DE102014215171A1 - Double clutch with support via a central warehouse on a friction plate - Google Patents

Abstract

The invention relates to a coupling device (1) for a drive train of a motor vehicle, comprising a first coupling part (2), which first coupling part (2) has a first group (3) in the axial direction juxtaposed friction plates (4a, 4b, 4c) the friction disks (4a, 4b, 4c) are non-rotatably connected to one, the friction plates (4a, 4b, 4c) at least in the radial direction supporting, first support member (5) are connected, and at least one, in an engaged position of the first coupling part (2) rotatably with the friction plates (4a to 4c) connected, the first clutch disc (6), wherein the first group (3) of friction plates (4a, 4b, 4c) and the first support member (5) rotatably mounted about a radial support bearing (7) are, wherein a first friction plate (4a) of the first group (3) forms a receiving area (8), in which receiving area (8) the support bearing (7) is mounted.

Description

The invention relates to a coupling device, preferably a double clutch, for a drive train of a motor vehicle, such as a car, truck, bus or agricultural utility vehicle, with a first coupling part, which first coupling part has a first group in the axial direction juxtaposed friction plates, the friction plates rotatably with a, the friction plates at least in the radial direction supporting, first support member are connected, and which first coupling part at least one, in an engaged position of the first coupling member rotatably connected to the friction plates, first clutch disc, wherein the first group of friction plates and the first support member are mounted rotatably about a radial support bearing.

Coupling devices are already known from the prior art in various designs. The Applicant is already known internally prior art, which has already been filed as a German patent application to the German Patent and Trademark Office, but has not yet been published. This on July 25, 2013 at German Patent and Trademark Office filed patent application with the official file number 10 2013 214 505 discloses a powertrain for a motor vehicle, comprising a gearbox housed in a transmission and at least one rotatably mounted by means of a gearbox bearing on the transmission housing and a transmission input shaft mounted on the at least one transmission input friction clutch, wherein the at least one transmission input shaft between an axial fixed bearing of the friction clutch and the at least a transmission input shaft and the transmission bearing is torsionally coupled axially biased.

Another internal, not yet published prior art is the applicant from the already filed on 25 March 2014 at the German Patent and Trademark Office German patent application with the official file number 10 2014 205 506 known. With this patent application, a double clutch for a drive train of a motor vehicle is disclosed, wherein the dual clutch has two rotatably connected to each other and at least one friction disc receiving outer carrier. The first outer carrier is driven in an operating state of the clutch from an output shaft of an internal combustion engine and with its at least one friction disc rotatably connected to a, a first transmission input shaft driving, first inner carrier connectable. A second outer support is rotatably connected with its at least one friction disc with a second transmission input shaft driving, second inner support connected. In addition, a first and the second outer support rotatably relative to the transmission input shafts rotatably bearing bearing element is present, wherein the bearing element is designed as a, the first and the second outer support axially and radially bearing central warehouse.

From this state of the art clutches are still known, wherein the actuated for actuating the respective coupling parts actuating force, for example, is introduced in a pressure pot, which in turn is supported via one or more contact plates / friction plates to the plate carrier / the support member and the support bearing. However, these known constructions have the disadvantage that the necessary stacking of the support element, the pressure plates, the friction plates / clutch plates and the pressure pots of the respective coupling parts requires a relatively large axial space. In addition, this axial space is further increased in dry-running clutches, since the dry-running clutches usually need thick pressure plates / friction plates. In addition, in particular, the Ankllamellen / friction plates / pressure plates of the inner clutch, i. of the inner (first) coupling part, have a relatively high loss of material in the production of individual parts. Furthermore, ventilation of the end plate / first friction plate is not ensured when the clutch is open, since the support element / the plate carrier surrounds the blades. It may possibly even happen that the end plate remains in contact with the clutch disc / the friction disc even with the clutch open and an additional drag torque is generated.

It is an object of the present invention to overcome these known from the prior art disadvantages and to exploit the space of couplings in the axial direction more efficient or reduce, further, the number of items should be reduced and / or the items are to be made easier , which in turn should reduce the cost of producing the clutch.

This is inventively achieved in that a first friction plate of the first group forms a receiving area (preferably immediately), in which receiving area the support bearing mounted / arranged / fixed.

This makes it possible to directly connect one of the already existing friction plates of Reiblamellenpaketes / the first group of friction plates directly to the support bearing and thus to effect a direct radial and preferably axial bearing of the friction plates as possible. As a result of the connection of the first carrier element to the first friction plate, the first carrier element is again mounted in the radial direction. This can do that first support member / the first disc carrier are made much simpler and the previously extending in the radial direction of the friction plates extending side / bottom portion of the first support member are omitted. As a result, the axial space is better utilized and the coupling can be made more compact in the axial direction. In addition, the rigidity is increased due to the support of the first friction plate.

Further advantageous Ausführungsfomen are claimed in the dependent claims and explained in more detail below.

It is advantageous if the support bearing is designed as a roller bearing, preferably as an angular contact ball bearing. The rolling bearing further preferably holds at least the first friction plate in the radial and in the axial direction. As a result, the support bearing is made very compact.

It is also advantageous if the support bearing has a bearing outer ring which is rotatably connected to the receiving region of the first friction plate. Thus, the support bearing is directly and directly connected to its bearing outer ring with the friction plate and secured thereto. More preferably, the bearing outer ring is held by means of a press fit in the receiving area of the first friction plate.

Even more preferably, in the bearing outer ring of the support bearing, a retaining ring snapped into a recess, which circlip rests with a radially outer region on the first friction plate and thus the first friction plate is supported in the axial direction. As a result, the support bearing connection is further improved.

When the first friction plate of the first group is disposed at an axial end portion of the first group (i.e., the first friction plate is arranged in an axial direction first and last, respectively), the first coupling portion is particularly easily configured.

More preferably, the first friction fin of the first group has a higher wall thickness (i.e., sheet thickness) than the first support element. This allows a particularly rigid support and a stable construction of the first coupling part.

It is also expedient if the first friction disk is disc-shaped / plate-shaped and has a centric hole, the receiving area being formed on an inner peripheral side of the first friction disk. Thus, the first friction plate can be made particularly compact and inexpensive.

The first friction plate of the first group and the first support element are further preferably non-rotatably connected to each other by means of a positive connection, particularly preferably by means of a toothing. This allows the support element and the friction plates are particularly easy to install.

It is also advantageous if the first friction plate of the first group has at least one weight reduction and / or air inlet opening, whereby the efficiency of the clutch can be further improved by either reducing the weight or cooling air can be conveyed past the friction plates in the operating state of the clutch ,

If the first friction disk of the first group is supported / held in the axial direction on the first support element by means of a securing ring, a particularly effective transport safety device is provided.

Preferably, a connecting web element is present, which rotatably connects the first support element of the first coupling part with a second support element of a second coupling part. The coupling device is therefore further preferably designed as a double clutch. Thus, the two supporting elements of the coupling parts can be particularly easily connected to each other.

In this context, it is also useful if the connecting web element is formed integrally with the first support element, whereby the structure is further simplified.

The coupling device is also designed as a dry-running or wet-running coupling device / clutch / double clutch.

In other words, a dry, alternatively wet-running mehrscheibige, ie multiple friction plates having double clutch is present, in which the outer disk carrier of the K2 (ie the first support member of the first coupling part) via a central support bearing axially on an outer transmission input shaft / a hollow shaft , The torque transmission preferably takes place via a toothing on the plate carrier, wherein the axial force support on the support bearing takes place directly over the end plate / the first friction plate and no longer on the plate carrier / the first support member. The plate carrier can be shortened accordingly and in particular no longer be supported on the transmission input shaft. To secure the transport is a locking ring between the outer disk carrier and the end of the K2 be provided.

The invention will now be described in more detail below with reference to figures in connection with several embodiments.

Show it:

1 a longitudinal sectional view of an inventive, designed as a double clutch coupling device according to a first embodiment, wherein in particular the first friction plate of the first coupling part can be seen and the first support member via a positive connection (toothing) rotatably connected to the connecting web element, and

2 a longitudinal sectional view of an inventive designed as a double clutch coupling device according to a further second embodiment, which coupling device is formed substantially according to the first embodiment, the first support member, however, is formed integrally with the connecting web element.

The figures are merely schematic in nature and are for the sole purpose of understanding the invention. The same elements are provided with the same reference numerals. Different features of the embodiments can be combined with each other.

In the 1 and 2 is in principle in each case an embodiment of a coupling device according to the invention 1 shown. The coupling device 1 is designed as a double clutch and therefore below as a double clutch 1 designated. Further preferred is the coupling device 1 Also designed as a single clutch.

Designed as a multi-plate clutch / multi-plate clutch coupling device 1 / Double coupling 1 is intended for a drive train of a motor vehicle, namely a car, truck, bus or agricultural utility vehicle and usually arranged in this drive train between a crankshaft and two transmission input shafts of a transmission. The double clutch 1 always has a first coupling part 2 up in the two in the 1 and 2 illustrated embodiments designed as an internal coupling part and is also referred to as K2 coupling part. The first coupling part 2 has a first group 3 in the axial direction juxtaposed friction plates 4a . 4b . 4c on. These several friction plates 4a . 4b . 4c the first group 3 are non-rotatable with one, the friction plates 4a . 4b . 4c at least in the radial direction supporting, first support element 5 (Also referred to as the first plate carrier) connected. The first support element 5 supports the friction plates 4a . 4b . 4c in a radial direction to the outside. In addition, the first coupling part 2 at least one, namely several / two first clutch discs 6 on, in an engaged position of the first coupling part 2 rotatably with the friction plates 4a . 4b . 4c ie with the first group 3 on friction plates 4a . 4b . 4c are connected. The first group 3 of friction plates 4a . 4b . 4c and the first support element 5 are about a radial support bearing 7 rotatably mounted. A first friction plate 4a the first group 3 of friction plates has a receiving area 8th and forms this directly from, in which receiving area 8th the support bearing 7 directly attached / arranged / attached.

The following will now first closer to the first embodiment 1 However, the basic properties and properties as well as the modes of operation also apply to the second embodiment 2 apply and are considered integrated.

The first coupling part 2 has, as already described, the first group 3 of friction plates 4a . 4b . 4c on. This is indicated by the first group 3 specifically three disc-shaped / plate-like friction plates 4a . 4b . 4c on. In addition to the first friction plate 4a are also a second friction plate 4b and a third friction plate 4c provided, which friction plates 4a . 4b . 4c all spaced in the axial direction and are arranged side by side. In a respective axial space between the first friction plate 4a and the second friction plate 4b or the second friction plate 4b and the third friction plate 4c is a first clutch disc 6 arranged. The total of two first clutch discs 6 are connected to each other in a rotationally fixed manner.

The two first clutch discs 6 are in an operating state of the double clutches 1 further rotatably connected to a here not shown for clarity, the first transmission input shaft of a transmission of the motor vehicle. The first transmission input shaft is designed as a hollow shaft.

On the first transmission input shaft / hollow shaft is the first friction plate 4a by means of the support bearing 7 stored and supported during operation. The central support bearing 7 (Also referred to as a central warehouse) has a bearing outer ring 9 on, the rotation with the first friction plate 4a namely the recording area 8th , connected is. Also, the support bearing points 7 a relative to the bearing outer ring 9 rotatably arranged bearing inner ring 10 on which bearing inner ring 10 in turn is rotatably connected to the outer peripheral side of the first transmission input shaft. The support bearing 7 is designed as an angular contact ball bearing and therefore by means of a plurality of rolling elements uniformly distributed along the circumference 11 (rolling elements 11 are designed as balls) rotatably mounted.

On a radial outer peripheral side / surface of the bearing outer ring 9 is the recording area 8th the first friction plate 4a directly and directly held / attached. For this purpose, the first friction plate 4a in the area of the recording area 8th such that, formed by a central hole, it has an inner circumferential surface which is dimensioned with respect to its inner diameter such that it essentially forms a press fit with the bearing outer ring 9 received. As additional axial securing is a (first) locking ring 12 provided in a circumferential groove of the bearing outer ring 9 namely, on a groove along the outer peripheral surface of the bearing outer ring 9 is engaged. With a radial outer side supports the first retaining ring 12 again directly an axial side of the first friction plate 4a off, leaving the first friction plate 4a over this first circlip 12 is supported in an axial direction. The first circlip 12 supports the first friction plate 4a from one axial side, that of the second friction plate 4b turned away, additionally off. The support bearing 7 thus serves both as an axial and as a radial bearing element for the first friction plate 4a ,

The first friction plate 4a is from the three friction plates 4a to 4c the first group 3 at one axial end of the group 3 arranged so that they also as end fin 4a is designated. The third friction plate 4c is designed as a first pressure plate and consequently as the first pressure plate 4c designated. For closing the first coupling part 2 is a first pressure pot 13 provided for moving the first coupling part 2 in a engaged position / in the engaged position is used. The first pressure pot 13 is provided for this purpose on the first pressure plate 4c to push and the the first clutch discs 6 thus between the friction plates 4a to 4c clamp so that the first clutch discs 6 frictionally engaged with the friction plates 4a connect. To disengage the first pressure pot 13 again in an axial direction away from the friction plates 4a to 4c moves, causing the first pressure plate 4c from the other friction plates 4b . 4c removed and the Reibkraftschluss is finally solved, so that in the disengaged position of the first coupling part 2 no more torque between the friction plates 4a to 4c and the first clutch discs 6 is transferable.

In the radial direction outside the first group 3 of friction plates 4a . 4b . 4c is the first support element 5 , also known as the first plate carrier of the K2 is designated arranged. The first support element 5 supports the friction plates 4a to 4c in the radial direction to the outside. The first support element 5 also serves as a guide member for at least the second and third friction plate 4b and 4c in the axial direction. These two friction plates 4b and 4c are displaceable in the axial direction, but fixed in the radial direction with the first support element 5 connected. The first support element 5 is vorzugszeise on its inner peripheral side by means of a positive connection in the form of a toothing 14 with the first friction plate 4a connected. The first support element 5 extends substantially in the axial direction and is sleeve-shaped. At a first end region of the first support element 5 , namely at an end region in which the first support element 5 with the first friction plate 4a is another (second) circlip 15 provided to an axial stop for the first friction plate 4a embody.

In addition, the first friction plate 4a in a radial area between the receiving area 8th and the gearing 14 a plurality of openings distributed along the circumference 23 , which may also be called or formed as windows or through-holes / through-holes introduced. These openings 23 serve for weight reduction and / or air intake to cool during operation, such as air in a dry-running dual clutch 1 in the region of frictional engagement between the first clutch discs 6 and the friction plates 4a to 4c initiate.

At a second (axial) end region of the first support element facing away from the first (axial) end region 5 is a connecting bridge element 16 mounted in the form of a substantially disc-shaped support member. This connecting web element 16 is on its radially inner side by means of a toothing, not shown here for clarity form-fitting and thus rotationally fixed to the first support member 5 connected. At a radial outside (connecting web element 16 extends from the first support element 5 away in the radial outward direction) is the connecting web element 16 then in turn rotatably also by means of a further toothing with a second support member 17 , which is also referred to as a second plate carrier connected.

The second support element 17 is part of a second coupling part 2 which is substantially in the radial direction outside of the first coupling part 2 is arranged. The second coupling part 18 (Also referred to as K1 coupling part) is essentially like the first coupling part 2 formed and also has a group of friction plates, namely a second group 19 of friction plates on. Here are two friction plates 20a and 20b , hereinafter also referred to as fourth and fifth friction plate 20a and 20b are designated in the second group 19 intended. The two friction plates 20a and 20b are arranged in the axial direction next to each other and at a distance, wherein in a space between these friction plates 20a and 20b a second clutch disc 21 is arranged. The second clutch disc 21 is again in an engaged state of the second coupling part 18 rotatable with the second group 19 connected and thus rotationally fixed to the second support member 17 connected. The second clutch disc 21 is in turn connected to a second transmission input shaft, not shown for clarity, which is designed as a solid shaft. The second support element 17 is cup-shaped. The second support element 17 is also in the operating state with a dual mass flywheel and the dual mass flywheel rotatably connected to a crankshaft.

For actuating the second coupling part 18 Here is a second pressure pot 22 provided for actuating the second coupling part 18 is displaceable in the axial direction and thus the second coupling part 18 between a coupled and a disengaged position according to the first pressure pot 2 of the first coupling part 2 moved back and forth.

It should also be noted that the double clutch 1 as they are in 1 is shown, designed as a dry-running clutch and is directly operated. Alternatively, however, it can also be used as a wet-running, preferably directly actuated double clutch 1 be designed.

In 2 Then, the second embodiment is formed, but essentially as the double clutch 1 of the first embodiment according to 1 is designed and functioning. Unlike the 1 Here is only the first support element 5 integral with the connecting web element 16 educated. Thus, the first support element 5 a substantially cup-shaped configuration, wherein at an axial end portion of the connecting web element 16 is integrally formed.

In other words, a bearing of a multi-plate clutch (dual clutch 1 ) via a support bearing 7 implemented on a transmission input shaft, wherein the torque transmission via a toothing 14 on the disk carrier (first support element 5 ) and the axial force support on the support bearing 7 directly over the end lamella 4a takes place and no longer on the plate carrier 5 , For a single or double clutch 1 takes over the plate carrier 5 the torque transmission the support of a spring element. The contact force is no longer axially supported on the plate carrier 5 but directly on the end plate 4a and the support camp 7 , The inner diameter of the end plate 4a is up to the support camp 7 reduced. The plate carrier 5 no longer needs to support camp 7 be drawn. For double clutches 1 can this outer plate carrier 5 with the connecting bridge 16 be unified. Three individual parts are simplified in two. In addition, the interior of the connecting bridge 16 better exploited. A transport lock from the end lamella 4a in the plate carrier 5 can by an axial circlip 15 in the plate carrier 5 installed and thus easily realized. Into the interior of the end lamella 4a can recesses 23 be provided to reduce moments of inertia and a ventilation of the clutch 1 to enable. The end lamella 4a has a larger wall thickness than the plate carrier 5 , whereby the coupling stiffness is increased.

LIST OF REFERENCE NUMBERS

1

 Coupling device / double clutch

2

 first coupling part

3

 first group of three friction plates

4a

 first friction plate

4b

 second friction plate

4c

 third friction plate

5

 first support element

6

 first clutch disc

7

 support bearings

8th

 reception area

9

 Bearing outer ring

10

 Bearing inner ring

11

 rolling elements

12

 first circlip

13

 first pressure pot

14

 gearing

15

 second circlip

16

 Connecting web element

17

 second support element

18

 second coupling part

19

 second group

20a

 fourth friction plate

20b

 fifth friction plate

21

 second clutch disc

22

 second pressure pot

23

 opening

QUOTES INCLUDE IN THE DESCRIPTION

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

Cited patent literature

• DE 102013214505 [0002]
• DE 102014205506 [0003]

Claims (10)

Coupling device ( 1 ) for a drive train of a motor vehicle, with a first coupling part ( 2 ), which first coupling part ( 2 ) a first group ( 3 ) in the axial direction juxtaposed friction plates ( 4a . 4b . 4c ), wherein the friction plates ( 4a . 4b . 4c ) rotatably with one, the friction plates ( 4a . 4b . 4c ) supporting at least in the radial direction, the first support element ( 5 ), and at least one, in a coupled position of the first coupling part ( 2 ) rotatably with the friction plates ( 4a to 4c ), first clutch disc ( 6 ), the first group ( 3 ) of friction plates ( 4a . 4b . 4c ) and the first support element ( 5 ) about a radial support bearing ( 7 ) are rotatably mounted, characterized in that a first friction plate ( 4a ) of the first group ( 3 ) a receiving area ( 8th ) in which receiving area ( 8th ) the support bearing ( 7 ) is attached. Coupling device ( 1 ) according to claim 1, characterized in that the support bearing ( 7 ) is formed as a rolling bearing. Coupling device ( 1 ) according to claim 1 or 2, characterized in that the support bearing ( 7 ) a bearing outer ring ( 9 ) which is non-rotatable with the receiving area ( 8th ) of the first friction plate ( 4a ) connected is. Coupling device ( 1 ) according to one of claims 1 to 3, characterized in that the first friction plate ( 4a ) at an axial end region of the first group ( 3 ) is arranged. Coupling device ( 1 ) according to one of claims 1 to 4, characterized in that the first friction plate ( 4a ) has a greater wall thickness than the first support element ( 5 ) having. Coupling device ( 1 ) according to one of claims 1 to 5, characterized in that the first friction plate ( 4a ) and the first support element ( 5 ) are rotatably connected to each other by means of a positive connection. Coupling device ( 1 ) according to one of claims 1 to 6, characterized in that the first friction plate ( 4a ) at least one weight reduction and / or air inlet opening ( 23 ) having. Coupling device ( 1 ) according to one of claims 1 to 7, characterized in that the first friction plate ( 4a ) in the axial direction on the first support element ( 5 ) by means of a retaining ring ( 15 ) is supported. Coupling device ( 1 ) according to one of claims 1 to 8, characterized in that a connecting web element ( 16 ), which is the first support element ( 5 ) of the first coupling part ( 2 ) with a second support element ( 17 ) of a second coupling part ( 18 ) rotatably connected, wherein the coupling device ( 1 ) is formed as a double clutch. Coupling device ( 1 ) according to claim 9, characterized in that the connecting web element ( 16 ) integral with the first support element ( 5 ) is trained.

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