DE102015201306A1 - clutch disc - Google Patents

Abstract

In a clutch disc for a friction clutch Eeknoise in particular is robustly avoided during operation by this includes a vibration damper effective in the radial direction.

Description

The invention relates to a clutch disc and a friction clutch with such a clutch disc.

In friction clutches there are noise phenomena whose cause is to be sought in self-excited vibrations of the clutch disc in the frictional contacts with the countermeasures involved (Eeknoise). Characteristic of this phenomenon are two eigenmodes in which the clutch disc oscillates in two mutually perpendicular directions, parallel to the friction planes. This eigenform can arise because both the involved masses (clutch disc and the associated transmission input shaft proportionately by bending) and the stiffnesses involved (bending stiffness of the associated transmission input shaft) are the same. The coupling of these two modes creates the sound.

Measures are known which detune the coupling of the two eigenmodes, for example an adaptation of the pad spring stiffness in the relevant area or a change in the clogging of the countermeasures involved in the region of the friction surface, preferably in the case of the axially movable pressure plate.

Measures are further known which change the rigidities associated with the eigenmodes to one another, for example by introducing a clearance between the two coaxial transmission input shafts arranged bearing in dual-clutch transmissions.

In the solutions mentioned above, a high degree of accuracy is required in the case of significant item characteristics, and the parameters must not change over the service life over a narrow range. This requires a high production cost. In addition, there is a risk that the chosen solution is not sufficiently robust over the life of the clutch, with the time so the unwanted noise can occur.

An object of the invention is therefore to provide a robust solution for combating the noise phenomenon mentioned above. In addition, the solution should be easily integrated into existing systems.

This problem is solved by a clutch disc according to claim 1 and a friction clutch according to claim 10. Preferred embodiments or developments of the invention are specified in the dependent claims.

The above problem is solved in particular by a clutch disc for a friction clutch comprising a vibration damper acting in the radial direction. The vibration damper is in particular a damping mass effective in the radial direction, whose tiger effect is based on a movement of the absorber mass relative to its suspension or attachment. The vibration damper comprises in one embodiment of the invention, a damping ring disc, which is arranged resiliently in the radial direction on a carrier disc of the clutch disc. The resilient suspension allows movement of the damping disc relative to the carrier disc. The clutch disc comprises the carrier disc on which friction linings are applied or attached on both sides, for example riveted. The elastically mounted damping element forms a vibration damper or vibration damper in the radial direction relative to the axis of rotation of the clutch disc.

The above problem is also solved by a clutch disc for a friction clutch, with an annular disc-shaped friction lining, which is arranged on a carrier disc, wherein on the carrier disc, a radially elastically mounted damping element is arranged. Clutch discs are generally made of several parts in the prior art, in particular, which are in frictional contact with the clutch pressure plate and its counter-pressure surfaces of an optimal material for the friction, the friction linings exist. The friction linings are attached to a carrier disc, usually riveted.

The elasticity of the connection of the damping ring disk to the carrier disk is the same in all directions in one embodiment of the invention. The damping ring disk is therefore isotropic, at least with regard to its elasticity, in particular in the sense of spring stiffness, and therefore has the same properties in different, in particular radial spatial directions. In an alternative embodiment of the invention, the elasticity of the connection of the damping ring disk to the carrier disk is different in at least two directions. The mounting of the damping ring disk is therefore anisotropic, at least with regard to its elasticity, in particular in the sense of spring stiffness, and thus has different properties in different, in particular radial spatial directions. The spatial directions here are in particular different directions or directional angles with respect to the axis of rotation of the coupling. These directions are angle coordinates in a polar coordinate system with the axis of rotation as pole. The polar coordinate system is fixed to the clutch disc, this rotates, so the coordinate system rotates with.

Between damping ring disk and carrier disk, in one embodiment of the invention, at least one damper effective in the radial direction is arranged. The damper is a viscous damper or a friction damper.

The damping ring disk is secured in one embodiment of the invention with spring tabs on the carrier disk. For this purpose, in one embodiment of the invention, the spring clip is riveted to the damping ring disk and / or to the carrier disk. The spring tabs are integrally formed in one embodiment of the invention to the damping ring disk, the damping disk can be produced for example as a stamped and bent part with molded-on spring tabs. Alternatively, the spring tabs are joined to the damping ring disk, for example, riveted, bolted or welded.

In one embodiment of the invention, the spring tabs are fastened partly on the side remote from the transmission and partly on the side of the carrier disk facing the transmission. Some of the spring tab are thus attached to the transmission-remote side and some on the gear-facing side, so the other side, the carrier disc attached. This type of attachment reduces or prevents tilting vibrations perpendicular to the axis of rotation.

The carrier disc in one embodiment of the invention comprises a frusto-conical portion. On the one hand, this is a typical design of the carrier disk for clutch plates for double clutches, but also for single clutches; on the other hand, this facilitates the attachment of the spring clip on both sides of the carrier disk. The carrier disc has recesses or recesses through which some of the spring tab are guided.

In one embodiment of the invention, the carrier disk is fastened to a coupling disk hub, wherein the carrier disk is frictionally and / or positively and / or materially connected to the coupling disk hub. It may therefore be a caulking, screw, rivet, welded connection or the like.

The problem mentioned at the beginning is also solved by a friction clutch, in particular a double clutch, comprising at least one clutch disc according to one of the preceding claims. If only one clutch disk of the double clutch is a clutch disk according to the invention, this is in particular the clutch disk assigned to the outer hollow shaft. Especially with this, the phenomena mentioned above can occur, since this is indirectly supported by the inner shaft against radial movements and superimpose or add the elasticities of the supports.

Embodiments of the invention are explained below with reference to the accompanying drawings. Showing:

1 a schematic diagram of an embodiment of a dual clutch according to the invention in a sectional view:

2 a schematic diagram of a natural frequency with eigen forms of the hollow shaft;

3 a diagram of natural frequencies to a eigenform;

4 An embodiment of a clutch disc according to the invention.

1 shows an embodiment of a double clutch according to the invention as a schematic diagram in a sectional view. The double clutch 1 includes a first clutch 2 that with an inner shaft 4 , which is designed here as a solid shaft, cooperating and a second clutch 3 that with an outer shaft 5 , which is a hollow shaft, cooperates. The inner wave 4 and the outer shaft 5 Are transmission input shafts of a parallel shift transmission, in which therefore act two parallel and independently switchable gear trains on a common output shaft. The double clutch 1 includes a dual mass flywheel 6 whose primary side 7 in installation position with screws 8th with a crankshaft 9 a combustion engine, not shown, is connected.

The dual mass flywheel includes a primary side 7 and a secondary side 18 that have a torsional vibration damper 19 resilient with respect to a relative rotation of the primary side 7 opposite the secondary side 18 connected to each other.

The primary side 7 includes a first flange part 10 and a second flange part 11 , which are welded together, for example, and a bow spring receptacle 12 form. In the bow-spring receptacle 12 are bow springs 13 arranged. The bow springs 13 are spiral compression springs and can also consist of several coaxially arranged inner and outer springs. The bow springs 13 are supported by a spring end on a primary-side support, not shown, and are supported by the other end of the spring on a flange 14 from. The flange part 14 is for example with a spline 17 with a secondary flange 21 connected. The flange part 14 is with a support plate unit 15 connected in the compression springs 16 are arranged, with which the flange part 14 opposite the spline 17 is strained to reduce the game between the two or cancel.

The secondary flange 21 is about rivets 22 with a centering pot 23 and a first reaction plate 24 connected. The centering pot 23 is supported by a crankshaft bearing 25 , which is designed as a ball bearing, on the crankshaft 9 from. This is in the crankshaft 9 a blind hole 26 brought in. About a designed as a ball bearing shaft bearing 27 the centering pot is supported 23 on the inner shaft 4 of the double clutch 1 downstream gearbox from. Between the inner shaft 4 and the outer shaft 5 is a trained as a needle bearing second shaft bearing 28 arranged. About the second shaft bearing is the outer shaft 5 opposite the inner shaft 4 centered, in turn, over the shaft bearing 27 , the centering pot 23 and the crankshaft bearing 25 opposite the crankshaft 9 is centered. The centering pot 23 also ensures centering of the secondary side 18 of the dual mass flywheel 6 opposite the crankshaft or the two transmission input shafts 4 and 5 ,

The first counterpressure plate 24 is fixed with a central plate 29 and a clutch housing 30 connected, for example, riveted, as by rivets 31 is shown. The central plate 29 acts as a counter pressure plate for the second clutch 3 , At the same time the central plate acts 29 as a stop for the first printing plate 33 , The first printing plate 33 is about a first pressure piece 34 that have an outer release bearing 35 with an outer ring piston 36 is in operative connection, operated. Will one between a slave cylinder housing 37 and the outer ring piston 36 enclosed outer pressure chamber 38 pressurized, so the outer ring piston 36 and thus also the outer release bearing 35 in the direction of the arrow 39 emotional. About the first pressure piece 34 , by corresponding not shown recesses in the central plate 39 protrudes, this movement is on the first pressure plate 33 transfer. When pressurizing the outer pressure chamber 38 will be the first printing plate 33 towards the first counterpressure plate 24 emotional. This will be a first clutch disc 40 between the first pressure plate 33 and the first counterpressure plate 24 clamped so that in the circumferential direction a frictional connection with the first clutch disc 40 is effected.

The first clutch disc 40 includes a first clutch disk hub 41 , for example, with a spline with the inner shaft 4 is connected, and a first carrier disc 42 that with the clutch disc hub 41 is caulked. As an alternative to a caulking connection, a screw or rivet connection or a welded connection can also be provided here. The first carrier disk 42 is with a first elastic clutch disc carrier 43 riveted. The elastic coupling disk carrier 43 is formed flexible in the axial direction with respect to the axis of rotation R. The first elastic clutch disc carrier 43 carries on the side facing the transmission and on the side facing away from the gear each friction linings 44 ,

The structure of the second clutch 3 that with the hollow shaft 5 is basically similar to the first clutch 2 , As a counter-pressure plate acts here, the central plate 29 ,

The second printing plate 45 is via a second pressure piece 46 that has an inner release bearing 47 with an inner ring piston 48 is in operative connection, operated. Will one between a slave cylinder housing 37 and the inner ring piston 48 enclosed inner pressure chamber 38 pressurized, so the inner ring piston 48 and with it the inner release bearing 47 in the direction of the arrow 50 emotional. About the second pressure piece 46 this movement will be on the second pressure plate 45 transfer. When pressurizing the inner pressure chamber 49 So is the second pressure plate 45 towards the central plate 29 emotional. This will create a second clutch disc 51 between the second pressure plate 45 and the central plate 29 clamped, so that in the circumferential direction a frictional connection with the second clutch disc 51 is effected.

The second clutch disc 51 includes a second clutch hub 52 , for example, with a spline with the outer shaft 5 is connected, and a second carrier disc 53 that with the clutch disc hub 52 is caulked. As an alternative to a caulking connection, a screw or rivet connection or a welded connection can also be provided here. The second carrier disk 53 is with a second elastic clutch disc carrier 54 riveted. The elastic coupling disk carrier 54 is formed flexible in the axial direction with respect to the axis of rotation R. The second elastic clutch disc carrier 54 carries on the side facing the transmission and on the side facing away from the gear each second friction linings 55 ,

The second carrier disk 53 comprises a radially inner and a radially outer respectively substantially radially extending region and a connecting them, in the sectional view obliquely extending region. The latter is a truncated cone in the three-dimensional representation. As a result, the radially inner connection region with which the carrier disk 53 with the clutch disc hub 52 is connected, and the radially outer portion of the elastic Clutch disc carrier 54 the friction linings 54 carries, offset in the axial direction to each other. The radial direction is here as well as the axial direction and the circumferential direction unless otherwise indicated on the axis of rotation R besogened.

The slave cylinder housing 37 is supported by a gearbox support 56 on the transmission housing, not shown. This is the gearbox support with screws 57 with the slave cylinder housing 37 and with screws 58 bolted to the transmission housing, not shown.

A damping ring 59 is on the second clutch disc 51 arranged. The damping ring 59 is with a springy connection 60 with the second clutch disc 51 connected. The elastic connection 60 is in 1 with the usual mechanical equivalent circuit diagrams for a spring between the damping ring 59 and the second carrier disk 53 the second clutch disc 51 is arranged, shown. Between the damping ring 59 and the second clutch disc 51 is a damping element 61 arranged. The damping element 61 may be a viscous damper or a dry friction damper. The damping element 61 Thus, one or more viscoelastic elements may exist between the damping ring 59 and the second clutch disc 51 are arranged and / or arranged between these friction elements, which are in dry frictional contact with each other. The damping ring 59 is thus on the one hand resiliently movable in the radial direction relative to the second clutch disc 51 or their carrier disk 53 arranged. This elastic radial movement possibility is provided by the damping element 61 viscous or steamed by dry friction.

The damping ring 59 forms a damping mass that can damp vibrations in the radial direction. The damping ring 59 , the elastic connection 60 and the damping element 61 form a radial vibration damper 62 , which radial vibrations of the second clutch disc 51 as well as the outer shaft 5 (Hollow shaft) dampens.

2 shows a sketch to illustrate such vibrations. Shown is a part of a hollow shaft 5 that for the hollow shaft 5 in 1 stands. The open end of the shaft, the one with the second clutch hub 52 in 1 Equipped shaft end, can oscillate in the radial direction, this is by two double arrows 63 and 64 designated, execute. The double arrows 63 and 64 in 2 are perpendicular to each other and are in the radial plane, this is a plane perpendicular to the axis of rotation R level arranged. The double arrows 63 and 64 each stand for a eigenform of the wave 5 , Is the wave 5 anisotropic, this means that it has the same material properties in all (radial) spatial directions, so the eigenfrequencies belonging to both eigenmodes are the same.

3 shows a sketch for the inventive shift associated with the orthogonal natural modes belonging natural frequencies. In the left part of the 3 are shown on each other three frequency scales. The frequency f is plotted in the diagram a), b), and c) on the horizontal axis. Without the radial vibration damper 62 both modes have the same eigenfrequency f ₀ as in 3a is shown. The frequency f of the eigenform in the direction of the co-rotating x-axis is shown by a solid line, the perpendicular thereto arranged co-rotating y-axis is shown in dashed lines. The x and y axes correspond to the arrows 62 and 63 a co-rotating coordinate system.

In the anisotropic radial vibration damper 62 For example, the damping effects in two mutually perpendicular directions of a co-rotating coordinate system are different from each other. With the anisotropic radial vibration damper 62 , this is in a plan view along the axis of rotation R in 3d sketched as a schematic diagram, the natural frequencies are shifted in both co-rotating spatial directions. In the direction in which the radial vibration damper 62 works, this is in the 3d the y-axis, now enters an additional resonant frequency by the existence of the radial vibration damper 62 on. Thus, instead of only one resonance frequency, two resonance frequencies f _y1 and f _{y2 are} present in the eigen-form oscillating in the direction of the y-axis, which, however, is different from the resonance in the x-axis direction f _x lying perpendicular to the y-axis. The vibrations in the x-axis and y-axis are different in this way in an anisotropic vibration damper.

3c shows a diagram of the resonance frequencies in an isotropic radial vibration damper 62 like this one in 3e according to the representation of 3d outlined. In the case of the isotropic radial vibration damper 62 the damping effects in two mutually perpendicular directions of a co-rotating coordinate system are the same. As a result, two eigenfrequencies, each of which, however, are congruent, are denoted as f ₁ and f ₂ for both orthogonal eigenmodes. In this case, the vibration damping effect is essentially due to the damping introduced into the system due to the damping element 61 ,

4 shows an embodiment of a clutch disc according to the invention. In principle the configuration for the first clutch disc 40 and the second clutch disc 51 equal. Whether the solution according to the invention for the first clutch disc 40 or the second clutch disc 51 is used in principle does not change anything in the structure. The following embodiment is for the second clutch disc 51 described. The structure can be easily on the first clutch disc 40 transmitted, since their structure is basically the same.

In the description of the 4 is used instead of second clutch disc 51 , second clutch hub 52 , second carrier disk 53 and second elastic clutch disc carrier 54 and second friction linings 55 the adjective "second" is suppressed for easy readability.

In 4 an embodiment of a clutch disc according to the invention is shown 51 in a spatial representation. The clutch disc 51 includes a carrier disk 53 , on the radially outside of an elastic clutch disc carrier 54 is arranged. The elastic coupling disk carrier 54 is on both sides with friction linings 55 Mistake. The carrier disk 53 is with the clutch disc hub 52 connected. The damping ring 59 is with two opposite front spring tabs 65 with the carrier disk 53 connected. The front spring tabs 65 are designed substantially rod-shaped and comprise at its radially inner end in each case a fastening head 66 , the T-shaped on either side of a central axis of the spring tabs 65 extends. The fastening head 66 is each with studs 67 with the carrier disk 53 riveted. The fastening heads 66 are in the installation position of the clutch disc 51 the primary side 7 and thus the crankshaft 9 facing side of the clutch disc 51 arranged. Rear spring tabs 68 extend from the damping ring 59 essentially radially inward and protrude through recesses 69 the carrier disk 53 , The rear spring tabs 68 include in 4 invisible mounting heads with rivets 70 with the carrier disk 53 riveted. The rear spring tabs 68 are with their mounting heads on in the installation position of the primary side 7 or the crankshaft 9 opposite side of the carrier disk 53 arranged. The rear spring tabs 68 are each on both sides of the front spring tabs 65 arranged so that an arrangement of a front spring tab with both sides of this arranged rear spring tabs facing each.

The damping ring 59 is with two axial bolts 71 damped in the radial direction on the carrier disk 53 stored. The axial bolts 71 are about the circumference of the damping ring 59 Seen between the previously discussed opposite spring tab assemblies arranged. The axial bolts 71 are at the carrier disk 53 attached. To a radial movement of the damping ring 59 opposite the carrier disk 53 to enable, is the damping ring 59 in the area of penetration 72 through the axial bolt 71 optional. The damping takes place in the embodiment shown by a pre-loaded in the axial direction frictional contact between the damping ring 59 and axial bolts 71 instead of.

The above-described storage of the damping ring 59 at the carrier disk 53 illustrates an example of an anisotropic mounting, in which the elasticity of the connection in the direction parallel to the opposite front spring tabs 65 is less than perpendicular to it.

LIST OF REFERENCE NUMBERS

1

 Double coupling

2

 first clutch (for solid shaft)

3

 second coupling (for hollow shaft)

4

 inner shaft (full wave)

5

 outer shaft (hollow shaft)

6

 Dual Mass Flywheel

7

 primary

8th

 screw

9

 crankshaft

10

 first flange part

11

 second flange part

12

 Arch spring mount

13

 bow spring

14

 flange

15

 Gusset unit

16

 compression springs

17

 splines

18

 secondary side

19

 torsional vibration damper

20

 tensioning device

21

 Sekundärflansch

22

 rivet

23

 Zentriertopf

24

 first counterpressure plate

25

 crankshaft bearings

26

 Blind hole

27

 shaft bearing

28

 second shaft bearing

29

 Central plate

30

 clutch housing

31

 rivet

32

 rivet

33

 first printing plate

34

 first pressure piece

35

 outer release bearing

36

 outer ring piston

37

 Slave cylinder housing

38

 outer pressure chamber

39

 arrow

40

 first clutch disc

41

 first clutch disc hub

42

 first carrier disk

43

 first elastic clutch disc carrier

44

 first friction linings

45

 second pressure plate

46

 second pressure piece

47

 inner release bearing

48

 inner ring piston

49

 inner pressure chamber

50

 arrow

51

 second clutch disc

52

 second clutch hub

53

 second carrier disk

54

 second elastic clutch disc carrier

55

 second friction linings

56

 gearbox support

57

 Screw slave cylinder housing

58

 Screws gearbox housing

59

 damping ring

60

 elastic connection

61

 damping element

62

 radial vibration

63

 double arrow

64

 double arrow

65

 front spring tabs

66

 fastening head

67

 rivet

68

 rear spring tabs

69

 recesses

70

 rivet

71

 axial bolts

72

 Area of penetration

Claims (10)

Clutch disc ( 51 ) for a friction clutch ( 1 ), characterized in that it has a radially effective vibration damper ( 62 ). Clutch disc according to claim 1, characterized in that the vibration damper ( 62 ) a damping ring disk ( 59 ), which in the radial direction resiliently on a carrier disc ( 53 ) of the clutch disc ( 51 ) is arranged. Clutch disc according to claim 1 or 2, characterized in that the elasticity of the connection of the damping ring disc ( 59 ) on the carrier disk ( 53 ) is the same in all directions or in at least two directions ( 63 . 63 , x, y) is different. Clutch disc according to one of the preceding claims, characterized in that between the damping ring disc ( 59 ) and carrier disc ( 53 ) at least one effective in the radial direction damper ( 61 ) is arranged. Clutch disc according to one of the preceding claims, characterized in that the damping ring disc ( 59 ) with spring tabs ( 65 . 68 ) on the carrier disk ( 53 ) is attached. Clutch disc according to one of the preceding claims, characterized in that the spring straps ( 65 . 68 ) with the damping ring disk ( 59 ) and / or with the carrier disk ( 53 ) are riveted. Clutch disc according to one of the preceding claims, characterized in that the spring straps ( 65 . 68 ) partly on the gear side remote and partly on the gear side facing the carrier disc ( 53 ) are attached. Clutch disc according to one of the preceding claims, characterized in that the carrier disc ( 53 ) comprises a frusto-conical region. Clutch disc according to one of the preceding claims, characterized in that and the carrier disc ( 53 ) on a clutch disc hub ( 52 ), wherein the carrier disc ( 53 ) frictionally and / or positively and / or cohesively with the coupling disc hub ( 52 ) connected is. Friction clutch, in particular double clutch ( 1 ) comprising at least one clutch disc ( 51 ) according to any one of the preceding claims.

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