DE102011017655A1 - Friction clutch, particularly wet running friction clutch for use in drive train of vehicle, has clutch housing and friction surface formation coupling at driving end for common rotation with drive element around rotational axis - Google Patents

Abstract

The friction clutch has a clutch housing (16) and a friction surface formation (36) coupling at driving end for common rotation with a drive element around a rotational axis (A). The friction surface formation is coupled with a driven element (50) and is brought into frictional engagement with the driving end friction surface formation by a pressure element (54). A deflection mass pendulum unit (66) is provided with a deflection mass carrier (68) and a deflection mass arrangement (70) that is displaced against reset effect of a spring arrangement (72) related to the deflection mass carrier.

Description

The present invention relates to a friction clutch, for example designed as a so-called wet-running friction clutch, which can be used in the drive train of a vehicle to transmit torque from a drive unit, such as an internal combustion engine, to the following parts of a drive train, such as a transmission.

The DE 102 36 752 A1 discloses a hydrodynamic torque converter, in which a generally wet-running lock-up clutch can be used to transmit torque in the lock-up state directly from a converter housing to a driven member, ie a hub of the torque converter, and thus to a transmission input shaft. In the torque transmission path between this lock-up clutch and the output member is a torsional vibration damper, to which a deflection mass unit is coupled with a Auslenkungsmassenträger and against the return action of a spring assembly with respect to this deflectable Auslenkungsmassenanordnung. In the case of vibration excitation, this deflection mass unit or the deflection mass thereof is excited to oscillate with a natural frequency defined by the mass ratios and the rigidity of the spring arrangement, so that here a vibration damping characteristic tuned to a fixed frequency by the natural frequency of the deflection mass unit is obtained. In general, such Auslenkungsmasseneinheiten are also referred to as Festfrequenztilger.

An essential characteristic of such Auslenkungsmasseneinheiten or the Festfrequenztilgers is that they are coupled to the torque transmission by either Auslenkungsmassenträger provides a component of the torque transmission path or is coupled to a component of the torque transmitting assemblies, but that the torque to be transmitted not via the spring assembly of Displacement mass unit is passed. Rather, only the Auslenkungsmassenanordnung on Auslenkungsmassenträger is supported on this spring arrangement, d. H. with respect to this supported in particular when performing an oscillating deflection movement, so that the stiffness of the spring assembly can be tuned solely to the required vibration behavior of the Auslenkungsmassenanordnung, but not in terms of to be transmitted via a drive train torques must be dimensioned.

The DE 100 24 191 A1 discloses a hydrodynamic torque converter in which a housing driven for rotation by a drive shaft not only surrounds a turbine wheel and a lock-up clutch, but also an impeller. The impeller is coupled via a spring arrangement for transmitting torque to the converter housing, so that this spring arrangement transmits the torque introduced into the converter housing to the impeller or in the engagement state to the lock-up clutch. This spring arrangement thus acts with the converter housing as a primary-side mass and the impeller as a secondary mass in the manner of a torsional vibration damper, via whose spring arrangement the torque to be transmitted is passed.

It is the object of the present invention to provide a friction clutch, in particular wet-running friction clutch, which has an improved vibration damping behavior in a compact design.

According to the invention this object is achieved by a friction clutch, in particular wet-running friction clutch, comprising a clutch housing, a friction-side formation for common rotation with a drive member about a rotation axis engageable by a pressing member in frictional engagement with the drive-side friction surface formation and with a driven member for rotation about Rotary axis coupled output side friction surface formation, a Auslenkungsmassenpendeleinheit with a Auslenkungsmassenträger and a deflectable against the return action of a spring assembly with respect to the Auslenkungsmassenträgers from a basic relative position Auslenkungsmassenanordnung, wherein the coupling housing provides at least a portion of the Auslenkungsmassenanordnung and / or the Auslenkungsmassenträgers.

In the structure according to the invention, a functional fusion takes place in the components of the friction clutch insofar as the clutch housing is used as part of the deflection mass pendulum unit. By providing a portion of the deflection mass assembly and / or the deflection mass carrier, it is not necessary to provide an additional assembly that incorporates this functionality. In particular, when the coupling housing provides a part of the Auslenkungsmassenanordnung or possibly the entire Auslenkungsmassenanordnung, the comparatively large mass and thus the comparatively large moment of inertia of the coupling housing can be used to obtain a corresponding vote on a stimulating and preferably to be eliminated vibration frequency.

It can be provided in a structurally simple to implement variant that the coupling housing is mounted with respect to a drive-side friction surface formation having input module. The input assembly may include an input hub and / or a friction element carrier for the drive-side friction surface formation. It should be noted here that of course the input hub and Reibelemententräger can be realized on one and the same component or can be provided as separate, but nevertheless interconnected components.

When providing an input module with an input hub, the bearing of the coupling housing on the input hub offers as structurally simple to implement design.

In particular, when the friction clutch is designed as a wet-running friction clutch, so a fluid to be filled or filled interior of the clutch housing must be substantially fluid-tight encapsulated, it can be provided that the at least one part of the Auslenkungsmassenanordnung providing the clutch housing filled with fluid or fillable interior surrounds fluid-tight and that the spring assembly is disposed in the interior.

In this case, a further function merger can be achieved in that the deflection mass carrier comprises the input module. This means that two assemblies to be provided in any case, namely the coupling housing on the one hand and the input module on the other hand, provide essential constituent groups of the deflection mass units.

In an alternative embodiment it can be provided that the input module together with a first housing shell provides an inner clutch housing and a fluid-filled or fillable interior substantially fluid-tight surrounds and that a second housing shell together with the first housing shell provides an outer clutch housing, wherein the Auslenkungsmassenanordnung includes the second housing shell. In this variant, an at least partially double-shell design of the coupling housing is realized, in which case an inner shell region or an inner coupling housing realizes the fluid-tight seal, while an outer coupling housing is used to provide the Auslenkungsmassenanordnung, wherein the Auslenkungsmassenträger may comprise the first housing shell.

Since in this embodiment, the Auslenkungsmassenanordnung outside the fluid-tight encapsulated interior, it is advantageous if the spring assembly is disposed outside of this interior.

In this case, it may be provided, for example, that the second housing shell surrounds the input module at its radial outside and preferably also at its axial side facing away from the first housing shell.

In order to further improve the vibration damping behavior of the friction clutch according to the invention, it is proposed that the drive-side friction surface formation is coupled to a secondary side of a first Torsionsschwingungsdämpferanordnung and a primary side of the first Torsionsschwingungsdämpferanordnung with the drive member can be coupled. It can further be provided that the output-side friction surface formation is coupled to the output member by means of a second torsional vibration damper arrangement. Thus, in addition to the repayment functionality provided by the deflection mass unit, by providing at least one torsional vibration damper in the torque flux of the torque to be transmitted, it is possible to further widen the attenuation spectrum such that even in the case of vibrational excitations or rotational nonuniformities defined by the natural frequency of the displacement mass unit , a damping functionality may be provided.

The present invention will be described below in detail with reference to the accompanying drawings. It shows:

1 a wet-running friction clutch having a torsional vibration damper assembly arranged upstream of the torque flow;

2 one of the 1 corresponding representation of an alternative Ausgestaltungsart.

In 1 is a wet-running friction clutch 10 with one with two housing shells 12 . 14 built-up clutch housing 16 shown. The two in their radially outer region by welding firmly interconnected housing shells 12 . 14 enclose an interior 18 which is filled with a fluid, for example oil, at least in the torque transmission mode. With the housing shell 12 , which is to be positioned facing a gearbox, is a housing hub 20 connected, which engages in a transmission housing.

A general with 22 designated input assembly of the friction clutch 10 includes an input hub 24 on which the clutch housing 16 with its housing shell 14 is mounted fluid-tight and rotatable. In order to produce the fluid-tight seal, an outer peripheral groove of the input hub can be formed 24 inserted sealing element 26 serve. In the axial direction is the housing shell 14 by a step-like radial expansion 28 on the one hand and one on the input hub 24 to be determined circlip 30 on the other hand.

With the input hub 24 For example, by welding a generally pot-shaped friction element carrier 32 firmly connected. This carries in its radially outer region a plurality of, for example, lamellar, ring-disk-like friction elements 34 a drive-side friction surface formation 36 , The friction elements 34 are with the Reibelemententräger 32 rotatably supported with respect to this, however, movable in the direction of a rotation axis A.

To the friction elements 34 the drive-side friction surface formation 36 For example, lamellar, annular disk-like friction elements are alternating 38 a second friction surface formation 40 arranged. These are in their radially inner region with a driven-side friction element carrier 42 coupled to the common rotation about the axis of rotation A, but with respect to this axially displaceable. The driven-side friction element carrier 42 is with a primary side comprising two cover disk elements 44 a torsional vibration damper assembly 46 connected by riveting. A one between the two cover disk elements of the primary side 44 engaging central disk element comprehensive secondary side 48 the torsional vibration damper assembly 46 is radially inward with an effective as output drive output hub 50 firmly connected, here by integral design, but alternatively also by welding, riveting or the like. The primary side 44 and the secondary side 48 are against the return action of a, for example, a plurality of approximately circumferentially extending helical compression springs comprehensive damper element arrangement 49 rotatable relative to each other about the axis of rotation A. The output hub 50 is by gearing engagement with an output shaft 52 , For example, transmission input shaft, coupled for common rotation about the axis of rotation A.

At the entrance assembly 22 is a clutch piston effective as a pressing 54 carried so that this together with the Reibelemententräger 32 one from the interior 18 delimited pressure fluid space 56 limited. This can be done by the output shaft 52 be fed through with pressurized fluid, whereby the with the input module 22 For example, rotatably held clutch piston 54 towards the two friction surface formations 36 . 40 is moved to and their friction elements 34 . 38 can press in the mutual friction fit. In this way, the torque transmission state of the friction clutch 10 getting produced.

In the torque flow between an in 1 not shown and effective as a drive member drive shaft, such as crankshaft of an internal combustion engine, and the input module 22 is another torsional vibration damper assembly 56 , This comprises a primary side formed with two cover disk elements 58 and one formed with a central disk element and with this central disk element at least partially between the cover disk elements of the primary side 58 lying secondary side 60 , Against the effect of a damper element arrangement 62 For example, comprising a plurality of approximately circumferentially extending helical compression springs are the primary side 58 and the secondary side 60 in the circumferential direction with respect to each other about the axis of rotation rotatable.

The central disk element 60 is for example via a plurality of flexible, leaf spring-like or annular disk-like elements with a damper hub 64 rotatably connected, which by gearing engagement with the input module 22 , in particular the input hub 24 , is coupled for common rotation about the axis of rotation A.

At the in 1 As described, the structure delivered by the drive shaft and the Torsionsschwingungsdämpferanordnung 56 Forwarded torque via the input module 22 into the wet-running friction clutch 10 initiated. This input module 22 Gives the torque over the frictionally engageable friction surface formations 36 . 40 and the torsional vibration damper assembly 46 to the output hub 50 and thus the output shaft 52 further. The coupling housing 16 with its two housing shells 12 . 14 and also the housing hub 20 does not lie in the torque flow, so it is not used for torque transmission.

A general with 66 designated deflection mass pendulum unit comprises a deflection mass carrier 68 , which is substantially provided here by an axial end portion of the Reibelemententrägers 32 that is the input module 22 , Furthermore, the deflection mass pendulum unit comprises 66 a deflection mass arrangement 70 , which in the illustrated example is essentially provided by the coupling housing 16 , so primarily the two housing shells 12 . 14 , and, if present, also the attached housing hub 20 , Because the housing shell 14 on the input hub 24 is rotatably supported, can the clutch housing 16 with respect to the torque-transmitting assemblies, in particular so the input module 22 and the friction surface formations 36 . 40 to move the rotation axis A. By a spring arrangement 72 is the deflection mass arrangement 70 , essentially the clutch housing 16 , with respect to the deflection mass carrier 68 So the input module 22 , biased in a basic relative position. The spring arrangement 72 may include a plurality of circumferentially successive helical compression springs, which are located on respective support areas of the Auslenkungsmassenträgers 68 on the one hand and the coupling housing 16 on the other hand can be supported in the circumferential direction. For this purpose, the deflection mass carrier 68 comprise radially outwardly cross-supporting sections, which in the manner of a central disk element axially between two through the housing shell 16 on the one hand and the housing shell 14 on the other hand provided, acting like a disc-like areas and, as well as the cover disc-like acting areas, Umfangsabstützkanten for the springs of the spring assembly 72 provides.

When vibration excitation occurs is contrary to the resetting effect of the spring assembly 72 the deflection mass arrangement 70 to the vibration with respect to the Auslenkungsmassenträgers 68 stimulated. Essentially defined by the stiffness of the spring assembly 72 and the moment of inertia of the deflection mass arrangement 70 has the deflection mass pendulum unit 66 a natural frequency. With this natural frequency, the Auslenkungsmassenpendeleinheit 66 be tuned to a stimulating frequency, which is primarily damped or eradicated so that the Auslenkungsmassenpendeleinheit 66 can be effective as Festfrequenztilger. Here, too, the effect is essentially utilized that the Auslenkungsmassenpendeleinheit 66 or their spring arrangement 72 is not in the torque flow, so is not used, that of a drive shaft to the output shaft 52 to transmit torque to be transmitted. While the damper element arrangements 49 . 62 the two torsional vibration damper assemblies 46 . 56 must be dimensioned so that they can also transmit this drive or braking torque, the spring assembly 72 the deflection mass pendulum unit 66 only be designed to take into account the inertia of the Auslenkungsmassenanordnung 70 their vibration with respect to the Auslenkungsmassenträgers 68 to enable.

One recognizes that at the in 1 illustrated embodiment, the essential components of the Auslenkungsmassenpendeleinheit 66 by assemblies of the friction clutch 10 be provided, namely the input module 22 on the one hand and the clutch housing 16 on the other hand. In this way, it is taking advantage of the comparatively large moment of inertia of the clutch housing 16 possible to obtain a comparatively compact size. Furthermore, the springs of the spring assembly are 72 in the from the clutch housing 16 enclosed interior 18 and are thus by the interior 18 lubricated existing fluid, so that, for example, with respect to the coupling housing 16 occurring friction effects that could affect the vibration behavior can be largely avoided.

Because in this Ausgesaltungsform the clutch housing 16 and thus also the housing hub 20 when vibrational excitation undergoes one of the already existing rotational movement superimposed oscillatory motion, it may be advantageous for a supply of the interior 18 pump used with fluid, for example in a transmission, not through the housing hub 20 to drive, but by a separate, such as electric motor drive. In this way, oscillations in the pumping behavior, which can also lead to a comparatively heavy load on such a pump, can be avoided.

An alternative embodiment is in 2 shown. Components which correspond to components described above in terms of construction or function are denoted by the same reference numeral. In the following, only to the embodiment according to 1 existing differences.

At the in 2 illustrated embodiment form the gearbox side to be positioned housing shell 12 of the coupling housing 16 and the input module 22 together an inner clutch housing 74 , The friction element carrier 32 the input module 22 is at its free axial end portion with the housing shell 12 for example, firmly connected by welding and encloses together with this the interior 18 essentially fluid-tight.

Together with the housing shell 14 forms the housing shell 12 in this embodiment, an outer clutch housing 76 , It surrounds the housing shell 14 the Reibelemententräger 32 in its radially outer region and also on its from the housing shell 12 facing away from the axial side and surrounds it to the outside. The housing shell 14 is on the input hub 24 rotatably supported. As the fluid-tight completion of the interior 18 here by the Reibelemententräger 32 is realized is a fluid-tight connection of the housing shell 14 where they are at the input hub 24 is stored, not required.

In her over the connection area with the Reibelemententräger 32 outgoing end portion forms the housing shell 14 the deflection mass carrier 68 the deflection mass pendulum unit 66 , At this area of the housing shell 12 are Umfangsabstützbereiche for the springs of the spring assembly 72 provided, as well as at the axial end portion of the housing shell 14 , so that under compression of the springs of the spring assembly 72 similar to a torsional vibration damper, the Auslenkungsmassenanordnung 70 in the circumferential direction with respect to the housing shell 12 and thus with respect to the clutch housing 16 can move.

Also in this embodiment, thus the Auslenkungsmassenanordnung 70 , which here essentially just the one together with the housing shell 12 the outer case 76 providing housing shell 14 , perform a vibratory motion without the Auslenkungsmassenpendeleinheit 66 , in particular the spring arrangement 72 the same, would be integrated into the torque transmission path. Due to the fact that in this embodiment, the Auslenkungsmassenanordnung 70 not including the fluid-tight termination of the interior 18 provides is the spring assembly 72 here for reasons of simpler structural design outside the interior 18 arranged. It can be seen further that in this embodiment, the clutch housing 16 both the deflection mass arrangement 70 the deflection mass pendulum line 66 , as well as the deflection mass carrier 68 provides.

The principles of the present invention may, of course, be modified in various forms or used in other environments. So could the wet-running clutch assembly 10 not like in 1 and 2 shown to be formed without hydrodynamic circuit, but it could be formed with a hydrodynamic circuit, ie in the manner of a hydrodynamic torque converter or a fluid coupling, in which case the two friction surface formations 36 . 40 are essentially friction surface formations of a lock-up clutch. Furthermore, it goes without saying that in particular in the 2 illustrated embodiment, the Auslenkungsmassenanordnung 70 could be formed with other geometric design. For example, it could be the inner clutch housing 74 essentially only annular, so be formed on the radially outer region surrounding.

It should also be noted that the spring arrangement 72 instead of the above-explained and due to their stability and durability particularly advantageous helical compression springs may also be formed with elastomeric elements. Furthermore, the embodiment could also be such that in particular in the in 2 illustrated variant, the spring assembly 72 the inner case 74 For example, comprising annularly surrounding elastomeric material, which to the inner housing 74 on the one hand and the deflection mass arrangement 70 on the other hand, for example, materially connected and under deformation thereof a relative rotational movement of the Auslenkungsmassenanordnung 70 with respect to the deflection mass carrier 68 , which then essentially through the inner housing 74 , For example, the Reibelemententräger 32 , is provided.

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 10236752 A1 [0002]
• DE 10024191 A1 [0004]

Claims (12)

Friction clutch, in particular wet-running friction clutch, comprising: - a clutch housing ( 16 ), - one for common rotation with a drive member about a rotational axis (A) coupled drive-side friction surface formation ( 36 ), - one by a pressing member ( 54 ) in frictional engagement with the drive-side friction surface formation ( 36 ) can be brought and with a power take-off ( 50 ) for the rotation about the axis of rotation (A) coupled output-side friction surface formation ( 40 ), - a deflection mass pendulum unit ( 66 ) with a deflection mass carrier ( 68 ) and one against the restoring action of a spring arrangement ( 72 ) with respect to the deflection mass carrier ( 68 ) from a basic relative position deflectable Auslenkungsmassenanordnung ( 70 ), wherein the coupling housing ( 16 ) at least a part of the deflection mass arrangement ( 70 ) and / or the deflection mass carrier ( 68 ). Friction clutch according to claim 1, characterized in that the clutch housing ( 16 ) with respect to a drive-side friction surface formation ( 36 ) input module ( 22 ) is stored. Friction clutch according to claim 2, characterized in that the input module ( 22 ) an input hub ( 24 ) and / or a friction element carrier ( 32 ) for the drive-side friction surface formation ( 36 ). Friction clutch according to claim 3, characterized in that the clutch housing ( 16 ) on the input hub ( 24 ) is stored. Friction clutch according to one of claims 1 to 4, characterized in that the at least one part of the Auslenkungsmassenanordnung ( 70 ) providing coupling housing ( 16 ) a fluid filled or fillable interior ( 18 ) surrounds fluid-tight and that the spring arrangement ( 72 ) in the interior ( 18 ) is arranged. Friction clutch according to claim 3 and claim 5, characterized in that the deflection mass carrier ( 68 ) the input module ( 12 ). Friction clutch according to claim 3 or claim 4, characterized in that the input module ( 22 ) together with a first housing shell ( 12 ) an inner clutch housing ( 74 ) and a fluid filled or fillable interior space ( 18 ) encloses substantially fluid-tight and that a second housing shell ( 14 ) together with the first housing shell ( 12 ) an outer clutch housing ( 76 ), wherein the deflection mass arrangement ( 70 ) the second housing shell ( 14 ). Friction clutch according to claim 7, characterized in that the second housing shell ( 14 ) the input module ( 22 ) on its radially outer side and preferably also of the first housing shell ( 12 ) facing away from the axial side. Friction clutch according to claim 7 or claim 8, characterized in that the deflection mass carrier ( 69 ) the first housing shell ( 12 ). Friction clutch according to one of claims 7 to 9, characterized in that the spring arrangement ( 72 ) outside the interior ( 18 ) is arranged. Friction clutch according to one of claims 1 to 10, characterized in that the drive-side friction surface formation ( 36 ) with a secondary side ( 60 ) of a first torsional vibration damper arrangement ( 56 ) and a primary page ( 58 ) of the first torsional vibration damper arrangement ( 56 ) is coupled to the drive member. Friction clutch according to one of claims 1 to 11, characterized in that the driven-side friction surface formation ( 40 ) by means of a second torsional vibration damper arrangement ( 46 ) with the output member ( 50 ) is coupled.

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