DE102018116587A1 - Transmission device for a hybrid vehicle - Google Patents

Abstract

The invention relates to a device for transmitting torque, in particular for a motor vehicle, comprising:
a torque input element (2) which is suitable for non-rotatably coupling to a crankshaft of an internal combustion engine,
a first torque output element (5) which is suitable for non-rotatably coupling to a first input shaft (6) of a transmission,
- A rotary electric machine (12) comprising a rotor (13) which is arranged in the direction of torque transmission between the input member (2) and the first output member (5), wherein the rotor selectively connected to the input member by an input clutch (15) wherein the rotor is selectively connected to the first output member by a first output clutch (16),
a first stage of springs (31) between the input member and the rotor, characterized in that the apparatus includes a rotor support (35) comprising a substantially transverse partition wall (36) disposed axially between the input clutch (15 ) and the first output clutch (16) is arranged.

Description

The present invention relates to the field of transmissions for motor vehicles. It relates in particular to a transmission device which is intended to be arranged in the drive train between an internal combustion engine and a transmission.

In particular, the invention relates to the transmission devices for a hybrid type of motor vehicle in which an electric machine is also disposed between the engine and the transmission.

In the prior art transmission units are known, which are arranged between the transmission and the internal combustion engine and comprise an electric machine and an engine-side clutch, which makes it possible to rotatably couple the crankshaft of the internal combustion engine with the rotor of the electric machine. So it is possible to turn off the engine each time the vehicle stops and restart thanks to the electric machine. The electric machine may also be an electric brake or provide additional energy to the engine to assist or prevent it from stalling. The electric machine can also ensure the drive of the vehicle. When the engine is rotating, the electric machine plays the role of an alternator. Such a transmission unit may also connect the electric machine to the transmission through two separate torque paths, each comprising an output clutch and a transmission input shaft. Such a device is particularly in the document DE 10 2007 003 107 A1 disclosed.

In the document DE 10 2007 003 107 A1 The device comprises three separate actuators for the actuation of the clutches. These actuators are here radially stacked and offset with respect to the clutches, which makes the device less compact, especially in the radial direction. Moreover, the supply of oil to the farthest actuator of the rotary axis of the apparatus requires a complex distance which must be covered. Finally, the intermediate piece has a complex shape, in particular between the input and output clutches. Finally, the oil supply takes place on the combustion engine side in a crowded environment.

In this device, it is also not intended to arrange a torsion damper in the interior of the electric machine. Such devices are optionally less powerful in terms of filtering the rotational irregularities or axially bulky when such a damper is provided upstream between the device and the internal combustion engine.

The object of the invention is to propose a device for torque transmission, which makes it possible to meet the requirements of an axial compactness, but without affecting the filtering of the torsional vibrations.

• - ein Drehmomenteingangselement, das geeignet ist, drehfest mit einer Kurbelwelle eines Verbrennungsmotors gekoppelt zu sein,
• - ein erstes Drehmomentausgangselement, das geeignet ist, drehfest mit einer ersten Eingangswelle eines Getriebes gekoppelt zu sein,
• - eine elektrische Drehmaschine, umfassend einen Rotor, der in Richtung der Drehmomentübertragung zwischen dem Eingangselement und dem ersten Ausgangselement angeordnet ist, wobei der Rotor selektiv mit dem Eingangselement durch eine Eingangskupplung verbunden ist, wobei der Rotor selektiv mit dem ersten Ausgangselement durch eine erste Ausgangskupplung verbunden ist,
• - eine erste Stufe von Federn zwischen dem Eingangselement und dem Rotor,

dadurch gekennzeichnet, dass die Vorrichtung einen Träger des Rotors umfasst, umfassend eine im Wesentlichen quer verlaufende Trennwand, die axial zwischen der Eingangskupplung und der ersten Ausgangskupplung angeordnet ist.The invention achieves this according to one of its aspects with the aid of a device for transmitting torque, in particular for a motor vehicle, comprising:

• a torque input element adapted to be non-rotatably coupled to a crankshaft of an internal combustion engine,
• a first torque output element adapted to be non-rotatably coupled to a first input shaft of a transmission,
• a rotary electric machine comprising a rotor disposed in the direction of torque transmission between the input member and the first output member, the rotor being selectively connected to the input member through an input clutch, the rotor being selectively connected to the first output member through a first output clutch is
• a first stage of springs between the input member and the rotor,

characterized in that the device comprises a support of the rotor comprising a substantially transverse partition disposed axially between the input clutch and the first output clutch.

Such a rotor carrier makes it possible to guide the rotor of the electric machine effectively. Such a rotor carrier makes it possible to establish the functional connection between the input clutch and the output clutches.

According to one aspect of the invention, the partition may transmit the torque between the input member and the first output member. The bulkhead transmits the torque from the engine to the transmission. The bulkhead also transmits torque from the electric motor to the transmission in a forward direction of torque transmission or to the engine in a reverse direction of torque transmission.

In one aspect of the invention, the input clutch is of the multi-disc type. After one Another aspect is the first multi-disc type output clutch.

According to one aspect of the invention, the partition may form a counter support for the input clutch and / or for the first output clutch.

The partition wall makes it possible to use no specific part in order to realize the counter-supports of the multi-plate units.

The mating support function makes it possible to limit the axial displacement of the multi-disc unit in response to the operating force. The counter-support is claimed in the engaged position of the coupling.

In particular, the partition may form a counter support for the input clutch and for the first output clutch.

The counter support can be applied in a localized zone of the coupling, in particular a middle zone, so that the coupling does not bend in response to the actuating force.

The counter supports can be elevations provided in the partition wall. They can also be formed by an attached element. The counter supports preferably extend over the entire circumference. The backrests may be continuous throughout the circumference or may include discrete locations distributed around a circumference.

In one aspect of the invention, the carrier may be carried by the first output member. The carrier may be centered on the first output member.

For the purposes of the application there is no torque transfer at the interface when one part is carried by another.

A plurality of axially offset ball bearings, in particular two, may be provided between the carrier and the first output member. As a variant, plain bearings can be used.

As a variant, the carrier may be carried by the input member. The input member in this case comprises an axial skirt disposed between the first output member and the carrier. The ball bearings are now provided between this skirt and the rotor arm.

According to a further aspect of the invention, the carrier may comprise an inner sleeve for the arrangement of an actuating element of the input clutch.

The inner sleeve may be provided in the extension of an inner end of the partition. The sleeve can be connected in one piece with the partition wall or with this in particular by welding.

The actuator may comprise an actuation chamber bounded in part by the inner sleeve and by a force transmitting member which is axially movable relative to the inner sleeve and adapted to cooperate with the input clutch. The force transmitting member is movable under the effect of the pressure of the fluid in the actuating chamber. This actuator is also called "piston type" actuator.

Connected to the actuation chamber, the actuation element may comprise a compensation chamber, which is bounded in part by the force transmission element and by the inner sleeve. This chamber can also be tight.

The power transmission element may form a barrier between the two chambers. The compensation chamber is intended to resist the forces associated with the pressure of a hydrodynamic oil of the actuation chamber on the transfer element. The power transmission member may also be axially displaced by relative oil pressure variation of the actuating and balancing chambers.

The ball bearings can be arranged axially on either side of the actuating chamber, preferably on both sides of the actuating and compensation chambers.

According to another aspect of the invention, the first output element may be centered on the input element.

The first output member may include a first flange which is non-rotatably connected to, for example, a spline connection with a first output shaft, which may be the first input shaft of the transmission.

The input member may comprise a primary inertia member adapted to be attached to a crankshaft nose, for example by a plurality of screws.

A centering ring may be provided between the crankshaft lobe and the first output shaft to readjust the mounting clearance between the engine and the transmission.

According to a further aspect of the invention, the first output network comprises a fluid line network for supplying the actuating element of the input clutch.

The fluid line network may include a first series of axial channels, at least one, circumferentially offset, disposed in the first output shaft, and opening into a same circumferential groove to provide fluid to the actuating chamber of the input clutch actuator. The first output shaft is thus a hollow shaft.

Opposite the circumferential groove, openings are provided in the inner sleeve for passage of the fluid to the actuation chamber. When the rotor carrier is supported by the input member, openings are also provided in the axial skirt opposite to the circumferential groove.

According to another aspect of the invention, the fluid line network may also include a second series of axial channels, at least one, circumferentially offset and opening into a same circumferential groove in the region of the input coupling for the passage of a cooling fluid of the input clutch.

Finally, according to another aspect of the invention, the fluid line network may also include a third series of axial channels, at least one, circumferentially offset and opening into a same circumferential groove to provide fluid to the compensation chamber of the input clutch actuator. According to another aspect of the invention, the cooling and balance fluids may be identical.

The rows of axial channels may be circumferentially offset two and two.

Sealing rings, such as plastic, may be provided on either side of each circumferential groove.

According to a further aspect of the invention, the device may also comprise a second torque output element which is adapted to be non-rotatably coupled to a second input shaft of the transmission.

The second output member may be disposed in parallel with the first torque output member in the direction of torque transmission, the rotor being selectively connected to the second output member through a second output clutch. The second output clutch is of the multi-disc type. The second clutch may be on the same side as the first output clutch with respect to the bulkhead.

The second output member may include a second flange disc rotatably connected, for example by a spline connection, to a second output shaft, which may be the second input shaft of the transmission.

The second output shaft may be coaxial with the first output shaft, in particular, it may be hollow and surround the first output shaft.

According to a further aspect of the invention, the support may comprise a secondary partition disposed substantially axially on the other side of the first and second output couplings with respect to the partition wall. The output couplings are thus axially framed by two partitions of the rotor carrier.

The secondary bulkhead may extend radially inwardly through a secondary inner sleeve for the placement of a first actuator and a second actuator of the first and second output clutches, respectively. The sleeve is thus used shared for the two actuators.

The secondary sleeve can be carried by a fixed manifold. The manifold may include a fluid line network for the fluid supply of the first and second actuators.

The actuators may comprise an actuating chamber bounded in part by the secondary sleeve and by a power transmission element which is axially movable relative to the secondary sleeve and adapted to cooperate with one of the output clutches.

Associated with the actuation chamber, each actuation element may comprise a compensation chamber bounded in part by the force transfer element and by the secondary sleeve. This chamber may also be tight, at least radially outward.

The power transmission element may form a barrier between the two chambers. The compensation chamber is designed to resist the effects associated with the hydrodynamic oil pressure of the actuation chamber on the transfer element. The power transmission element can thus be displaced axially by relative oil pressure variation of the actuating and compensation chambers.

The actuation chambers of each of the actuators may be on a same radial Be arranged height, which makes it possible to release the space under the rotor to use here, for example, the first spring stage.

Like the fluid conduit network of the first output member, the fluid conduit network of the manifold for each actuation chamber may include a first series of axial channels, at least one, circumferentially offset and opening into a same circumferential groove also provided in the manifold around the actuation chambers to supply with fluid.

Opposite the circumferential groove are provided openings in the secondary sleeve for passage of the fluid to the actuation chamber.

The fluid line network may also include a second series of axial channels, at least one, circumferentially offset and opening into a same circumferential groove for passage of a cooling fluid of the output couplings. Openings in the secondary sleeve may be provided in the secondary bulkhead or at the foot of the bulkhead for passage of the cooling fluid.

The fluid line network may also comprise, for each compensation chamber, a third series of channels, at least one, circumferentially offset and opening into a same circumferential groove for providing fluid to the compensation chamber.

The cooling and balance fluids may be identical.

Preferably, the second and third rows of axial channels are identical and there is only a single circumferential groove for the cooling fluid and the balance fluid.

The axial channels may be offset in the circumferential direction two and two.

Sealing rings, such as plastic, may be provided on either side of each circumferential groove.

The distributor thus has a ribbed outer periphery formed by the succession of circumferential grooves.

The secondary partition may be framed by the actuation chambers of each of the actuators.

Needle bearings may be provided between the secondary sleeve and the manifold, preferably two, located axially on either side of the actuation chambers so as to be at the level of the axial ends of the secondary sleeve.

According to another aspect of the invention, the first and second output clutches are radially stacked. This makes it possible to improve the axial compactness of the device.

The first output clutch may be radially outside the second output clutch.

The power transmission member of the first output clutch may have an outer periphery provided with a plurality of fingers having an axial orientation and each passing through the opening through the secondary partition wall.

The fingers are suitable and intended to cooperate with the first clutch.

The secondary partition may form a counter support for the second output clutch to limit the axial displacement of the multi-plate unit in response to the actuating force. This counter support may be an increase of the secondary partition, it may also be formed by an attached element. The counter-support preferably extends over the entire circumference.

• - einen Eingangsscheibenträger, der in Drehung von dem Eingangselement angetrieben wird, was die Eingangskupplung einerseits betrifft, und drehfest mit dem Rotorträger verbunden ist, was die erste und zweite Ausgangskupplung andererseits betrifft,
• - einen Ausgangsscheibenträger, der drehfest mit dem Rotorträger verbunden ist, was die Eingangskupplung einerseits betrifft, und mit dem ersten und zweiten Ausgangselement verbunden ist, was die erste bzw. zweite Ausgangskupplung andererseits betrifft,
• - eine Mehrscheibeneinheit, umfassend mindestens eine Reibungsscheibe, die drehfest mit einem der Eingangs- und Ausgangsscheibenträger verbunden ist, mindestens zwei Platten, die jeweils beiderseits jeder Reibungsscheibe angeordnet und drehfest mit dem anderen der Eingangs- und Ausgangsscheibenträger verbunden sind, und Reibbeläge, die zwischen den Platten und einer Reibungsscheibe angeordnet sind, wobei die Kupplung eine ausgerückte Position und eine eingerückte Position beschreibt, in der die Platten und die Reibungsscheibe die Reibbeläge einklemmen, um ein Drehmoment zwischen den Eingangs- und Ausgangsscheibenträgern zu übertragen.

According to another aspect of the invention, each of the couplings of the device may comprise:

• an input disk carrier which is driven in rotation by the input member as far as the input clutch is concerned, and is non-rotatably connected to the rotor carrier with respect to the first and second output clutches on the other hand,
• an output disk carrier rotationally fixedly connected to the rotor carrier with respect to the input clutch, on the one hand, and being connected to the first and second output members, with respect to the first and second output clutches, respectively,
• a multi-disc unit comprising at least one friction disc non-rotatably connected to one of the input and output disc carriers, at least two plates each disposed on either side of each friction disc and non-rotatably connected to the other of the input and output disc carriers, and friction pads interposed between the Plates and a friction disc are arranged, wherein the clutch describes a disengaged position and an engaged position in which the plates and the friction disc clamp the friction linings to transmit torque between the input and output disc carriers.

The pads can on the friction discs in particular by gluing, in particular by Rivets, in particular be attached by molding. As a variant, the pads are attached to the plates.

Each disk carrier can synchronize the entirety of the disks or the entirety of the friction disks in rotation. The disc carriers may include a cylindrical skirt on which the plates and the friction discs are mounted.

The plates and discs may cooperate with the disc carriers along one of their radial peripheries by positive engagement. The cylindrical aprons, the plates and the friction discs may be grooved, for example.

According to a further aspect of the invention, the plates for each clutch may be non-rotatably connected to the disk carrier which is rotatably connected to the rotor carrier. This makes it possible to form the counter supports for each coupling through the partitions which are connected to the rotor carrier.

According to a further aspect of the invention, the output disk carrier of the first output clutch is arranged radially inside and the output disk carrier of the second output clutch is arranged radially outward.

The clutches can be wet or dry clutches. Preferably, the clutches comprise between two to seven friction discs, preferably four or five friction discs.

The clutches may be of the "normally open" type, a force must be exerted by the force transmitting elements to transmit a torque.

The power transmission means may exert an axial force on the multi-disk units to displace the disks to the disks, in particular to an end plate of the multi-disk unit. The actuation is thus of the "pressed" type.

According to another aspect of the invention, the first spring stage is arranged between the input element and the output element in the direction of torque transmission. The first spring stage can be arranged in the interior of the electric machine, in particular radially between the input clutch and the rotor. The first spring stage may also be called a torsion damper device. The first spring stage or torsion damper device is used to filter the rotational irregularities of the internal combustion engine. The torsion damper device or the first spring stage is located radially above the input clutch.

According to a further aspect of the invention, a second spring stage between the input member and the rotor may be provided in the direction of the torque transmission, wherein the two spring stages are arranged in series.

The two spring stages may be located upstream of the input clutch. The two spring stages may be provided radially between the input clutch and the rotor. The two spring stages can be arranged at the same radial height.

According to a further aspect of the invention, a pendulum damping device can be arranged between the two spring stages. As a variant, the pendulum damping device may be arranged between the first spring stage and the input clutch, if only one spring stage is provided.

An intermediate member is disposed between the spring stages to transmit the torque and to synchronize the springs.

The pendulum damping device may comprise a pendulum carrier connected to the intermediate element, at least one pendulum body movable relative to the carrier, and at least one rolling element connected to a rolling track connected to the beam and to at least one rolling track connected to the pendulum body is, cooperates.

The pendulum damping device may comprise a plurality of pendulum bodies which are regularly arranged on a circumference of the rotation axis. Each pendulum body can interact with two rolling elements. Each pendulum body may comprise two pendulum masses, which are arranged on either side of the carrier. The pendulum bodies can be arranged radially outside the springs, preferably at a same radial height as the stator.

The pendulum carrier may be made in one piece with the intermediate element, or they may be connected by rivets, for example.

The intermediate element can be carried by the input element. A ball bearing may be provided between the intermediate element and the input element.

According to an arrangement variant of the second spring stage, the input clutch may be arranged in the direction of the torque transmission between the two spring stages.

According to another aspect of the invention, the electric machine can be a Be synchronous machine with permanent magnets. Such a machine has a large diameter, which is favorable for the installation of the parts of the device.

• - 1 ist eine Axialschnittansicht eines Beispiels der erfindungsgemäßen Vorrichtung,
• - 2 ist eine Axialschnittansicht nach einem zweiten Beispiel der Vorrichtung, und
• - 3 ist eine Axialschnittansicht nach einem dritten Beispiel der Erfindung.

The invention will be better understood, and further objects, details, features and advantages thereof will become more apparent from the following description of several specific embodiments of the invention, given by way of illustration and not limitation and with reference to the accompanying drawings.

• - 1 is an axial sectional view of an example of the device according to the invention,
• - 2 is an axial sectional view according to a second example of the device, and
• - 3 is an axial sectional view according to a third example of the invention.

• - ein Drehmomenteingangselement 2, das geeignet ist, drehfest mit einer Kurbelwelle 3 eines Verbrennungsmotors gekoppelt zu sein,
• - ein erstes Drehmomentausgangselement 5, das geeignet ist, drehfest mit einer ersten Eingangswelle 6 eines Getriebes gekoppelt zu sein,
• - ein zweites Drehmomentausgangselement 8, das geeignet ist, drehfest mit einer zweiten Eingangswelle 9 des Getriebes gekoppelt zu sein.

With reference to 1 is a device for torque transmission 1 to see, comprising:

• - A torque input element 2 , which is suitable rotatably with a crankshaft 3 to be coupled to an internal combustion engine,
• a first torque output element 5 , which is suitable rotatably with a first input shaft 6 coupled to a transmission,
• a second torque output element 8th , which is suitable rotatably with a second input shaft 9 coupled to the transmission.

In the example in question, the second output element 8th parallel to the first output element 5 arranged in the direction of torque transmission.

The device also includes an electric lathe 12 comprising a rotor 13 in the direction of torque transmission between the input element 2 on the one hand and the first output element 5 and the second output element 8th is arranged.

• - mit dem Eingangselement 2 durch eine Mehrscheiben-Eingangskupplung 15,
• - mit dem ersten Ausgangselement 5 durch eine erstes Mehrscheiben-Ausgangskupplung 16, und
• - mit dem zweiten Ausgangselement 8 durch eine Mehrscheiben-Ausgangskupplung 17.

In the example in question is the rotor 13 selectively connected:

• - with the input element 2 through a multi-disc input clutch 15 .
• - with the first output element 5 through a first multi-plate output clutch 16 , and
• - With the second output element 8th through a multi-disc output clutch 17 ,

The first transmission input shaft 6 is non-rotatable with the crankshaft 3 coupled and is driven by this in rotation when the first clutch 15 and the first output clutch 16 are arranged in a so-called engaged position. In this configuration, the rotor can 13 also provide an excess of energy to the transmission.

The first transmission input shaft 6 is non-rotatable with the rotor 13 coupled and driven by this in rotation when the first clutch 15 is set in a so-called disengaged position and the first output clutch 16 is set in the engaged position. The first gear shaft is now driven only by the rotor. In this configuration, the electric machine may also act as a brake and be in an energy recovery mode.

In an analogous way, the second transmission input shaft 9 with the crankshaft 3 rotatably coupled and is driven by this in rotation when the first clutch 15 and the second output clutch 17 are arranged in a so-called engaged position.

The second transmission input shaft 6 is non-rotatable with the rotor 13 coupled and driven by this in rotation when the first clutch 15 is arranged in a so-called disengaged position and the first output clutch 16 is arranged in the engaged position. The second gear shaft is now driven only by the rotor.

If the first and the second output clutch 16 . 17 In the disengaged configuration, and the input clutch is in the engaged configuration, the rotor can 13 be driven by the internal combustion engine. The electric motor is now in an energy recovery mode.

Of course, each coupling may take on any configuration between the engaged configuration and the disengaged configuration.

In the entirety of referring to the 1 to 3 Examples considered are the first output clutch 16 intended to adjust the odd gears of the transmission, and is the second output clutch 17 intended to adjust the straight gears and the reverse gear of the transmission. Alternatively, those from the first output clutch 16 and the second output clutch 17 assumed courses are turned over in each case.

The clutches are intended to alternatively transmit a so-called input power - a torque and a rotational speed - of the internal combustion engine to one of the two transmission input shafts, depending on the respective configuration of each output clutch 16 and 17 and the input clutch 15 ,

The output couplings 16 . 17 are intended not to be in the same indented configuration at the same time. On the other hand, they can be set up in their disengaged position at the same time.

In the example in question are the output couplings 16 . 17 stacked radially, the first output clutch is radially outward.

In the example in question, the input element comprises 2 a primary inertia element 20 that on a crankshaft nose 21 through a variety of screws 23 , for example, on the entire circumference of the axis of rotation X of the device 1 are regularly distributed, is attached. The primary inertia element extends radially to the periphery of the electric machine 12 , in particular to the periphery of a stator 14 the electric machine. The primary inertia element 20 its is a revolution section located on the side of the internal combustion engine (not shown).

In the example in question, the first and second output elements comprise 5 . 8th a first and a second flange disc 25 . 28 formed by a spline connection with the first and second input shaft 6 . 9 the transmission is connected. The second input shaft 9 is hollow and surrounds the first input shaft 6 ,

In the example in question is the electric machine 12 a synchronous machine with permanent magnets. The stator 14 Being firm is outside the rotor 13 , The electric machine 12 also includes a position sensor of the rotor 30 , in particular a contactless sensor.

In the example in question, the device comprises 1 also a torsion damper device. The torsion damper device serves to filter the rotational irregularities of the internal combustion engine. The torsion damper device comprises a first spring stage 31 and a second spring stage 32 , which is arranged in series with the first spring stage. The two spring stages are between the input element 2 and the rotor 13 in particular upstream of the input clutch 15 arranged in the direction of torque transmission. In a variant, not shown, the input clutch may be arranged between the two spring stages.

In the example in question, the torsional damper device is arranged radially between the input clutch and the rotor. The torsion damper device is disposed radially above the input clutch. An intermediate element 34 is arranged between the two stages to transmit the torque and to synchronize the springs. The intermediate element 34 here has a cross-section substantially in the form of a "Y".

In the example in question, the springs are curved springs which are regularly arranged on a circumference of the axis X. The spring stages are here offset axially from each other, but it is conceivable that the first and the second group of springs are at a same axial height. In the circumferential direction, a portion of the intermediate element is now arranged between each spring of the first group and each spring of the second group. In this configuration, the springs can be straight springs.

In the example in question, the spring stages comprise 31 . 32 four springs each.

In the example in question, the device comprises 1 also a rotor carrier 35 for its axial hold. This carrier 35 in particular comprises a substantially transverse partition wall 36 that is axially between the input clutch 15 on the one hand and the first and second output clutches 16 . 17 on the other hand is arranged.

The carrier 35 also includes a grooved outer sleeve 37 which cooperates with the rotor whose inner surface is also grooved. A holding means in translation 38 For example, a snap ring is also between the rotor 13 and the partition 36 provided to properly position the rotor relative to the stator when assembling the rotor with the rest of the device 1 to enable.

In the example in question, the carrier comprises 35 also a secondary partition 40 that are substantially axially on the other side of the first and second output couplings with respect to the dividing wall 36 is arranged. The output couplings 16 . 17 are thus axially of two partitions of the carrier 35 framed.

For greater clarity, the numerals have been added to the couplings of the device 1 are assigned to 2 transfer. There is no structural difference in comparison with the one in 1 considered example, as far as the clutches are concerned.

• - einen radial äußeren Eingangsscheibenträger 42, der in Drehung von dem Eingangselement 2 unter Vermittlung der Federstufen 31, 32 angetrieben wird,
• - einen radial inneren Ausgangsscheibenträger 43, der drehfest mit dem Träger 35 verbunden ist,
• - eine Mehrscheibeneinheit 44, umfassend eine Vielzahl von Reibungsscheiben, die drehfest mit dem Eingangs- und Ausgangsscheibenträger verbunden sind, mindestens zwei Platten, die jeweils beiderseits jeder Reibungsscheibe angeordnet und mit dem Ausgangsscheibenträger drehfest verbunden sind, und Reibbeläge, die zwischen den Platten und einer Reibungsscheibe angeordnet sind.

In the example in question, the input clutch comprises 15 :

• - A radially outer input disk carrier 42 which is in rotation from the input element 2 under the mediation of spring stages 31 . 32 is driven,
• - a radially inner output disk carrier 43 , which rotates with the carrier 35 connected is,
• - a multi-disc unit 44 comprising a plurality of friction discs rotatably connected to the input and output disc carrier, at least two plates each disposed on either side of each friction disc and rotationally connected to the output disc carrier, and friction pads disposed between the plates and a friction disc.

• - einen radial äußeren Eingangsscheibenträger 46, der drehfest mit dem Träger 35 verbunden ist,
• - einen radial inneren Ausgangsscheibenträger 47, der mit der ersten Flanschscheibe 25 verbunden ist, insbesondere mit der Flanschscheibe aus einem Stück ist,
• - eine Mehrscheibeneinheit 48, umfassend eine Vielzahl von Reibungsscheiben, die drehfest mit dem Eingangs- und Ausgangsscheibenträger verbunden sind, mindestens zwei Platten, die jeweils beiderseits jeder Reibungsscheibe angeordnet und mit dem Ausgangsscheibenträger drehfest verbunden sind, und Reibbeläge, die zwischen den Platten und einer Reibungsscheibe angeordnet sind.

In the example in question, the first output clutch comprises 16 :

• - A radially outer input disk carrier 46 , which rotates with the carrier 35 connected is,
• - A radially inner output disk carrier 47 that with the first flange 25 is connected, in particular with the flange is in one piece,
• - a multi-disc unit 48 comprising a plurality of friction discs rotatably connected to the input and output disc carrier, at least two plates each disposed on either side of each friction disc and rotationally connected to the output disc carrier, and friction pads disposed between the plates and a friction disc.

• - einen radial inneren Eingangsscheibenträger 49, der drehfest mit dem Träger 35 verbunden ist,
• - einen radial äußeren Ausgangsscheibenträger 50, der mit der zweiten Flanschscheibe 28 verbunden ist, insbesondere mit der Flanschscheibe aus einem Stück ist,
• - eine Mehrscheibeneinheit 51, umfassend eine Vielzahl von Reibungsscheiben, die drehfest mit dem Eingangs- und Ausgangsscheibenträger verbunden sind, mindestens zwei Platten, die jeweils beiderseits jeder Reibungsscheibe angeordnet und mit dem Ausgangsscheibenträger drehfest verbunden sind, und Reibbeläge, die zwischen den Platten und einer Reibungsscheibe angeordnet sind.

In the example in question, the second output clutch comprises 17 :

• - A radially inner input disk carrier 49 , which rotates with the carrier 35 connected is,
• - A radially outer output disk carrier 50 that with the second flange disc 28 is connected, in particular with the flange is in one piece,
• - a multi-disc unit 51 comprising a plurality of friction discs rotatably connected to the input and output disc carrier, at least two plates each disposed on either side of each friction disc and rotationally connected to the output disc carrier, and friction pads disposed between the plates and a friction disc.

In their engaged configuration, the clutches jam 15 . 16 . 17 , the plates and the friction disc, the friction linings to transmit torque between the input disc carrier and the output disc carrier.

Each of the multi-disc units 44 . 48 . 51 includes five discs with a friction pad on each side. Each unit also includes six plates, the plates defining the axial ends of the multi-disc unit.

In the example in question, each disk carrier synchronizes the entirety of the disks or the entirety of the friction disks as they rotate. Each disc carrier comprises a cylindrical skirt on which the plates and friction discs are mounted. The plates and discs cooperate with the disc carriers along one of their radial peripheries by positive engagement. The cylindrical aprons, the plates and the friction discs are grooved.

In the example in question are the disk carrier of the output couplings 47 . 50 opposite each other, there is no intervening part between them. The disk carrier of the first output clutch allows the rotary drive of the secondary partition 40 through the partition 36 , wherein this disc carrier the torque to the second output clutch 17 transfers.

In the example in question, the input disk carrier extends 50 the second clutch axially from the secondary partition 40 out.

In the example in question, the carrier comprises 35 also an inner sleeve 55 for the arrangement of an actuating element 56 the input clutch. This inner sleeve is located in the extension of an inner end of the partition 36 , The sleeve is here in one piece with the partition 36 , The numerical references associated with actuation of the clutches are also on 2 transfer.

In the example in question, the actuating element comprises 56 an actuation chamber 58 , in part from the inner sleeve 55 and a power transmission element 59 is limited, which is axially movable and suitable with respect to the inner sleeve, with the input clutch 16 cooperate, in particular with an end plate of the multi-disc unit 44 , The force transmitting member is movable under the effect of the pressure of the fluid in the actuating chamber. This actuator is also called "piston type" actuator.

An axial holding means 60 is provided to limit the movement of the actuating chamber, leaving only the power transmission element 59 moved axially. The axial holding means here comprises a retaining ring 61 and a reinforcing ring 62 ,

A means of return to open position 64 is also provided to reset the power transmission element when the pressure in the drive chamber is lower than a threshold. This return means is here a diaphragm spring, outside the actuation chamber 56 between the transmission element and a support element connected to the carrier 35 , in particular with the output disk carrier 43 , is connected, is arranged.

In the example in question, the first input shaft comprises 6 the transmission a fluid line network 66 for the supply of the actuating element 56 , The fluid line network comprises an axial channel 67 a first row, which is in a circumferential groove 68 flows to the actuation chamber 58 to supply with fluid.

Opposite the circumferential groove are openings, which are not visible in the sectional plane of the figures, in the inner sleeve 55 for the passage of the fluid to the actuation chamber 58 intended.

The fluid line network 66 Also includes a second series of axial channels, at least one offset in the circumferential direction and in a same circumferential groove 69 at the level of the input clutch for the passage of a cooling fluid of the input clutch open.

Three sealing rings 70 , For example, plastic, each circumferential groove are provided on both sides.

In the example in question, the secondary partition extends 40 radially inward through a secondary inner sleeve 71 for the arrangement of a first 72 and a second one 73 Actuating element of the first and the second output clutch 16 . 17 , The secondary sleeve 71 thus becomes for the two actuators 72 . 73 used shared.

In the example in question, the secondary sleeve 71 from a fixed distributor 74 carried. This distributor is concentric with the transmission input shafts. The distributor 74 includes a fluid line network 75 for fluid supply of the first and second actuators 72 . 73 ,

The actuators 72 . 73 each comprise an actuating chamber 76 . 77 , in part from the secondary sleeve 71 and a power transmission element 79 . 80 axially movable relative to the secondary sleeve and adapted to cooperate with one of the output clutches.

In the example in question, the power transmission element of the first output clutch 73 an outer periphery on, with a variety of fingers 82 equipped, which have an axial orientation and respectively through the secondary partition through an opening 83 pass. The finger 82 are suitable and intended to, with the first output clutch, in particular with an end plate of the multi-disc unit 44 to cooperate.

In an identical way as the actuator 56 the input clutch 15 The actuators each comprise a return means in the open position 84 respectively. 85 , and an axial holding means 86 . 87 in the same configurations as those of the input clutch actuator. In particular, the return means in the open position 84 The first output clutch is a diaphragm spring, which is between the secondary bulkhead 40 and the power transmission element 79 is arranged.

In the example in question, the actuation chambers 76 . 77 be arranged at a same radial height. The secondary partition 40 is from the actuation chambers 76 . 77 framed.

In the example in question, the fluid line network comprises 75 of the distributor an axial channel 110 which is in a circumferential groove 111 that in the distributor 74 is provided, opens to the actuating chamber 76 to supply the first output clutch with fluid. Other axial channels, in the circumferential direction to the axial channel 110 are offset and in the same circumferential groove 111 may define a first series of axial channels. Opposite the circumferential groove are openings which are not visible in the sectional plane of the figures in the secondary sleeve 71 for the passage of the fluid to the actuation chamber 76 intended.

Such an axial channel is not visible in the sectional plane of the figures, but the previous paragraph is also for the second output coupling 17 applicable.

The fluid line network may also include a second series of axial channels, at least one, circumferentially offset and in a same circumferential groove 113 for the passage of a cooling fluid of the output couplings 16 . 17 lead. Openings in the secondary sleeve may be provided in the secondary bulkhead or at the foot of the bulkhead for passage of the cooling fluid.

Four sealing rings 114 , For example, made of plastic, can be provided on either side of each circumferential groove.

In the example in question are two needle roller bearings 90 between the secondary sleeve 71 and the distributor 74 provided axially on both sides of the actuating chambers 76 . 77 intended.

In the example in question forms the secondary partition 40 a counter support 95 for the second output clutch 17 to the axial displacement of the multi-disc unit 51 in response to the operating force limit. The counter support 95 Here is an increase, which preferably extends over the entire circumference.

In the example in question forms the partition 36 a counter support 96 for the input clutch 15 and a counter support 97 for the first output clutch 16 , This partition makes it possible to avoid a specific part for the realization of the counter-supports of the multi-disc units.

The counter support is in a localized zone of the multi-disc units 44 . 48 applied.

The counter supports 96 . 97 are elevations of the dividing wall 36 which preferably extend over the entire circumference.

In the example in question, the first input shaft 6 on the entrance element 2 centered, in particular by means of a centering ring 92 that is between the nose of the crankshaft 21 and the first input shaft 6 is provided.

In the relevant examples of the 1 and 2 becomes the carrier 35 from the first input shaft 6 worn and is on the first transmission input shaft 6 centered. Two ball bearings 93 , which are axially offset, are provided, they axially frame the actuating chamber of the input clutch 15 and the radial channels 68 of the fluid line network. Camps 93 are "O-shaped" mounted to an axial displacement of the first transmission input shaft 6 to support.

In the example of the 3 becomes the carrier 35 from an axial apron 105 of the input element 2 worn between the inner sleeve and the first shaft 6 the transmission is arranged. The ball bearings 93 are now provided between this apron and the rotor arm. Openings are also in the axial apron 105 opposite to the circumferential groove associated with the actuating chamber and the cooling fluid.

In the example of the 3 are the inner sleeve 55 and the partition 36 two separate parts assembled by welding. Openings are also in the axial skirt opposite the openings 69 provided the sleeve.

What with reference to 1 is described for the description of 3 applicable, with the exception of the last two paragraphs.

Finally, the example in question differs 2 from that of 1 in that a pendulum damping device 98 between the two spring stages 31 . 32 is arranged. The pendulum damping device 98 includes a pendulum carrier 99 at least one pendulum body, which is movable with respect to the carrier, and at least one rolling element, which is connected to at least one Wälzbahn, which is connected to the carrier, and at least one Wälzbahn, which is connected to the pendulum body , cooperates.

The device may comprise a plurality of pendulum bodies which are regularly distributed on a circumference of the axis X. Each pendulum body can interact with two rolling elements. Each pendulum body comprises two pendulum masses 100 , on both sides of the carrier 99 are arranged.

In the example in question, the pendulum bodies are radially outside the springs, preferably at a same radial height as the stator 14 arranged.

The pendulum carrier 99 is here of two riveted to each other and to the intermediate element 34 formed welded parts. The intermediate element is from the input element 2 with the help of a rolling bearing 102 worn between the intermediate element 34 and the input element 2 is provided.

QUOTES INCLUDE IN THE DESCRIPTION

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

Cited patent literature

• DE 102007003107 A1 [0003, 0004]

Claims (11)

Device (1) for transmitting torque, in particular for a motor vehicle, comprising: - a torque input element (2) which is suitable for non-rotatably coupled to a crankshaft of an internal combustion engine, - a first torque output element (5) which is suitable with a rotationally fixed a rotary electric machine (12) comprising a rotor (13) arranged in the direction of torque transmission between the input member (2) and the first output member (5), the rotor is selectively connected to the input member through an input clutch (15), the rotor being selectively connected to the first output member by a first output clutch (16), - a first stage of springs (31) between the input member and the rotor, characterized in that the device comprises a support (35) of the rotor, comprising a substantially transverse dividing wall (36) is disposed axially between the input clutch (15) and the first output clutch (16). Device (1) for torque transmission to Claim 1 wherein the partition wall (36) forms a counter-support (86, 87) for the input clutch (15) and / or for the first output clutch (16). A torque transmission device (1) according to any one of the preceding claims, characterized in that the carrier (35) is carried by the first output member (5) or the input member (2). A torque transmitting device (1) according to any one of the preceding claims, wherein the carrier (35) comprises an inner sleeve (55) for the disposition of an input member (56) of the input clutch. Device (1) for transmitting torque according to one of the preceding claims, characterized in that the first output element (5) is centered on the input element (2). A torque transmitting apparatus (1) according to any one of the preceding claims, wherein the first output member (5) comprises a fluid line network (66) for supplying the input clutch actuator (56). Torque transmission device (1) according to any one of the preceding claims, characterized in that it also comprises a second torque output element (8) adapted to be non-rotatably coupled to a second input shaft (9) of a transmission, the second output element being in the direction of rotation the torque transmission is arranged parallel to the first torque output element (5), wherein the rotor (12) is selectively connected to the second output element by a second output clutch (17). A torque transmitting device (1) according to the preceding claim, characterized in that the carrier (35) comprises a secondary partition (40) substantially axially spaced on the other side of the first and second output clutches (16) with respect to the partition wall (35) 17), wherein the second partition wall (40) is arranged radially inward by a secondary inner sleeve (71) for the arrangement of a first actuating element (72) and a second actuating element (73) of the first and the second output clutches (16, 17 ), wherein the secondary sleeve (71) is carried by a fixed manifold (74), the manifold comprising a fluid line network (75) for fluidly supplying the first and second actuators. Device (1) for torque transmission to Claim 7 or 8th , characterized in that the first and second output clutches (16, 17) are stacked radially. Device (1) for transmitting torque according to one of the preceding claims, characterized in that a second spring stage (32) between the input member (2) and the rotor (13) is provided, wherein the two spring stages (31, 32) are arranged in series wherein the two spring stages are arranged upstream of the input clutch (15). Device (1) for torque transmission according to the preceding claim, characterized in that a pendulum damping device (98) between the two spring stages (31, 32) is arranged.

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