阅读说明：本技术 摩擦离合器 (Friction clutch ) 是由 R·戴克勒 D·伯梅 P·许贝尔 E·瓦格纳 R·伊什穆拉托夫 F·福伊雷尔 S·帕策 于 2019-01-22 设计创作，主要内容包括：本发明所述的摩擦离合器(1),尤其适用于机动车的动力总成系统,用于耦合输入轴与第一输出轴和/或第二输出轴,带有一个双层的中心板(2),一个第一压紧板(3),所述第一压紧板为了在所述第一压紧板(3)与所述中心板(2)之间压紧第一离合器从动盘装置(26)的至少一个第一摩擦片(28)而可以轴向移动,和一个第二压紧板(4),所述第二压紧板为了在所述第二压紧板(4)与所述中心板(2)之间压紧第二离合器从动盘装置(27)的至少一个第二摩擦片(29)而可以轴向移动,其中,通过所述第一(3)和所述第二压紧板(4)的轴向移动可以在各个压紧板(3、4)的摩擦面(30、42)与各个离合器从动盘装置(26、27)的摩擦片(28、29)之间建立摩擦连接以及在各个离合器从动盘装置(26、27)的摩擦片(28、29)与所述中心板(2)的摩擦面(43、44)之间取消摩擦连接,其特征在于,至少一个下述元件：所述第一压紧板(3)的第一摩擦面(30),所述第二压紧板(4)的第二摩擦面(42)和所述中心板(2)至少一个摩擦面(43、44)设计有至少一个凹槽(7、15),所述凹槽分别从所述各个摩擦面(30、42、43、44)的内边缘(31)延伸到所述各个摩擦面(30、42、43、44)的外边缘(32)。(The friction clutch (1) according to the invention, in particular for a drive train of a motor vehicle, for coupling an input shaft to a first output shaft and/or a second output shaft, comprises a double-layered central plate (2), a first pressure plate (3) which is axially displaceable for pressing at least one first friction disk (28) of a first clutch driven disk arrangement (26) between the first pressure plate (3) and the central plate (2), and a second pressure plate (4) which is axially displaceable for pressing at least one second friction disk (29) of a second clutch driven disk arrangement (27) between the second pressure plate (4) and the central plate (2), wherein the axial displacement of the first pressure plate (3) and the second pressure plate (4) can move the respective pressure plate (3, 4), 4) Establishing a frictional connection between the friction surfaces (30, 42) of the respective clutch driven disc arrangement (26, 27) and the friction linings (28, 29) of the respective clutch driven disc arrangement (26, 27) and canceling the frictional connection between the friction linings (28, 29) of the respective clutch driven disc arrangement (26, 27) and the friction surfaces (43, 44) of the centre plate (2), characterized by at least one of the following elements: the first friction surface (30) of the first pressure plate (3), the second friction surface (42) of the second pressure plate (4) and at least one friction surface (43, 44) of the central plate (2) are designed with at least one recess (7, 15) which extends from an inner edge (31) of the respective friction surface (30, 42, 43, 44) to an outer edge (32) of the respective friction surface (30, 42, 43, 44).)

1. A friction clutch (1), in particular for a drive train of a motor vehicle, for coupling an input shaft to a first output shaft and/or a second output shaft, having a double-walled central plate (2), a first pressure plate (3) which is axially displaceable for pressing at least one first friction disk (28) of a first clutch disk (26) between the first pressure plate (3) and the central plate (2), and a second pressure plate (4) which is axially displaceable for pressing at least one second friction disk (29) of a second clutch disk (27) between the second pressure plate (4) and the central plate (2), wherein the first pressure plate (3) and the second pressure plate (4) can be axially displaced between the respective pressure plates (3, 4), 4) Establishing a frictional connection between the friction surfaces (30, 42) of the respective clutch driven disc arrangement (26, 27) and the friction linings (28, 29) of the respective clutch driven disc arrangement (26, 27) and canceling the frictional connection between the friction linings (28, 29) of the respective clutch driven disc arrangement (26, 27) and the friction surfaces (43, 44) of the centre plate (2), characterized by at least one of the following elements:

-a first friction surface (30) of the first pressure plate (3),

-a second friction surface (42) of the second pressure plate (4) and

-at least one friction face (43, 44) of the centre plate (2)

At least one groove (7, 15) is provided, which extends from the inner edge (31) of the respective friction surface (30, 42, 43, 44) to the outer edge (32) of the respective friction surface (30, 42, 43, 44).

2. Friction clutch (1) according to claim 1, wherein at least one groove (7, 15) is designed as a continuous structure.

3. Friction clutch (1) according to one of the preceding claims, wherein at least one groove (7, 15) is designed at a non-zero angle (35) with respect to the radial direction (36).

4. The friction clutch (1) according to one of the preceding claims, wherein at least one of the following components is designed in sheet material: the first compression plate (3), the second compression plate (3), a first center plate member (5) forming a first tier of the center plate (2), and a second center plate member (6) forming a second tier of the center plate (2).

5. Friction clutch (1) according to one of the preceding claims, wherein the at least one centre plate member (5, 6) constituting the centre plate (2) layer has at least one of said grooves (7, 15) in the respective friction face (43, 44) and the centre plate member (6, 5) constituting the other layer has at least one first elevation (34) of the same height (H) as the respective groove (7, 15) on the side opposite the respective friction face.

6. Friction clutch (1) according to claim 5, wherein said at least one first projection (34) has a position coinciding with the position of absence of said groove (7, 15) in said central plate member (5, 6) constituting the other layer of said central plate (2).

7. Friction clutch (1) according to any of the preceding claims, wherein at least one of the following elements: the first pressure plate (3), the second pressure plate (4), the first central plate member (5) constituting a first layer of the central plate (2) and the second central plate member (6) constituting a second layer of the central plate (2) comprise at least one wear stop (17) defining a minimum distance between adjacent elements which may constitute a friction connection.

8. The friction clutch (1) according to one of the preceding claims, wherein the second pressure plate (4) has at least two second continuous structures (33) for co-acting with a locking element of another component in order to define the position of this component when mounted on the second pressure plate (4).

Technical Field

The invention relates to a friction clutch designed as a double clutch, in particular for a drive train of a motor vehicle.

Background

Double clutches are considered known. A double clutch of this kind with a triple-mass design is known, for example, from DE 102017102732 a1, which has a central plate and two axially displaceable pressure plates. Such double clutches often have durability problems due to the formation of abrasive particles and thermal problems, since the frictional heat formed cannot be dissipated sufficiently quickly.

The object of the present invention is therefore to overcome at least partially the problems known from the background art and in particular to provide a dual clutch which is improved with regard to abrasive particle emission and thermal characteristics.

Disclosure of Invention

The object is achieved by the features of the independent claim 1. Further advantageous embodiments of the invention are given in the dependent claims. The features listed individually in the dependent claims may be combined with one another in a technically sensible manner and may define further embodiments of the invention. Furthermore, the features given in the claims are explained and illustrated in more detail in the description, in which further preferred embodiments of the invention are explained.

The friction clutch according to the invention, in particular for a drive train of a motor vehicle, for coupling an input shaft to a first output shaft and/or a second output shaft, has a double-layered central plate, a first pressure plate which is axially displaceable for pressing at least one first friction disk of a first clutch driven disk between the first pressure plate and the central plate, and a second pressure plate which is axially displaceable for pressing at least one second friction disk of a second clutch driven disk between the second pressure plate and the central plate, wherein a frictional connection between the friction surfaces of the respective pressure plate and the friction disks of the respective clutch driven disk and a frictional connection between the friction disks of the respective clutch driven disk and the friction surfaces of the central plate can be established and cancelled by an axial displacement of the first and second pressure plates, characterized by at least one of the following elements:

a first friction surface of the first pressure strip,

a second friction surface of a second pressure plate and

center plate at least one friction face

At least one groove is provided, which extends from the inner edge of the respective friction surface to the outer edge of the respective friction surface.

The design of the grooves running continuously from the inner edge of the friction surface to the outer edge of the respective friction surface results in an inward and outward transport of abrasive particles during rotation, based on the centripetal force present and the air flowing through the grooves. The grooves may be designed in one or more, even all, of the elements. One or more recesses can be provided in each case. The grooves also improve the cooling of the individual components, since the air used for cooling can be passed through the grooves by rotation. The frictional heat formed can thus be transported away at least partially by the air flowing through the grooves.

According to an advantageous embodiment, at least one groove is provided as a continuous structure.

The recess can be produced simply, inexpensively and accurately by means of such a shaping process, in particular when the respective component is produced inexpensively from sheet material. In particular, the continuous structure also has relatively steep flanks which increase the groove cross section for circulating air and carrying away abrasive particles. The projection on the other side of the respective element, which projection corresponds to the recess, can be used in an advantageous manner as a contact surface for the other centre plate members, in particular when the recess is designed in the layer of the centre plates or the centre plate members constituting said layer, in order to increase the rigidity of the centre plate.

According to an advantageous embodiment, at least one groove is formed at a different angle to the radial direction than the groove.

The inclination of the grooves further improves the transport characteristics in the grooves. Depending on the type of impeller, the individual grooves lead to an increased amount of air that can flow through during rotation.

According to an advantageous embodiment, at least one of the following components is formed from sheet metal: a first compression plate, a second compression plate, a first center plate member forming a first tier of center plates, and a second center plate member forming a second tier of center plates.

By designing at least one of the components from sheet material, costs can be reduced when providing a corresponding friction clutch. The remaining components may be made of a cast material.

According to an advantageous embodiment, at least one central plate element forming the central plate layer has at least one groove in each friction surface, and the central plate element forming the other layer has at least one first elevation of the same height as the height of the respective groove on the side opposite the respective friction surface.

By designing the first projection more contact points are provided, which in turn increases the rigidity of the centre plate. Preferably, a plurality of first projections are distributed, in particular uniformly distributed, over the circumference of the central plate. In this respect it is also advantageous if at least one first projection has a position which is the same as the position of the absence of a recess in the centre panel member constituting the other layer of the centre panel. Contact points can thus be formed outside the recess, whereby the rigidity of the centre plate can be suitably adjusted by the position of the first projections and the definition of the contact points.

According to an advantageous embodiment, at least one of the following elements: the first compression plate, the second compression plate, the first center plate member forming the first layer of the center plates, and the center plate member forming the second layer of the center plates include at least one wear stop that defines a minimum distance between adjacent elements that can form a frictional connection.

This makes it possible to define the axial end distance which is still available for the individual clutch driven disk arrangements to be clamped in the worn state.

According to an advantageous embodiment, the second pressure plate has at least two second continuous structures for interacting with a locking element of another component, in particular of the pressure tank, in order to define the position of this component when mounted on the second pressure plate.

In addition, a motor vehicle having a corresponding friction clutch in the drive train is also proposed.

It should be noted as a precaution that the terms "first", "second", etc. are used herein primarily (only) to distinguish a plurality of objects, dimensions, or processes of the same type, and thus there is no mandatory definition of a relationship and/or order of such objects, dimensions, or processes to each other, among others. It will be obvious to the expert that when relationships and/or sequences are required, they will be explained in more detail here or when studying the specifically described design.

The invention and the technical scope will be further explained below with reference to the schematic drawings. It must be noted that the illustrated embodiments should not limit the invention. In particular, some aspects of the facts described in the drawings may also be extracted and combined with other elements and knowledge in the present description and/or drawings, unless otherwise specified. It is to be noted in particular that the drawings and in particular the dimensional proportions shown are purely diagrammatic. The same reference numerals denote the same objects, and thus, reference may be made to the descriptions in other drawings as necessary.

Drawings

FIG. 1: one example of a friction clutch;

FIGS. 2 and 3: one example of a first compression plate;

FIGS. 4 and 5: one example of a second compression plate;

fig. 6 and 7: one example of a second center panel member;

fig. 8 and 9: one example of a first center panel member;

FIGS. 10 to 12: three views of a center panel comprised of a first center panel member and a second center panel member; and

FIG. 13: details of the friction clutch have been assembled.

Description of the reference numerals

1 center plate 3, first pressure plate 4, second pressure plate 5, first center plate member 6, second center plate member 7, groove 8, edge 9, first coupling element 11, second coupling element 12, stop 13, groove 15, edge 17, wear stop 18, protrusion 19, edge 17, wear stop 18, edge 21, wear stop 18, edge 23, connection 25, mating surfaces 26, first clutch driven plate 27, second clutch driven plate 28, first friction plate 29, second friction plate 30, inner edge 31, outer edge 32, second continuous structure 34, first protrusion 35, angle 36, radial axis 37, third coupling element 38, fourth coupling element 39, rivet 40, pull rod 41, second friction surface 43, friction surface 44, rivet 40, plate 41, friction surface 44, friction surface 32, friction

d the height of the axis of rotation H.

Detailed Description

The same reference numerals are provided for the same parts in the description of the drawings. Fig. 1 shows an example of a friction clutch 1 designed as a dual clutch. The friction clutch has a double center plate 2 and a first pressure plate 3 and a second pressure plate 4. The center panel 2 of the double layer is formed of a first center panel member 5 and a second center panel member 6. The first pressure plate 3 and the second pressure plate 4 are designed so as to be axially displaceable relative to the axis of rotation d, as a result of which the first clutch disk arrangement 26 can be pressed between the central plate 2 and the first pressure plate 3 and the second clutch disk arrangement 27 can be pressed between the central plate 2 and the second pressure plate 4, so that a frictional connection can be established between the first pressure plate 2, the first clutch disk arrangement 26 with the first friction linings 28 and the central plate 2 on the one hand, and the second pressure plate 4, the second clutch disk arrangement 27 with the second friction linings 29 and the central plate 2 on the other hand, in order to be able to transmit torque. Frictional connections are formed between the friction surfaces 30, 42 of the pressure plates 3, 4 and the friction linings 28, 29 of the clutch disk assemblies 26, 27, and between the friction linings 28, 29 of the clutch disk assemblies 26, 27 and the friction surfaces 43, 44 of the center plate 2.

Fig. 2 and 3 show a possible embodiment of the first pressure strip 3 in two different views. The first pressure plate has a recess 7 on a first friction surface 30 facing the center plate 2 in its assembled state. The grooves are designed as a continuous structure, thus forming protrusions 9 on the opposite side (see fig. 2). The recesses 7 each have an edge 8 of a specific height. The groove 7 is designed such that the inner edge 31 of the first friction surface 30 is connected to the outer edge 32 of the second friction surface 30. The recess 7 forms a non-zero angle 35 with the radial direction 36.

Abrasive particles from the first friction lining 8 or the first friction surface 30 can be discharged through the grooves 7 to the outer edge 32. In addition, the recesses 7 improve the ventilation and thus better dissipate the heat energy which is generated as a result of the frictional connection being established.

The first press plate 3 additionally has a first connecting element 10 and a second connecting element 11.

Fig. 4 and 5 show two views of an example of a second pressure plate 4 with a second friction surface 42 from opposite directions. The second pressure plate has a second continuous structure 33, which interacts with a locking element of another component, in particular of a pressure tank of the friction clutch 1, which is not shown here, in order to define the position of this component when it is mounted on the second pressure plate 4. In this case, the second continuous structure 22 can be used to achieve lateral centering while preventing rotation.

Fig. 6 and 7 show two views of the second center panel member 6 from opposite directions. In the mounted state, the friction surface 43 of the second centre plate member faces the second pressure plate 4. The second center panel member 6 has a first projection 34 that is also designed in a continuous configuration. The height H of the first protrusion 34 is the same as the height H of the groove 7.

Fig. 8 and 9 show two views of the first center panel member 5 from opposite directions. In the mounted state, the friction surface 44 of the first centre plate member 5 faces the first pressure plate 3. The friction face 44 has grooves 15 which are likewise designed as continuous structures with corresponding projections 18 opposite the first centre plate member 5. The grooves 15 have corresponding edges 16 and extend from the inner edge 31 of the friction face 44 to the outer edge 32 of the friction face 44. The grooves 15 are aligned obliquely with respect to the radial direction. The first and second center panel members 5 and 6 are joined together to illustrate in detail the side of the second center panel member 5 that is directed toward the projection 18 of the first center panel 5 in the direction of the first projection 34 of the second center panel 6 with reference to fig. 10 through 12. The first centre plate member 5 additionally has a wear stop 17 which defines the smallest distance possible from the associated member.

Fig. 10 to 11 show two views of the installed centre plate from opposite directions, and fig. 12 shows a view in enlarged form of the area 19 shown in fig. 11. The first centre plate member 5 (see fig. 8, 9) is designed with three grooves 7 aligned at an angle 35 with respect to the radial direction 36, and the second centre plate member 6 is designed as shown in fig. 6 and 7. Here, the first center panel member 5 has a third connecting element 37 and the second center panel member 6 has a fourth connecting element 38. The connecting elements 37, 38 are connected by means of rivets 39, thus forming the central panel 2.

Fig. 12 shows a detail of the centre plate 2 in terms of the area 19 shown in fig. 11. In this case, the first projection 34 and the recess 15 and the corresponding projection 18 are matched to one another over their height H in such a way that: a plurality of contact points are formed between the first and second center panel members 5, 6 to increase the rigidity of the center panel 2. As shown on the left, the location of the first projection 34 in the second center panel member 6 does not correspond to the location of the recess 15 in the second center panel member 5.

As shown in the present example, a very high and circumferentially uniform rigidity can be achieved for the central plate 2 if these contact points are of largely symmetrical design in the circumferential direction. By arranging the plurality of recesses 15 at an angle 35 with respect to the radial direction 36 and evenly distributed over the circumference of the central plate 2, an efficient ventilation and thus cooling of the central plate 2 during rotation is achieved. In particular, the grooves 15 and the corresponding projections 18 will act as active cooling elements depending on the type of impeller, by virtue of their alignment direction.

The respective grooves 7, 15 may be provided in one or all of the following components: a first compression plate 3, a second compression plate 4, a first center plate member 5, and/or a second center plate member 6. The number of grooves 7, 15 in the members 3, 4, 5, 6 may be the same or different. The angle 35 with respect to the radial direction 36 may be the same or different for all grooves 7, 15 in all members 3, 4, 5, 6. By a suitable choice of the number of grooves 7, 15 in the respective component 3, 4, 5, 6 and a suitable choice of the angle 35 in the respective component 3, 4, 5, 6 and/or in the respective groove 7, 15 relative to the radial direction 36, it is possible to adjust, for example, the thermal power to be discharged and/or the abrasive particles formed.

Fig. 13 shows a detail of an assembled friction clutch comprising a centre plate 2 and a first pressure plate 3. The first central plate element 5 facing the first pressure plate 3 has a wear stop 17 which defines a minimum distance to a stop 21 of the associated component, here the corresponding counter surface 25 of the first pressure plate 3. A connection 23 is also provided, which simultaneously connects the tension rod 38 and the leaf spring 39 to the first pressure plate 3. The tie rod 38 is fixed to the first pressure plate 3 by means of the connection 24.