DE102015213873A1 - Axial multi-plate clutch - Google Patents

Abstract

A clutch unit comprises at least two partial clutches, wherein each partial clutch is designed as a multi-plate clutch with a disk set. The clutch assembly includes actuators for axial compression of the two disc packs independently of each other to allow a torque flow through each of the partial clutch, which is associated with the compressed disc pack. In this case, actuating directions of the actuators, each directed axially to the compression of the first and second plate packs, and elastic elements are provided which act counter to the actuating directions on the actuators, wherein at least one of the elastic elements is arranged radially within the disk packs.

Description

The present invention relates to a dual clutch, in particular for use in a drive train of a motor vehicle. Double clutches are z. B. from the DE 10 2010 051 447A1 known. Here, the disk sets of the individual clutches of the double clutch are arranged radially to each other. As a result, a relatively large radial space is needed. An axial arrangement of several partial couplings with different outer diameters is in DE 20 2013 226 359 A1 proposed.

The object of the invention is to reduce the radial space of a double multi-plate clutch. The object is achieved by a double multi-plate clutch according to claim 1. Further developments of the invention are described in the subclaims.

A clutch unit comprises at least two partial clutches, wherein each partial clutch is designed as a multi-plate clutch with a disk set. The clutch assembly includes actuators for axial compression of the two disc packs independently of each other to allow a torque flow through each of the partial clutch, which is associated with the compressed disc pack. In this case, actuating directions of the actuators, each directed axially to the compression of the first and second plate packs, and elastic elements are provided which act counter to the actuating directions on the actuators, wherein at least one of the elastic elements is arranged radially within the disk packs.

The elastic element can be advantageously provided in this way space-saving or with little design effort in the region of the clutch unit.

It is further preferred that the other elastic element is arranged radially within the disk packs. An available space for the clutch unit can be further exploited so improved. The elastic elements can be structurally easily connected to each other, for example, to be jointly supported axially or in the circumferential direction.

In a particularly preferred embodiment, the elastic elements, each of which can also be called a release spring, are arranged between axially outer boundaries of the disk packs. In other words, the elastic elements can not axially exceed axial limits of a unit that includes both disk packs. The space available radially and axially within the arrangement of disk packs can thereby be utilized in an improved manner.

In a further embodiment, the elastic elements are arranged radially offset. This measure can help to keep an axial space requirement of the clutch unit small. In addition, elements for the transmission of actuating forces can be designed so easier to the individual disk packs.

It is preferred that each actuator comprises a hydraulic piston-cylinder unit and the pistons of the two units are axially moved in the same direction when actuated. The piston-cylinder units can thus be supported on the same axial side against the resulting actuating forces. The piston-cylinder units can be carried out in particular advantageously integrated with each other. In one embodiment, the piston-cylinder units are designed concentrically to each other.

An actuator may be provided between an actuator and a disk pack, wherein the elastic elements act on the actuating means. The transmission of the actuating forces from the piston-cylinder units to the disk packs and the transmission of restoring forces from the elastic elements to the actuators can be done with reduced effort by means of the same element.

It is further preferred that the actuating means are cup-shaped. A radial interleaving of the actuating means can be used so easy to build the clutch unit compact.

It is generally preferred that the coupling unit is set up to run in a liquid bath or in a space which is not completely filled with oil. One speaks in this context of a wet or wet-running clutch unit or a double clutch.

A clutch unit preferably comprises a radially small double-wet clutch (DK), which can be actuated by means of a hydrostatic actuator. In this DK, the two partial clutches are arranged axially, with CSCs can be operated in the same axial direction. The actual actuator does not rotate. A CSC (Concentric Slave Cylinder) comprises a release bearing and a hydraulic slave piston, which are preferably combined in a separately manageable unit. A double CSC preferably used on the clutch unit comprises two concentrically arranged assemblies the type described for the independent operation of both partial clutches of a double clutch.

The dual CSC is preferably screwed against the bell bottom via three arms that protrude radially beyond the coupling. The power flow takes place internally via the cover bearing. The CSC and the DK may form an assembly, as will become more apparent from the following and from the attached figures.

In one embodiment, the dual CSC may be disconnected from the coupling assembly and bolted to the bell bottom as a single assembly. The power flow then takes place via the main bearing via the clutch cover in the transmission. The clutch cover may include a radial bearing for supporting a shaft of the dual clutch.

The proposed dual clutch may include different embodiments, some of which are outlined below:
A clutch unit comprises at least two partial clutches, which are in each case multi-plate clutches, wherein the two partial clutches are arranged one behind the other in the axial direction and the plate packs of the partial clutches are arranged without overlapping in the axial direction.

The plate packs of the partial clutches may each have an end plate and be axially displaced via an actuator, the end plate to bring the input disks and output disks in abutment with each other, so that torque can be transmitted. In this case, the actuator consists of a piston-cylinder unit and the piston-cylinder units for the two partial clutches are preferably provided radially nested one inside the other, in particular in a unit in the manner of a double Concentric Slave Cylinder (CSC).

In this embodiment, the CSC via actuating means from one axial side, preferably the transmission side, acting on both end plates of both partial clutches to actuate the clutches.

The partial clutches may each have operable end plates for actuating the partial clutch and the end plates of the partial clutches may each be axially displaceable in the same direction, preferably from the transmission side to the motor side.

In the clutch assembly according to any one of Embodiments 2 or 3, the double CSC may be fixed to the housing with respect to the transmission case.

The double CSC may comprise a housing having a plurality, preferably three, radially extending arms, wherein the arms preferably radially exceed the multi-plate clutches of the partial clutches. The housing is fixed to the clutch bell via the arms, d. H. connected to the transmission housing.

The double CSC and the partial couplings can be an assembly and the power flow can be closed via a cover bearing between the clutch cover and CSC housing inside the clutch.

Alternatively, the dual CSC and the partial clutches may be two assemblies, with the CSC connected to the transmission housing, preferably by means of a screw connection. The power flow during actuation can be closed via a main bearing on the motor side via a sealing cover of the clutch unit and via the gearbox housing.

The clutch unit may include a wet clutch unit. The elements of the clutch unit run in a liquid environment, for example in an oil bath (see above). A flow of liquid to predetermined locations of the clutch assembly may be effected, for example, by means of a pump and / or a fluid passage.

Other embodiments of the clutch assembly, to which the invention is not limited and from which may arise independent features of the invention are shown in the accompanying figures. Show it:

1 a dual clutch device with power flow via a transmission-side cover bearing;

2 an alternative embodiment of a dual clutch device to 1 with power flow via a motor-side main bearing;

3 the dual clutch device after 1 on a device for transmitting torque;

4 a further embodiment of the dual clutch device according to 1 ;

5 Yet another embodiment of the dual clutch device according to 1 ;

6 Yet another embodiment of the dual clutch device of 1 ; and

7 different views of a holding element of the dual clutch device of 6 ,

The 1 and 2 Both show a double clutch, which is constructed in each case in wet construction and axially. In 1 the power flow takes place via a cover bearing. In 2 the power flow takes place via a motor-side main bearing, which is supported in the seal cover.

In 1 is the general structure of the double clutch, as he up to the storage also for the 2 applies, shown. The actuation of the slats takes place via pressure pots but also the use of levers, such. B. disc springs is conceivable. The arrangement of the CSC is shown here on the transmission side. A motor-side arrangement is conceivable. It is essential that the cylinders of the CSC are respectively displaced in the axially same direction in order to actuate the slats or the pistons are actuated in the same direction in order to compress the disk packs.

1 shows a clutch unit 100 with a rotation axis 105 for transmitting torque in a drive train, in particular between a drive motor 110 and a gearbox 115 (both not shown). The clutch unit 100 is as a double clutch with a first part clutch 120 and a second part clutch 125 designed. The partial clutches 120 and 125 can be operated separately from each other, for example, a transfer of torque between the drive motor 110 and a first input shaft of the transmission 115 and between the drive motor 110 and a second input shaft of the transmission 115 to control independently of each other. The dual clutch can be used in particular in connection with a dual-clutch transmission. In this case, the clutch unit 100 axially between the drive motor 110 and the transmission 115 be provided and firmly connected or integrated with one or both of the elements.

An outer disc carrier 130 , which is adapted to torque-locking with an output shaft of the drive motor 110 to be connected, and a first inner disc carrier 135 , which is adapted to torque-locking with the first input shaft of the transmission 115 to be connected, carry in a radial gap a first plate pack 140 the first part clutch 120 , The first disc pack 140 includes first entrance louvers 145 and first output louvers 150 which are arranged axially alternately. The first entrance slats 145 are torque-locking and axially displaceable with the outer disk carrier 130 and the first output louvers 150 torque-locking and axially displaceable with the first inner disk carrier 135 connected; a reverse assignment is also possible.

The first disc pack 140 is supported on one side axially against one of the disk carrier, preferably with respect to the outer disk carrier 130 , On the other axial side is a first end plate 155 , It is irrelevant whether the first end plate 155 an entrance lamella 145 or an outlet fin 150 is. The first end lamella 155 can be moved axially to the first disc pack 140 to compress axially. This creates a positive connection between the input lamellae 145 and the exit louvers 150 , so that a torque between the outer disk carrier 130 and the first inner disc carrier 135 can be transferred. This process is also referred to as the first partial clutch 120 to press, so she closes. For actuating the first part clutch 120 or for compression of the first disk pack 140 is an actuator 160 provided, which is adapted to provide an axially acting actuating force. This actuating force is applied to the first end plate 155 transferred, preferably by means of a first actuating means 165 , which may be executed in particular cup-shaped, wherein it is also referred to as a pressure pot. The first actuator 160 is preferably formed hydraulically and comprises a piston-cylinder unit. In the present case, this is a first piston 170 provided, which preferably via a first thrust bearing 175 on the first actuating means 165 acts. To the first actuating means 165 against the first piston 170 and to press this into the cylinder is a first elastic element 180 intended. This allows the first end plate 155 be relieved when an actuation of the first part clutch 120 not done or wears off. The first part clutch 120 This can cause slippage or separation, so that the torque transmission via the first part clutch 120 reduced or canceled.

The second part clutch 125 is essentially the same as the first part clutch 120 built up; their elements bear corresponding reference numerals, each with a dash. So are a second inner disc carrier 135 ' , a second disc pack 140 ' , second entrance slats 145 ' , second output lamellae 150 ' , a second end plate 155 ' , a second actuator 160 ' , a second actuating means 165 ' , a second piston 170 ' , a second thrust bearing 175 ' and a second elastic element 180 ' intended. For these elements, generally the above with respect to the first part clutch apply 120 Variations given. The second inner disk carrier 135 ' is for connection to a second input shaft of the transmission 115 provided and the second part clutch 125 is intended to transfer torque between the drive motor 110 and control the second input shaft.

The two elastic elements 180 . 180 ' are radially offset and can overlap axially partially or completely. On the one axial side of the elastic elements 180 . 180 ' are the actuating means 165 . 165 ' which are substantially parallel to each other. The second actuating means 165 ' leads directly to the second end plate 155 ' while the first actuating means 165 through recesses in the slats 145 ' . 150 ' is guided to the first end plate 155 to reach. At the other axial side of the elastic elements 180 . 180 ' is a (first) holding element 182 provided, the outer disc carrier 130 leads. This leads the holding element 182 on an axial side of the second part clutch 125 over, the first part clutch 120 turned away. The holding element 182 includes recesses for carrying out the actuating means 165 . 165 ' ,

It is preferred that the partial clutches 120 and 125 are arranged axially to each other. In particular, it is preferred that axial inner and outer boundaries of the disk packs 140 . 140 ' agree with each other. It is further preferred that actuating directions, in each case an axial force on the end plates 155 . 155 ' is exercised to the respective part coupling 120 . 125 to operate or the assigned disk set 140 . 140 ' axially compress, are the same direction.

It is further preferred that the actuators 160 . 160 ' concentric with each other and in particular concentric with the axis of rotation 105 are arranged. In addition, the actuators 160 . 160 ' around the input and output shafts of the clutch unit 100 be rotatably mounted. Cylinder of actuators 160 . 160 ' can be so easily integrated with each other. In the present embodiment, the cylinders are in a carrier device 185 integrated with each other, having concentric axial annular grooves into which the hollow cylindrical piston 170 . 170 ' are introduced axially. It is preferred that the carrier device 185 the partial clutches 120 . 125 or their associated disk packs 140 . 140 ' axially exceeds, that is, at least partially extends radially outward than the elements of the partial clutches 120 . 125 , For this purpose, the carrier device 185 comprise one or more radial arms. The carrier device 185 is preferably in a region radially outside of the partial couplings 120 . 125 or their disk packs 140 . 140 ' axially or circumferentially relative to a transmission housing 190 supported by the transmission 115 includes or for connection to the transmission 115 can be provided. The illustrated section of the gearbox 190 is also called clutch bell because of its shape. The illustrated and preferred embodiment of the actuators 160 . 160 ' is also called CSC (Concentric Slave Cylinder), the carrier device 185 can therefore be called CSC housing.

It is preferred that the elastic elements 180 . 180 ' radially inside the disk packs 140 . 140 ' are arranged. Preferably, the elastic elements are 180 . 180 ' in an axial region caused by axial limitations of an arrangement of both disk sets 140 . 140 ' is defined. In one embodiment, the elastic elements 180 . 180 ' arranged radially offset.

In one embodiment, a housing element 195 provided, an enclosure of the clutch unit 100 , Especially in the form of the transmission housing 190 , axially in the direction of the drive motor 110 concludes. The housing element 195 is also called clutch cover and can be part of the drive motor 110 or for connection to the drive motor 110 be furnished. On the housing element 195 usually a radial bearing is provided to one to the drive motor 110 store leading wave. This radial bearing is also called a cover bearing.

To an actuating force on the Endlamellen 155 . 155 ' To exercise, the actuators must 160 . 160 ' be supported axially. For this purpose, it is preferable that the frictional connection within the clutch assembly 100 to close, that is, the cylinders of the actuators 160 . 160 ' - The present from the carrier device 185 are formed - axially relative to the outer disk carrier 130 support, which the axial abutment of the disk packs 140 . 140 ' on the end blades 155 . 155 ' opposite axial side forms. In the in 1 illustrated embodiment, this is a thrust bearing 205 provided on the gearbox 115 facing axial side of the partial clutches 120 . 125 or their disk packs 140 . 140 ' lies. The thrust bearing 205 is also called cover stock. About a radial support member transmits the thrust bearing 205 axial forces between the support means 185 and the outer disc carrier 130 ,

2 shows an alternative embodiment of a dual clutch device 100 to the in 1 illustrated embodiment, wherein the power flow is closed in another way. Here is in place of the thrust bearing 205 one on the axial side of the drive motor 110 lying thrust bearing 210 intended. The thrust bearing 210 supports axial forces acting on the outer disc carrier 130 act against another element. This element can be used with the drive motor 110 be connected. Preferably, this element comprises the clutch cover 195 that is axially opposite to the support means 185 is supported, for example via the transmission housing 190 or a dedicated housing of the coupling device 100 ,

It is generally preferred that the clutch unit 100 in a liquid environment, especially in an environment of oil. The liquid can simultaneously as a hydraulic fluid of the actuators 160 . 160 ' be used. The liquid may in a known manner on a predetermined channel to predetermined locations in the clutch unit 100 be guided.

3 shows a double clutch device 100 by type of 1 at a facility 305 for transmitting torque to the drive motor 110 , The device 305 may in particular comprise one or more circumferentially acting elastic elements for vibration damping. In a corresponding manner, the coupling arrangement 100 from 2 at the facility 305 be used.

4 shows a further embodiment of the dual clutch device according to 1 with an alternative arrangement of the elastic elements 180 . 180 ' , This embodiment can be combined with one of the embodiments of 1 to 3 be combined. Again, the elastic elements 180 . 180 ' offset radially and partially overlap in the axial direction.

In the illustrated embodiment, the second inner disc carrier leads 135 ' between the two elastic elements 180 . 180 ' through, so that the elastic elements 180 . 180 by means of separate holding elements 182 must be supported. A first holding element 182 supports the first elastic element 180 and a second retaining element 182 ' the second elastic element 180 ' each with respect to the outer disk carrier 130 from. The second holding element 182 ' is essentially as guided as the (only) holding element 182 in the embodiment of 1 while the first holding element 182 in an area axially between the partial clutches 120 . 125 radially outward to the outer disk carrier 130 runs. The opposite end of the first elastic element 180 also does not act directly on the first actuating means 165 but is in the range axially between the partial clutches 120 . 125 by means of an intermediate element 183 connected with him. The intermediate element 183 axially crosses the retaining element 182 wherein the one element passes through a recess in the other element. In this solution, it may be advantageous for the mass moment of inertia of the second inner disk carrier 135 ' due to the smaller axial extent compared to the air spring arrangement in 1 - 3 , may be lower.

5 shows yet another embodiment of the dual clutch device after 1 , which also with one of the embodiments of 1 to 3 can be combined. Here are the elastic elements 180 . 180 ' radially offset and may additionally, as shown, axially offset completely or partially. The second actuating means 165 ' leads between the two elastic elements 180 . 180 ' through and the first elastic element 180 is axially and / or radially between portions of the first actuating means 165 and the second actuating means 165 ' , The first elastic element 180 acts on an axial end directly on the first actuating means 165 and is at the other axial end by means of the holding element 182 supported, and preferably at a portion of the support means 185 that is radial between the actuators 160 and 160 ' lies.

The second elastic element 180 ' preferably acts at an axial end directly on the second actuating means 165 ' and is at the other end by means of the second holding element 182 ' supported, preferably against a portion of the support means 185 that is radially inward of both actuators 160 lies. The elastic elements 180 . 180 ' are each supported at least at one axial end by means of a thrust bearing against the rotational movement of the adjacent component. These thrust bearings may each comprise rolling bearings, in particular needle bearings, or plain bearings.

6 shows a further embodiment of a dual clutch device 100 similar to the embodiments shown in the preceding figures. In particular, the illustrated embodiment is based on that of 3 at.

The outer disc carrier 130 is in a gearbox 115 facing axial region by means of a holding element 605 and a warehouse 610 , which may be formed in particular as a ball bearing, axially relative to the support means 185 supported. A security element 615 , secures the outer disc carrier 130 in a first axial direction on the holding element 605 , Thus, the axial actuation forces of the partial clutches 120 and 125 on the part of the carrier device 185 (the CSC lid) are introduced into the outer disc carrier. In the illustrated embodiment, the securing element 615 formed by a retaining ring in a radially inwardly open, circumferential groove of the outer disk carrier 130 lies. Preferably, the retaining ring is not closed, so that it can be pressed radially together for assembly or disassembly.

7 shows different views of the retaining element 182 the double clutch device 100 from 6 , The cup-shaped retaining element 182 preferably has one or more breakthroughs 705 , in particular also for the passage of a liquid, in particular oil, on, but also to a penetration of the actuating means 165 ' to enable. The openings are preferably in a radially outer region of the retaining element 182 ,

The holding element 182 lies radially outward on an inner boundary of the outer disk carrier 130 at. In addition, the holding element lies 182 in a radially outer region on one axial side on the shoulder 620 at. To both a good radial centering and a good axial contact of the holding element 182 on the outer disk carrier 130 To realize, are radially outward on the holding element a number of tabs 710 issued, which extend radially further outward than a radially outer boundary of the retaining element 182 between the tabs 710 , The tabs 710 are also axially exposed so that they are the axial boundary of the retaining element 182 in an area between the tabs 710 axially exceed. The tabs 710 are adapted to radially outward and unilaterally axially on the outer disk carrier 130 to rest. As a result, both a radial and an axial fit can be effected. An undercut on the outer disk carrier 130 between a radial and an axial bearing surface for the holding element 182 so can be omitted. Durability of the compound or its connection partners can be unaffected.

LIST OF REFERENCE NUMBERS

100

 Clutch assembly, clutch device, clutch assembly, dual clutch device

105

 axis of rotation

110

 drive motor

115

 transmission

120

 first part clutch

125

 second part clutch

130

 External disk carrier

135

 first inner disk carrier

140

 first plate pack

145

 first entrance lamellae

150

 first exit lamellae

155

 first end plate

160

 first actuator

165

 first actuating means (pressure pot)

170

 first piston

175

 first thrust bearing

180

 first elastic element

135 '

 second inner disk carrier

140 '

 second disc pack

145 '

 second input fins

150 '

 second exit lamellae

155 '

 second end plate

160 '

 second actuator

165 '

 second actuating means (pressure pot)

170 '

 second piston

175 '

 second thrust bearing

180 '

 second elastic element

182

 retaining element

182 '

 retaining element

183

 intermediate element

185

 Supporting device (CSC housing)

190

 gearbox

195

 Housing element (clutch cover) (seal cover) (engine side)

205

 Thrust bearing (cover bearing) (gearbox side)

210

 Thrust bearing (main bearing) (engine side)

305

 Device for transmitting torque

605

 retaining element

610

 camp

615

 fuse element

620

 paragraph

705

 breakthrough

710

 flap

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 102010051447 A1 [0001]
• DE 202013226359 A1 [0001]

Claims (10)

A clutch unit ( 100 ) comprises at least two partial couplings ( 120 . 125 ), - whereby each partial coupling ( 120 . 125 ) as a multi-plate clutch with a disk set ( 140 . 140 ' ), - with actuators ( 160 . 160 ' ) for the axial compression of the two disk packs ( 140 . 140 ' ) independently of each other to a torque flow through each of the partial clutch ( 120 . 125 ) which allow the compressed disc pack ( 140 . 140 ' ) assigned; - Wherein actuation directions of the actuators ( 160 . 160 ' ), in each case for compressing the first and the second disk pack ( 140 . 140 ' ), are directed axially equal; - where elastic elements ( 180 . 180 ' ) are provided, which against the actuating directions on the actuators ( 160 . 160 ' ), and one of the elastic elements ( 180 . 180 ' ) radially within the disk packs ( 140 . 140 ' ) is arranged. Clutch unit ( 100 ) according to claim 1, wherein the other elastic element ( 180 . 180 ' ) also radially within the disk packs ( 140 . 140 ' ) is arranged. Clutch unit ( 100 ) according to claim 1 or 2, wherein the elastic elements ( 180 . 180 ' ) between axially outer boundaries of the disk packs ( 140 . 140 ' ) are arranged. Clutch unit ( 100 ) according to one of the preceding claims, wherein the elastic elements ( 180 . 180 ' ) are arranged offset radially. Clutch unit ( 100 ) according to any one of the preceding claims, wherein each actuator ( 160 . 160 ' ) comprises a hydraulic piston-cylinder unit and the pistons ( 170 . 170 ' ) of the two units are moved axially in the same direction when actuated. Clutch unit ( 100 ) according to any one of the preceding claims, wherein between an actuator ( 160 . 160 ' ) and a disk pack each have an actuating means ( 165 ) is provided and the elastic elements ( 180 . 180 ' ) each on the actuating means ( 165 . 165 ' ) Act. Clutch unit ( 100 ) according to claim 6, wherein the actuating means ( 165 . 165 ' ) are cup-shaped. Clutch unit ( 100 ) according to one of the preceding claims, wherein the clutch unit ( 100 ) is adapted to run in a liquid bath. Clutch unit ( 100 ) according to one of the preceding claims, wherein a retaining element ( 182 ) for supporting the elastic element ( 180 ) is provided. Clutch unit ( 100 ) according to claim 9, wherein the retaining element ( 182 ) Breakthroughs ( 705 ) for permitting a penetration of the actuating means ( 165 ).

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