 31 such that it extends as closely as possible adjacent to the second outer sheet holder 12.

The outer plate carrier 2 has a radial through-opening 29, which is conventional per se, here in the form of a circumferentially distributed elongated hole, which also exists in the region of the outer plate carrier 12 radially adjacent to the first clutch device 2. Since the lubricant is prevented from further flowing to the first clutch device 2 by the closed, non-perforated shielding plate 30. The lubricant thus flows axially sideways as shown in fig. 3 and to some extent "behind" the disc-shaped or annular connecting member.

In this case, a separate shielding plate 30 is provided for the purpose of radial shielding, while in the embodiment according to fig. 1 the second outer plate carrier 12 is perforated by means of the through-openings 29 only in certain regions, which are not adjacent to the first clutch device 2 when viewed in the radial direction.

It is of course conceivable to integrate a shielding plate 30 as shown in fig. 3 also in the dual clutch device 1 in fig. 1.

List of reference numerals

1 double clutch device

2 Clutch device

3 outer sheet support

4 outer sheet

5 inner sheet support

6 inner sheet

7 drive shaft

8 output hub

9 sheet pack

10 operating element

11 clutch device

12 outer sheet support

13 outer sheet

14 inner sheet support

15 inner sheet

16 connecting member

17 output hub

18 sheet pack

19 operating element

20 lubricant passage

21 lubricant passage

22 lubricant supply hole

23 lubricant supply hole

24 support plate

25 penetrating part

26 through part

27 penetration part

28 cradle section

29 penetration part

30 shield plate

31 edge

Claims

1. Double clutch device comprising a first clutch device (2) comprising a first outer disk carrier (3) having an associated first outer disk (4) and comprising a first inner disk carrier (5) having an associated first inner disk (6), and comprising a first outer disk carrier (3) having an associated first outer disk (4), wherein the first outer disk (4) and the first inner disk (6) form a first disk stack (9), and comprising a second outer disk carrier (12) having an associated second outer disk (13) and comprising a second inner disk carrier (14) having an associated second inner disk (15), wherein the second outer disk (13) and the second inner disk (15) form a second disk stack (18), wherein the first inner disk carrier (5) is connected in a rotationally fixed manner to a first output hub (8), the second inner plate carrier (14) is connected in a rotationally fixed manner to a second output hub (17), characterized in that a first lubricant duct (20) leading to the first plate package (9) and a second lubricant duct (21) leading to the second plate package (18) are provided, wherein the two lubricant ducts (20,21) are separated from one another, which separation is achieved in part by a support plate (24) arranged on the second inner plate carrier (14), and each lubricant duct (20,21) can be supplied with lubricant individually via at least one lubricant supply opening (22,23) provided in each of the first and second output hubs (8, 17).

2. A double clutch device according to claim 1, characterised in that at least one circumferential shielding plate (30) is arranged radially between the second outer plate carrier (12) and the first inner plate carrier (5), which shielding plate prevents lubricant flowing through the second plate set (18) and the second outer plate carrier (12) provided with a through-going portion (29) from flowing to the first plate set (9).

3. The double clutch device as claimed in claim 2, characterized in that the shielding plate (30) is stretched radially inward with an edge region such that an edge (31) is arranged directly adjacent to the second outer sheet metal carrier (12).

4. The double clutch device as claimed in claim 2 or 3, characterized in that the shielding plate (30) is connected with the second outer plate carrier (12) or with a connecting member (16) connecting the first and second outer plate carriers (3, 12).

5. A double clutch device according to claim 1, characterised in that the second outer plate carrier (12) is provided with through-openings (29) only in carrier sections (28) which are axially offset with respect to the first plate pack (9).

6. The double clutch device as claimed in claim 5, characterized in that the through-section (29) is arranged in a region which, viewed in the radial direction, is behind a connecting member (16) connecting the first and second outer plate carriers (3, 12).