Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D21/00—Systems comprising a plurality of actuated clutches
  • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
  • F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D13/00—Friction clutches
  • F16D13/22—Friction clutches with axially-movable clutching members
  • F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
  • F16D13/52—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member
  • F16D13/54—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member with means for increasing the effective force between the actuating sleeve or equivalent member and the pressure member
  • F16D13/56—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member with means for increasing the effective force between the actuating sleeve or equivalent member and the pressure member in which the clutching pressure is produced by springs only
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D13/00—Friction clutches
  • F16D13/58—Details
  • F16D13/60—Clutching elements
  • F16D13/64—Clutch-plates; Clutch-lamellae
  • F16D13/68—Attachments of plates or lamellae to their supports
  • F16D13/683—Attachments of plates or lamellae to their supports for clutches with multiple lamellae
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D21/00—Systems comprising a plurality of actuated clutches
  • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
  • F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
  • F16D2021/0676—Mechanically actuated multiple lamellae clutches

Definitions

• the present invention relates to a multiple clutch device having a first multiple disk clutch for optionally coupling a drive element to a first output element for the transmission of torque, which first multiple disk clutch has a first drive-side multiple disk carrier and having a second multiple disk clutch for optionally coupling the drive element to a second output element so as to transmit torque, which second multiple disk clutch has a second drive-side multiple disk carrier, the first and second drive-side multiple disk carriers being connected in a rotary driving manner via a torque transmission element.
• Multiple clutch devices, in particular dual clutch devices, which have a first multiple disk clutch and a second multiple disk clutch are known from the prior art.
• the first multiple disk clutch serves to optionally couple a drive element, such as a crankshaft of an engine, to a first output element, such as a first transmission input shaft, so as to transmit torque
• the second multiple disk clutch serves to optionally couple the drive element to a second output element, such as a second transmission input shaft, so as to transmit torque
• the multiple disk clutches have in each case a drive-side multiple disk carrier and an output-side multiple disk carrier, between which in each case one multiple disk assembly is arranged, the drive-side multiple disk carriers of the two multiple disk clutches being connected to one another in a rotary driving manner or being connected to one another in a rotationally fixed manner.
• the drive-side multiple disk carriers which are usually configured as outer multiple disk carriers are as a rule of cup-shaped configuration and are divided into a tubular multiple disk carrying section and a plate-shaped support section for the radial support of the multiple disk carriers on a clutch hub of the multiple clutch device, to which the support sections are welded, with the result that the clutch hub acts as a torque transmission element between the drive-side multiple disk carriers.
• the multiple clutch device which is preferably a dual clutch device, particularly preferably a radially nested and/or wet running dual clutch device has a first multiple disk clutch and a second multiple disk clutch which are assigned in each case a drive-side multiple disk carrier and an output-side multiple disk carrier.
• the first multiple disk clutch serves to optionally couple a drive element, preferably a crankshaft of an engine, to a first output element, preferably a first transmission input shaft, so as to transmit torque
• the second multiple disk clutch serves to optionally couple the drive element to a second output element, preferably a second transmission input shaft, so as to transmit torque.
• the first drive- side multiple disk carrier that is to say the drive-side multiple disk carrier of the first multiple disk clutch, which drive-side multiple disk carrier is preferably the first drive-side outer multiple disk carrier
• the first and/or second drive-side multiple disk carrier have/has protruding drivers which are plugged into cutouts in the torque transmission element with the production of a rotary driving connection between the first and/or second drive-side multiple disk carrier and the torque transmission element.
• the drivers on the drive-side multiple disk carriers on one side and the cutouts on the torque transmission element on the other side firstly a reliable rotary driving connection can be achieved which secondly can be produced particularly simply, without it being necessary for the two drive-side multiple disk carriers to be welded to one another. Rather, it is only required to plug the drivers into the cutouts, as a result of which the manufacturing expenditure is reduced.
• the advantage that simple dismantling of the respective drive-side multiple disk carrier from the torque transmission element is also possible, in order for it to be possible for subsequent modifications, reworking or repairs to be carried out quickly and simply on the multiple clutch device, such as after a negative moment uniformity test.
• the multiple disk assembly of the respective multiple disk clutch can be accessed particularly quickly and simply, in order for it to be possible (for example, after a negative moment uniformity test) to modify it simply or even to replace it completely.
• both the first and the second drive-side multiple disk carriers have protruding drivers which are plugged into cutouts in the torque transmission element between the first and second drive-side multiple disk carriers on one side and the torque transmission element on the other side.
• the drive-side multiple disk carriers which are connected to the torque transmission element via the protruding drivers in a rotary driving manner are of substantially tubular configuration, preferably of exclusively tubular configuration.
• the drive-side multiple disk carriers thus no longer have to have a radial support section, as is the case in conventional cup-shaped multiple disk DKT08070A - 4 - carriers; rather, lhe radial support of said drive-side multiple disk carriers can be brought about by other components, such as the drive-side driver plate or the like, as a result of which the construction is simplified further.
• the drive-side multiple disk carriers are supported radially via a torque transmission element which is lengthened radially to the inside and can be supported for this purpose, for example, in the radial direction on a clutch hub.
• the drivers on the drive-side multiple disk carrier could be formed by the internal or external toothing which is present in any case on said multiple disk carrier for the multiple disks, which would therefore be radially protruding drivers.
• the drivers are configured, however, as axially protruding drivers which are plugged in the axial direction into the cutouts in the torque transmission element. In this way, plugging the drivers into the associated cutouts is realized in a substantially simpler way, especially since there are clearances between the drivers, which clearances ensure improved clarity during assembly. Moreover, said clearances contribute to reducing the weight of the drive-side multiple disk carrier.
• the cutouts are configured as window-like cutouts in one particularly preferred embodiment of the multiple clutch device according to the invention.
• the individual driver is therefore surrounded completely by the edge of the associated cutout, with the result that bending of the drivers is counteracted at high rotational speeds.
• the multiple clutch device can be actuated mechanically, it being possible here for a mechanical actuation to be understood both as a purely mechanical actuation and as an electromechanical actuation.
• At least one of the multiple disk clutches is assigned a disk spring for actuating the multiple disk clutch, with the result that one can also speak of a disk spring actuating system.
• the disk spring in order to avoid additional expenditure for the support of DKT08070A - 5 - the disk spring, in particular for the support on the edges of the latter within the multiple clutch device, in the design variant mentioned last, it is particularly preferred, furthermore, if at least one of the disk springs is supported indirectly or directly in the axial direction on the torque transmission element or the drivers which protrude through the cutouts.
• At least one support element is arranged on the drivers or the torque transmission element, via which support element the disk spring is supported indirectly in the axial direction on the drivers or the torque transmission element.
• the abovementioned support element can be, for example, a simple securing ring which is arranged on the inner side of the drivers.
• the support element which is arranged on the drivers engages behind the drivers in the radial direction from the outside in a further particularly preferred embodiment of the multiple clutch device according to the invention.
• the drivers can be engaged behind only partially from the outside, although it is preferred if the individual driver is engaged behind completely from the outside, in order to preclude bending of the drivers reliably.
• the support element is a securing ring, supported via a securing ring in the axial direction on the drivers or the torque transmission element or connected, preferably welded, with a material to material fit to the drivers or the torque transmission element.
• the support element is a sheet metal ring, the sheet metal ring preferably having window-like cutouts, through which the drivers extend in the axial direction, with the result that the drivers can be plugged in simply and ensure a reliable hold of the sheet metal ring on the drivers.
• the sheet metal ring preferably has an L-shaped cross section or part cross section with an axial and a radial limb, the axial limb surrounding the drivers or the DKT08070A - 6 - torque transmission element from the outside or vice versa.
• the axial limb can thus in turn counteract bending of the drivers in the radial direction at high rotational speeds, it being possible for the axial limb to be welded, for example, to the drivers.
• the individual disk spring is assigned at least two support elements which are arranged in the axial direction on opposite sides of the disk spring, with the result that the disk spring is supported indirectly both in one and in the opposite other axial direction.
• at least one of the support elements is configured as an axially resilient support element for prestressing the disk spring against the other support element. In this way, playfree clamping is brought about, which is necessary in order for it to be possible to transmit the actuating forces to the multiple disk clutch quickly and reliably.
• an undulating wire ring might be suitable as axially resilient support element.
• the axially resilient support element is formed by a further disk spring or an annular disk having an undulating profile in the circumferential direction.
• the axially resilient support elements which are configured in this way have the advantage that the contact points on the disk spring are displaced to a less pronounced extent by prestressing. Moreover, the spring force of said support elements is less dependent on the rotational speed than is the case in an undulating wire ring.
• the axially resilient support element is formed by a sheet metal ring with a curved or kinked profile in cross section.
• a support element of this type has the same advantages which have already been mentioned in the preceding text over an undulating wire ring and, moreover, can be produced particularly simply.
• sheet metal rings which have an L-shaped, U-shaped or G-shaped cross section have proven advantageous, in particular.
• bending tabs which are spaced apart from one another in the circumferential direction are provided on the sheet metal DKT08070A - 7 - ring, lhe bending labs preferably being arranged on an edge of the cross section of the sheet metal ring and particularly preferably facing the disk spring.
• a further preferred embodiment of the multiple clutch device according to the invention has proven particularly advantageous and simple, in which the torque transmission element is configured substantially, preferably exclusively, in the shape of an annular disk, especially since it can be produced particularly simply in this way.
• the torque transmission element has an outer radial section which extends substantially in the radial direction, is preferably in the shape of an annular disk and is connected to the first drive-side multiple disk carrier in a rolary driving manner and/or is configured in one piece with the latter.
• the first drive-side multiple disk carrier can therefore be connected to the torque transmission element in a rotary driving manner or else can be configured in one piece with the latter.
• the second drive- side multiple disk carrier would then be connected to the torque transmission element in the manner according to the invention.
• the torque transmission element has a central radial section for receiving the disk spring partially or completely for actuating one of the multiple disk clutches, which central radial section follows the outer radial section in the radial direction to the inside, extends substantially in the axial direction and is preferably tubular.
• the central radial section therefore provides a receptacle for the disk spring, which receptacle is particularly large in the radial direction, with the result that the disk spring which is received in it can have a correspondingly large external diameter which is indispensable for applying particularly high actuating forces.
• the central radial section forms the second drive-side multiple disk carrier and/or is configured in one piece with the latter. In the lastmentioned variant, only the first drive-side multiple disk carrier would be connected to the torque transmission element in the DKT08070A - 8 - manner according to the invention.
• the torque transmission element has an inner radial section which follows the central radial section in the radial direction to the inside, extends substantially in the radial direction, is preferably in the shape of an annular disk, is arranged offset in the axial direction with respect to the radially outer section, and is connected to the second drive-side multiple disk carrier in a rotary driving manner and/or is configured in one piece with the latter.
• the disk spring can be received in the central radial section reliably and with a short overall axial length. It is particularly preferred in this embodiment if the torque transmission element or its inner radial section brings about the radial support of the two drive-side multiple disk carriers.
• At least one axially displaceable actuating piston is provided for transmitting the force from the disk spring to a multiple disk assembly of the respective multiple disk clutch.
• the axially displaceable piston can be configured, for example, as an annular piston.
• the actuating piston is preferably composed in two or more pieces from at least one first piston part which is assigned to the disk spring and one second piston part which is assigned to the multiple disk assembly, which are operatively connected to one another via axially protruding fingers on the first and/or second piston part, which fingers extend through windows within the torque transmission element.
• the operative connection should be designed in such a way that the second piston part follows every movement of the first piston part.
• this embodiment makes an improved adaptation of the actuating piston to the high DKT08070A - 9 - rolalional speeds possible.
• both the first and the second piston part are of annularly closed configuration.
• the two piston parts which are annularly closed that is to say continuous in the circumferential direction, thus prevent the actuating piston widening at very high rotational speeds, as is the case in conventional actuating pistons with only one piston part in the region of the fingers.
• the second piston part does not widen in the radial direction, with the result that a constant contact face is always ensured for the multiple disk assembly of the multiple disk clutch.
• the second piston part is preferably connected indirectly to the respective drive-side multiple disk carrier in a rotary driving manner, by the second piston part engaging, for example, into the toothing of the drive-side multiple disk carrier, which toothing is provided for the rotationally fixed arrangement of the multiple disks.
• a restoring element is provided for restoring the actuating piston in the direction of the disk spring.
• Spring elements such as helical springs, which are supported on one side on the actuating piston and on the other side on one of the multiple disk carriers or elsewhere are classically used as restoring elements for the actuating piston of a clutch device.
• the restoring element in contrast acts on one side on the actuating piston and on the other side on the disk spring. In this way, the movement of the disk spring and the movement of the actuating piston are coupled to one another in a particularly simple way, without the overall axial length of the multiple clutch device being increased.
• the restoring element can also be of rigid configuration, especially since the movements of the disk spring and the actuating piston only have to be coupled, although a slight spring action of the restoring element certainly has advantages.
• a restoring element is considered particularly preferred which is formed by an annular part with protruding fingers, the fingers of the annular part extending through the intermediate spaces between the disk spring tabs of the disk spring, with DKT08070A - 10 - the result that the disk spring tabs on one side and the actuating piston on the other side can be engaged behind by the annular part.
• the fingers do not have to be configured on the annular part in such a way that they engage behind the disk spring tabs or the actuating piston without further aids.
• the actuating piston which is preferably annular has a U-shaped cross section or part cross section, within which the restoring element is arranged.
• This embodiment makes reliable placing and arranging of the restoring element possible, as a result of which the assembly is simplified further.
• the opening of the U-shaped cross section or part cross section preferably faces away from the disk spring, in order to make corresponding support of the restoring element possible on a part of the multiple clutch device which lies opposite ' the disk spring, such as the torque transmission element.
• the transmission/clutch arrangement according to the invention has a transmission and a multiple clutch device of the above-described type.
• the first output element is preferably formed by a first transmission input shaft
• the second output element is preferably formed by a second transmission input shaft.
• the multiple clutch device is arranged within a transmission housing, preferably in a transmission housing bell, the axial actuating forces which are introduced into the multiple clutch device via the disk springs being supported on the transmission housing or a transmission housing cover for closing the transmission housing.
• the support is preferably carried out via a clutch input hub of the multiple clutch device which is mounted in the transmission housing cover such that it can be rotated but cannot be displaced substantially axially.
• Fig. 1 shows a cross-sectional view of a first embodiment of the multiple clutch device according to the invention, DKT08070A - 11 -
• Fig. 2 shows a cross-sectional view of a second embodiment of the multiple clutch device according to the invention
• Fig. 3 shows a cross-sectional view of a third embodiment of the multiple clutch device according to the invention
• Fig. 4 shows a cross-sectional view of a fourth embodiment of the multiple clutch device according to the invention
• Fig. 5 shows a cross-sectional view of a fifth embodiment of the multiple clutch device according to the invention
• Fig. 6 shows a cross-sectional view of a sixth embodiment of the multiple clutch device according to the invention
• Fig. 7 shows a cross-sectional view of a seventh embodiment of the multiple clutch device according to the invention
• Fig. 8 shows a cross-sectional view of an eighth embodiment of the multiple clutch device according to the invention
• Fig. 9 shows a cross-sectional view of a ninth embodiment of the multiple clutch device according to the invention
• Fig. 10 shows a cross-sectional view of a tenth embodiment of the multiple clutch device according to the invention
• Fig. 11 shows a cross-sectional view of an eleventh embodiment of the multiple clutch device according to the invention
• Fig. 12 shows a cross-sectional view of a twelfth embodiment of the multiple clutch device according to the invention
• Fig. 13 shows a cross-sectional view of a thirteenth embodiment of the multiple clutch device according to the invention
• Fig. 14 shows a cross-sectional view of a fourteenth embodiment of the multiple clutch device according to the invention
• Fig. 15 shows a cross-sectional view of a fifteenth embodiment of the multiple clutch device according to the invention
• Fig. 16 shows a cross-sectional view of a sixteenth embodiment of the multiple clutch device according to the invention, DKT08070A - 12 -
• Fig. 17 shows a cross-sectional view of a seventeenth embodiment of the multiple clutch device according to the invention
• Fig. 18 shows a cross-sectional view of an eighteenth embodiment of the multiple clutch device according to the invention
• Figs. 19 a to f show side views of the actuating pistons from figs. 1 to 18, shown alone and in a sectional illustration
• Figs. 19 a to f show side views of the actuating pistons from figs. 1 to 18, shown alone and in a sectional illustration
• Fig. 20 shows a perspective illustration of one embodiment of a restoring element for the actuating piston.
• Figs. 1 to 18 show different embodiments of the multiple clutch device according to the invention, first of all the basic construction of all the embodiments being described in the following text with reference to fig. 1.
• the multiple clutch device 2 is configured in each case as a radially nested, wet running dual clutch device.
• the axial directions 4, 6 which are opposed to one another, the radial directions 8, K) which are opposed to one another and the circumferential directions 12, 14 which are opposed to one another of the multiple clutch device 2 are indicated using corresponding arrows, the rotational axis which extends in the axial direction 4, 6 being provided with the designation 16.
• the multiple clutch device 2 has an input hub 18 which can be connected or is connected in a rotationally fixed manner in the axial direction 4 to a drive element
• the input hub 18 is in turn connected in a rotationally fixed manner to a driver plate 20.
• the driver plate 20 is connected in a rotationally fixed manner to a first drive-side multiple disk carrier 22, the connection preferably being achieved by an axial plug-in connection, as will be explained in greater detail later.
• the first drive-side multiple disk carrier 22 is configured as an outer multiple disk carrier of a first multiple disk clutch 24, it also being possible for the first multiple disk clutch 24 to be denoted as outer multiple disk clutch of the multiple clutch device 2.
• the first multiple disk clutch 24 is assigned a first output-side multiple disk carrier 26 which is configured as an inner multiple disk carrier, the first output-side multiple disk carrier 26 being connected to a first output element 28 in a rotary driving manner, the DKT08070A - 13 - latter being a first transmission input shaft in the present example.
• the first multiple disk clutch 24 therefore serves to optionally couple the drive element (not shown) to the first output element 28 in the form of the first transmission input shaft so as to transmit torque.
• the multiple disk clutch 2 has a second multiple disk clutch 30 which is configured as an inner multiple disk clutch.
• the second multiple disk clutch 30 has a second drive-side multiple disk carrier 32, which is configured as an outer multiple disk carrier, and a second output-side multiple disk carrier 34, the latter being configured as an inner multiple disk carrier and being connected to a second output element 36 in the form of a second transmission input shaft in a rotary driving manner.
• the second drive-side multiple disk carrier 32 is connected in a rotary driving manner via a torque transmission element 38 to the first drive-side multiple disk carrier 22, with the result that an optional torque transmitting coupling of the drive element (not shown) to the second output element 36 in the form of the second transmission input shaft is also possible via the second multiple disk clutch 30.
• the two multiple disk clutches 24, 30 can be actuated in each case mechanically or electromechanically.
• the multiple disk clutches 24, 30 are assigned in each case a disk spring 40, 42.
• the disk springs 40, 42 have in each case a radially outer section 44 which is closed annularly in the circumferential direction 12, 14 and from which disk spring tabs 46 extend in the radial direction 10 to the inside in such a way that intermediate spaces remain in the circumferential direction 12, 14 between the disk spring tabs 46.
• the disk spring tabs 46 can be loaded with an axial force at their radially inwardly pointing end and can be displaced in the axial direction 4, 6, corresponding engagement bearings 48 being provided for this purpose.
• the disk spring tabs 46 act like levers for transmitting the actuating force to the corresponding multiple disk clutch 24, 30.
• each of the disk springs 40, 42 is assigned, furthermore, an axially displaceable actuating piston 50, 52 which is preferably configured as an annular piston and in two or more pieces, as will be explained later in greater detail.
• Both the first and the second drive-side multiple disk carriers 22, 32 are of substantially tubular configuration and have a multiple disk carrying section 54, 56.
• a multiplicity of drivers 58, 60 which are spaced apart in the circumferential direction 12, 14 and protrude in the axial direction 6 adjoin the multiple disk carrying section 54, 56.
• the torque transmission element 38 which is configured substantially in the shape of an annular disk has cutouts 62, 64 which are preferably of window-like configuration, as shown in fig. 1 , inter alia.
• the drivers 58, 60 are plugged into the cutouts 62, 64 in the axial direction 6, with the result that a rotary driving connection is produced by this plug in connection between the first and second drive-side multiple disk carriers 22, 32 on one side and the torque transmission element 38 on the other side.
• the multiple clutch device 2 can be mounted particularly simply and optionally can be dismantled again.
• the multiple disk carriers 22, 32 are preferably fixed on the torque transmission element 38 in the axial direction 4, 6 via securing rings.
• the radially outer section 44 of the disk spring 40 is supported in the axial direction 4, 6 on the drivers 58 which protrude through the cutouts 62 in the axial direction 6, while the radially outer section 44 of the disk spring 42 is supported in the axial direction 4, 6 on the drivers 60 which protrude through the cutouts 64 in the axial direction 6.
• the radially outer sections 44 are supported indirectly via support elements 66, 68 on the associated drivers 58, 60, the support elements 66, 68 in turn being fixed on the drivers 58, 60 in the axial direction 4, 6 via securing rings (no designation).
• the support element 68 is configured as a substantially DKT08070A - 15 - nonelastic support element and is formed by a sheet metal ring which has a plurality of window-like cutouts 70 which are distributed in the circumferential direction and through which the drivers 58, 60 extend in the axial direction 6. Thanks to the window-like cutouts 70, the support element 68 engages behind the drivers 58, 60 in the radial direction 10 from the outside, with the result that the support elements 68 which are configured as sheet metal rings likewise bring about a centrifugal force safeguard, that is to say, at high rotational speeds, the support element 68 prevents bending of the drivers 58, 60 in the radial direction 8 to the outside. Although it is advantageous but not necessarily required here for the support elements 68 to engage behind the drivers completely, as in the present example, this effect already occurs in support elements 68 which engage behind the drivers only partially from the outside.
• the disk spring 40 is assigned two support elements 66, 68 which are arranged in the axial direction 4, 6 on opposite sides of the radially outer section 44, while the disk spring 42 is assigned two support elements 68, 68 which are arranged in the axial direction 4, 6 on opposite sides of the radially outer section 44
• at least one of the two support elements 66, 88 and 68, 68 should be configured as an axially resilient support element, in order in this way to bring about play free clamping of the disk spring 40, 42, which clamping is necessary in order for it to be possible to transmit the actuating forces quickly and reliably Io the multiple disk clutches 24, 30.
• this is shown by way of example using the support element 66.
• the support element 66 serves to prestress the outer section 44 of the disk spring 40 in a resilient manner against the other support element 68.
• the axially resilient support element 66 is formed by a sheet metal ring of curved or kinked profile in cross section, the cross section being of U-shaped configuration in the embodiment shown.
• bending tabs 72 are provided on the sheet metal ring, which bending tabs 72 are, furthermore, spaced apart from one another in the circumferential direction 10, 12, extend starting from an edge of the U-shaped cross section of the sheet metal ring, and face the disk spring 40 or the radially outer section 44 of the latter.
• Fig. 2 shows a second embodiment of the multiple clutch device 2 according to the invention, only the differences to the preceding embodiments being explained in the following text, identical designations being used for identical or similar parts, and the preceding description otherwise being correspondingly valid.
• the torque transmission element 38 has an outer radial section 74 which extends substantially in the radial direction 8, 10, is preferably in the shape of an annular disk, and is connected in the above-described manner to the first drive-side multiple disk carrier 22 in a rotary driving manner.
• a central radial section 76 follows the outer radial section 74, the central radial section 76 being of substantially tubular configuration and extending in the axial direction 4.
• the central radial section 74 serves to receive the disk spring 42 of the second multiple disk clutch 30 at least partially and at the same time forms the second drive-side multiple disk carrier 32 in the embodiment shown or is configured integrally with the latter.
• the radially outer section 44 of the disk spring 42 of the second multiple disk clutch 30 is fixed here on the torque transmission element 38 or its radial sections 74, 76 in the axial direction 4, 6, one support element 68 being fastened, preferably welded fixedly, to the outer radial section 74, and the other support element 68 being formed by a securing ring which is fixed in the axial direction 4, 6 on the central radial section 76 or the second drive-side multiple disk carrier 52.
• the second drive- side multiple disk carrier 32 is supported in the radial direction 10 to the inside via an additional support plate 78.
• the actuating piston 50 of the first multiple disk clutch 24 is configured in two or more pieces.
• the actuating piston 50 is composed of a first piston part 80 which is assigned to the disk spring 40 and a second piston part 82 which is assigned to the multiple disk assembly of the first multiple disk clutch 24, the two piston parts 80, 82 being operatively connected to one another via axially protruding fingers 84 on the first and/or second piston part 80, 82, that is to say the fingers 84 bring about a situation where the second piston part 82 follows the movement of the first piston part 80. Said fingers 84 are required, since the torque transmission element 38 is arranged in the axial direction between the two piston parts 80, 82.
• windows 86 are provided in the torque DKT08070A - 17 - transmission element 38, through which windows 86 the fingers 84 extend in the axial direction 4, 6.
• Both piston parts 80, 82 are of a ⁇ nularly closed configuration, with the result that they widen only slightly even at high rotational speeds.
• the second piston part 82 is connected directly to the first drive-side multiple disk carrier 22 in a rotary driving manner, by corresponding toothing on the second piston part 82 engaging into the internal toothing of the first drive-side multiple disk carrier 22, which internal toothing serves to receive the multiple disks in a rotationally fixed manner.
• Fig. 3 shows a third embodiment of the multiple clutch device 2 according to the invention, only the differences from the preceding embodiments being explained in the following text, identical designations being used for identical or similar parts, and the preceding description otherwise being correspondingly valid.
• the third embodiment corresponds substantially to the second embodiment according to fig. 2.
• the central radial section 76 of the torque transmission element 38 has a greater axial extent, with the result that the radially outer section 44 of the disk spring 42 for the second multiple disk clutch 30 can be fixed in the axial direction on the central radial section 76 via two support elements 68 in the form of simple securing rings. Thanks to the securing rings, simpler dismantling than in the second embodiment is possible, should it be required.
• Fig. 1 shows a third embodiment of the multiple clutch device 2 according to the invention, only the differences from the preceding embodiments being explained in the following text, identical designations being used for identical or similar parts, and the preceding description otherwise being correspondingly valid.
• the third embodiment corresponds substantially to the
• the torque transmission element 38 has, furthermore, an inner radial section 88 which follows the central radial section 76 in the radial direction 10 to the inside, extends substantially in the radial direction 10, is in the shape of an annular disk, and is arranged offset in the axial direction 4 with respect to the outer radial section 74.
• the central radial section 76 does not form the second drive-side multiple disk carrier 32, but rather serves only to receive and axially fix the disk spring 42 of the second multiple disk clutch 30. In this way, the disk spring 42 has a greater external diameter. Rather, the second DKT08070A - 18 - drive-side multiple disk carrier 32 is connected in a rotary driving manner via the abovementioned plug in connection to the inner radial section 88 of the torque transmission element 38.
• fig. 4 shows for the first time restoring elements 90, 92 for restoring the actuating pistons 50, 52 in the direction of the associated disk spring 40, 42, which restoring elements 90, 92 can also be used in a corresponding way in the preceding or following embodiments.
• the restoring element 90 acts on one side on the actuating piston 50 and on the other side on the disk spring 40, with the result that the two elements are coupled directly to one another.
• the restoring element 90 is formed by an annular part 94 with protruding fingers 96, which annular part 94 is shown in perspective in fig. 20. As can be seen from fig.
• the annular part 94 firstly engages behind the actuating piston 50 in the axial direction 6, while the fingers 96 extend through the intermediate spaces between the disk spring tabs 46, which intermediate spaces exist in the circumferential direction 12, 14, with the result that said disk spring tabs 46 can engage behind in the axial direction 4.
• the engaging behind of the disk spring tabs 46 takes place with the interposition of a support ring 97.
• the actuating piston 50 follows this movement thanks to the coupling via the restoring element 90 which makes a particularly small overall axial length possible.
• the restoring element 92 is configured as a simple disk spring which is supported on one side on the inner radial section 88 and on the other side on the actuating piston 52.
• Fig. 5 shows a fifth embodiment of the multiple clutch device 2 according to the invention, only the differences from the preceding embodiments being explained in the following text, identical designations being used for identical or similar parts, and the preceding description otherwise being correspondingly valid.
• the fifth embodiment corresponds substantially to the fourth embodiment according to fig. 4, the axially resilient support element 66 not being configured as a disk spring but rather again as a sheet metal ring which, in contrast to the embodiment according to fig. 1 , has a G-shaped cross section, however.
• the restoring element 92 is also not configured as a disk spring, but rather in the manner of the restoring element 90 from DKT08070A - 19 - fig. 4.
• Fig. 6 shows a sixth embodiment of the multiple clutch device 2 according to the invention, only the differences from the preceding embodiments being explained in the following text, identical designations being used for identical or similar parts, and the preceding description otherwise being correspondingly valid.
• the sixth embodiment corresponds substantially to the embodiment according to fig. 5.
• the support element 68 for supporting the disk spring 40 is formed by a sheet metal ring with an L-shaped cross section or part cross section.
• the cross section or part cross section is composed of an axial limb 98 and a radial limb 100, the axial limb 98 surrounding the drivers 58 in the radial direction 10 from the outside, in order in this way to suppress bending of the drivers 58 in the radial direction 8 to the outside at high rotational speeds.
• the abovementioned window-like openings in the sheet metal ring are then no longer necessarily required, but could contribute to a boosting of this effect.
• the actuating piston 52 for the second multiple disk clutch 30 has a U-shaped cross section or part cross section, as can be gathered from fig. 6, the opening of the U-shaped cross section or part cross section pointing in the axial direction 4 and facing away from the disk spring 42.
• the restoring element 92 for the actuating piston 52 is arranged within the U-shaped cross section or part cross section, with the result that the restoring element 92 is supported or can be supported on one side in the axial direction 4 on the inner radial section 88 and on the other side in the axial direction 6 on the actuating piston 52.
• a reliable arrangement of the restoring element 92 is therefore ensured.
• the restoring element 92 can be, for example, an annular disk with an. undulating profile in the circumferential direction.
• the restoring element 92 can likewise be configured as an ondular washer with, for example, a plurality of inwardly and/or outwardly extending tabs or fingers which bring about improved contact between the actuating piston 52 and the restoring element 92.
• Fig. 7 shows a seventh embodiment of the multiple clutch device 2 according to the invention, only the differences from the preceding embodiments being explained in the following text, identical designations being used for identical or DKT08070A - 20 - similar parts, and the preceding description otherwise being correspondingly valid.
• the torque transmission element 38 is configured in one piece with the first drive-side multiple disk carrier 22, while the second drive-side multiple disk carrier 32 is plugged into the torque transmission element 38 in the above-described way.
• the support elements 68 are connected, preferably welded, in each case to the torque transmission element 38 and/or to one another.
• Fig. 8 shows an eighth embodiment of the multiple clutch device 2 according to the invention, only the differences from the preceding embodiments being explained in the following text, identical designations being used for identical or similar parts, and the preceding description otherwise being correspondingly valid.
• the eighth embodiment is substantially similar to the embodiment according to fig. 6, the torque transmission element 38 having, furthermore, on the outer radial section, a tubular section 102 which extends in the axial direction 6 starting from the outer radial section 74 and on which the disk spring 40 is fixed in the axial direction 6.
• the free ends of the drivers 58 can serve as a support for the disk spring 40.
• the outer section 44 of the disk spring 40 is advantageously held in the axial direction 6 by a support element 68 in the form of a combination of a wire ring and a securing ring.
• Fig. 9 shows a development of the embodiment according to fig. 8.
• the radially outer section 44 of the disk spring 40 is no longer supported in the axial direction 4 at the ends of the drivers 58, but rather is supported on an axially resilient support element 66 in the axial direction 4 which in turn is supported on the torque transmission element 38.
• the support element 68 for supporting the disk spring 42 in the axial direction 6 is arranged in such a way that said support element 68 likewise serves to support the restoring element 90 of the actuating piston 50.
• the support element 68 is connected, preferably welded, to the torque transmission element 38.
• Fig. 10 shows a tenth embodiment of the multiple clutch device 2 according to the invention, only the differences from the preceding embodiments being explained in the following text, identical designations being used for identical or similar parts, and the preceding description otherwise being correspondingly valid.
• the tenth embodiment is a development of the embodiment according to fig. 2.
• An additional support plate 78 for radially supporting the second drive-side multiple disk carrier 32 is therefore omitted; rather, the torque transmission element 38 again has the abovementioned inner radial section 88, via which the multiple disk carrier 32 is supported in the radial direction 10, the latter being formed by the central radial section 76 of the torque transmission element 38.
• Fig. 1 1 shows an eleventh embodiment of the multiple clutch device 2 according to the invention, only the differences from the preceding embodiments being explained in the following text, identical designations being used for identical or similar parts, and the preceding description otherwise being correspondingly valid.
• the eleventh embodiment corresponds substantially to the embodiment according to fig. 4, but the second drive-side multiple disk carrier 32 is not plugged into the inner radial section 88; rather, it is configured in one piece with the latter.
• the inner radial section 88 no longer brings about the support in the radial section 10; rather, this is taken over by a supporting section 104 of the multiple disk carrier 32 which extends in the radial direction 8, 10, adjoins the tubular multiple disk carrying section 56 and is configured in one piece with the latter.
• Fig. 13 shows a thirteenth embodiment of the multiple clutch device 2 according to the invention, only the differences from the preceding embodiments being explained in the following text, identical designations being used for identical or similar parts, and the preceding description otherwise being correspondingly valid.
• the thirteenth embodiment develops the embodiment according to fig. 1 in an advantageous way.
• the torque transmission element 38 is not pulled inward in the radial direction 10 to such an extent that it serves for radial support; rather, in a similar manner to the embodiment according to fig. 12, the second drive-side multiple disk carrier 32 has a dedicated support section 104 for supporting the second drive-side multiple disk carrier 32 in DKT08070A - 22 - the radial direction 10 to the inside.
• Fig. 14 shows a fourteenth embodiment of the multiple clutch device 2 according to the invention, only the differences from the preceding embodiments being explained in the following text, identical designations being used for identical or similar parts, and the preceding description otherwise being correspondingly valid.
• the fourteenth embodiment corresponds substantially to the embodiment according to fig. 7, the axially resilient support element 66 for the disk spring 40 being formed here by a plurality of spiral springs, while the axially resilient support element 66 for the disk spring 42 is formed by an additional disk spring.
• Fig. 15 shows a fifteenth embodiment of the multiple clutch device 2 according to the invention, only the differences from the preceding embodiments being explained in the following text, identical designations being used for identical or similar parts, and the preceding description otherwise being correspondingly valid.
• the fifteenth embodiment corresponds substantially to the embodiment according to fig. 1 , even if in each case the sheet metal rings already described with reference to fig. 6 and having a substantially L-shaped cross section are used for the support elements 68 for supporting the disk springs 40, 42 in the axial direction 6. Moreover, the actuating piston 50 is restored by restoring elements 90 in the form of helical springs. Furthermore, one advantageous refinement of the transmission/clutch arrangement can be seen from fig. 15, which transmission/clutch arrangement is composed of a transmission and a multiple clutch device 2 of the type according to the invention.
• the multiple clutch device 2 is thus arranged within a transmission housing (not shown), preferably a transmission housing bell, it being possible for the axial actuating forces which are introduced into the multiple clutch device 2 via the engagement bearings 48 and the disk springs 40, 42 to be supported on the transmission housing or a transmission housing cover 106 for closing the transmission housing, and the support preferably being effected via the input hub 18 of the multiple clutch device 2 which is mounted in the transmission cover 106 such that it can be rotated but cannot be displaced substantially axially.
• a transmission housing not shown
• Fig. 16 shows a sixteenth embodiment of the multiple clulch device 2 according to the invention, only the differences from the preceding embodiments being explained in the following text, identical designations being used for identical or similar parts, and the preceding description otherwise being correspondingly valid.
• the drivers on the first drive-side multiple disk carrier 22 are formed by the internal toothing present anyway for the multiple disks of the first multiple disk clutch 24. They are therefore radially protruding drivers which engage into corresponding radial cutouts in the torque transmission element, with the result that the first drive-side multiple disk carrier 22 is weakened to a less pronounced extent, as a result of which, however, the assembly is also made more difficult.
• Fig. 17 shows a seventeenth embodiment of the multiple clutch device 2 according to the invention, only the differences from the preceding embodiments being explained in the following text, identical designations being used for identical or similar parts, and the preceding description otherwise being correspondingly valid.
• the seventeenth embodiment corresponds substantially to the embodiment according to fig. 13. It has proven advantageous here if the restoring elements 90, 92 for the actuating pistons 50, 52 are supported via an axial bearing, as is shown in fig. 17 by way of example using an axial bearing 108.
• the restoring element 92 for the actuating piston 52 (in the form of a disk spring) is supported in the axial direction 4 on the axial bearing 108, the axial bearing 108 being arranged on the second output- side multiple disk carrier 34.
• Fig. 18 shows an eighteenth embodiment of the multiple clutch device 2 according to the invention, only the differences from the preceding embodiments being explained in the following text, identical designations being used for identical or similar parts, and the preceding description otherwise being correspondingly valid.
• the eighteenth embodiment corresponds substantially to the embodiment according to fig. 1 ; however, in the eighteenth embodiment, radially protruding drivers are DKT08070A - 24 - again provided on the first drive-side multiple disk carrier 22, as has already been shown with reference to fig. 16.
• the axially resilient support elements 66 which are used in the embodiments described in the preceding text are advantageously configured as the described sheet metal rings with the respective cross section.
• undulating wire rings could also be used at this point.
• the mentioned sheet metal rings, disk springs or annular disks with an undulating profile in the circumferential direction 10, 12 have the advantage that the contact points on the disk spring are displaced to a less pronounced extent by prestressing.
• the spring force of the mentioned support elements 66 is less dependent on the rotational speed than is the case in an undulating wire ring, with the result that said support elements 66 are to be preferred over an undulating wire ring.
• Figs. 19 a to f show advantageous refinements of the integral or multiple part actuating pistons which are used or can be used in the embodiments described in the preceding text. There is thus the advantage in the multiple part actuating pistons 50, 52 according to figs. 19a, c and e that the second piston part 82 surrounds the fingers 84 on the first piston part 80 from the outside and therefore prevents the fingers 84 widening or bending over in the radial direction 8 to the outside.

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• Mechanical Engineering (AREA)
• Mechanical Operated Clutches (AREA)

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• 2009
  • 2009-03-09 DE DE102009012283A patent/DE102009012283A1/de not_active Withdrawn
  • 2009-04-09 WO PCT/US2009/040034 patent/WO2009129114A2/en active Application Filing

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