WO2009105401A1

WO2009105401A1 - Clutch device with a flex plate

Info

Publication number: WO2009105401A1
Application number: PCT/US2009/034206
Authority: WO
Inventors: Hans Jürgen HAUCK
Original assignee: Borgwarner Inc.
Priority date: 2008-02-18
Filing date: 2009-02-16
Publication date: 2009-08-27
Also published as: DE102008032273B4; DE102008032273A1

Abstract

The present invention relates to a clutch device (2) having at least one output hub (46), which can be rotationally locked to a transmission input shaft (50), an input hub (16), in which an assembiy opening (54) is provided, so that a fastener (58) for axially fixing the output hub (46) to the transmission input shaft (50) can be introduced by way of the assembly opening (54), and a flex plate (74), on which a hub part (56) is provided, which can be rotationally locked to the input hub (16). According to the invention the hub part (56) can be connected to the input hub (16) in such a way that the assembly opening (54) is closed by the hub part (56).

Description

CLUTCH DEVICE WITH A FLEX PLATE

DESCRIPTION

The present invention relates to a clutch device having at least one output hub, which can be rotationaily locked to a transmission input shaft, an input hub, in which an assembly opening is provided, so that a fastener for axially fixing the output hub to the transmission input shaft can be introduced via the assembly opening, and a flex plate, on which a hub part is provided, which can be rotationaily locked to the input hub.

The state of the art discloses clutch devices, in particular multiple- dutch devices, such as dual clutches, for example, which are provided with an input hub and at least one output hub. DE 10 2005 045 158 A1 , for example, describes a dual clutch device with an input hub and two output hubs, the latter each having the facility for rotational locking to a transmission input shaft of a transmission. The input hub of the known clutch device can be directly connected to an engine output shaft of an engine and has a central assembly opening. Once the known clutch device has been inserted into the transmission bell housing, so that the output hubs are each rotationaily locked to a transmission input shaft, a fastener for axially fixing one of the two output hubs to the associated transmission input shaft can be introduced via the assembly opening, if the fastener, in this case a boit, is introduced via the assembly opening and the one output hub is therefore axially fixed to one of the transmission input shafts, the assembly opening must then be sealed by means of a closing or sealing part, in order to prevent oil escaping from the wet-running dual clutch device. Any operation of the known dua! clutch device is therefore possible only once the closing or sealing part has been fitted.

Also known in the case of hydrodynamic torque converters is the provision of so-calied flex plates between the input side of the torque converter and an output side of a power unit, which on the one hand can transmit a torque from the drive side to the input side of the torque converter and on the other is capable of cushioning axial misalignments of the drive- side component in such a way that these are not transmitted to the input side of the torque converter. It is to be noted, however, that the fiex piates used for this purpose generally have a low flexibility and primarily serve for said transmission of torque from the drive side to the input side of the torque converter and for the connection to a flywheel, the connection diameter of 5 which is particularly iarge. in the past such flex plates have also been used between a power unit on the one hand and a clutch device on the other, in order to prevent the axial misalignment of the drive-side component being transmitted to the clutch device. Thus the state of the art in particular discloses clutch devices, the input hub of which is rotationally locked to a flex i o plate, the flex plate additionally being rotationaliy locked to a flywheel on the drive side.

Although the dual clutch device described above with reference to DE 10 2005 045 158 A1 has been tried and proven, the use of a fiex plate, which can be rotationally locked to the input hub of the known dual ciutch device,

15 would entail an exceptionally high assembly outlay. For example, the fastener would first have to be introduced through the assembly opening, before then closing the assembly opening by means of the closing or sealing part. The rotationally fixed attachment of the fiex plate can here be done before or after the aforementioned assembly operations.

20 The object of the present invention, therefore, is to create a clutch device having an input hub, in which an assembly opening is provided, and a flex piate which can be rotationally locked to the input hub, the intention being to make assembly of the clutch device according to the invention especially rapid and easy.

25 This object is achieved by the features specified in claim 1.

Advantageous embodiments form the subject matter of the dependent claims.

The clutch device according to the invention comprises at least one output hub, which can be rotationally locked to a transmission input shaft.

30 The clutch device may be a multiple-clutch device, for example, preferably a dual clutch device, which therefore has two output hubs, which can each be rotationaily locked to a transmission input shaft of a transmission, in this way a torque can be transmitted from the clutch device via the respective output hub to the associated transmission input shaft. The clutch device further comprises an input hub, via which a torque can be introduced into the clutch device. Thus the input hub, for example, can be rotationally locked to a drive- side component of the drivetrain. A preferably central assembly opening is provided in the input hub. The assembly opening aliows a fastener for axially 5 fixing the output hub to the transmission input shaft to be introduced via or through the assembly opening. The clutch device can therefore be fixed as a module to the transmission, so that at least one transmission input shaft extends into the dutch device, which means that only then does the output hub need to be axially fixed to one of the transmission input shafts by i o inserting the fastener through the assembly opening. The clutch device according to the invention further comprises a so-cailed flex plate, on which a hub part is provided, which can be rotationally locked to the input hub. The meaning of the term 'flex piate' is here the same as the English-tanguage term 'fiexplate' used among experts. A flex plate can therefore be taken to

15 mean, in particular, a torque-transmitting piate, which is of a flexible design in an axial direction, such that an axial misalignment of the input side in relation to the output side of the torque-transmitting plate is not transmitted to the output side of the torque-transmitting plate or vice-versa. Reference may be made to the state of the art with regard to this. According to the invention the

20 hub part provided on the flex plate can be connected to the input hub in such a way that the assembly opening can be closed by the hub part itself. in the case of the clutch device according to the invention this can first be arranged as a moduie on the transmission of the drivetrain, so that at least one transmission input shaft extends into the clutch device and is 25 rotationally locked to least one output hub. A fastener, preferably a retainer ring or a bolted part, for axially fixing the output hub to the transmission input shaft can then be introduced via or through the assembly opening. Once the output hub has been axially fixed to the transmission input shaft by means of the fastener, there is no need to introduce a separate closing or sealing part

30 into the assembly opening. Instead the flex plate merely has to be rotationally locked to the input hub via the hub part provided thereon, so that the hub part at the same time closes the assembly opening in the input hub. This firstly reduces the number of parts in the clutch device and secondly makes it possible to dispense with an additional assembly operation. The assembly of - A -

the clutch device and its incorporation into a drivetrain is therefore permanentiy simplified.

In an advantageous embodiment of the clutch device according to the invention the hub part can be connected to the input hub in such a way that 5 the assembly opening can be closed with a preferably fluid-tight seal, more preferably still an oil-tight seal, by the hub part. For this purpose further sealing means, for example, may be provided on the input hub and/or the hub part of the flex plate. The sealing function of the hub part means that the clutch device can therefore be operated as a wet-running clutch device, i o without the clutch fluid, preferably oil, being able to escape via the assembly opening, which would inevitably lead to a functional impairment of the wet- running clutch device.

In a particularly advantageous embodiment of the clutch device according to the invention the hub part on its side remote from the input hub

15 comprises a first projection, preferably a so-called pilot spigot. The first projection may be nested in a radial direction with an output shaft of a power unit, that is to say the first projection may enclose the output shaft of a power unit in a radial direction and/or may be enclosed in a radial direction by the output shaft. It is preferable here, however, if the first projection can be

20 introduced into a centra! end-face recess in the output shaft. The first projection means that the clutch device is especially easy to incorporate into the drivetrain, the term Output shaft of a power unit' being taken to mean not only the actual engine output shaft, but also the components having a rotationai drive connection thereto, such as a flywheel, for example. 25 In a further advantageous embodiment of the clutch device according to the invention the first projection and the output shaft can preferably be nested in a radia! direction in such a way that these are capable of supporting one another in a radial direction. This also substantially facilitates the incorporation of the clutch device according to the invention into a drivetrain,

30 especially since it also serves to bring the axes of rotation of the output shaft and the clutch device into alignment one behind the other. In this context it is more preferable still if the first projection and the output shaft are configured in such a way that these center one another when fitted into one another. - D -

In order to prevent the first projection tilting inside the central end-face recess in the output shaft in the event of any skewing of the axis of rotation of the drive components in relation to the axis of rotation of the clutch device, the first projection in the axiai direction comprises a section facing the input hub and a support section remote from the input hub, the output shaft being supportable solely on the support section. Consequently no support is afforded on the section facing the input hub, so that tilting is reliably prevented, in this embodiment the first projection is preferably of a mushroom-shaped design, so as to further enhance the aforementioned advantage.

In order to further facilitate the assembly of the flex plate with the hub part on the input hub of the clutch device, in a preferred embodiment of the dutch device according to the invention the hub part may be rotationalty locked to the input hub by means of a slip-on gearing. !n order to form the slip-on gearing, the hub part together with the flex plate merely has to be brought together with the input hub in an axial direction, the slip-on gearing preferably being formed by an internal toothing on the one hand and an external toothing on the other. Thus the internal toothing may be provided on the hub part of the flex plate, for example, whilst the external toothing is provided on the input hub of the clutch device, it is preferable, however, if the interna! toothing is provided on the input hub, whilst the external toothing is formed on the hub part of the flex plate, as will be explained in more detail below with reference to a further embodiment. In either case it is more preferable stili, if the internal toothing and the external toothing are formed as straight teeth, in order to facilitate assembly.

In a particularly preferred embodiment of the clutch device according to the invention the siip-on gearing is embodied as a press-fit toothing free of torsional play. This serves to prevent rattling noises in the transmission of torque from the hub part to the input hub, which derive from an alternating collision of the gear tooth profiles of the internal and external toothing. The clutch device according to the invention in this embodiment is therefore particularly quiet in operation. - b -

in a further advantageous embodiment of the clutch device according to the invention the press-fit toothing free of torsional p!ay formed by the slip- on gearing is embodied in such a way that during operation of the clutch device the hub part is in an axial direction immovably fixed to the input hub. 5 In this embodiment the internal and external toothing forming the press-fit toothing must therefore be dimensioned in such a way that even in the event of an axial misalignment of the input side of the flex plate in relation to the output side of the flex plate, no shifting of the hub part occurs in an axiai direction relative to the input hub. in this embodiment a compensation for i o axial tolerances between the drive-side components and the clutch device inside the drivetrain is brought about during the assembly or press-fitting process, in that the hub part together with the flex plate is inserted or pressed to a greater or lesser extent into or onto the input hub. The clutch device according to the invention therefore allows an especially simple and durable

15 compensation for tolerances between the clutch device on the one hand and the drive-side components of the drivetrain on the other. in order to facilitate the rotationally locked connection of the hub part to the input hub and in particular the production of a press-fit toothing free of torsional play between the hub part and the input hub, in a further preferred

20 embodiment of the clutch device according to the invention at least one recess is provided in the hub part or the flex plate, whilst at least one retaining device is provided on the input hub, in such a way that in a predefined rotational or assembly position of the hub part and the flex plate relative to the input hub the retaining device is arranged at least on a 25 common radial with the recess. Thus a retaining element of a pressing tool for producing the press-fit toothing, such as a hook-shaped retaining element, for example, can be fed through the recess and connected to the retaining device. The retaining element can then be used to exert a tensile force on the input hub in an axial direction, whilst a punch or the like of the

30 pressing tool might exert a compressive force on the hub part in the opposite axial direction. In this way the hub part and the input hub are assembled or pressed together forming the press-fit toothing free of torsional play. In this embodiment it is preferred if the recess is provided in the flex plate. This has the advantage, compared to a recess in the hub part, that the recess in the flex plate gives it a greater flexibility. Furthermore a recess in the thin-wailed flex piate is substantiaiiy easier to produce than a recess in the more solid hub part. A recess in the hub part, on the other hand, has the advantage that depending on the design of the hub part the recess can be arranged further 5 inwards in a radiai direction. In addition it is furthermore preferred if the retaining device and the recess are arranged in such a way that in the predefined rotational or assembly position of the hub part and the fiex piate relative to the input hub the retaining device is arranged in alignment with the recess in an axial direction, in the case of the last aforementioned design i o variant, an especially rapid access to the retaining device by means of the retaining element of the pressing tool is possible, thereby further facilitating the process of fitting the hub part and the flex piate to the input hub. Regardless of which design variant of this embodiment is selected, multiple recesses may be provided in the hub part or the flex piate, but preferably in

15 the hub part, which in the predefined rotational or assembly position are each assigned to a continuous retaining device or each assigned to one of a plurality of retaining devices on the input hub. Thus two or more recesses should preferably be provided, in order to allow a uniform compression of the hub part and the input hub. in this context it is also preferable if at least two

20 recesses are arranged uniformly distributed or spaced in a circumferential direction. The same applies analogously to the retaining devices, if more than one retaining device is provided.

In a further particularly preferred embodiment of the clutch device according to the invention the retaining device is arranged on the end face of 25 the input hub. If the retaining device, in the predefined rotational or assembly position of the hub part and the flex plate, is here furthermore arranged in axial alignment with the recess in the hub part or the flex plate, this affords an especially direct and rapid access to the retaining device by means of the retaining element of the pressing tool. Furthermore in this case the retaining

30 element need not necessarily be hook-shaped. Instead it is here preferred if the end-face retaining device is embodied as a tapped hole, so that the retaining element of the pressing tool may also be embodied as a rod or shaft provided with a mating thread, such as a bolt, for example. In this case the tapped hole affords an especially secure hold for the retaining element inside the retaining device in the form of the tapped hole. in a further preferred embodiment of the clutch device according to the invention, which represents an alternative development of the embodiment previously described, the retaining device is formed by a circumferential 5 groove, with which the retaining element of the pressing tool can be brought into engagement, and/or a circumferential collar on the input hub, behind which the retaining element of the pressing tool can grip, in such a case a hook-shaped retaining element of the pressing tool would again iend itself to this purpose, in order to allow the input hub to grip securely over the retaining i o device provided thereon. Said two retaining devices are moreover particularly easy to produce.

In a further advantageous embodiment of the clutch device according to the invention the hub part, on its side facing the input hub, comprises a second projection, which is capable of nesting in a radial direction with the

15 input hub. This means that the second projection can enclose the input hub or the input hub can enclose the second projection in a radial direction. It is preferred, however, if the input hub externally encloses the second projection and the second projection can be introduced into the assembly opening. In each case the second projection and the input hub are formed in such a way

20 that these can be supported against one another in a radial direction. This allows an especially easy positioning of the hub part and the flex plate in relation to the input hub during the assembly process. In order to afford the fastest possible matching of the axis of rotation of the hub part to the axis of rotation of the input hub when fitting the hub part to the input hub, it is 25 furthermore preferred for the hub part and the input hub to be configured in such a way that the hub part can be centered in relation to the input hub by means of the second projection.

In a further preferred embodiment of the clutch device according to the invention the second projection in the axial direction comprises a toothed

30 section with an external toothing. The toothed section therefore forms an axial section of the second projection. The input hub by contrast comprises an internal toothing, which is preferably provided inside the assembly opening of the input hub. The external and internal toothing form the slip-on gearing in the rotationaliy locked connection of the hub part to the input hub. in a further advantageous embodiment of the clutch device according to the invention the second projection in the axial direction comprises a preferably cylindrical seating section. The sealing section therefore forms an axial section of the second projection. In the rotationaliy locked connection of 5 the hub part to the input hub the sealing section seals off a gap formed between the hub part and the input hub. It is preferred here if the sealing effect is achieved with the interposition of a seal between the sealing section on the one hand and the input hub on the other. Such a seai may be a simple ring seal, for example, it is particularly advantageous here if the seal is i o arranged on or pre-fitted to the sealing section. This is advantageous particularly where the sealing section is a sealing section which can be introduced into the assembly opening, especially since the seal can then simply be externally applied around the sealing section. It is furthermore preferred if in the sealing section a preferably circumferential groove is

15 provided, in which the seal can be securely arranged, before the hub part is rotationaliy locked to the input hub.

In the embodiment of the clutch device previously described the sealing section, with the possible interposition of a seal, seals off a gap formed between the hub part and the input hub. In a further preferred

20 embodiment of the clutch device according to the invention the sealing section is further embodied as a centering section, that is to say the sealing section acting as centering section not only seals off but also centers the hub part in relation to the input hub, so that their axes of rotation coincide. This obviates the need for an additional axial section in the form of a centering 25 section, thereby reducing the overall axial length of the hub part and hence the weight. In addition a sealing section embodied as centering section also assumes the function of a support section, which reliably prevents a tilting of the hub part in relation to the input hub. Thus any tilting forces occurring can be absorbed by the sealing section serving as support section.

30 In order to allow particularly easy production and assembly of the input hub and the hub part, the toothed section is in the axial direction formed on the side of the second projection facing the input hub, whilst the sealing section is formed on the side of the second projection remote from the input hub. This means that in the case of a hub part according to this embodiment the tip diameter of the externa! or interna! toothing on the hub part, for example, can correspond approximately to the outside or inside diameter of the sealing section, so that the production cost for such a hub part is relatively low. Similarly the root diameter of the internal or external toothing 5 on the input hub can correspond approximately to the inside or outside diameter of the assembly opening, thereby also reducing the production cost for the input hub.

In a further advantageous embodiment of the clutch device according to the invention the second projection has a central end-face depression, into i o which the transmission input shaft can be introduced, preferably endways. This means that the second projection can have a sufficient overall axial length to bring about both the rotationaily locked connection to the input hub and the sealing of the gap between the input hub on the one hand and the hub part on the other, without any unwanted end-face collision occurring with

15 the transmission input shaft. It is preferred here if the transmission input shaft can be or is supported in a radial direction on the second projection, this preferably being achieved by way of a radial bearing. The latter moreover produces a centering of the hub part and the input hub in relation to the transmission input shaft. Supporting the transmission input shaft in a radiai

20 direction on the second projection furthermore largely precludes any tilting movement of the hub part and the input hub in relation to the transmission input shaft. in a further advantageous embodiment of the clutch device according to the invention the flex plate rotationaily locked to the hub part together with 25 the hub part forms a continuous module that can be connected to the input hub. This module therefore does not consist of individual parts, which would have to be successively connected to the input hub and the clutch device. Instead the continuous module comprising the flex plate and the hub part can be connected as a whole to the input hub. It is preferred here if the flex plate

30 is integrally formed with the hub part. The latter design variant is to be chosen, however, only if the flex plate has substantially the same wall thickness as the hub part. Since this is rarely the case, especially as the flex plate is generally of more thin-walled design than the hub part, the flex plate is alternatively fixed to the hub part by a materially cohesive joint, this being done more preferably stiil by welding the flex plate to the hub part. In a further preferred alternative the flex plate is connected to the hub part by force closure and/or positively interlocking connection, being more preferably still bolted or riveted to the hub part.

5 The aforementioned fiex plate makes it possible to compensate for axial misatignments of the drive-side components, so that these are transmitted only in an attenuated form, if at all, to the input hub of the clutch device, it is furthermore advisable to cushion the torque fluctuations deriving from the power unit in such a way that these are not transmitted to the i o transmission input shaft. For this reason the clutch device further comprises a torsional vibration damper, the input hub of the clutch device being formed by the input hub of the torsional vibration damper. Thus the torsional vibration damper is preferably integrated into the housing of the clutch device and is arranged in the wet chamber inside the clutch housing. The clutch device is

15 here preferably embodied as a multiple-clutch device, more preferably still as a wet-running multiple-clutch device, for example as a dual clutch device.

The invention will be explained in more detail below on the basis of exemplary embodiments and with reference to the drawings attached, in which:

20 Fig. 1 in a sectional representation shows a partially side view of a first embodiment of the clutch device according to the invention,

Fig. 2 an enlarged representation of the detail A from Fig. 1 ,

Fig. 3 shows the clutch device from Fig. 1 when fitting the hub part and the flex plate to the input hub and 25 Fig. 4 in a sectional representation shows a partially side view of a second embodiment of the clutch device according to the invention in the area of the input hub.

Fig. 1 shows an embodiment of the clutch device 2 according to the invention and its arrangement in a drivetrain of a motor vehicle. The clutch

30 device 2 shown is embodied as a wet-running multiple-clutch device, in this case as a dual-clutch device. The clutch device 2 further comprises an input- side torsional vibration damper 4, which is integrated into the clutch device 2. The axis of rotation of the clutch device 2 is denoted in the drawings by the reference numeral 6, whilst the two opposing axial directions 8, 10 are - i z -

indicated by arrows. In addition the opposing radiai directions 12, 14 are iikewise represented by arrows.

The clutch device 2 comprises an input hub 16 arranged in an axiat direction 8, that is to say on the drive side, which equaiiy represents the input 5 hub 16 of the torsional vibration damper 4. The input hub 16 is rotationaliy locked to a primary element 18 in the form of a torque-transmitting plate. Supported on the primary element 18 in a radially outward direction 12 are spring devices 20 running in a circumferential direction, which bring about a rotational drive connection to a secondary element 22 of the torsional i o vibration damper 4 and are embodied in such a way that any torque surges of the primary element 18 are cushioned or attenuated, so that the torque surges are transmitted from the primary element 18 to the secondary element 22 of the torsional vibration damper 4 only to a limited extent. in an axial direction 10 the secondary element 22 is rotationaliy locked

15 to a housing-shaped outer piate carrier 24. The outer plate carrier 24 comprises two substantially tubular support sections 26, 28, which are rotationaliy locked to outer plates 30, 32. The outer plates 30, 32 are arranged so that they are axialiy displaceable on the associated support section 26, 28, inner plates 34, 36 being arranged between the outer plates

20 30, 32 in an axiai direction 8 or 10. Thus the outer plates 30 together with the inner plates 34 form a first plate pack 38, whilst the outer piates 32 together with the inner plates 36 form a second plate pack 40. The two plate packs 38, 40 are arranged nested in a radial direction 12 or 14, that is to say in this case the first plate pack 38 externally encloses the second piate pack 40 in a 25 radial direction 12.

The inner plates 34 of the first plate pack 38 are rotationaily locked to, but axialiy displaceable with a first inner plate carrier 42, whilst the inner plates 36 of the second plate pack 40 are axialiy displaceable with and rotationaliy locked to a second inner piate carrier 44. in a radiaily inward

30 direction 14 a first output hub 46 adjoins the first inner plate carrier 42, whilst the second inner plate carrier 44 comprises a second output hub 48 situated inside in a radial direction 14. Whilst the first output hub 46 can be rotationaliy locked via a siip-on gearing to an inner first transmission input shaft 50, the second output hub 48 can likewise be rotationaliy locked via a siip-on gearing to a second transmission input shaft 52, situated outside or embodied as a hoiiow shaft, shown in the already fitted state in Fig. 1.

The further construction of the input hub 16 wiil be explained in more detail below with reference to Figs. 1 and 2. The input hub 16 has a central 5 assembly opening 54 passing right through it in an axia! direction 8 or 10. The assembly opening 54 is dimensioned in such a way that a fastener for axiaily fixing the first output hub 46 to the first transmission input shaft 50 can be introduced in an axial direction 10 via or through the assembly opening 54 into the clutch device 2, provided that the hub part 56, described in more i o detail beiow, has not yet been inserted into the assembly opening 54. in this embodiment the fastener for axiaily fixing the first output hub 46 to the first transmission input shaft 50 is formed by a retainer ring 58 that can be attached to the first transmission input shaft 50. in addition a further retainer ring 60 can be introduced in an axial direction 10 through the assembly

15 opening 54 into the clutch device 2, the further retainer ring 60 serving for the axial fixing of a radial bearing 62, used to support the first output hub 46 on the input hub 16 from a radially inward direction 12.

The input hub 16 further comprises an internal toothing 64 facing the assembly opening 54, which takes the form of a straight teeth, the teeth of

20 the interna! toothing 64 extending parallel to the axis of rotation 6. The internal toothing 64 is here formed in an axial section of the input hub 16, which is offset in an axial direction 10 in relation to an end-face axial section 66 situated in an axial direction 8. The root diameter of the interna! toothing 64 here preferably corresponds to the inside diameter of the assembly 25 opening 54 in the area of the end-face axial section 66. in the area of the end-face axial section 66 a retaining device 68, the significance of which will be examined in more detail with reference to Fig. 3, is provided on the input hub 16 or the outer circumference thereof. The retaining device 68 consists on the one hand of a groove 70, running in a

30 circumferential direction and inset in an axial direction 10, and on the other of a collar 72 running in a circumferential direction and defining the circumferentiai groove 70 in an axial direction 8. The clutch device 2 further comprises a flex plate 74, which in an inward radial direction 14 is rotationally locked to the aforementioned hub part 56. The hub part 56 can be rotationally locked to the input hub 16, as will be explained in more detaii below. The flex plate 74 rotationaliy locked to the 5 hub part 56 together with the hub part 56 forms a continuous module that can be connected to the input hub 16, the module comprising the hub part 56 and the flex plate 74 being shown in the already fitted state in Figs. 1 and 2, in which a rotationally locked connection exists between the hub part 56 and the input hub 16. in order to obtain a rotationally locked connection between i o the flex plate 74 and the hub part 56, the flex plate 74 could be integrally formed with the hub part 56, for example, that is to say the flex plate 74 and the hub part 56 could have been produced from a continuous basic workpiece. Since this is relatively difficult to achieve, however, owing to the different wall thickness of the flex plate 74 and the hub part 56, in the

15 embodiment shown the flex plate 74 is welded to the hub part 56 via welding points 76, in order to obtain a cohesive material connection or attachment. Alternatively, however, the flex plate 74 couid also be connected to the hub part 56 by force closure and/or a positively interlocking joint, this preferably being done by bolting or riveting.

20 The flex plate 74, which can also be described as a torque-transmitting plate flexible in an axiai direction 8 or 10, can in an outer area in a radial direction 12 be rotationaily locked to a drive-side component, the drive-side component in this example being formed by the drive-side flywheel 78. The rotationaily locked connection of the flex piate 74 to the flywheel 78 is in this

25 example achieved by means of a bolted connection 80. The flywheel 78 is in turn rotationaliy locked at its end pointing inwards in a radial direction 14 to an output shaft 82 of a power unit, not shown further, in a radial direction 12 or 14 between the welding points 76 and the boited connection 80 the flex plate 74 further comprises multiple recesses 84 passing through it in an axial

30 direction 8 or 10, which in the radiai direction 12 or 14 are situated approximately on a ievei with the retaining device 68 on the input hub 16 and the function of which wiil be explained in more detaii below. Although the recesses 84, in the embodiment shown in Figs. 1 to 3, are provided in the flex piate 74, these may also be located inside the hub part 56, as will be - I S -

described later with reference to a second embodiment.

The hub part 56 will be described in more detai! below with reference to Figs. 1 and 2. The hub part 56 on its side remote from the input hub 16, comprises a first projection 86, which is preferably embodied as a pilot spigot 5 and extends in an axial direction 8 in the direction of the output shaft 82. This first projection 86 may be nested with the output shaft 82 in a radial direction 12 or 14. For this purpose a central recess 88, into which the first projection 86 embodied as piiot spigot can be introduced in an axial direction 8, is provided in the end face of the output shaft 82 remote from the power unit. i o The first projection 86, which is of a substantially mushroom-shaped design, substantially consists of two axiai sections, that is to say a section 90 facing the input hub 16 and a support section 92 remote from the input hub 16. The outside diameter of the support section 92 is matched to the inside diameter of the central recess 88 in the output shaft 82 in such a way that the output

15 shaft 82 can be supported in a radial direction 14 on the outer circumference of the support section 92, and vice-versa. The section 90 facing the input hub 16 on the other hand has a smaller diameter, so that the output shaft 82 cannot be supported on the section 90 of the first projection 86 in a radiai direction 14. It is preferred here if the support section 92 and the central

20 recess 88 are matched to one another in such a way that the hub part 56 is centered in relation to the output shaft 82 when the first projection 86 is introduced into the central recess 88 of the output shaft 82.

On its side facing the input hub 16 and remote from the first projection 86 the hub part 56 has a second projection 94, which extends in an axial 25 direction 10. The second projection 94 may be arranged nested with the input hub 16 in radial direction 12 or 14, this being achieved in the embodiment shown in that the second projection 94 can be introduced in an axial direction 10 into the assembly opening 54 in the input hub 16, Figs. 1 and 2 showing the already fitted state.

30 The second projection 94 is also divided into multiple axial sections.

Thus the second projection 94 first comprises an end-face toothed section 96, which is provided with an external toothing 98. The external toothing 98 of the toothed section 96 is, like the interna! toothing 64 of the input hub 16, embodied as straight teeth, the teeth of the external toothing 98 likewise extending parallel to the axis of rotation 6. The externa! toothing 98 together with the internal toothing 64 can therefore form a slip-on gearing 100, which with the hub part 56 in the fitted state brings about a rotationaily locked connection between the hub part 56 and the input hub 16. The externa! 5 toothing 98 should here be matched to the internal toothing 64 in such a way that in inserting the hub part 56 into the input hub 16 a press-fit toothing free of torsional piay is produced, as will be explained in more detail below with reference to Fig. 3. in an axial direction 8 an intermediate section 102 adjoins the toothed i o section 96, the outside diameter of which is smaller than the tip diameter of the external toothing 98 and smaller than the root diameter thereof, in an axial direction 8 the intermediate section 102 is succeeded by a sealing section 104, which can also function as a support section. The cylindrical sealing section 104 of the second projection 94 of the hub part 56 has an

15 outside diameter, which corresponds approximately to the tip diameter of the externa! toothing 98, but should be designed slightly larger, in the outer circumference of the sealing section 104 a circumferential groove 106 is provided, inside which a seal 108 in the form of a sealing ring is arranged. The sealing section 104 or the outside diameter thereof is matched to the

20 end-face axiai section 66 or the inside diameter thereof in such a way that the second projection 94 of the hub part 56 can be supported in a radiai direction 12 on the inside of the input hub 16, and vice-versa. Here the sealing section 104 and the end-face axial section 66 of the input hub 16 are preferably designed in such a way that the hub part 56 is centered in relation 25 to the input hub 16 when the hub part 56 is inserted with the second projection 94 into the assembly opening 54. The sealing section 104 can also in this respect be described as a centering section.

As will be apparent from Figs. 1 and 2 and the associated description, the toothed section 96 in the axial direction 8 or 10 is therefore formed on the

30 side of the second projection 94 facing the input hub 16, whilst the sealing section 104 is formed on the side of the second projection 94 remote from the input hub 16. This substantially facilitates the production of the externa! toothing 98 on the hub part 56 on the one hand and the production of the interna! toothing 64 on the input hub 16 on the other. in order to be able to form both the toothed section 96 and the sealing section 104, the second projection 94 must have a large overall axial length.

However, this may possibly lead to a restriction of the overall axial length of the transmission input shaft 50. in order to prevent this, the second projection

5 94 has an end-face central depression 110 facing the transmission input shaft 50. The end section of the transmission input shaft 50 facing the hub part 56 can be introduced into the depression 110 in an axial direction 8, so that the transmission input shaft 50 can also in a radial direction 12 or 14 be arranged nested with the second projection 94 of the hub part 56. The i o transmission input shaft 50 can here preferably be supported in a radial direction 12 on the second projection 94, this preferably being achieved by way of a radial bearing 112. The nesting of the hub part 56 with the transmission input shaft 50 is also intended to produce a centering of the hub part 56 in relation to the transmission input shaft 50, in order to prevent the

15 occurrence of unbalances during the operation of the drivetrain.

Further features of the clutch device 2 according to the invention and the procedure for rotationally fixed locking of the hub part 56 to the input hub 16 will be described beiow with reference to the Fig. 3.

First the dutch device 2 without the module comprising the flex plate 74

20 and the hub part 56 is pushed in an axiai direction 10 onto the transmission input shafts 50, 52, so that the transmission input shafts 50, 52 extend in an axial direction 8 into the clutch device 2. This brings about a rotationaliy iocked connection between the first output hub 46 and the first transmission input shaft 50 and between the second output hub 48 and the second 25 transmission input shaft 52, which is achieved by the aforementioned slip-on gearings. Before the hub part 56 of the continuous module comprising the hub part 56 and the fiex plate 74 is rotationally locked to the input hub 16, the retainer ring 58 is first introduced in an axial direction 10 through the assembly opening 54 in the input hub 16, the retainer ring 58 axialiy fixing the

30 first output hub 46 to the first transmission input shaft 50. The retainer ring 60 can also be introduced in an axial direction 10 through the assembly opening 54 in the input hub 16, which then axiaily fixes the radiai bearing 62 to the first output hub 46. However the retainer ring 60 may also have already been fitted to the clutch device 2 whilst assembling the torsional vibration dampers 4. The clutch device 2 is now therefore axially fixed to the first transmission input shaft 50.

Whereas in conventional clutch devices with an assembly opening in the input hub a separate closing or sealing part would have to be introduced 5 into the assembly opening, in order to prevent a subsequent escape of the coolant and lubricant from the wet-running clutch device, this additional operation is no longer necessary in the case of the clutch device according to the invention. Instead, after axially fixing the clutch device 2 to the transmission input shaft 50, it is possible to proceed immediately with the i o rotationally locked attachment of the module, comprising the hub part 56 and the flex plate 74, to the input hub 16, a possible procedure for this being described below.

The hub part 56 of the module comprising the hub part 56 and the flex plate 74 is first rotated about the axis of rotation 6 into a predefined rotational

15 or assembly position of the hub part 56 relative to the input hub 16, so that the external toothing 98 of the hub part 56 can be inserted in an axial direction 10 into the internal toothing 64 of the input hub 16. In the predefined rotational or assembly position of the hub part 56, the retaining device 68 on the input hub 16 is located on a common radial with the recesses 84 in the

20 flex plate 74 and the hub part 56, when the components are viewed in an axial direction 8 or 10. Substantial parts of the retaining device 68 are furthermore arranged in alignment with the recesses 84 in an axial direction 8 or 10. In this rotational or assembly position multiple hook-shaped retaining elements 114 can now be fed in an axial direction 10 through the recesses

25 84, in order to be connected to the retaining device 68 on the input hub 16. The hook-shaped retaining element 114 is here connected to the retaining device 68 in that the hook-shaped retaining element 114 of the pressing too! is brought into engagement with the circumferential groove 70 or the hook- shaped retaining element 114 is made to grip behind the circumferential

30 collar 72. The pressing tool further comprises a central punch 1 16, which is brought in an axial direction 10 up to the end face of the first projection 86 of the hub part 56 and into contact with the latter. - I Q -

The punch 1 16 is then pressed against the hub part 56 in an axiai direction 10, whilst the retaining elements 114 remain in their position shown in Fig. 3. As a result the second projection 94 of the hub part 56 is pressed into the assembly opening 54 in the input hub 16, producing the press-fit 5 toothing between the external toothing 98 and the internal toothing 64. Under continuing pressure the sealing section 104 of the hub part 56 also passes into the assembly opening 54, so that with the interposition of the seal 108 between the hub part 56 on the one hand and the input hub 16 on the other the hub part 56 brings about not only a closure but also a sealing of the i o assembly opening 54. In the process the assembly opening 54, by virtue of the hub part 56 and the seal 108 arranged thereon is closed with a preferably fluid-tight seai, more preferably still an oil-tight seal, the final assembly position being shown in Figs. 1 and 2. The press-fit toothing between the external toothing 98 on the one hand and the internal toothing 64 on the

15 other should here be designed in such a way that the hub part 56 is immovably fixed to the input hub 16 in an axial direction 8 or 10 on completion of the pressing process, as has been described with reference to Fig. 3, and during subsequent operation of the clutch device 2. In the process of pressing the hub part 56 in, a compensation for axial tolerances can

20 therefore be achieved, among other things between the clutch device 2 on the one hand and the drive-side components, such as the flywheel 78 or the output shaft 82, for example, on the other, by pressing the hub part 56 further or less far into the input hub 16 in axial direction 10.

A second embodiment of the clutch device according to the invention 2 25 will be described below with reference to Fig. 4, the construction of the clutch device 2 in the second embodiment corresponding substantially to the embodiment in Figs. 1 to 3, so that it is proposed to examine below only the differences compared to the first embodiment, the description above otherwise applying analogously. Furthermore the same reference numerals

30 will be used for identical or similar parts.

As already explained with reference to the first embodiment of the clutch device 2, the recesses 84 in the second embodiment are not located in the flex plate 74 but in the hub part 56, in order to obtain especially deep interna! recesses 84 in the radial direction 14. Alternatively it would also be possible in this case, however, to provide the recesses 84 in the flex piate 74, which then, however, should extend particularly far inwards in a radial direction 14. in addition the retaining device 68 in the second embodiment does not 5 consist of a circumferential groove and a circumferential collar, but is instead formed by multiple tapped holes 118 arranged on the end face of the input hub 16. The tapped holes 1 18, like the recesses 84, are uniformly distributed or spaced at an interval from one another in a circumferential direction. Thus in the rotational or assembly position of the hub part 56 a tapped hole 118 in i o each case aligns in an axial direction 8 or 10 with a recess 84 in the hub part 56. As retaining element of the pressing tool, a threaded shank (not shown) can now be passed in an axial direction 10 through the recesses 84 and screwed into the respective tapped hoie 118. This gives the retaining element of the pressing too! an especially secure hoid on the input hub 16. Otherwise

15 the procedure for pressing the hub part 56 into the input hub 16, producing the press-fit toothing, is as described with reference to Fig. 3.

Alternatively it would also be feasible here to turn the threaded shanks serving as retaining eiements about their longitudinal axis, so that the punch 116 is pressed in an axial direction 10 against the hub part 56 and presses

20 the hub part 56 into the input hub 16, producing the press-fit toothing.

Claims

1. A clutch device (2) having at least one output hub (46, 48), which can be rotationally locked to a transmission input shaft (50, 52), an

5 input hub (16), in which an assembly opening (54) is provided, so that a fastener (58, 60) for axially fixing the output hub (46) to the transmission input shaft (50) can be introduced via the assembly opening (54), and a flex plate (74), on which a hub part (56) is provided, which can be rotationaily locked to the input hub (16), characterized in that the hub part (56) can be o connected to the input hub (16) in such a way that the assembly opening (54) can be closed by the hub part (56).

2. The ciutch device (2) as claimed in claim 1 , characterized in that the hub part (56) can be connected to the input hub (16) in such a way5 that the assembly opening (54) can be closed with a preferably fluid-tight seal, more preferably still an oil-tight seal, by the hub part (56).

3. The clutch device (2) as claimed in either of the preceding claims, characterized in that the hub part (56) on its side remote from the 0 input hub (16) comprises a first projection (86), preferably a pilot spigot, which in a radial direction (12, 14) is capable of nesting with an output shaft (82) of a power unit and can preferably be introduced into a central end-face recess (88) in the output shaft (82), so that the first projection (86) and the output shaft (82) can preferably be supported against one another in a radial5 direction (12, 14), and more preferably still can be centered in relation to one another.

4. The clutch device (2) as claimed in claim 3, characterized in that the first projection (86) in the axial direction (8, 10) comprises a section 0 (90) facing the input hub (16) and a support section (92) remote from the input hub (16), the output shaft (82) being supportable solely on the support section (92) and the first projection (86) preferably being of mushroom- shaped design.

5. The clutch device (2) as claimed in one of the preceding claims, characterized in that the hub part (56) can be rotationally locked to the input hub (16) by means of a slip-on gearing (100), the slip-on gearing (100)

5 preferably being formed by an internal toothing (64) on the one hand and an external toothing (98) on the other, which are more preferably still formed as straight teeth.

6. The clutch device (2) as claimed in claim 5, characterized in i o that the slip-on gearing (100) is a press-fit toothing free of torsional play, the press-fit toothing preferably being designed in such a way that during operation of the clutch device (2) the hub part (56) is in an axial direction (8, 10) immovably fixed to the input hub (16).

15 7. The clutch device (2) as claimed in claim 6, characterized in that at least one recess (84) is provided in the hub part (56) or the flex plate (74), preferably the flex plate (74), and at least one retaining device (68) is provided on the input hub (16) in such a way that in a predefined rotational or assembly position of the hub part (56) and the flex plate (74) relative to the

20 input hub (16) the retaining device (68) is arranged at least on a common radial with the recess (84), and preferably also in axial alignment with the recess (84), so that a retaining element (1 14) of a pressing tool for producing the press-fit toothing can be fed through the recess (84) and connected to the retaining device (68).

25

8. The clutch device (2) as claimed in claim 7, characterized in that the retaining device (68) is arranged on an end face of the input hub (16), preferably embodied as a tapped hole (118), or that the retaining device (68) is formed by a circumferential groove (70), with which the

30 retaining element (1 14) of the pressing tool can be brought into engagement, and/or a circumferential collar (72) on the input hub (16), behind which the retaining element (114) of the pressing tool can grip.

9. The dutch device (2) as claimed in one of the preceding claims, characterized in that the hub part (56), on its side facing the input hub (16), comprises a second projection (94), which is capable of nesting in a radial direction (12, 14) with the input hub (16) and can preferably be introduced 5 into the assembly opening (54), so that the second projection (94) and the input hub (16) can be supported against one another in a radial direction (12, 14), the hub part (56) preferably being centered in relation to the input hub (16) by means of the second projection (94).

i o 10. The ciutch device (2) as claimed in claim 9, characterized in that the second projection (94) in the axial direction (8,

10) comprises a toothed section (96) with an external toothing (98), whilst the input hub (16) comprises an internal toothing (64), the external and internal toothing (98, 64) forming the siip-on gearing (100) in the rotationaily locked connection of the

15 hub part (56) to the input hub (16).

11. The ciutch device (2) as claimed in one of claims 9 or 10, characterized in that the second projection (94) in the axial direction (8, 10) comprises a preferably cylindrical sealing section (104), which in the

20 rotationaily locked connection of the hub part (56) to the input hub (16) seals off a gap formed between the hub part (56) and the input hub (16), preferably with the interposition of a seal (108), which is more preferably still arranged on the sealing section (104), possibly inside a groove (106) in the sealing section (104), the sealing section (104) preferably also being embodied as a 25 centering section.

12. The ciutch device (2) as claimed in claim 11 , characterized in that the toothed section (96) is formed in the axial direction (8. 10) on the side of the second projection (94) facing the input hub (16) and the sealing

30 section (104) is formed on the side of the second projection (94) remote from the input hub (16).

13. The ciutch device (2) as ciaimed in one of claims 9 to 12, characterized in that the second projection (94) has a central end-face depression (110), into which the transmission input shaft (50) can be introduced, the transmission input shaft (50) preferably being supportable in

5 a radial direction (12, 14) on the second projection (94), possibly by way of a radial bearing (112).

14. The ciutch device (2) as claimed in one of the preceding ciaims, characterized in that the flex plate (74), rotationaliy locked to the hub part i o (56), together with the hub part (56) forms a continuous module that can be connected to the input hub (16), the fiex plate (74) preferably being integrally formed with the hub part (56), fixed by a materially cohesive joint to the hub part (56), more preferably stiil welded to the hub part (56), or fixed to the hub part (56) by force closure and/or positively interlocking connection, more

15 preferably still bolted or riveted to the hub part (56).

15. The ciutch device (2) as claimed in one of the preceding claims, characterized in that the clutch device (2) further comprises a torsional vibration damper (4) and the input hub (16) of the clutch device (2) is formed

20 by the input hub of the torsional vibration damper (4), the ciutch device (2) preferably being embodied as a multiple-clutch device, more preferably stili as a wet-running multiple-clutch device.