DE102020107604A1 - Multi-disc clutch - Google Patents

Abstract

The invention relates to a multi-disc clutch (10) with inner and outer discs (1-4; 11-13) which are connected to disc carriers (5, 6) in a rotationally fixed but displaceable manner in the axial direction. To improve the efficiency of the multi-disc clutch (10), At least one of the disk carriers (5, 6) in a friction area (7, 8), in which the disks (1-4; 11-13) have frictional contact with the disk carrier (5,6) during an axial relative movement, at least two axial friction sections (16-20,21-24) with different frictional resistances.

Description

The invention relates to a multi-disk clutch with inner and outer disks which are connected to disk carriers in a rotationally fixed but displaceable manner in the axial direction.

From the German Offenlegungsschrift DE 10 2011 089 751 A1 a wet multi-disk clutch with first and second disks is known, the second disks being clamped between two first disks against the effect of compulsory disconnection forces, the compulsory disconnection forces being generated hydraulically with the aid of hydraulic medium.

The object of the invention is to improve the efficiency of a multi-disk clutch with inner and outer disks which are connected to disk carriers in a rotationally fixed but displaceable manner in the axial direction, in particular with regard to increasing operating speeds, as occur in hybrid applications in the automotive sector.

In the case of a multi-disk clutch with inner and outer disks, which are connected to disk carriers in a rotationally fixed but axially displaceable manner, at least one of the disk carriers is in a friction area in which the disks have frictional contact with the disk carrier during an axial relative movement , has at least two axial friction sections with different frictional resistances. The term axial refers to an axis of rotation of the multi-plate clutch. Axial means in the direction or parallel to the axis of rotation of the multi-plate clutch. To represent the non-rotatable connection between the lamellae and the lamellae carriers, the latter are advantageously equipped with a toothing into which a complementary toothing, which is provided on the lamellae, engages. In an open state of the multi-disc clutch, the discs are at least slightly spaced from one another, so that no torque is transmitted with the multi-disc clutch. To close the multi-disc clutch, a force is exerted on the disc pack with the inner and outer discs, for example with a piston, in order to move them axially towards one another and against a stop. The inner lamellae come into frictional contact with the outer lamellae. When the multi-disc clutch is closed, a torque is transmitted via the discs in frictional contact. The multi-disc clutch is preferably a wet-running multi-disc clutch. Wet running means that the plates of the multi-plate clutch come into contact with a lubricating and / or cooling medium such as oil during operation. In the case of wet multi-plate clutches, drag torque is playing an increasingly important role because, particularly in hybrid applications in the automotive sector, the speeds that occur during operation are significantly higher than in conventional internal combustion engine applications. A torque that is transmitted when the clutch is completely open is referred to as drag torque. It is a disadvantage here if individual lamellae are not separated. Due to the different frictional resistances in the axial friction sections, the separation of the lamellas in the open state can be effectively improved. As a result, the efficiency can be improved, especially at high speeds. Finally, a lamella wobble, which is undesirable per se, is prevented or at least reduced by the different frictional resistances in a particularly advantageous manner.

A preferred exemplary embodiment of the multi-disc clutch is characterized in that the frictional resistance in at least one friction section is increased in a targeted manner such that the axial movement of the multi-disc is restricted. Due to the different friction sections or friction zones on the plate carrier, the movements of the plates can be restricted in a defined manner. The friction area with the friction sections is provided, for example, on a toothing of the disk carrier. Due to the targeted increase in the friction in the at least one friction section, the axial movement of the lamella can be limited in a defined manner. In this way, for example, undesired sticking of two lamellae can advantageously be prevented or at least reduced. In addition, wobbling movements with high amplitudes can be prevented from being formed by the spatial limitation of the axial movement with the aid of the friction sections. Additional components in the form of separating springs can thus advantageously be dispensed with. As a result, the installation space that is required for the multi-plate clutch can in turn be reduced. If there are several friction sections with increased frictional resistance, the frictional resistance in these friction sections can be the same. The increased frictional resistances can, however, also be of different sizes in these friction sections.

Another preferred embodiment of the multi-plate clutch is characterized in that the friction section with the increased frictional resistance is designed and arranged relative to the plate in such a way that the axial movement of the plate is restricted in an open state of the multi-plate clutch. This can effectively prevent unwanted contacts between the lamellae.

Another preferred embodiment of the multi-plate clutch is characterized in that the frictional resistance in the friction section with the increased frictional resistance compared to the other friction section is approximately twenty percent is increased. Depending on the size and the design of the disks, in particular friction disks that come into contact with steel disks, the frictional resistance in the friction section with the increased frictional resistance can also be significantly greater. The friction area advantageously comprises at least two or three friction sections with increased frictional resistance.

Another preferred exemplary embodiment of the multi-disc clutch is characterized in that the friction section with the increased frictional resistance is assigned to a first inner disc in an inner disc row which begins at a stop for the first inner disc. This advantageously prevents the first inner lamella from coming into contact with a first outer lamella when the clutch is disengaged.

Another preferred exemplary embodiment of the multi-disc clutch is characterized in that a second friction section with the increased frictional resistance is assigned to a second inner disc in the inner row of discs. In this way, it can advantageously be prevented that the second inner lamella comes into contact with a second outer lamella in the open state of the multi-plate clutch.

Another preferred embodiment of the multi-disc clutch is characterized in that the or a further friction section with the or an increased frictional resistance of a first outer disc is assigned in an outer row of discs. This advantageously prevents the first outer lamella from coming into contact with a second inner lamella when the multi-plate clutch is open.

Another preferred embodiment of the multi-disc clutch is characterized in that a last friction section with an increased frictional resistance is assigned to a last inner disc in the inner row of discs. As a result, the last inner lamella is held in the lamella pack in a simple manner in the axial direction.

Another preferred exemplary embodiment of the multi-disc clutch is characterized in that a last friction section with an increased frictional resistance is assigned to a last outer disc in the outer row of discs. Here too, an axial limitation is created for the last outer plate in the plate pack.

The friction area with the different friction sections is provided, for example, on a tooth flank of a toothing on the disk carrier. In the event of an axial relative movement, the tooth flank represents a guide flank for the lamellae. Due to the targeted arrangement of the friction sections, the respective tooth flank has different frictional resistances in the axial direction. In many applications it is sufficient if the friction area with the different friction sections is provided on only one tooth flank of two tooth flanks, because the lamellas mainly come into contact with this tooth flank or guide flank in one direction of rotation, in particular in a pulling operation in a pulling direction of rotation. In hybrid applications, however, there is an increasing change between pulling mode and pushing mode, so that the lamellae come into contact with opposing tooth flanks or guide flanks. It is then advantageous if a friction area with different friction sections is provided on each of the two tooth flanks or guide flanks.

The invention also relates to a disk carrier for a disk clutch described above. The lamellar carrier can be traded separately.

• 1 eine schematische Darstellung einer nasslaufenden Lamellenkupplung in einem geschlossenen Zustand;
• 2 die Lamellenkupplung aus 1 im geöffneten Zustand; und
• 3 einen Ausschnitt eines Lamellenträgers mit einer Innenverzahnung in perspektivischer Darstellung.

Further advantages, features and details of the invention emerge from the following description, in which various exemplary embodiments are described in detail with reference to the drawing. Show it:

• 1 a schematic representation of a wet multi-plate clutch in a closed state;
• 2 the multi-plate clutch off 1 when open; and
• 3 a section of a plate carrier with internal teeth in a perspective view.

In the 1 and 2 is a wet multi-plate clutch 10 shown schematically in a closed and in an open state. The multi-disc clutch 10 includes inner slats 1 , 2 , 3 , 4th and outer slats 11 , 12th , 13th which are arranged alternately in a known manner. The inner slats 1 until 4th are designed as steel plates and with an internal toothing in a complementary toothing of an inner plate carrier 5 hooked.

The outer slats 11 until 13th are designed as friction plates and provided with a coating. The outer slats 11 until 13th are with an external toothing in a complementary toothing of an outer disk carrier 6th hooked.

The inner slats 1 until 4th are arranged in an inner row of lamellas that adjoin a stop 9 of the inner lamellar carrier 5 for the first inner lamella 1 begins. The outer slats 11 until 13th are arranged analogously in an outer row of lamellas, which in 1 left with the first outer lamella 11 begins. The first outer lamella 11 is in the axial direction between the inner lamellae 1 , 2 clampable. The outer lamellae are analogous 12th ; 13th in the axial direction between the inner lamellae 2 , 3 ; 3 , 4th clampable.

In 1 is the wet multi-plate clutch 10 shown in their closed state. By a piston 15th is one in the axial direction in 1 Actuating force acting from right to left on the plate pack with the plates 1 until 4th and 11 until 13th upset.

In 2 is the wet multi-plate clutch 10 shown in their open state. In the open state of the multi-disc clutch 10 lamellae 1 to 4 and 11 to 13 are spaced apart from one another by small axial gaps. The sum of these axial gaps is called the clearance.

During an actuation process of the wet multi-plate clutch 10 the toothed contact of the lamellas engages 1 until 4th and 11 until 13th on the flanks of the lamellar carriers 5 , 6th at. The flanks of the lamellar carriers 5 , 6th have at least one friction area 7th , 8th on that in the 1 and 2 is illustrated schematically by different hatching.

The inner friction area 7th comprises a total of five axial friction sections 16 until 20th with different frictional resistances. The outer friction area 8th comprises a total of four friction sections 21 until 24 with different frictional resistances.

The friction sections can also be referred to as friction zones or friction sections or friction zones. In the friction sections 18th until 20th and 23 , 24 is the frictional resistance versus the frictional resistance in the friction sections 16 , 17th , 21 , 22nd specifically increased, for example by around twenty percent.

The actual actuation process of the wet multi-plate clutch 10 is not influenced by the different frictional resistances. In addition, the axial friction sections 16 until 24 dimensioned and arranged so that a desired separation of the slats 1 until 4th ; 11 until 13th is not obstructed after actuation.

The slats 1 until 4th and 11 until 13th should be in their actuation stroke, the one with the piston 15th when actuating the wet multi-plate clutch 10 run over a consistent, low-friction surface. This is due to the arrangement and design of the friction sections 16 , 17th and 21 , 22nd ensured.

The inner lamella 1 does not have to perform an axial movement for release. Hence the inner lamella 1 through the friction section 18th with increased frictional resistance directly prevented from axial movement. The second inner lamella 2 is in the open position towards the piston 15th through the friction section 19th limited with increased frictional resistance. As a result, only one movement in the closing direction can occur.

The inner lamella 3 is deliberately not restricted in its axial movement in the example shown, as otherwise the desired axial movements of the other inner lamellae would be negatively influenced.

The inner lamella 4th is through the piston 15th limited in their opening direction. Through the friction zone 20th however, a very strong wobbling movement during operation at high speeds can advantageously be limited.

The outer lamellae, also known as friction lamellae 11 until 13th also cannot all be limited in their axial movement. Nevertheless, undesirable wobbling of the friction plates can occur 12th and 13th through the outer friction sections 23 , 24 be limited.

The first outer friction plate 11 is in its axial movement in 2 to the right through the outer friction section 23 limited with the increased frictional resistance. The second friction plate 12th or outer lamella 12th cannot be limited in their axial movement in the illustrated embodiment, since otherwise axial movements of the other friction plates would be undesirably influenced. The friction disc 13th is moved through the friction zone in its axial movement in the direction of the piston 24 limited.

In 3 is based on the example of a lamellar carrier 30th shown in a perspective excerpt, like the one in the 1 and 2 schematically illustrated arrangement of friction sections 38 until 42 can be realized with different frictional resistances. The lamellar carrier 30th includes grooves 31 , 32 , 33 that have a gearing 34 show in which lamellae with complementary teeth can be hooked in order to rotate them with the lamellae carrier 30th connect to.

The groove 32 has two groove flanks 35 , 36 on which the in 3 slats, not shown, come to rest in pulling mode and pushing mode. On the groove flank 35 is a friction area 37 indicated. In the friction area 37 have the friction sections 40 until 42 a higher frictional resistance than the friction sections 28, 39.

List of reference symbols

1

inner lamella

2

inner lamella

3

inner lamella

4th

inner lamella

5

inner lamella carrier

6th

outer lamella carrier

7th

inner friction area

8th

outer friction area

9

attack

10

wet multi-plate clutch

11

outer lamella

12th

outer lamella

13th

outer lamella

15th

Pistons

16

Friction section

17th

Friction section

18th

Friction section

19th

Friction section

20th

Friction section

21

Friction section

22nd

Friction section

23

Friction section

24

Friction section

30th

Lamellar carrier

31

Groove

32

Groove

33

Groove

34

Interlocking

35

Groove flank

36

Groove flank

37

Friction area

38

Friction section

39

Friction section

40

Friction section

41

Friction section

42

Friction section

QUOTES INCLUDED IN THE DESCRIPTION

This list of the documents listed by the applicant was 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.

Patent literature cited

• DE 102011089751 A1 [0002]

Claims (10)

Multi-disk clutch (10) with inner and outer disks (1-4; 11-13) which are connected to disk carriers (5, 6; 30) in a rotationally fixed but displaceable manner in the axial direction, characterized in that at least one of the disk carriers (5, 6; 30) in a friction area (7,8; 37) in which the disks (1-4; 11-13) have frictional contact with the disk carrier (5,6; 30) during an axial relative movement, at least two axial friction sections ( 16-20,21-24; 38-42) with different frictional resistances. Multi-disc clutch after Claim 1 , characterized in that the frictional resistance in at least one friction section (18-20; 23,24; 40-42) is specifically increased so that the axial movement of the lamella (1,2,4; 11,13) is restricted. Multi-disc clutch after Claim 2 , characterized in that the friction section (18-20; 23,24; 40-42) is designed with the increased frictional resistance and is arranged relative to the lamella (1,2,4; 11,13) that the axial movement of the Disc (1,2,4; 11,13) is restricted in an open state of the multi-disc clutch (10). Multi-disc clutch after Claim 2 or 3 , characterized in that the frictional resistance in the friction section (18-20; 23,24; 40-42) with the increased frictional resistance compared to the other friction section (16,17; 21,22; 38,39) is increased by about twenty percent . Multi-disc clutch according to one of the Claims 2 until 4th , characterized in that the friction section (18) with the increased frictional resistance is assigned to a first inner lamella (1) in an inner lamella row which begins at a stop (9) for the first inner lamella (1). Multi-disc clutch after Claim 5 , characterized in that a second friction section (19) with the increased frictional resistance is assigned to a second inner lamella (2) in the inner lamella row. Multi-disc clutch according to one of the Claims 2 until 6th , characterized in that the or a further friction section (23) with the or an increased frictional resistance of a first outer lamella (11) is assigned in an outer lamella row. Multi-disc clutch according to one of the Claims 2 until 7th , characterized in that a last friction section (20) with an increased frictional resistance is assigned to a last inner lamella (4) in the inner lamella row. Multi-disc clutch according to one of the Claims 2 until 8th , characterized in that a last friction section (24) with an increased frictional resistance is assigned to a last outer lamella (13) in the outer lamella row. Disk carrier (5, 6; 30) for a wet-running disk clutch (10) according to one of the preceding claims.

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