DE102020200886A1 - Drive system for a vehicle - Google Patents

Abstract

A drive system for a vehicle comprises a drive system input area (44) to be coupled to a drive unit (14), a drive system output area (62) to be coupled to a transmission arrangement (20), a start-up assembly (24), the start-up assembly (24) comprises a starting assembly input area (42) coupled to or providing the drive system input area (44) and a starting assembly output area (50) coupled to or providing the drive system output area (62), the starting assembly (24) in the torque transmission path between the start-up assembly input area (42) and the start-up assembly output area (50) comprises a hydrodynamic circuit (32) with a pump wheel (34) and a turbine wheel (38), an interruption coupling (26) in the torque transmission path between the turbine wheel (38) and the Start-up assembly output area (50), with the interruption clutch ( 26) the start-up assembly input area (42) is connected to the start-up assembly output area (50) for torque transmission and, when the interruption clutch (26) is in a disengaged state, the start-up assembly input area (42) is not connected to the start-up assembly output area (50), and an electric machine (28) coupled to the starting assembly output area (50) and / or the drive system output area (62).

Description

The present invention relates to a drive system for a vehicle having a drive system input area to be coupled to a drive unit and a drive system output area to be coupled to a transmission arrangement and an electric machine.

Such a drive system is from US 8,298,105 B2 famous. In this known drive system, a start-up assembly in the form of a hydrodynamic torque converter with an impeller connectable to a housing by means of a clutch and a turbine wheel arranged in an interior of the housing and coupled to an output area of the start-up assembly is used. A coupling acting between the pump wheel and the turbine wheel can bridge the hydrodynamic circuit built up with the pump wheel, the turbine wheel and a stator and thus provide a fixed mechanical torque transmission connection from the housing providing an input area of the start-up assembly to the output area of the start-up assembly. An electric machine is positioned outside the housing of the start-up assembly and is coupled to the pump wheel in order to transmit a drive torque to the output area of the start-up assembly and thus also an output area of the drive system via the pump wheel, the clutch acting between the pump wheel and the turbine wheel and the turbine wheel.

It is the object of the present invention to provide a drive system for a vehicle, in which increased efficiency in operation is achieved with efficient utilization of installation space.

• - einen mit einem Antriebsaggregat zu koppelnden Antriebssystem-Eingangsbereich,
• - einen mit einer Getriebeanordnung zu koppelnden Antriebssystem-Ausgangsbereich,
• - eine Anfahrbaugruppe, wobei die Anfahrbaugruppe einen mit dem Antriebssystem-Eingangsbereich gekoppelten oder diesen bereitstellenden Anfahrbaugruppe-Eingangsbereich und einen mit dem Antriebssystem-Ausgangsbereich gekoppelten oder diesen bereitstellenden Anfahrbaugruppe-Ausgangsbereich umfasst, wobei die Anfahrbaugruppe im Drehmomentübertragungsweg zwischen dem Anfahrbaugruppe-Eingangsbereich und dem Anfahrbaugruppe-Ausgangsbereich einen hydrodynamischen Kreislauf mit einem Pumpenrad und einem Turbinenrad umfasst,
• - eine Unterbrechungskupplung im Drehmomentübertragungsweg zwischen dem Turbinenrad und dem Anfahrbaugruppe-Ausgangsbereich, wobei in einem Einrückzustand der Unterbrechungskupplung der Anfahrbaugruppe-Eingangsbereich mit dem Anfahrbaugruppe-Ausgangsbereich zur Drehmomentübertragung verbunden ist und in einem Ausrückzustand der Unterbrechungskupplung der Anfahrbaugruppe-Eingangsbereich nicht mit dem Anfahrbaugruppe-Ausgangsbereich verbunden ist,
• - eine mit dem Anfahrbaugruppe-Ausgangsbereich oder/und dem Antriebssystem-Ausgangsbereich gekoppelte Elektromaschine.

According to the invention, this object is achieved by a drive system for a vehicle, comprising:

• - a drive system entrance area to be coupled with a drive unit,
• - a drive system output area to be coupled with a gear arrangement,
• A start-up assembly, the start-up assembly comprising a start-up assembly input area coupled to or providing the drive system input area and a start-up assembly output area coupled with or providing the drive system output area, the start-up assembly in the torque transmission path between the start-up assembly input area and the start-up assembly. Output area comprises a hydrodynamic circuit with a pump wheel and a turbine wheel,
• - An interruption coupling in the torque transmission path between the turbine wheel and the starting assembly output area, the starting assembly input area being connected to the starting assembly output area for torque transmission when the interrupting clutch is engaged and the starting assembly input area not being connected to the starting assembly output area when the interrupting clutch is disengaged is,
• - An electric machine coupled to the starting assembly output area and / or the drive system output area.

Since in the inventive construction of a drive system the interruption clutch is arranged in the torque flow after the turbine wheel of the hydrodynamic circuit, the entire hydrodynamic circuit is decoupled from the starting assembly output area when the interruption clutch is disengaged. This means that in an operating state in which a drive torque is supplied by the electric machine, no system areas assigned to the hydrodynamic circuit are dragged along.

For a compact structure, it is proposed that the start-up assembly comprises a housing filled or fillable with fluid, the pump wheel being provided on the housing and the turbine wheel being arranged in a housing interior, and that the interruption coupling is arranged in the housing interior and the electric machine outside the Housing interior is arranged.

The start-up assembly can, for example, be designed as a hydrodynamic torque converter and comprise a stator in association with the pump wheel and the turbine wheel. Particularly when configured as a hydrodynamic torque converter, the start-up assembly can include a lock-up clutch, the lock-up clutch being designed to establish a torque transmission connection between the start-up assembly input area and the interruption clutch while at least partially bridging the hydrodynamic circuit. Thus, different torque transmission paths are set up in the start-up assembly depending on whether the lock-up clutch is engaged or disengaged. However, the torque flow present in the torque transmission mode is fundamentally not interrupted by engaging or disengaging the lock-up clutch, but only between shifted the lock-up clutch and the hydrodynamic circuit.

In order to be able to transmit a torque essentially directly between the starting assembly input area and the starting assembly output area when the lock-up clutch is engaged, it is proposed that an output area of the lock-up clutch be coupled to an input area of the breaker clutch.

In order to be able to dampen torsional vibrations occurring in a drive train, the output area of the lock-up clutch can be coupled to an input area of the interruption clutch via at least one torsional vibration damper.

For efficient torque transmission in the area of the interruption clutch, it can be provided that an input area of the interruption clutch comprises at least one conical, i.e. frustoconical, input friction surface that is concentric with respect to a starting assembly rotation axis, and that an output area of the interruption clutch comprises at least one concentric, conical with respect to the starting assembly rotation axis , ie frustoconical, includes output friction surface, each input friction surface being in friction contact with an output friction surface when the interruption clutch is engaged.

In order to be able to disengage or engage the interruption clutch in a simple manner, it is proposed that one area of the input area and output area of the interruption clutch comprises at least one friction element that can be displaced in the direction of the starting assembly axis of rotation to carry out actuation processes of the interruption clutch, and that the other area of The input area and the output area comprise at least one counter-friction element which is axially essentially stationary when carrying out actuation processes with respect to the starting assembly axis of rotation.

In particular for the transmission of higher torques, one area of the input area and output area of the interruption clutch can comprise a friction element which is essentially stationary axially with respect to the starting assembly axis of rotation when carrying out actuation processes, the other area of the input area and output area of the interruption clutch being located between the axially displaceable friction element and the comprises axially essentially stationary friction element of the one area of the input area and output area of the interruption clutch arranged counter-friction element.

For a common frictional effect of the axially fixed friction element and the axially displaceable friction element of one area, it can be provided that the axially displaceable friction element of one area of the input area and output area of the interruption coupling is rotationally fixed with respect to the axially fixed friction element of one area of the input area and output area of the interruption coupling is held.

To actuate the interruption clutch, the at least one axially displaceable friction element can be assigned an actuating member that can be acted upon by pressure fluid.

In this case, the actuating element can be pressable against the friction element in order to act on the at least one axially displaceable friction element. In an alternative embodiment, which is advantageous due to the small number of components, the actuating element can form part of the axially displaceable friction element.

Furthermore, for actuation of the interruption coupling that can be carried out in a simple manner, it is proposed that a pressure fluid chamber which can be filled with pressure fluid for actuating the interruption coupling is formed between the actuating member and an axially fixed abutment element.

In this case, the number of components for supporting a compact structure can be kept low in that the abutment element comprises a turbine wheel carrier coupled to the input area of the interruption coupling.

One area can be the input area of the break clutch and the other area can be the output area of the break clutch.

The start-up assembly input area can include the housing, which can be coupled to a drive shaft of the drive unit, which is designed, for example, as an internal combustion engine, via known coupling means, such as a flexplate or the like.

The starting assembly output area can comprise an output hub which is arranged in the housing and which can be coupled by meshing engagement with a transmission input shaft that forms the or part of the drive system output area or with an intermediate shaft coupled to it.

The invention also relates to a drive train for a vehicle, comprising a drive unit coupled to a transmission arrangement by means of a drive system constructed according to the invention.

• 1 in prinzipartiger Darstellung ein Fahrzeug mit einem ein Antriebsaggregat und eine Getriebeanordnung umfassenden Antriebsstrang;
• 2 in schaltbildartiger Darstellung den Antriebsstrang des Fahrzeugs der 1;
• 3 eine Teil-Längsschnittansicht einer als hydrodynamischer Drehmomentwandler ausgebildeten Anfahrbaugruppe des Antriebsstrangs der 2;
• 4 eine der 3 entsprechende Darstellung einer alternativen Ausgestaltungsart einer Anfahrbaugruppe;
• 5 eine der 3 entsprechende Darstellung einer alternativen Ausgestaltungsart einer Anfahrbaugruppe;
• 6 eine Detailansicht einer weiteren alternativen Ausgestaltungsart einer Anfahrbaugruppe.

The present invention is described in detail below with reference to the accompanying figures. It shows:

• 1 a schematic representation of a vehicle with a drive train comprising a drive unit and a transmission arrangement;
• 2 the drive train of the vehicle in a circuit diagram-like representation 1 ;
• 3 a partial longitudinal sectional view of a start-up assembly of the drive train in the form of a hydrodynamic torque converter 2 ;
• 4th one of the 3 corresponding representation of an alternative embodiment of a start-up assembly;
• 5 one of the 3 corresponding representation of an alternative embodiment of a start-up assembly;
• 6th a detailed view of a further alternative embodiment of a start-up assembly.

In 1 a vehicle shown in principle is designated generally by 10. The vehicle 10 includes a drive train 12th , in which the drive unit designed as an internal combustion engine 14th provided drive torque on driven wheels 16 , 18th is transmitted. The powertrain 12th includes between the internal combustion engine 14th and a gear assembly 20th a drive system, generally designated 22, with a start-up assembly 24 , an interrupt coupling 26th and an electric machine 28 . By the electric machine 28 can when the interruption clutch is engaged 26th supportive to that of the drive unit 14th delivered drive torque an assist torque can be delivered to the vehicle 10 in a hybrid drive mode both by the drive unit 14th , as well as the internal combustion engine 28 to drive. Furthermore, in the engaged state of the interrupter clutch, the drive unit 14th by means of the electric machine 28 to be started. In the disengaged state of the break clutch 26th is the drive unit 14th from which to the break clutch 26th following area of the drive train 12th decoupled so that the vehicle 10 in an electromotive operating mode solely by the electric machine 28 can be driven.

the 2 illustrates in more detail the within the meaning of the present invention as a drive system 22nd designated and essentially between the drive unit 14th and the gear assembly 20th lying area of the drive train 12th .

The drive system 22nd includes the start-up assembly as the central assembly 24 , which in the illustrated embodiment example as a hydrodynamic torque converter with one in a housing 30th established hydrodynamic circuit 32 is trained. This hydrodynamic cycle 32 is through a to the housing 30th coupled impeller, that is to say coupled with it for common rotation 34 , one in an interior 36 of the housing 30th arranged turbine wheel 38 and one radially inward between the impeller 34 and the turbine wheel 38 arranged idler 40 built up. The case 30th forms a start-up module input area in the configuration example shown 42 over which that from the drive unit 14th output torque in the start-up assembly 24 and thus the drive system 22nd is initiated. Thus, in the illustrated embodiment, the housing 30th at the same time as a drive system entrance area 44 to be viewed as.

The case 30th , i.e. the start-up module input area 42 or the drive system entrance area 44 , can for example by means of a flex plate or the like to a drive shaft of the drive unit 14th , in particular a crankshaft of the drive unit designed as an internal combustion engine 14th to be coupled.

Inside the housing 36 is also parallel to the hydrodynamic cycle 32 a lock-up clutch 46 arranged. By means of the lock-up clutch 46 can parallel to the hydrodynamic cycle 32 a torque on the turbine wheel 38 or a turbine wheel carrier supporting this 48 and via this to a start-up module output area 50 be transmitted. Depending on whether the lock-up clutch 46 is engaged or disengaged, torque is generated between the startup assembly input area 42 and the start-up module output area 50 either via the hydrodynamic cycle 32 and thus with circulation in the interior of the housing 36 existing fluids, generally oil, or the torque is transmitted via the lock-up clutch which establishes a mechanical connection 46 transfer. When the lock-up clutch is slipping 46 can use both torque transmission paths for a part of the in the start-up assembly 24 introduced torque to the starting module output area 50 be transmitted.

Inside the housing 36 is also the break clutch 26th arranged. A Entrance area 52 the break clutch 26th is at an exit area 54 the lock-up clutch 46 coupled while an entrance area 56 the lock-up clutch to the housing 30th is coupled or provided by this. An exit area 58 the break clutch 26th is at the start-up module output area 50 coupled.

Through the inside of the housing 36 arranged break coupling 26th the possibility is created in the start-up assembly 24 the torque flow between the start-up assembly input area 42 and the start-up module output area 50 interrupt or allow a torque transmission. With the break clutch disengaged 26th becomes independent of the state in which the lock-up clutch is 46 is, no torque between the start-up module input area 42 and the start-up module output area 50 transfer. With the break clutch engaged 26th will be regardless of whether the lock-up clutch 46 is engaged or disengaged that is in the startup module input area 42 initiated or that of the turbine wheel 38 Output torque to the starting module output area 50 transfer.

The start-up module output area 50 can, as set out below, for example one with a transmission input shaft 60 or an output hub connected to this intermediate shaft. For example, the intermediate shaft or the transmission input shaft 60 a drive system exit area 62 provide over which a torque in the gear assembly 20th can be initiated.

The electric machine 28 or a rotor assembly 64 the same is at the start-up assembly output area 50 or the drive system output area 62 coupled and thus firmly connected for torque transmission. For example, the rotor assembly 64 the electric machine 28 , their stator arrangement 66 can be carried on a stationary assembly to the transmission input shaft 60 or one of the transmission input shaft 60 with the start-up module output area 50 coupling intermediate shaft be coupled.

In the drive train described above 12th or drive system 22nd can create a torque in the drive train 12th for starting the drive unit 14th for example by means of the electric machine 28 be transmitted when the break clutch 26th and also the lock-up clutch 46 be indented. Alternatively, a starter could also be provided which, for example, is connected to the starter assembly input area 42 is coupled and a starting torque for the drive unit 14th can provide.

When driving, a drive torque of the drive unit 14th on the drive system output area 62 and thus into the gear assembly 20th be transmitted when the break clutch 26th is indented. Depending on the driving situation, the lock-up clutch can be engaged or disengaged or operated in slip mode. In this state, i.e. with the break clutch engaged 26th , can by the electric machine 28 an assisting torque can be delivered to the vehicle 10 operate in a hybrid propulsion mode. Alternatively, the electric machine 28 can be operated as a generator in this state or also in an engine braking state, in order to generate one in the vehicle 10 to charge the existing battery. In the engine braking state in particular, the entire engine braking torque can be generated by the electric machine 28 are provided when the in the start-up assembly 24 provided break coupling 26th is disengaged and thus the drive unit 14th is disconnected. In this way, very efficient charging of the battery can be achieved in recuperation mode without losing any system areas of the start-up assembly 24 Have to be dragged along.

The interruption clutch is in the purely electromotive operating mode 26th disengaged, leaving a drive torque solely through the electric machine 28 into the drive system exit area 62 and via this into the gear assembly 20th is directed. Even in this state, there is no need for any system areas of the start-up module that lead to significant energy losses 24 be dragged along.

With reference to the 3 until 6th Constructive configurations of the start-up assembly explained above with regard to its basic structure 24 described in detail.

the 3 shows the start-up assembly designed as a hydrodynamic torque converter 24 whose as the output hub 68 trained start-up assembly output area 50 to the drive system exit area 62 providing transmission input shaft 60 is coupled by meshing. The start-up module input area 42 and also the drive system entrance area 44 providing housing 30th is with two housing shells 70 , 72 built up. The housing shell represents 70 essentially also the impeller 34 or a pump wheel shell of the same ready. The turbine wheel 38 or a turbine wheel shell of the same is on the radially inside on the Output hub 68 rotatably mounted turbine wheel carrier 48 coupled for example by riveting. Via the idler 40 is the turbine wheel carrier 48 regarding the housing shell 70 with regard to this and also with regard to the stator 40 rotatably supported axially.

The lock-up clutch 46 includes a radially inward on the output hub 68 fluid-tight axially displaceable supported clutch piston 74 . Through one inside the housing 36 The clutch piston can build up fluid pressure 74 in a manner known per se against the housing shell 70 are pressed to thereby the lock-up clutch 46 to engage. The case 30th thus represents with its housing shell 70 the entrance area 56 the lock-up clutch 46 ready.

The clutch piston 74 forms the exit area 54 the lock-up clutch 46 . In the embodiment shown, this is via a torsional vibration damper 76 at the entrance area in a radially central section 52 the break clutch 26th providing turbine carrier 48 coupled. It should be noted that the torsional vibration damper 76 can be constructed in a conventional manner and can comprise springs arranged one after the other or also nested in one another in the circumferential direction, which springs on the one hand with respect to the clutch piston 74 and on the other hand with respect to the turbine carrier 48 can support and thus a limited relative rotation between them about an axis of rotation A of the start-up assembly 24 allow.

In the already mentioned central area of the turbine wheel carrier 48 this has a conical or frustoconical section 78 on, which in this embodiment example is an axially essentially stationary friction element 80 , within the meaning of the present invention, a counter-friction element 83 , the entrance area 52 the break clutch 26th with an input friction surface formed on its radial inside. A ring-like formed friction element 82 also has a conical section 84 on, the radially inside of the conical section 78 of the turbine carrier 48 is positioned and on the radially outer side of which an output friction surface is provided. The friction element 82 is for example by meshing with a on the output hub 58 for example, by welding firmly attached transmission element 86 connected in such a way that the friction element 82 and the transmission element 86 are coupled for common rotation about the axis of rotation A and the friction element 82 axially with respect to the transmission element 86 can be relocated.

The break coupling 26th also includes a on the output hub 68 fluid-tight axially movably guided actuator 88 . Between the actuator 88 and as an axially fixed abutment element 90 acting transmission element 86 is a pressurized fluid chamber 92 educated. Over in the output hub 68 openings formed and one, for example, in the transmission input shaft 60 channel formed can into the pressure fluid chamber 92 Pressurized fluid are introduced. With support on the transmission element 86 the pressurized fluid presses the actuator 88 in the representation of the 3 in the direction of also the friction element 80 providing turbine carrier 48 and thus presses the axially displaceable friction element 82 of the exit area 58 the break clutch 26th with its conical section 84 radially inside against the conical section 78 des through the turbine wheel carrier 48 provided friction elements 80 of the input area of the interruption coupling 26th , ie against the axially fixed counter-friction element 83 . This causes the two friction elements to occur 80 , 82 with their surfaces acting as input friction surface or output friction surface in frictional contact with one another and thus provide a torque transmission connection between the input area 52 and the exit area 58 the break clutch 26th ready.

It should be pointed out that in order to increase the frictional interaction on at least one of these two friction elements 80 , 82 a friction lining which increases the frictional force can be provided. Basically the friction elements are 80 , 82 provided as formed sheet metal parts and can then, if not on any of these friction elements 80 , 82 a friction lining is provided, are brought into frictional interaction with one another with their metallic surface.

For a fluid-tight closure of the pressure fluid chamber 92 is in the example shown on the actuator 80 a generally designated 94 sealing arrangement is provided, for example, on the actuator 80 fixed, for example formed from sheet metal sealing element 95 includes, for example with the interposition of a sealing ring sealingly on a cylindrical portion of the transmission element 86 and can act axially guided with respect to this.

The electric machine described above 28 can in an axial area between the start-up assembly 24 and the transmission assembly to the transmission input shaft 60 be coupled.

With the break clutch engaged 26th , i.e. with friction elements pressed against one another 80 , 82 , is thus a torque directly from the turbine carrier 48 on the output hub 68 transfer. Depending on whether the Lock-up clutch 46 is engaged or disengaged, the torque is in the turbine carrier 48 via the lock-up clutch 46 or the hydrodynamic cycle 32 and thus the turbine wheel 38 initiated and via the transmission element 86 on the essentially by the output hub 68 provided starting element output area 50 transfer.

As with the break clutch 26th the transmission element 86 and the actuator 88 In principle, do not perform any relative rotation with respect to one another, the dynamic seals acting between these radially inward and radially outward are not rotating, but essentially translating when the actuating member is axially displaced 88 burdened. These seals can comprise ring-like sealing elements which can have an open or a closed cross section. In the area of the transmission element 86 is the pressurized fluid chamber 92 through the welded connection of the transmission element 86 to the output hub 68 sealed fluid-tight. As the output hub 68 in both axial directions with respect to the housing shell 70 on the one hand and with respect to the housing shell 72 via the idler 40 on the other hand, is held in an axially defined manner, there is also an axially defined positioning for the transmission element 86 given.

A reset of the actuator 88 to disengage the break clutch 26th can for example by a between this and the turbine wheel carrier 48 acting spring element take place. By means of this or a further spring element, the friction element can also 82 in the direction of disengaging the interrupter coupling 26th be biased. Alternatively, pressure fluid actuation of the actuating member in the direction of disengagement can also be provided, including that in the area of the pressure fluid chamber 92 built-up fluid pressure with respect to that in the surrounding area of the housing interior 36 built-up fluid pressure is lowered. It should also be pointed out that in the torque transmission path between the output area 54 the lock-up clutch 46 and the entrance area 52 the break clutch 26th several serially arranged torsional vibration dampers can act. Alternatively or additionally, for example, on the turbine wheel carrier 48 one or more absorbers, for example fixed-frequency absorbers or speed-adaptive absorbers, can be coupled.

An alternative embodiment of the start-up assembly 24 is in 4th shown. The basic structure of the start-up assembly 24 corresponds to the preceding with reference to the 3 described structure, so that reference can be made to the relevant statements.

The in 4th The structure shown includes the interruption coupling 26th on the transmission element 86 a basically conically shaped and thus the conical section 84 providing friction element 82 of the exit area 58 the break clutch 26th intended. The friction element 82 is designed in this embodiment as an axially fixed friction element and is on the transmission element 86 for example, by a form fit, in particular by tooth-like engagement, held axially fixed and rotationally fixed. The friction element 82 thus provides an axially fixed counter-friction element within the meaning of the present invention 83 ready.

The entrance area 52 the break clutch 26th comprises an axially movable and as an integral part of the actuating member 88 provided friction element 80 which corresponds to the conical section 84 of the friction element 82 corresponding conical section 78 provides.

The entrance area 52 the break clutch 26th comprises a further, axially fixed friction element 80 ' which has a conical section 78 ' provides or is basically already conical in shape. The friction element 80 ' is on the turbine wheel carrier, which is constructed in two parts in the embodiment example shown 48 axially fixed and non-rotatably connected, for example by welding and / or form fit.

Associated with the two on the conical section 84 provided output friction surfaces, provide the two input-side friction elements 80 , 80 ' one input friction surface that can be brought into frictional engagement with one of the two output friction surfaces.

The actuator 88 is with the friction element formed thereon 80 with respect to the axially fixed friction element 80 ' of the entrance area 52 the break clutch 26th basically axially movable, but is by form fit or by tooth-like engagement with respect to this and / or with respect to the turbine wheel carrier 48 held non-rotatably.

The two friction elements 80 , 80 ' of the entrance area 52 the break clutch 26th are radial on both sides with respect to the friction element 82 of the exit area 58 the break clutch 26th arranged. By moving the actuator axially 88 in the representation of the 4th to the left, i.e. from the turbine wheel 38 away, the friction element becomes 80 with its conical section 78 against the friction element 82 pressed, which in turn is located radially on the axially fixed friction element 80 ' supports. As a result, due to a doubling of the compared to the embodiment of the 3 effective friction surface pairings a doubling of the over the interruption coupling 26th transmittable maximum torque reached. Multiple staggering of the input-side and output-side friction elements of the interruption clutch is also possible in order to achieve a corresponding increase in the friction surface pairings that work with one another and, accordingly, an increase in the maximum transmittable torque.

At the in 4th The embodiment shown is the actuator 88 radially inward on an axially extending portion 96 of the turbine carrier 48 axially movably supported. Since there is also a relative rotation between the actuating element in this embodiment variant 88 and the turbine carrier 48 will essentially not occur, both radially inward is that between the actuator 88 and the turbine carrier 48 effective seal, as well as through the sealing arrangement 94 provided sealing of the pressure fluid chamber 92 essentially loaded only on translation and not on rotation.

For pretensioning the actuator 88 in the direction of disengagement, for example, one between this and the as an abutment element 90 effective transmission element 86 acting biasing spring can be provided, which can be designed, for example, as a plate spring or a plurality of springs arranged distributed in the circumferential direction, for example helical compression springs or the like.

Between the axially extending portion 96 of the turbine carrier 48 and the output hub 68 can be a barrel made of hardened metal material, for example 98 be arranged. One on the actuator 88 provided and for the tight closure of the pressure fluid chamber 92 Contributing support element formed from sheet metal 100 the sealing arrangement 94 can also be used as an axial stop for the actuator 88 in the direction of the turbine wheel carrier 48 to be effective.

the 5 shows a modification of the in 4th illustrated embodiment. In this modification, the actuator is 88 than from the friction element 80 separately formed component provided and pressed to engage the interruption clutch 26th against a radially inner flange portion 102 of the friction element 80 .

Another modification of the start-up assembly 24 is in 6th shown. This modification relates in particular to the structure of the interruption coupling 26th . The axially fixed friction element 80 , so the counter-friction element 83 of the entrance area 52 the break clutch 52 , is in turn by a conical section 78 of the turbine carrier 48 , which can be provided, for example, by a radially inwardly lengthened section of a turbine wheel outer shell, and is thus coupled to it. The only axially movable friction element in this case 82 the home page 58 the break clutch 26th is through a radially outer, conical section 84 of the actuator 88 provided. The actuator 88 is radially on the inside in a toothing area 104 non-rotatably, but axially displaceable on the output hub 68 coupled. The radially inner area of the turbine carrier 48 is axial with respect to the output hub by means of appropriate axial bearings 68 supported in a fluid-tight manner, but basically rotatable with respect to this and also provides the abutment element 90 for the pressure fluid chamber 92 ready. By a ring-like sealing element 106 is the actuator 88 fluid-tight and axially movable to the output hub 68 connected. By lowering the fluid pressure in the pressurized fluid chamber 92 with respect to the surrounding fluid pressure or by increasing the fluid pressure in the surrounding area with respect to the fluid pressure in the pressurized fluid chamber 92 becomes the actuator 88 in the representation of the 6th to the left on the radially inner area of the turbine carrier 48 to acted upon, whereby the two friction linings 80 , 82 of the entrance area 52 or the output area 58 the break clutch 26th are pressed into mutual friction system and the break clutch 26th gets into their engaged state.

In order to be able to build up or maintain this pressure difference, it is located radially on the inside of the turbine wheel carrier 48 acting axial support designed so that this also a fluid-tight closure of the pressure fluid chamber at the same time 92 guaranteed. In this embodiment, too, the supply or discharge of pressurized fluid to or from the pressurized fluid chamber can be performed 92 over in the output hub 68 provided openings or one or more in the with the output hub 68 non-rotatably coupled shaft provided channels take place.

List of reference symbols

10

vehicle

12th

Powertrain

14th

Drive unit

16

drive wheel

18th

drive wheel

20th

Gear arrangement

22nd

Drive system

24

Start-up assembly

26th

Interrupt coupling

28

Electric machine

30th

casing

32

hydrodynamic cycle

34

Impeller

36

Housing interior

38

Turbine wheel

40

Idler

42

Start-up module input area

44

Drive system entrance area

46

Lock-up clutch

48

Turbine wheel carrier

50

Start-up module output area

52

Input area of the break coupling

54

Lock-up clutch output area

56

Entrance area of the lock-up clutch

58

Output area of the interruption coupling

60

Transmission input shaft

62

Drive system exit area

64

Rotor assembly

66

Stator assembly

68

Output hub

70

Housing shell

72

Housing shell

74

Clutch piston

76

Torsional vibration damper

78

conical section

78 '

conical section

80

Friction element

80 '

Friction element

82

Friction element

83

Counter-friction element

84

conical section

86

Transmission element

88

Actuator

90

Abutment element

92

Pressurized fluid chamber

94

Sealing arrangement

95

Sealing element

96

axial section

98

Barrel sleeve

100

Support element

102

Flange section

104

Toothing area

106

Sealing element

QUOTES INCLUDED IN THE DESCRIPTION

This list of the documents listed 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

• US 8298105 B2 [0002]

Claims (17)

Drive system for a vehicle, comprising: - A drive system input area (44) to be coupled to a drive unit (14), - A drive system output area (62) to be coupled to a gear arrangement (20), - A start-up assembly (24), the start-up assembly (24) having a start-up assembly input area (42) coupled to or providing the drive system input area (44) and a start-up assembly output area (42) coupled to or providing the drive system output area (62) ( 50), the start-up assembly (24) comprising a hydrodynamic circuit (32) with a pump wheel (34) and a turbine wheel (38) in the torque transmission path between the start-up assembly input area (42) and the start-up assembly output area (50), - An interruption clutch (26) in the torque transmission path between the turbine wheel (38) and the starting assembly output area (50), wherein in an engaged state of the interruption clutch (26) the starting assembly input area (42) is connected to the starting assembly output area (50) for torque transmission and when the interrupter clutch (26) is in a disengaged state, the start-up assembly input area (42) is not connected to the start-up assembly output area (50), - An electric machine (28) coupled to the starting assembly output area (50) and / or the drive system output area (62). Drive system according to Claim 1 , characterized in that the start-up assembly (24) comprises a fluid-filled or fillable housing (30), the pump wheel (34) being provided on the housing (30) and the turbine wheel (38) being arranged in a housing interior (36) , and that the interruption coupling (26) is arranged in the housing interior (36) and the electric machine (28) is arranged outside the housing interior (36). Drive system according to Claim 1 or 2 , characterized in that the start-up assembly (24) is designed as a hydrodynamic torque converter and, in association with the pump wheel (34) and the turbine wheel (38), comprises a stator (40), and / or that the start-up assembly (24) has a lock-up clutch (46 ), wherein the lock-up clutch (46) is designed to produce a torque transmission connection between the starting assembly input area (42) and the interruption clutch (26) while at least partially bridging the hydrodynamic circuit (32). Drive system according to Claim 3 , characterized in that an output area (54) of the lock-up clutch (46) is coupled to an input area (52) of the interruption clutch (26). Drive system according to Claim 4 , characterized in that the output area (54) of the lock-up clutch (46) is coupled to an input area (52) of the interruption clutch via at least one torsional vibration damper (76). Drive system according to one of the preceding claims, characterized in that an input area (52) of the interruption coupling (26) comprises at least one conical input friction surface which is concentric with respect to a starting assembly axis of rotation (A), and that an output area (58) of the interruption coupling (26) comprises at least a conical output friction surface which is concentric with respect to the starting assembly axis of rotation (A), each input friction surface being in friction contact with an output friction surface when the interruption clutch (26) is engaged. Drive system according to Claim 6 , characterized in that an area of the input area (52) and output area (58) of the interruption coupling (26) comprises at least one friction element (80; 82) which can be displaced in the direction of the starting assembly axis of rotation (A) to carry out actuation processes of the interruption coupling (26) , and that the other area of the input area (52) and the output area (58) comprises at least one counter-friction element (83) which is axially essentially fixed in relation to the starting assembly axis of rotation (A) when carrying out actuation processes. Drive system according to Claim 7 , characterized in that the one area of the input area (52) and output area (58) of the interrupter coupling (26) comprises a friction element (80 ') which is axially essentially fixed when carrying out actuation processes with respect to the starting assembly axis of rotation (A), and that the other area of the input area (52) and output area (58) of the interruption coupling (26) between the axially displaceable friction element (80) and the axially essentially stationary friction element (80 ') of one area of the input area (52) and output area (58) the interlocking clutch (26) arranged counter-friction element (83) comprises. Drive system according to Claim 8 , characterized in that the axially displaceable friction element (80) of one region of the input region (52) and output region (58) of the Interruption coupling (26) is held in a rotationally fixed manner with respect to the axially fixed friction element (80 ') of one area of the input area (52) and output area (58) of the interruption coupling (26). Drive system according to Claim 7 , 8th , or 9, characterized in that the at least one axially displaceable friction element (80; 82) is assigned an actuating member (88) which can be acted upon by pressurized fluid. Drive system according to Claim 10 , characterized in that the actuating member can be pressed against the friction element (80; 82) to act on the at least one axially displaceable friction element (80; 82), or that the actuating member (88) forms part of the axially displaceable friction element (80; 82) . Drive system according to Claim 10 or 11 , characterized in that a pressurized fluid chamber (92) which can be filled with pressurized fluid is formed between the actuating member (88) and an axially fixed abutment element (90) for actuating the interruption coupling (26). Drive system according to Claim 12 , characterized in that the abutment element (90) comprises a turbine wheel carrier (48) coupled to the input region (52) of the interruption coupling (26). Drive system according to one of the Claims 7 - 13th , characterized in that one area is the input area (52) of the interruption coupling (26) and the other area is the output area (58) of the interruption coupling (26). Drive system according to Claim 2 or one of the Claims 3 - 14th , provided on Claim 2 referred back, characterized in that the start-up assembly input area (42) comprises the housing (30). Drive system according to Claim 2 or one of the Claims 3 - 15th , provided on Claim 2 referred back, characterized in that the starting assembly output area (50) comprises an output hub (68) arranged in the housing (30). Drive train for a vehicle, comprising a drive unit (14) coupled to a transmission arrangement (20) by means of a drive system (22) according to one of the preceding claims.

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