DE102022106436A1 - Composite disc retainer and wet clutch with this composite disc retainer - Google Patents

Abstract

Composite disc holder (30) for a wet clutch, comprising: - a splined hub (31a, 31b, 31c, 31d, 31e, 31f, 31g) having an axis of rotation X provided with internal splines for torque transmission, - a Disc carrier (32a, 32b, 32c, 32d, 32e, 32f, 32g) having a shape of revolution about the axis X, provided with external serrations arranged to cooperate with a multiple disc assembly, the disc carrier (32a, 32b, 32c , 32d, 32e, 32f, 32g) rests axially on the knurled hub (31a, 31b, 31c, 31d, 31e, 31f, 31g),- an oil retaining cavity (33) concentric to the axis (X) which is formed at least by the union of surfaces emerging from the knurled hub and the disc carrier, the knurled hub forming an oil feed duct (34) which opens into the oil retaining cavity (33) closed by the inner surface of the disc carrier.

Description

The present invention relates to a composite disk retainer and a wet clutch using the composite disk retainer. The invention also relates to a wet double clutch and a wet triple clutch with this assembled disk holder.

The present invention relates to the field of motor vehicle torque transmission chains, particularly between an internal combustion engine and a transmission.

More specifically, the invention relates to a wet-running triple clutch for a hybrid motor vehicle in which a rotating electrical machine is arranged in the torque transmission chain.

In the prior art, hybrid motor vehicles are known with a wet-running double clutch, which is arranged between an internal combustion engine and a transmission, with a rotating electrical machine and a torque separating clutch, which is also referred to as "clutch K0", and with a member for actuating this torque separating clutch, with which a crankshaft of the internal combustion engine can be rotatably coupled to or decoupled from a rotor of the rotary electric machine. It is thus possible to stop the engine every time the vehicle stops and restart it with the rotary electric machine. The rotating electric machine can also provide an electric brake or provide additional power to the internal combustion engine to assist it or prevent it from stalling. When the internal combustion engine is operated, the electric machine can have the function of an alternator. The rotary electric machine can also ensure driving of the vehicle independently of the engine.

Such a rotating electric machine can be in line with the wet double clutch, ie the axis of rotation of the rotor of the rotating electric machine coincides with the axis of rotation of the clutches, as in FIG EP2517915 described. As a variant, the rotating electric machine can be offset in relation to the wet double clutch, ie the axis of rotation of the rotor of the rotating electric machine is offset to the axis of rotation of the wet double clutch.

In the recent development of hybridization of automobiles, it is required to have a torque transmission chain that incorporates an electric power source without sacrificing the axial compactness of the transmission chain. It was therefore necessary to develop a wet-running triple clutch with a radial design that would make it possible to feed the various clutches with cooling fluid and pressure fluid without changing the space requirements of the torque transmission chain. The invention is based on this search for axial compactness.

The radial configuration of this wet triple clutch sometimes makes it difficult to supply cooling fluid, such as oil, to the multi-plate assemblies of the various wet clutches. The oil feed channels are complicated to manufacture and do not always ensure good distribution of the cooling oil within the clutches. Insufficient lubrication and cooling can cause the friction discs to heat up and consequently impair the correct torque transmission.

The invention aims to improve the existing design while benefiting from a wet triple clutch capable of meeting axial compactness requirements while ensuring a good supply of cooling oil to the clutches.

• - eine geriffelte Nabe mit der Drehachse X, die mit einer inneren Riffelung zur Drehmomentübertragung versehen ist,
• - einen Scheibenträger aus Blech mit einer Rotationsform um die Achse X, der mit einer äußeren Riffelung versehen ist, die zur Zusammenwirkung mit einer Mehrscheibenbaugruppe angeordnet ist, wobei der Scheibenträger axial an der geriffelten Nabe anliegt,
• - mindestens eine Ölzuführungsleitung,
• - einen ringförmigen und zur Achse X konzentrischen Ölrückhaltehohlraum, der zumindest durch die Vereinigung von Oberflächen gebildet ist, die aus der geriffelten Nabe und dem Scheibenträger hervorgehen,

wobei die geriffelte Nabe vollständig oder teilweise die mindestens eine Ölzuführungsleitung bildet, die in den Ölrückhaltehohlraum ausmündet, der von der Innenfläche des Scheibenträgers verschlossen wird.To this end, according to one of its aspects, the invention proposes a composite washer for a wet clutch, comprising:

• - a knurled hub with the axis of rotation X, which is provided with an internal knurling for torque transmission,
• - a disc carrier made of sheet metal with a shape of revolution about the axis X, provided with external serrations arranged to cooperate with a multi-disc assembly, the disc carrier abutting axially on the serrated hub,
• - at least one oil supply line,
• - an annular oil retaining cavity concentric to the X axis, formed at least by the union of surfaces emerging from the knurled hub and the disc carrier,

the knurled hub forming wholly or partially the at least one oil feed duct opening into the oil retaining cavity closed by the inner surface of the disc carrier.

This structure of the assembled disc holder allows for the orderly For operation of the wet clutch, cooling oil is required first via the oil feed line into the knurled hub and then into the oil retention cavity before being discharged within the wet clutch multi-disc assembly. The flow of cooling oil is effectively channeled within the multi-disc assembly of the wet clutch.

The oil retaining cavity is formed at least from the components "serrated hub" and "disk carrier", in particular from an outer surface of the splined hub and an inner surface of the disk carrier. The inner and outer surfaces can be raw, unfinished surfaces, the union of which creates a cavity. Manufacturing costs can be reduced by using components with simple rotational molds. The assembled disk holder then fulfills the various functions of torque transmission, supporting the friction disks and conducting the cooling oil with little axial space requirement.

The disk carrier may preferably have openings formed on the outer corrugation and arranged to drain the oil contained in the oil retention cavity. The openings can be distributed circumferentially about the axis X and formed at the tooth tips of the outer corrugations. With this construction of the composite disc retainer, the flow of cooling oil that collects in the oil retention cavity is evenly distributed in the multi-disc assembly of the wet clutch. Thus, the oil retention cavity has no space where the cooling oil stays blocked.

Advantageously, the disc carrier may be riveted, crimped, welded or force fitted to the knurled hub.

The oil supply line can preferably form an arc with an axially extending line section and a radially extending line section. The radial orientation of the conduit allows for efficient management of cooling oil flow within the wet clutch multi-disc assembly.

According to one embodiment, the composite disc holder may include an annular baffle attached to the knurled hub and having external teeth cooperating with the profile of the inner surface of the disc holder, the oil retaining cavity being formed by the union of surfaces formed by the knurled hub , the disc carrier and the guide plate emerge. Advantageously, the oil retention cavity is formed at least from the components “corrugated hub”, “baffle plate” and “disk carrier”, in particular from an outer surface of the corrugated hub, a flank of the baffle plate and an inner surface of the disk carrier. The inner and outer surfaces can be raw, unfinished surfaces, the union of which creates a cavity.

According to one embodiment, the oil supply passage may form an arc having an axially extending passage portion formed by joining the surfaces of the corrugated hub and the baffle and a radially extending passage portion formed by joining the surfaces of the knurled hub and the baffle e.g. by a groove formed in the knurled hub which cooperates with a flank of the baffle.

According to a further embodiment, the oil supply line may form an arc with an axially extending line section formed only by the corrugated hub and a radially extending line section formed by the union of the surfaces of the corrugated hub and the baffle, e.g a groove formed in the knurled hub which cooperates with a flank of the baffle.

According to a further embodiment, the oil supply line may form an arc with an axially extending line section formed only by the corrugated hub and a radially extending line section formed by the union of the surfaces of the corrugated hub and the baffle, e.g at least one groove formed on the flank of the baffle cooperating with a flank of the knurled hub.

Advantageously, the baffle may have a flat surface arranged to engage a thrust bearing, for example an annular surface, and openings located radially beyond this flat surface, the openings communicating directly with the oil retention cavity. The baffle may have grooves, the openings being angularly distributed about the axis X and located between the baffle grooves.

The baffle may preferably have an internal spline at least partially abutting the splined hub, the clearance available between the teeth of the internal spline and the splined hub forming the axially extending conduit portion. The internal teeth may comprise at least three teeth angularly distributed around the X axis.

Advantageously, the baffle can be made by sheet metal stamping or by plastic injection of synthetic material, for example PA66-type polyamide plastic or PEEK-type polyetheretherketone. These plastics have high dimensional stability and are resistant to high temperatures.

• - der Ölrückhaltehohlraum kann teilweise durch eine Umfangsnut gebildet sein, die am Außenumfang der geriffelten Nabe ausgebildet ist;
• - der sich radial erstreckende Leitungsabschnitt kann durch Vereinigung der Oberflächen der geriffelten Nabe und des Scheibenträgers gebildet sein, und der sich axial erstreckende Leitungsabschnitt kann nur durch den Scheibenträger gebildet sein, z.B. mittels eines Lochs, das den Scheibenträger durchquert;
• - der sich radial erstreckende Leitungsabschnitt kann durch Bohren der geriffelten Nabe gebildet sein, und der sich axial erstreckende Leitungsabschnitt kann durch Gießen oder Schmieden direkt einstückig in der geriffelten Nabe erhalten werden;
• - der sich radial erstreckende Leitungsabschnitt und der sich axial erstreckende Leitungsabschnitt können durch Vereinigung der Oberflächen der geriffelten Nabe und des Scheibenträgers gebildet sein;
• - der sich radial erstreckende Leitungsabschnitt kann durch Vereinigung der Oberflächen der geriffelten Nabe und des Leitblechs gebildet sein;
• - die geriffelte Nabe kann eine erste bearbeitete Axiallagerauflagefläche aufweisen;
• - die geriffelte Nabe kann eine zweite bearbeitete Axiallagerauflagefläche aufweisen, die axial entgegengesetzt zur ersten Axiallagerauflagefläche angeordnet ist;
• - der Scheibenträger kann direkt auf die geriffelte Nabe drücken;
• - das Leitblech kann direkt auf die geriffelte Nabe drücken;
• - die geriffelte Nabe kann Ölzuführungsleitungen aufweisen, die winkelmäßig um die Achse X verteilt sind und in den Ölrückhaltehohlraum ausmünden;
• - die geriffelte Nabe kann insgesamt eine Rotationsform mit einer zylindrischen Basis haben.

The invention can have one or the other of the features described below in combination with one another or independently of one another:

• - the oil retaining cavity may be formed in part by a peripheral groove formed on the outer periphery of the knurled hub;
• - the radially extending duct portion may be formed by merging the surfaces of the knurled hub and the disc carrier, and the axially extending duct portion may be formed solely through the disc carrier, eg by means of a hole traversing the disc carrier;
• the radially extending duct portion may be formed by drilling the knurled hub and the axially extending duct portion may be obtained integrally in the knurled hub directly by casting or forging;
• - the radially extending duct portion and the axially extending duct portion may be formed by merging the surfaces of the knurled hub and the disk carrier;
• - the radially extending duct section may be formed by merging the surfaces of the knurled hub and the baffle;
• - the knurled hub may have a first machined thrust bearing bearing surface;
• the knurled hub may have a second machined thrust bearing surface located axially opposite to the first thrust bearing surface;
• - the disc carrier can press directly on the knurled hub;
• - the baffle can press directly on the knurled hub;
• the knurled hub may have oil feed ducts angularly distributed around the axis X and opening into the oil retention cavity;
• - the knurled hub can have an overall shape of revolution with a cylindrical base.

Such a composite disk holder according to one or other of the features described above, in combination with each other or independently of each other, has the advantage of reducing the manufacturing costs through the use of annular attached parts. These annular shoulders allow for the inexpensive formation of an oil containment cavity and can also perform other functions within a wet clutch such as supporting and centering thrust bearings.

• - einen Drehmomenteingangsscheibenhalter, der zur drehbaren Verbindung mit einer Antriebswelle längs einer Drehachse X angeordnet ist;
• - eine Mehrscheibenbaugruppe mit Reibscheiben und Druckplatten, die axial gestapelt sind und von dem Drehmomenteingangsscheibenhalter in Drehung versetzt werden;
• - einen zusammengesetzten Scheibenhalter, der die oben genannten Merkmale vollständig oder teilweise aufnimmt und radial innerhalb der Mehrscheibenbaugruppe liegt und zur drehbaren Verbindung mit einer Abtriebswelle angeordnet ist.

According to one of its aspects, the invention also relates to a wet-running clutch for a torque transmission system, which has the following:

• - a torque input disc holder arranged for rotatable connection to a drive shaft along a rotation axis X;
• - a multiple disc assembly with friction discs and pressure plates stacked axially and rotated by the torque input disc holder;
• - a composite disc holder, embodying in whole or in part the above features, lying radially inward of the multi-disc assembly and arranged for rotatable connection to an output shaft.

• - einen zylindrischen Abschnitt,
• - einen Flansch, der sich ausgehend von dem zylindrischen Abschnitt radial erstreckt und fest mit dem Drehmomenteingangsscheibenhalter verbunden ist, und
• - mindestens einen in der mittleren Nabe ausgebildeten Kühlölzuführungskanal, der zumindest den zylindrischen Abschnitt durchquert und axial gegenüber der Ölzuführungsleitung des zusammengesetzten Scheibenhalters ausmündet, so dass das von der mittleren Nabe stammende Öl in die geriffelte Nabe des zusammengesetzten Scheibenhalters geleitet werden und in die Mehrscheibenbaugruppe ausmünden kann.

The wet clutch may preferably have a central hub with the axis of rotation X, the central hub having:

• - a cylindrical section,
• - a flange extending radially from the cylindrical portion and fixedly connected to the torque input disc holder, and
• - at least one cooling oil feed channel formed in the central hub, crossing at least the cylindrical portion and opening out axially opposite the oil feed duct of the composite disc holder, so that the oil coming from the central hub can be directed into the knurled hub of the composite disc holder and out into the multiple disc assembly .

With this structure of the wet clutch, the cooling oil provided by the vehicle is transferred from the central hub to the composite disc holder in a simplified manner directed. The oil originating from the center hub is axially aligned via the oil feed passage before entering the composite disc retainer oil feed line, then enters the oil retention cavity before being discharged within the wet clutch multi-disc assembly. The flow of cooling oil is effectively channeled within the multi-disc assembly of the wet clutch.

The central hub may preferably have a plurality of cooling oil feed passages and the composite disc holder may have a plurality of oil feed passages angularly distributed about the axis X, the outlets of the cooling oil feed passages being arranged on a diameter substantially equal to the arrangement diameter of the inlets of the oil feed passages.

Advantageously, a thrust bearing can be arranged axially between the central hub and the composite disc holder, the thrust bearing partially closing the cooling oil feed duct or ducts opening axially opposite the oil feed duct(s) of the composite disc holder.

• - eine erste Kupplung; und
• - eine zweite Kupplung vom Typ nasslaufende Kupplung, die die oben genannten Merkmale vollständig oder teilweise aufnimmt und radial innerhalb der ersten Kupplung angeordnet ist, wobei die erste und die zweite Kupplung zur wahlweisen Kopplung einer Antriebswelle an eine erste Abtriebswelle und eine zweite Abtriebswelle, z.B. eine erste und eine zweite Getriebewelle gesteuert werden, und wobei die mittlere Nabe der zweiten Kupplung und der ersten Kupplung gemeinsam ist.

According to another of its aspects, the subject matter of the invention is also a wet-running double clutch for a torque transmission system, which has the following:

• - a first clutch; and
• - a second clutch of the wet clutch type, incorporating the above features in whole or in part and disposed radially inward of the first clutch, the first and second clutches for selectively coupling an input shaft to a first output shaft and a second output shaft, e.g first and second transmission shafts are controlled, and wherein the center hub is common to the second clutch and the first clutch.

• - einen Flansch, der sich radial über die zweite Kupplung hinaus erstreckt,
• - einen ersten ringförmigen Hohlraum, der auf der Seite des Flansches liegt und zur Aufnahme eines Kolbens zur Betätigung der ersten Kupplung angeordnet ist, und
• - einen zweiten ringförmigen Hohlraum, der auf derselben Seite des Flansches wie der erste ringförmige Hohlraum liegt und zur Aufnahme eines Kolbens zur Betätigung der zweiten Kupplung angeordnet ist,
• - mindestens eine in der mittleren Nabe ausgebildete Ölrohrleitung, die den Flansch durchquert und in einen der ringförmigen Hohlräume ausmündet, wobei die Ölrohrleitung von dem Kühlölzuführungskanal der Mehrscheibenbaugruppe der zweiten Kupplung getrennt ist.

The central hub may advantageously include:

• - a flange extending radially beyond the second coupling,
• - a first annular cavity located on the side of the flange and arranged to receive a piston for actuating the first clutch, and
• - a second annular cavity located on the same side of the flange as the first annular cavity and arranged to receive a piston for actuating the second clutch,
• - at least one oil duct formed in the central hub, passing through the flange and opening into one of the annular cavities, the oil duct being separate from the cooling oil feed channel of the multi-disc assembly of the second clutch.

The invention also relates, in another of its aspects, to a wet triple clutch for a torque transmission system, comprising a torque disconnect clutch of the multi-plate clutch type controlled to selectively couple an input shaft to an electric machine, and a wet dual clutch comprising the foregoing Features fully or partially absorbs, the torque disconnect clutch is arranged radially beyond the wet dual clutch also.

Advantageously, the wet triple clutch may have the center hub of the wet dual clutch shared with the torque disconnect clutch, the center hub having a third annular cavity radially beyond the other two annular cavities and for receiving a piston for actuating the torque disconnect clutch the central hub having a drive cap fitted and arranged to be rotated by an electric machine, the drive cap forming in part the third annular cavity.

The three annular cavities can preferably be aligned in one and the same axial direction, in particular in the direction of the drive shaft.

The drive cover can advantageously enclose the outer circumference of the flange. This makes it possible to arrange the annular cavities associated with the three clutches radially in one and the same plane.

The oil pipes that feed the annular cavities can preferably open out on the outer circumference of the flange and be closed by the drive cover. The oil tubes may be angularly distributed around the cylindrical portion of the center hub. In this way, part of the oil pipelines can be sealed without having to use other expensive components.

Advantageously, the annular cavities of the separating clutch, the first clutch and the second clutch may be arranged radially one after the other as the axis X is approached.

This design of the wet triple clutch means that the clutches are arranged concentrically and radially in one and the same plane. The axial space requirement of such a wet-running triple clutch within a torque transmission system or a torque transmission chain is reduced as a result.

The first clutch is preferably actuatable by means of a first actuating piston which is axially movable with respect to the first annular cavity of the central hub between an engaged and a disengaged position of the first clutch, the displacement of the first actuating piston being controlled by means of a control chamber partially defined by the flange is controlled. In this way, the control chamber of the first clutch is contained in the first cavity, whereby the pressurized oil supply is as close as possible to the center hub, thereby reducing leakage within the wet-running triple clutch.

The second clutch can preferably be actuated by means of a second actuating piston which is axially movable with respect to the second annular cavity of the central hub between an engaged and a disengaged position of the second clutch, the displacement of the second actuating piston being controlled by means of a control chamber which is partially defined by the flange is controlled. In this way, the control chamber of the second clutch is contained within the second cavity, allowing the pressurized oil supply to be as close as possible to the center hub, thereby reducing leakage within the wet triple clutch.

According to one embodiment, the oil duct may be made by drilling successive ducts inside the central hub, the ducts merging into one another and arranged to feed the control chamber of the clutches with pressurized fluid.

According to one embodiment, the drive cover has an electrical connection area that can be rotatably connected to an electrical machine that rotates about an axis parallel to the axis of rotation X. The electrical connection area may be axially offset from the disconnect clutch and/or the first and second clutches. The electrical machine is then referred to as "offline".

Preferably, the drive cover may include corrugations arranged to receive the multiple disc assembly of the disconnect clutch, the corrugations being integral with the drive cover or being attached to the drive cover.

Advantageously, the drive cover can have a ring gear which can be rotatably connected to an electric machine which rotates about an axis parallel to the axis of rotation X.

This arrangement allows the electric machine to be positioned according to the available space in the vehicle's torque transmission chain. This arrangement makes it possible, in particular, not to have to arrange the electric machine axially after the clutches, which would be disadvantageous for the axial compactness. In particular, this arrangement makes it possible to avoid having to arrange the electric machine radially beyond the clutches, which would be disadvantageous for the radial compactness.

Alternatively, a chain or belt may be used to connect the rotating electric machine to the electrical connection area.

• - einen Drehmomenteingangsscheibenhalter, der zur drehbaren Verbindung mit einer Antriebswelle längs einer Drehachse X angeordnet ist;
• - eine Mehrscheibenbaugruppe mit Reibscheiben und Druckplatten, die axial gestapelt sind und von dem Drehmomenteingangsscheibenhalter in Drehung versetzt werden;
• - einen Drehmomentausgangsscheibenhalter, der radial innerhalb der Mehrscheibenbaugruppe liegt und zur drehbaren Verbindung mit einer Abtriebswelle angeordnet ist;
• - eine mittlere Nabe mit der Drehachse X, die fest mit dem Drehmomenteingangsscheibenhalter verbunden ist, wobei die mittlere Nabe einen zylindrischen Abschnitt und mindestens einen in der mittleren Nabe ausgebildeten Kühlölzuführungskanal aufweist, der zumindest den zylindrischen Abschnitt durchquert und axial gegenüber dem Drehmomentausgangsscheibenhalter ausmündet,

wobei sich die nasslaufende Kupplung dadurch auszeichnet, dass sie ein Axiallager aufweist, das axial zwischen der mittleren Nabe und dem Drehmomentausgangsscheibenhalter angeordnet ist, wobei das Axiallager den Kühlölzuführungskanal bzw. die Kühlölzuführungskanäle, die axial gegenüber dem Drehmomentausgangsscheibenhalter ausmünden, teilweise verschließt.According to another of its aspects, the subject matter of the invention is also a wet-running clutch for a torque transmission system, which has the following:

• - a torque input disc holder arranged for rotatable connection to a drive shaft along a rotation axis X;
• - a multiple disc assembly with friction discs and pressure plates stacked axially and rotated by the torque input disc holder;
• - a torque output disc holder radially inward of the multiple disc assembly and arranged for rotatable connection to an output shaft;
• - a central hub with axis of rotation X and integral with the torque input disc holder, the central hub having a cylindrical portion and at least one cooling oil feed channel formed in the central hub, crossing at least the cylindrical portion and opening out axially opposite the torque output disc holder,

the wet clutch being characterized by having a thrust bearing axially disposed between the center hub and the torque output disc retainer, the Axial bearing partially closes the cooling oil supply channel or the cooling oil supply channels, which open out axially opposite the torque output disc holder.

This design of the wet clutch makes it possible to adjust the amount of oil contained within the center hub. If the cooling oil feed channel also feeds the pressure compensation chamber of the wet-running clutch, the compensation pressure in this chamber can thus be adjusted.

The thrust bearing may preferably be a needle bearing comprising at least one rolling plate.

Advantageously, the rolling plate of the thrust bearing can partially close the cooling oil supply channel.

The thrust bearing may preferably be fitted onto the cylindrical portion of the center hub. The roller plate may have a cylindrical portion press-fitted into the cylindrical portion of the center hub.

• - 1 eine axiale Schnittansicht einer nasslaufenden Dreifachkupplung, die den zusammengesetzten Scheibenhalter gemäß einer ersten Ausführungsform der Erfindung aufweist.
• - 2 eine isometrische Ansicht des zusammengesetzten Scheibenhalters gemäß der ersten Ausführungsform der Erfindung von 1.
• - 3 eine isometrische Ansicht eines erfindungsgemäßen zusammengesetzten Scheibenhalters gemäß einer zweiten Ausführungsform der Erfindung.
• - 4 eine isometrische Ansicht eines erfindungsgemäßen zusammengesetzten Scheibenhalters gemäß einer dritten Ausführungsform der Erfindung.
• - 5 eine isometrische Ansicht eines erfindungsgemäßen zusammengesetzten Scheibenhalters gemäß einer vierten Ausführungsform der Erfindung.
• - 6 eine isometrische Ansicht eines erfindungsgemäßen zusammengesetzten Scheibenhalters gemäß einer fünften Ausführungsform der Erfindung.
• - 6a eine isometrische Ansicht der geriffelten Nabe des erfindungsgemäßen zusammengesetzten Scheibenhalters gemäß der fünften Ausführungsform der Erfindung.
• - 7 eine isometrische Ansicht eines erfindungsgemäßen zusammengesetzten Scheibenhalters gemäß einer sechsten Ausführungsform der Erfindung.
• - 8 eine Detailansicht im Axialschnitt einer nasslaufenden Dreifachkupplung, die den zusammengesetzten Scheibenhalter gemäß einer siebten Ausführungsform der Erfindung aufweist.
• - 9 eine isometrische Ansicht des zusammengesetzten Scheibenhalters gemäß der siebten Ausführungsform der Erfindung von 8.

In the course of the following description of a particular embodiment of the invention, given purely by way of non-limiting example with reference to the attached figures, the invention will be better understood and other aims, details, characteristics and advantages of the invention will become clearer. In the drawings show:

• - 1 Figure 14 is an axial sectional view of a wet triple clutch incorporating the assembled disk retainer according to a first embodiment of the invention.
• - 2 FIG. 14 is an isometric view of the assembled disk holder according to the first embodiment of the invention 1 .
• - 3 an isometric view of a composite disk holder according to the invention according to a second embodiment of the invention.
• - 4 an isometric view of a composite disk holder according to the invention according to a third embodiment of the invention.
• - 5 an isometric view of a composite disk holder according to the invention according to a fourth embodiment of the invention.
• - 6 an isometric view of a composite disk holder according to the invention according to a fifth embodiment of the invention.
• - 6a Figure 14 is an isometric view of the splined hub of the inventive composite disc retainer according to the fifth embodiment of the invention.
• - 7 an isometric view of a composite disc holder according to a sixth embodiment of the invention.
• - 8th Figure 12 is a detail view in axial section of a wet triple clutch incorporating the assembled disk retainer according to a seventh embodiment of the invention.
• - 9 14 is an isometric view of the assembled disk holder according to the seventh embodiment of the invention 8th .

In the remainder of the description and claims, for better understanding and in a non-limiting manner, the terms "front" or "rear" are used in the direction relative to an axial orientation determined by the main axis of rotation X of the transmission of the motor vehicle and the Terms "internal/internal" or "external/external" are used with respect to the X-axis and in a radial orientation orthogonal to the axial orientation.

the 1 and 2 show a first embodiment of an assembled disk holder 30 for a wet triple clutch 1. The wet triple clutch 1 is represented within a torque transmission chain of a motor vehicle by a transmission housing 100, which is equipped with two output shafts A1, A2 for the exit of the torque.

• - eine Drehmomenttrennkupplung K0 vom Typ Mehrscheibenkupplung, die so gesteuert wird, dass sie wahlweise eine Antriebswelle an eine elektrische Maschine koppelt,
• - eine erste Drehmomentausgangskupplung E1 und eine zweite Drehmomentausgangskupplung E2 jeweils vom Typ Mehrscheibenkupplung, die so gesteuert werden, dass sie die elektrische Maschine und/oder die Antriebswelle wahlweise an eine erste Abtriebswelle und eine zweite Abtriebswelle koppeln, wobei die erste und die zweite Kupplung E1, E2 radial übereinander angeordnet sind, und
• - eine mittlere Nabe 50, die die Steuerkammern der Drehmomenttrennkupplung K0, der ersten Kupplung E1 und der zweiten Kupplung E2 mit Öl speist.

In 1 shows a wet triple clutch 1, which has:

• - a K0 torque disconnect clutch of the multi-plate clutch type, controlled to selectively couple a drive shaft to an electric machine,
• - a first torque output clutch E1 and a second torque output clutch E2, each of the multi-plate clutch type, controlled so as to selectively couple the electric machine and/or the input shaft to a first output shaft and a second output shaft, the first and the second clutch E1, E2 are arranged radially one above the other, and
• - a central hub 50 which feeds oil to the control chambers of the torque separating clutch K0, the first clutch E1 and the second clutch E2.

The second wet clutch E2 includes the assembled disk retainer 30 according to the first embodiment of the invention.

• - einen zylindrischen Abschnitt 52,
• - einen Flansch 53, der sich ausgehend von dem zylindrischen Abschnitt 52 radial erstreckt,
• - einen ersten ringförmigen Hohlraum 56, der auf der Seite des Flansches liegt und zur Aufnahme eines Kolbens 15 zur Betätigung der ersten Kupplung E1 angeordnet ist,
• - einen zweiten ringförmigen Hohlraum 55, der auf derselben Seite des Flansches wie der erste ringförmige Hohlraum liegt und zur Aufnahme eines Kolbens 25 zur Betätigung der zweiten Kupplung E2 angeordnet ist,
• - einen dritten ringförmigen Hohlraum 57, der radial über die beiden anderen ringförmigen Hohlräume hinaus liegt und zur Aufnahme eines Kolbens 5 zur Betätigung der Drehmomenttrennkupplung K0 angeordnet ist, und
• - in der mittleren Nabe 50 ausgebildete Ölrohrleitungen 54a, 54b und 54c, die den zylindrischen Abschnitt 52 und den Flansch 53 durchqueren und getrennt in die ringförmigen Hohlräume ausmünden.

Specifically, the center hub 50 includes:

• - a cylindrical portion 52,
• - a flange 53 extending radially from the cylindrical portion 52,
• a first annular cavity 56 located on the side of the flange and arranged to house a piston 15 for actuating the first clutch E1,
• - a second annular cavity 55 located on the same side of the flange as the first annular cavity and arranged to house a piston 25 for actuating the second clutch E2,
• - a third annular cavity 57 radially beyond the other two annular cavities and arranged to receive a piston 5 for actuating the torque separating clutch K0, and
• oil ducts 54a, 54b and 54c formed in the central hub 50, passing through the cylindrical portion 52 and the flange 53 and opening separately into the annular cavities.

The annular cavities 57, 56, 55 of the torque separating clutch K0, the first clutch E1 and the second clutch E2 are aligned in one and the same direction, e.g. H. towards the internal combustion engine of the torque transmission chain.

The wet-running triple clutch 1 has at least one torque input element 2 about its axis of rotation X, which is rotatably connected to a drive shaft (not shown). The input element 2 is located on the front of the wet triple clutch 1.

In the first embodiment, the input member 2 , which is “L”-shaped as a whole, has a radially oriented portion formed by a torque input cover 3 and an axially oriented portion formed by a torque input hub 4 . The torque input member 2 is rotatably guided inside a housing 101 which is fixed with respect to the torque transmission chain.

The input element 2 for the entry of the torque is rotatably connected e.g. via corrugations formed at the output of a damping device (such as a dual mass flywheel, etc.), the input of which is connected in particular via an engine flywheel to the drive shaft formed by a crankshaft which rotated by an internal combustion engine equipped in the motor vehicle.

The torque input cover 3 has a corrugation on its outer radial end, which is arranged to accommodate the multi-plate assembly of the torque separating clutch K0.

In the example under consideration, the wet triple clutch 1 also includes a torque disconnect clutch K0 which selectively and frictionally couples the torque input cover 3 and a torque disconnect clutch K0 washer retainer 81 non-rotatably connected to the composite knurled hub 50 for oil delivery.

The torque separating clutch K0 has a multi-disc assembly with a plurality of friction discs 7, which are equipped with friction linings and are non-rotatably connected to the torque input cover 3, and a plurality of plates 6, which are arranged on one side and on the other side of each friction disc 7 and are non-rotatable with the intermediate disc holder 81 are connected. The torque separating clutch K0 is actuated by an actuating piston 5, which is movable axially, here from the back to the front, between a disengaged and an engaged position, which correspond to the open or closed state of the torque separating clutch K0. The operating piston 5 clamps the friction pads so that torque is transmitted between the torque input cover 3 and the washer holder 81 .

The plates 6 of the multi-plate assembly of the torque disconnect clutch K0 are rotatably connected to the center hub 50 via a knurl, and the friction plates 7 are rotatably connected to the input member 2.

The middle hub 50 has a drive cover 80 which is attached to the outer periphery of the flange 53. The central hub 50 has the task of transmitting the torque within the wet-running triple clutch 1 . For this purpose, the drive cover 80 is non-rotatably connected to the intermediate disk holder 81, in this case via a welded connection.

The drive cover 80 includes an electrical connection portion 82 that may be rotatably connected to a rotating electrical machine. In the present case, the electric machine rotates about an axis that is parallel runs to the axis of rotation X. The electric machine is referred to as "offline" because it is not concentric with the main shaft, but is aligned along a parallel shaft. The electrical connection area 82 can interact directly with a pinion of the rotating electrical machine.

The electrical connection portion 82 may be in the form of a collar engageable directly via a pinion of the rotating electrical machine (not shown) or indirectly (belt, chain...). The rim can have helical gearing whose shape is complementary to the pinion of the rotating electric machine.

The center hub 50 can transmit torque from two different sources, a thermal source and an electrical source. When the torque separating clutch K0 is closed, the torque originating from the internal combustion engine can then be transmitted to the coaxial transmission shafts A1, A2, depending on whether one or the other of the first clutch E1 or the second clutch E2 is closed.

The first output shaft A1 is rotated when the first clutch E1 is closed, and the second output shaft A2 is rotated when the second clutch E2 is closed.

The multi-disc assembly of the first clutch E1 includes plates 11 rotatably connected to a torque input disk holder 10 attached to the center hub 50 and friction disks 12 rotatably connected to an output disk holder 13. The friction discs 12 are uniformly arranged axially between two consecutive plates 11.

The output disc holder 13 of the first clutch E1 is rotatably connected to the first output shaft A1 by engagement with the friction discs 12 and by splined connection. The radially inner end of the output disk holder 13 is fixedly connected to an output splined hub.

The multi-disc assembly of the second clutch E2 includes plates 21 rotatably connected to the torque input disk holder 10 attached to the center hub 50 and friction disks 22 rotatably connected to a composite disk holder 30 constructed according to the first embodiment of the invention is executed. The composite disc holder 30 has a cylindrical splined hub 31a with axis of rotation X provided with internal serrations 310 for torque transmission, and a disk carrier 32a with a rotational shape about axis X. In this first embodiment, the disk carrier 32a is with an outer Corrugation 320 arranged to cooperate with a multi-disc assembly and provided with an inner skirt 321. Inner skirt 321 axially abuts knurled hub 31a. As in 2 shown, the disc carrier 32a is made of deep-drawn sheet steel. The disc carrier 32a is attached to the knurled hub 31a, in particular by a welded joint in the region of the inner skirt 321. The welded joint is continuous over 360° in this example.

As a variation, not shown, disk carrier 32a may be riveted, crimped or force-fitted to knurled hub 31a.

The composite disc holder 30 of the second clutch E2 is rotatably connected through the engagement of the outer serrations 320 with the friction discs 22 and the inner serrations 310 with the second output shaft A2. The composite disk holder 30 is axially arranged between the output disk holder 13 of the first clutch E<b>1 and the cylindrical portion 52 of the center hub 50 . The assembled disc holder 30 is axially arranged between two thrust bearings. For this purpose, the knurled hub 31a has a first machined thrust bearing bearing surface 301 and a second machined thrust bearing bearing surface 302 in which the thrust bearings are accommodated. The second thrust bearing bearing surface 302 is arranged axially opposite to the first thrust bearing bearing surface 301 .

As in 1 As shown, the torque input disc retainer 10 has outer serrations that engage the multi-plate assembly of the first clutch E1 and inner serrations that engage the multi-plate assembly of the second clutch E2. The torque input disc retainer 10 is fixedly attached to the center hub 50 by a weld.

In a variant, not shown, the inner and outer serrations that engage the multi-plate assemblies of clutches E1 and E2 may be distributed among two different torque input plate holders and attached to the center hub.

The wet-running triple clutch 1 is hydraulically controlled with a pressure fluid, usually oil.

In order to selectively control the state change of the torque disconnect clutch K0, the first clutch E1 and the second clutch E2, a wet triple clutch controller controls the supply of pressurized oil within separate control chambers. The control device is usually integrated in the transmission housing 100 . The control device is connected to the central hub 50 which has pressurized oil ducts 54a, 54b and 54c, for example three as in FIG 1 shown. The oil tubes 54a, 54b and 54c are angularly distributed around the cylindrical portion 52 of the center hub 50. As shown in FIG.

Each of the oil passages 54a, 54b and 54c consists of substantially radial and axial bores directed toward the control chambers of the torque disconnect clutch K0, the first and second clutches E1, E2.

The oil pipe 54a, the inlet opening of which is located axially in the vicinity of the flange 53, is associated, for example, with the control chamber of the second clutch E2. Oil tubing 54a is formed by drilling sequential axial and radial conduits within center hub 50. As shown in FIG. The lines merge into one another and are arranged to supply pressurized fluid to the control chamber of the second clutch E2. The oil duct 54a opens out into the second annular cavity 55 formed partly by the cylindrical portion 52 of the central hub 50 and partly by an annular appendage. In the present case, the ring-shaped added part on the flange of the center hub 50 is a part of the torque input disc holder 10 of the second clutch E2. The torque input disc holder 10 and the ring-shaped added part of the second cavity 55 form one and the same part.

The second clutch E2 has an actuating piston 25 which is movable axially, here from the rear to the front, between a disengaged and an engaged position which correspond to the open and closed states of the second clutch E2. The multi-disc assembly of the second clutch E2 is actuated directly by the second actuating piston 25, which is made of stamped sheet metal. The actuating piston 25 is axially movable with respect to the second annular cavity 55 of the center hub 50 . The displacement of the actuating piston 25 is controlled by means of a control chamber which is partially delimited by the annular part 10 attached.

The oil pipe 54b machined in the middle boss 50 is associated with the control chamber of the first clutch E1. Oil tubing 54b is formed by drilling sequential axial and radial tubing within center hub 50. As shown in FIG. The lines merge into one another and are arranged in such a way that they feed the control chamber of the first clutch E1 with pressurized fluid. The oil pipe 54b opens into the first annular cavity 56 .

The first clutch E1 has an actuating piston 15 which is movable axially, here from the back to the front, between a disengaged position and an engaged position which correspond to the open and closed states of the first clutch E1.

In the first embodiment, the oil pipes 54a, 54b and 54c open out at the outer periphery of the flange 53 and are closed by the drive cover 80. As shown in FIG.

As is known from the operation of a wet-running clutch, each control chamber is assigned a compensation chamber. The compensation chambers are fed with a fluid, e.g. The cooling fluid uses separate passages of the oil tubes 54a, 54b and 54c. These separate channels are formed in the center hub 50 as well.

The cooling fluid is also routed within the multiple disc assemblies of the wet clutches. For this purpose, a cooling oil supply channel 54d is formed in the middle hub 50 . This channel 54d traverses the cylindrical portion 52 and opens out axially opposite an oil feed duct 34 arranged in the composite disc-holder 30 so that the cooling oil coming from the central hub 50 is directed into the knurled hub 31a of the composite disc-holder 30 and into the multi-disc assembly of the second clutch E2.

The cooling oil supply channel 54d feeds the assembled disc holder 30 and the equalizing chambers of the wet triple clutch 1 with oil. The cooling oil feed passage 54d is formed by drilling consecutive axial and radial passages within the center hub 50. As shown in FIG. The lines merge into one another and are arranged to supply cooling fluid to the equalization chambers.

For efficiency, the center hub 50 has a plurality of cooling oil feed passages 54d which communicate with a plurality of oil feed ducts 34 angularly distributed about the axis X on the knurled hub 31a. In the example of the first embodiment, the knurled boss 31a has eight oil feed passages 34 distributed at an angle of 45°.

Each of the oil supply passages 34 forms an arc with an axially extending passage portion 36 and a radially extending passage portion 35. The radial orientation of the passage allows cooling oil flow to be efficiently directed within the multi-plate assembly of the second clutch E2. The cooling oil supply channels 54d are arranged on a diameter which essentially corresponds to the arrangement diameter of the axially extending line sections 36 .

To improve the efficiency of cooling fluid distribution within the second clutch E2, the composite disk holder 30 also has an annular oil retaining cavity 33 concentric with the axis X, formed by the union of surfaces resulting from the knurled hub 31a and the disk carrier 32a. Specifically, the oil retaining cavity 33 is formed in part by a circumferential groove formed on the outer periphery of the knurled boss 31a. Each of the oil supply lines 34 opens into the oil retaining cavity 33 which is closed by the inner surface 38 of the disc carrier 32a.

The disc carrier 32a has openings 39 formed on the outer corrugation 320 and arranged so that the oil contained in the oil retaining cavity 33 is drained. The openings 39 are distributed circumferentially about the axis X and are formed at the tips of the teeth of the outer serration 320 . With this construction of the composite disc retainer, the flow of cooling oil that collects in the oil retention cavity is evenly distributed in the multi-disc assembly of the wet clutch.

As in 2 As shown, the radially extending duct portion 35 is formed by boring the splined hub 31a, and the axially extending duct portion 36 is obtained integrally directly in the splined hub by casting or forging according to the method of manufacturing the splined hub 31a.

Other embodiments of the assembled disk holder 30 will now be presented. All of these composite disc retainers 30 perform the same functions of transferring torque, supporting the friction discs, and directing cooling oil within a wet clutch.

3 Figure 12 shows a composite disk holder 30 according to a second embodiment of the invention which is similar in at least general operation to the first embodiment.

This second embodiment differs from that referred to in FIG 1 and 2 In the illustrated embodiment, the disc carrier 32b is provided with outer knurling 320 arranged to cooperate with a multiple disc assembly and with an inner skirt 321 discontinuously welded to the knurled hub 31b.

The inner skirt 321 has a central bore 322 which partially forms the oil supply lines 34 . As before, each of the oil supply passages 34 forms an arc with an axially extending passage portion 36 and a radially extending passage portion 35. In this second embodiment, the radially extending passage portion 35 and the axially extending passage portion 36 are formed by joining the surfaces of the knurled hub 31b and the disk carrier 32b.

The disk carrier 32b rests axially on projections 313 formed on the knurled hub 31b, with the discontinuous welds being formed on these projections 313. The projections 313 are distributed around the cylindrical base of the knurled hub 31b. The inlet of each of the oil supply lines 34 is located between the projections 313, respectively.

An annular oil retaining cavity 33 concentric with axis X is formed by the union of surfaces resulting from knurled hub 31b and disc carrier 32b. Each of the oil supply lines 34 opens into the oil retaining cavity 33 which is closed by the inner surface 38 of the disc carrier 32b.

This second embodiment has the advantage that mainly the rough, i.e. unmachined, surfaces of the knurled hub and disc carrier are used to form the oil feed passages. The manufacturing cost of such a composite disk holder is reduced.

4 Figure 12 shows a composite disk holder 30 according to a third embodiment of the invention which is similar in at least general operation to the second embodiment.

This third embodiment differs from that referred to in FIG 3 illustrated embodiment characterized in that the radially extending conduit portion 35 is formed by combining the surfaces of the knurled hub 31c and the disc carrier 32c, while the axially extending conduit portion 36 only by the Disk carrier is formed. The inner skirt 321 of disc carrier 32c has a central bore 322 surrounding the cylindrical base of knurled hub 31c.

Elongated or circular openings 36 completely penetrate the inner skirt 321 and form the axially extending conduit sections 36. In this third embodiment, the disk carrier 32c is continuously welded to the knurled hub 31c.

5 Figure 12 shows a composite disk holder 30 according to a fourth embodiment of the invention which is similar in at least general operation to the first embodiment.

This fourth embodiment is different from that related to FIG 1 and 2 In the illustrated embodiment, the composite disk holder 30 includes an additional component, referred to as a baffle 37, which is annular and is attached to the knurled hub 31d. This baffle 37 has an external toothing 373 which interacts with the profile of the inner surface 38 of the disc carrier 32d.

As in 5 As shown, the assembled disc retainer 30 includes an oil retention cavity 33 formed by the union of surfaces resulting from the knurled hub 31d, disc carrier 32d and baffle 37. Advantageously, the oil retention cavity 33 is formed from an outer surface of the knurled hub 31d, a flank of the baffle 37 and an inner surface 38 of the disc carrier 32d.

The oil retaining cavity 33 is fed with cooling fluid via a plurality of oil feed ducts 34 angularly distributed about the X axis. Each of the oil supply passages 34 forms an arc with an axially extending passage portion 36 formed only by the knurled boss 31d and a radially extending passage portion 35 formed only by the knurled boss 31d. The radially extending line sections 35 are produced in particular by drilling.

The guide plate 37 is produced from a sheet steel by deep-drawing. The baffle 37 can be held on the knurled hub 31d by press fitting or welding. As a variant, the baffle 37 can be made by injection molding of synthetic material, e.g. B. of polyamide plastic type PA66 or polyetheretherketone type PEEK.

the 6 and 6a Figure 12 shows a composite disk holder 30 according to a fifth embodiment of the invention which is similar, at least in general operation, to the fourth embodiment.

This fifth embodiment differs from that referred to in FIG 5 illustrated embodiment in that the guide plate 37 rests directly on one of the flanks of the corrugated hub 31e, so that the oil supply line 34 can be formed by combining the surfaces of the corrugated hub 31e and the guide plate 37.

The baffle 37 has an external toothing 373 which cooperates with the profile of the inner surface 38 of the disc carrier 32e, and an internal bore 370 which forms the oil supply line 34 in part.

As in 6 As shown, the assembled disc retainer 30 has an oil retention cavity 33 formed by the union of surfaces resulting from the knurled hub 31e, disc carrier 32e and baffle 37. Advantageously, the oil retaining cavity 33 is formed from an outer surface of the knurled hub 31e, a flank of the baffle 37 and an inner surface 38 of the disc carrier 32e.

The oil retaining cavity 33 is fed with cooling fluid via a plurality of oil feed ducts 34 angularly distributed about the X axis. Each of the oil supply passages 34 forms an arc with an axially extending passage portion 36 formed solely by the knurled hub 31e and a radially extending passage portion 35 formed by the union of the surfaces of the knurled hub 31e and the baffle 37.

6a 12 shows the geometry of the splined hub 31e obtained by casting or forging according to the fifth embodiment of the invention. The knurled hub 31e has, in particular, protrusions 314 angularly distributed about the axis X and having the function of holding and centering the baffle 37. The projections 314 also enable centering of the thrust bearing. In this embodiment, the composite disk holder 30 has six oil supply passages 34 formed largely by the rough surfaces of the knurled boss 31e. Elongate or circular openings 36 completely traverse the knurled hub 31e and form the axially extending duct sections 36. The openings 36 open into radially extending grooves 351 which partially form the radially extending duct sections.

This fifth embodiment has the advantage that mainly raw, ie unmachined, surfaces of the knurled hub and the baffle are used to form the oil supply lines. The baffle 37 merely rests on the knurled hub 31e and is held axially in position by the bearing of the thrust bearings distributed on either side of the composite disc holder when this is installed in the wet clutch. The cost of manufacturing such a composite disk holder is reduced.

7 Figure 12 shows a composite disk holder 30 according to a sixth embodiment of the invention which is similar in at least general operation to the fifth embodiment.

This sixth embodiment is different from that related to FIG 6 and 6a illustrated embodiment in that the baffle 37 is attached to the flank of the knurled boss 31f oriented on the center boss 50 side of the second wet clutch E2. The baffle 37 is provided with an inner skirt 371 which attaches to bosses 313 formed on the knurled hub 31f. The inner skirt 371 has a central bore 372 which partially forms the oil supply lines 34 .

As before, the composite disc retainer 30 has an oil retention cavity 33 formed by the union of surfaces resulting from the knurled hub 31f, disc carrier 32f and baffle 37. Advantageously, the oil retention cavity 33 is formed from an outer surface of the knurled hub 31f, a flank of the baffle 37 and an inner surface 38 of the disc carrier 32f.

The oil retaining cavity 33 is fed with cooling fluid via a plurality of oil feed ducts 34 angularly distributed about the X axis. Each of the oil supply passages 34 forms an arc with an axially extending passage portion 36 and a radially extending passage portion 35. In this sixth embodiment, the radially extending passage portion 35 and the axially extending passage portion 3 are defined by the union of the surfaces of the knurled boss 31f and 31f of the guide plate 37 is formed.

Disc carrier 32f is welded to knurled hub 31f while baffle 37 rests axially on bosses 313 formed on knurled hub 31f. The projections 313 are distributed around the cylindrical base of the knurled boss 31f. The inlet of the oil supply lines 34 is located between the projections 313.

the 8th and 9 Figure 12 shows a composite disk holder 30 according to a seventh embodiment of the invention which is similar in at least general operation to the sixth embodiment.

• - einen Drehmomenteingangsscheibenhalter 10, der zur drehbaren Verbindung mit einer Antriebswelle längs einer Drehachse X angeordnet ist;
• - eine Mehrscheibenbaugruppe mit Reibscheiben 22 und Druckplatten 21, die axial gestapelt sind und von dem Drehmomenteingangsscheibenhalter 10 in Drehung versetzt werden;
• - einen Drehmomentausgangsscheibenhalter 30, der als zusammengesetzter Scheibenhalter ausgeführt ist, der radial im Inneren der Mehrscheibenbaugruppe angeordnet und zur drehbaren Verbindung mit einer Abtriebswelle angeordnet ist;
• - eine mittlere Nabe 50 mit der Drehachse X, die fest mit dem Drehmomenteingangsscheibenhalter 10 verbunden ist, wobei die mittlere Nabe 50 einen zylindrischen Abschnitt 52 und mindestens einen in der mittleren Nabe 50 ausgebildeten Kühlölzuführungskanal 54d aufweist, der zumindest den zylindrischen Abschnitt 52 durchquert und axial gegenüber dem Drehmomentausgangsscheibenhalter 30 ausmündet.

As explained above, the E2 wet clutch has the following:

• a torque input disc holder 10 arranged for rotatable connection to a drive shaft along a rotation axis X;
• - a multiple disc assembly comprising friction discs 22 and pressure plates 21 stacked axially and rotated by torque input disc holder 10;
• a torque output disc holder 30, embodied as a compound disc holder, disposed radially inward of the multi-disc assembly and arranged for rotatable connection to an output shaft;
• - a central hub 50 with the axis of rotation X, which is integral with the torque input disc holder 10, the central hub 50 having a cylindrical portion 52 and at least one cooling oil supply channel 54d formed in the central hub 50, which traverses at least the cylindrical portion 52 and is axial against the torque output disc holder 30 opens out.

This seventh embodiment differs from that referred to in FIG 7 illustrated embodiment in that the baffle 37 of the composite disc holder 30 has at least one stiffening groove 374 arranged to bear on a planar annular surface of the knurled hub. In the present case, the guide plate has a number of grooves. The grooves 374 formed on the flank of the guide plate 37 cooperate with a flank of the knurled hub 31g. The baffle can be made by plastic injection molding.

The composite disc retainer 30 serves as a torque output disc retainer and includes an oil retention cavity 33 formed by the union of surfaces resulting from the knurled hub 31g, disc carrier 32g and baffle 37. Advantageously, the oil retention cavity 33 is formed from an outer surface of the knurled hub 31g, a flank of the baffle 37 and an inner surface 38 of the disk carrier 32g. The disc carrier 32g is welded to knurled hub 31g while baffle 37 rests axially on knurled hub 31g.

This seventh embodiment has the advantage that mainly raw, i.e. unmachined, surfaces of the knurled hub, baffle and disc carrier are used to form the oil supply lines and the oil retaining cavity. The manufacturing cost of such a composite disk holder is reduced.

The oil retaining cavity 33 is fed with cooling fluid via a plurality of oil feed ducts 34 angularly distributed about the X axis. Each of the oil supply lines 34 forms an arc with an axially extending line portion 36 and a radially extending line portion 35. In this seventh embodiment, the radially extending line portion 35 and the axially extending line portion 36 are formed by uniting the surfaces of the knurled boss 31g and the Guide plate 37 formed.

As in 8th 1, the baffle 37 is attached to the flank of the knurled boss 31g, which is aligned on the center boss 50 side of the second wet clutch E2. The baffle 37 is provided with an inner skirt 371 attached to the flank of the knurled hub 31g. The inner skirt 371 has a central bore 372 which partially forms the oil supply lines 34 . The baffle 37 also has internal splines 377 which at least partially abut the knurled hub 31g, with the available clearance between the teeth of the internal splines 377 and the knurled hub 31g forming the axially extending conduit section 36. The internal toothing 377 forms the central bore 372. In the example shown, the internal toothing 377 comprises three teeth angularly distributed around the X axis.

The composite disk holder 30 is axially arranged between the output disk holder 13 of the first clutch E<b>1 and the cylindrical portion 52 of the center hub 50 . The assembled disc holder 30 is axially arranged between two thrust bearings 60,70. A first thrust bearing 70 is axially interposed between the center hub 50 and the composite disk retainer 30 . The baffle 37 has a flat surface 376 which is arranged to support the first thrust bearing 70 . The flat surface 376 is, for example, an annular surface. A second thrust bearing 60 is interposed axially between the output disc holder 13 of the first clutch E<b>1 and the composite disc holder 30 . For this purpose, the knurled hub 31g has a machined first thrust bearing bearing surface 302 in which the second thrust bearing 60 is accommodated. The first bearing surface 302 of the thrust bearing 60 is arranged axially opposite to the flat surface 376 of the guide plate 37 .

To adjust the equalizing pressure in the pressure equalizing chambers of the clutches E1, E2 and K0, a rolling plate 70a of the axial bearing 70 partially closes the cooling oil supply channel 54d. The amount of oil contained in the compensation chambers depends on the smallest inside diameter of the roller plate 70a, which partially closes the channel 54d.

As in 8th As shown, the thrust bearing 70 is fitted onto the cylindrical portion 52 of the center hub 50 . The rolling plate 70a has a cylindrical portion press-fitted into the cylindrical portion 52 . The cooling fluid is deflected in its flow by the smallest inner diameter of the roller plate 70a before entering the interior of the assembled disk holder 30 and thrust bearing 70.

In order to improve the efficiency of the cooling fluid distribution within the second clutch E2, openings 375 are arranged radially beyond the planar surface 376 of the baffle 37, which openings communicate directly with the oil retaining cavity 33. The part of the cooling fluid coming from the cooling oil feed channel 54d which enters the thrust bearing 70 exits the latter and flows into the oil retention cavity 33 via the openings 375. The openings 375 are distributed angularly about the axis X and between the grooves 374 of the baffle arranged. In this way, most of the cooling fluid coming from the central hub 50 is directed into the composite disc holder 30 and flows out into the multi-disc assembly of the second clutch E2.

On reading the above, it is apparent that the present invention proposes a wet triple clutch in which the clutches are arranged concentrically and radially in one and the same plane. The axial space requirement of such a wet-running triple clutch within a torque transmission chain is reduced. This wet triple clutch features a composite disc retainer in which the network of oil feed lines is easier to design and takes less time to manufacture.

However, the invention is not limited to the means and configurations described and shown here, but also extends to all equivalent means and configurations and to any technical combination involving such means operates. In particular, the shape of the assembled disc holder can be modified without affecting the invention, as long as these components ultimately perform the same functions as those described in this document.

In the claims, any reference sign in parentheses shall not be construed as a limitation of the claim.

QUOTES INCLUDED IN DESCRIPTION

This list of documents cited by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent Literature Cited

• EP 2517915 [0005]

Claims (19)

A composite disk retainer (30) for a wet clutch, comprising: - a knurled hub (31a, 31b, 31c, 31d, 31e, 31f, 31g) with the axis of rotation (X), which is provided with an internal knurling (310) for torque transmission, - a disk support (32a, 32b, 32c, 32d, 32e, 32f, 32g) made of sheet metal with a shape of revolution about the axis (X) and provided with external corrugations (320) arranged to cooperate with a multiple disk assembly, the disc carrier (32a, 32b, 32c, 32d, 32e, 32f, 32g) abutting axially on the knurled hub (31a, 31b, 31c, 31d, 31e, 31f, 31g), - at least one oil supply line (34), - an annular oil-retaining cavity (33) concentric with the axis (X) and formed at least by the union of surfaces emerging from the knurled hub and the disc carrier, the knurled hub forming wholly or partially the at least one oil feed duct (34). which opens into the oil retaining cavity (33) which is closed by the inner surface (38) of the disc carrier. Composite disc holder (30) according to claim 1 wherein the disc carrier (32a, 32b, 32c, 32d, 32e, 32f, 32g) has openings (39) formed on the outer corrugation (320) and arranged so that the oil contained in the oil retaining cavity (33) is drained wherein the openings (39) are distributed circumferentially about the axis (X) and are formed at the tooth tips of the outer serrations (320). Composite disc holder (30) according to claim 1 or 2 wherein the oil supply line (34) forms an arc with an axially extending line section (36) and a radially extending line section (35). Composite disc holder (30) according to claim 3 wherein the radially extending duct portion (35) is formed by boring the splined hub (31a, 31d) and the axially extending duct portion (36) is obtained by casting or forging directly integrally in the splined hub (31a, 31d). A composite disc retainer (30) as claimed in the preceding claim, wherein the oil retaining cavity (33) is defined in part by a circumferential groove formed on the outer periphery of the knurled boss (31a). Composite disc holder (30) according to claim 3 wherein the radially extending duct portion (35) and the axially extending duct portion (36) are formed by uniting the surfaces of the splined hub (31b) and the disk carrier (32b). Composite disc holder (30) according to claim 3 , wherein the radially extending duct portion (35) is formed by joining the surfaces of the knurled hub (31c) and the disc carrier (32c) and the axially extending duct portion (36) is formed only by the disc carrier (32c), e.g hole traversing the disc carrier. Composite disc holder (30) according to claim 1 or 2 with an annular baffle (37) which is attached to the knurled hub (31d, 31e, 31f, 31g) and has external teeth (373) which mate with the profile of the inner surface (38) of the disk carrier (32d, 32e, 32f, 32g), the oil retaining cavity (33) being formed by the union of surfaces consisting of the knurled hub (31d, 31e, 31f, 31g), the disc carrier (32d, 32e, 32f, 32g) and the baffle (37) emerge. Composite disc holder (30) according to claim 8 , wherein the oil supply pipe (34) forms an arc with an axially extending pipe section (36) formed only by the knurled boss (31e) and a radially extending pipe section (35) formed by merging the surface of the knurled boss (31e) and the guide plate (37), for example by a groove (351) formed in the corrugated hub (31e), which cooperates with a flank of the guide plate (37). Composite disc holder (30) according to claim 8 , wherein the oil supply pipe (34) forms an arc with an axially extending pipe section (36) formed by merging the surfaces of the knurled hub (31f) and the baffle (37) and a radially extending pipe section (35), which is formed by uniting the surfaces of the corrugated hub (31f) and the baffle (37), eg by a groove (351) formed in the corrugated hub (31f) which cooperates with a flank of the baffle (37), or eg by at least one groove (374) formed on the flank of the guide plate (37) and cooperating with a flank of the knurled hub (31g). Composite disc holder (30) according to claim 10 , wherein the guide plate (37) has a flat surface (376) which is arranged to support an axial bearing, for example an annular surface, and openings (375) disposed radially beyond said planar surface, said openings (375) communicating directly with said oil retention cavity (33). Composite disc holder (30) according to claim 11 the baffle (37) having grooves (374), the openings (375) being angularly distributed about the axis (X) and being located between the grooves (374) of the baffle (37). Composite disc holder (30) according to claim 10 , the baffle (37) having internal teeth (377) at least partially abutting the splined hub (31g), the clearance available between the teeth of the internal splines (377) and the splined hub (31g) defining the axially extending conduit section (36) forms. Wet clutch (E2) for a torque transmission system, comprising: - a torque input disc holder (10) arranged for rotatable connection to a drive shaft along an axis of rotation (X); - a multiple disc assembly comprising friction discs (12, 22) and pressure plates (11, 21) stacked axially and rotated by the torque input disc holder (10); - a composite disc holder (30) according to any one of the preceding claims disposed radially inward of the multiple disc assembly and arranged for rotatable connection to an output shaft. Wet clutch (E2) according to the preceding claim, which has a central hub (50) with the axis of rotation (X), the central hub (50) having: a cylindrical section (52), a flange (53) radially extending from the cylindrical portion (52) and fixedly connected to the torque input disk holder (10), and at least one cooling oil feed duct (54d) formed in the central hub (50), crossing at least the cylindrical portion (52) and opening out axially opposite the oil feed duct (34) of the composite disc-holder (30), so that the oil coming from the central hub be directed into the knurled hub of the composite disc holder (30) and discharge into the multi-disc assembly. Wet clutch (E2) according to the preceding claim, wherein the central hub (50) has a plurality of cooling oil feed passages (54d) and the composite disc holder (30) has a plurality of oil feed passages (34) angularly distributed about the axis (X), the outlets the cooling oil supply channels (54d) are arranged on a diameter which essentially corresponds to the arrangement diameter of the inlets of the oil supply lines (34). Wet clutch (E2) after claim 15 or 16 wherein a thrust bearing (70) is disposed axially between the center hub (50) and the composite disk holder (30), the thrust bearing (70) defining the cooling oil supply passage or passages (54d) axially opposite to the oil supply passage or passages ( en) (34) of the composite disk holder (30) open out, partially closed. Wet dual clutch (E1, E2) for a torque transmission system, comprising: - a first clutch (E1); and - a second clutch (E2) of the wet clutch type Claim 14 or 15 , which is arranged radially inside the first clutch (E1), the first and the second clutch (E1, E2) for selectively coupling a drive shaft to a first output shaft and a second output shaft, e.g. a first and a second transmission shaft (A1, A2 ) are controlled, and wherein the central hub (50) of the second clutch (E2) and the first clutch (E1) is common. A wet triple clutch for a torque transmission system having a multi-disc clutch type torque disconnect clutch (K0) controlled to selectively couple a drive shaft to an electric machine and a wet dual clutch (E1, E2) according to the preceding claim, wherein the torque disconnect clutch ( K0) is arranged radially beyond the wet double clutch (E1, E2).

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