DE102016226090A1 - The torque transfer device - Google Patents

Abstract

The invention relates to a torque transmission device (10, 20, 30, 40), a drive system with a torque transmission device (10, 20, 30, 40) and a vehicle, wherein the torque transmission device (10, 20, 30, 40) has a first input shaft (EW1 ), a Ravigneaux planetary gear set (PGS1 and PGS2), a further gear set (WG), three separating clutches (C1, C2, C3), a braking device (B1) and an output shaft (AW). The further gear set (WG) has an input side and an output side, wherein the input side to the input shaft (EW1) is rotatably connected and the output side by means of the third separating clutch (C3) with the first sun gear (S1) of the Ravigneaux planetary gear set (PGS1 and PGS2 ) is drehverbindbar and / or by means of the second separating clutch (C2) with the second sun gear (S2) of the Ravigneaux planetary gear set (PGS1 and PGS2). The first separating clutch (C1) is designed for the rotary connection of the first input shaft (EW1) with the planet carrier (PT) of the Ravigneaux planetary gear set (PGS1 and PGS2), the braking device (B1) is designed for releasably fixing the second sun gear (S2) of the Ravigneaux Planetary gear set (PGS1 and PGS2) and the output shaft (AW) is rotatably connected to the second ring gear of Ravigneaux planetary gear set (PGS1 and PGS2).

Description

The invention relates to a torque transmission device, preferably for a motor vehicle, in particular for a hybrid vehicle, wherein the torque transmission device comprises a first input shaft, a first planetary gear set, a second planetary gear set, a further gear set, a first. Disconnect coupling, a second disconnect clutch, a third disconnect clutch, a first brake device and an output shaft.

Furthermore, the invention relates to a drive system with at least one first drive motor, in particular an internal combustion engine, and a torque transmission device having a first input shaft, wherein the first drive motor with the first input shaft is rotatably connected or drehverbindbar.

Furthermore, the invention relates to a vehicle, in particular a motor vehicle, with a drive system with a torque transmission device.

Torque transmission devices having an input shaft and an output shaft and two planetary gear sets and a further gear set and a plurality of switching elements in the form of disconnect couplings and / or braking devices are basically known from the prior art, for example from DE 10 2015 222 594 A1 , of the US 8,246,500 B2 or the WO 2014/063980 A1 ,

The three aforementioned documents DE 10 2015 222 594 A1 . US 8,246,500 B2 as well as the WO 2014/063980 A1 relate in each case generic torque transmission devices for a drive system with a prime mover and a primary drive shaft, wherein the disclosed in the aforementioned documents torque transmitting devices each have two planetary gear sets, each forming a Ravigneaux planetary gear set, which each have a further transmission in the form of a simple planetary gear set upstream. Torque transmission devices with a Ravigneaux planetary gear set and an upstream, further planetary gear set are also referred to as so-called Lepelletier gear.

With the aid of several shifting elements in the form of separating clutches and braking devices, different gear stages can be switched, wherein in addition to the primary drive one secondary drive each can still be coupled to the torque transmission device, in particular in such a way that additional, additional gear steps result besides pure gear stages that can be driven via the primary drive. in which a pure drive by means of the secondary drive is possible and / or superimposed by means of the secondary drive drive, ie a so-called "boost" operation and / or a so-called CVT operation (Continuously Variable Transmission) can be realized, in which torque and speed can be variably adjusted continuously.

Depending on the arrangement and operative connection of the individual switching elements, i. the individual disconnect couplings and brake devices, each other and in operative connection with the individual transmission elements, different properties of the torque transmission device arise.

Based on this prior art, it is an object of the invention to provide an improved torque transmitting device suitable for power split. Furthermore, it is an object of the invention to provide a corresponding drive system and a corresponding vehicle.

This object is achieved by the teaching of the independent claims. Advantageous embodiments of the invention are the subject of the dependent claims and are explained in more detail below. The wording of the claims is made the subject of the description by express reference.

A torque transmission device according to the invention has a first planetary gear set, the first gear elements as a first. Sun gear, at least a first planetary gear that meshes with the first sun gear, and a planet carrier for rotatably supporting the at least one first planetary gear on.

The second planetary gear set of a torque transmission device according to the invention has a second sun gear, a second ring gear and at least one second planet gear, wherein the at least one second planetary gear meshes with the second sun gear, the second ring gear and one of the first planet gears and rotatably mounted on the planet carrier is supported, in particular on the same planet carrier as the at least one, first planetary gear.

The further set of gears of a torque transmission device according to the invention has an input side and an output side, wherein the input side of the other set of gears with the first input shaft is rotatably connected or drehverbindbar and the output side of the further set of gears by means of the third separating clutch with the first sun gear of the first Planetengetriebesatzes is drehverbindbar and / or by means of the second separating clutch with the second sun gear of the second planetary gear set.

The first separating clutch of a torque transmission device according to the invention is designed for rotational connection of the first input shaft with the planet carrier and the first braking device is designed for releasably fixing the second sun gear of the second planetary gear set. The output shaft is rotatably connected or drehverbindbar with the second ring gear of the second planetary gear set.

The first planetary gear set and the second planetary gear set form a Ravigneaux planetary gear set, which is preferably preceded by the further gear set in the power flow direction, starting from the first input shaft.

The first input shaft of a torque transmission device according to the invention is preferably rotatably connected to a first drive motor, in particular with an internal combustion engine.

The output shaft of a torque transmission device according to the invention is preferably rotatably connected or rotationally connected to a drivable axle of a vehicle.

At least one separating clutch of a torque transmission device according to the invention is preferably designed as a friction clutch, in particular as a multi-plate clutch.

In the context of the invention, an input shaft is understood to mean a component mounted in a rotatably movable manner which is suitable for receiving a torque from a drive motor and for transmitting the torque to a further component of the torque transmission device. In particular, the input shaft according to the invention is the input shaft of a transmission. Preferably, the input shaft is rotatably supported by a transmission housing of the torque transmitting device or mounted in the transmission housing.

Preferably, in a torque transmission device according to the invention at least one input shaft is formed as a shaft and at least partially supported in a, at least partially surrounding the torque transmission device transmission housing and / or stored in the transmission housing and / or in particular led out of the gearbox housing at least partially.

An output shaft according to the invention is a shaft or a transmission element, via which a mechanical power, in particular an output power can be dissipated by the torque transmission device.

Preferably, in a torque transmission device according to the invention, the output shaft is formed as a shaft and at least partially supported by the transmission housing and / or stored in the transmission housing and / or in particular at least partially led out of the transmission housing.

Under a planetary gear set in the context of the invention, a transmission is to be understood, which serves to convert an input torque into an output torque and to one or more transmission elements, wherein a planetary gear according to the invention preferably has at least two transmission elements, in particular at least one rotatable on a planet carrier supported planetary gear and a sun gear and / or a ring gear, wherein the at least one planetary gear meshes with the sun gear and / or the ring gear. In principle, each gear element can be acted upon by the input torque and the output torque can be tapped at each of the other transmission elements, which is not acted upon by the input torque.

A disconnect clutch according to the invention is a torque transmission device which can be operated in at least two switching states, preferably in a closed switching state in which a torque can be transmitted via the disconnect clutch, and in an open state in which a power flow between two each with the separating clutch, in particular mechanically connected components is separated and thus no torque can be transmitted via the separating clutch. For this purpose, a separating clutch preferably has at least two coupling parts, wherein the two coupling parts in a closed state of the separating clutch are mechanically preferably rotationally connected to each other, in particular frictionally engaged or positively, and in an open state, in particular independently of each other are rotatable relative to each other.

A braking device according to the invention is used for releasably fixing at least one rotatably connected to the braking device component, in particular for releasably fixing at least one transmission element, in particular for releasably fixing the associated transmission element to a torque transmission device surrounding the transmission housing. When the brake device is activated, ie when the brake device is closed, the fixed transmission element can not be moved, and therefore preferably can not rotate, and is thus blocked in particular in its rotational movement. By contrast, when the brake device is open, the transmission element is preferably movable in at least one of its intended degrees of freedom.

An input side of a transmission, in particular below the input side of the further transmission set, is understood to mean an area and / or at least one component of the associated transmission, via which a power, in particular a drive power, can be applied to the respectively associated transmission.

An output side of a transmission, in particular below the output side of the further transmission set, is to be understood in the sense of the invention in each case an area and / or at least one component, via which a power applied to the respectively associated transmission can be dissipated. The terms input side and output side are not to be understood as being spatially restrictive, i. the input side and the output side do not necessarily have to be on different sides of a gearbox, but may well be arranged close to each other on one side.

For the purposes of the invention, a rotationally fixed connection of two elements or components is understood to be rotationally connected or non-rotatably connected. Under a drehverbindbaren connection, however, a connection of two components understood that can be both rotationally and releasably, for example, a compound by means of a disconnect clutch, with a closed disconnect clutch is a rotationally fixed connection and with the disconnect clutch a dissolved rotary connection, that is when the separating clutch is open, the components connected by means of the separating clutch are rotatably movable relative to one another, but can be connected to one another in rotation by closing the separating clutch and can therefore be connected to one another by rotation.

With the above-described, inventive embodiment of a torque transmission device according to the invention, a torque transmission device can be provided in which as many translations as possible can be set with as few components as possible, in particular with the smallest possible overlapping range of the individual translations.

With a torque transmission device according to the invention, in particular with only four shift elements, in particular with three disconnect clutches and only one brake device, at least five gear stages drivable by a first drive motor can be realized, in particular in a particularly space-saving manner and with particularly advantageous gradations of the individual ratios of the various gear ratios ,

In an advantageous embodiment of a torque transmission device according to the invention, in particular in a particularly space-advantageous embodiment, the first sun gear of the first planetary gear set is rotatably connected to a first hollow shaft, wherein preferably within the first hollow shaft, the first input shaft is guided at least partially, and in particular for producing the rotary joint between the first sun gear and the output side of the further gear set the third separating clutch with the first hollow shaft is drehverbindbar.

In a further advantageous embodiment of a torque transmission device according to the invention, the further gear set at least a first spur gear on at least a first spur gear and a second spur gear, wherein preferably the first spur gear forms the input side of the further gear set and is rotatably connected to the first input shaft or drehverbindbar and with the second spur gear meshes. This makes it possible to provide a structurally particularly simple torque transmission device which has little or no loss of function compared to a Lepelletier transmission, but is particularly cost-effective due to the design of the further transmission set as a spur gear instead of a planetary gear set.

In a further advantageous embodiment of a torque transmission device according to the invention, the further gear set has a second spur gear with a third spur gear and a fourth spur gear, wherein the third spur gear meshes with the fourth spur gear, wherein preferably the third spur gear via an intermediate shaft with the second spur gear of the first spur gear is rotatably connected or drehverbindbar, and wherein in particular the fourth spur gear forms the output side of the further gear set. As a result, the flexibility in the design of the torque transmission device, in particular with regard to the gradation of the individual ratios in the different gear ratios, even further increase.

In a further advantageous embodiment of a torque transmission device according to the invention, in particular in a particularly space-saving design, the fourth spur gear of the second spur gear with a second Hollow shaft rotatably connected or drehverbindverbind, wherein preferably within this second hollow shaft at least partially the first input shaft and / or at least partially guided the first hollow shaft.

In a further advantageous embodiment of a torque transmission device according to the invention, the torque transmission device has a fourth disconnect clutch, which is preferably configured for rotational connection of the first input shaft with the first sun gear of the first planetary gear set, wherein the first input shaft by means of the fourth separating clutch in particular via the first hollow shaft with the first sun gear the first planetary gear set is drehverbindbar. The additional, fourth clutch can be realized in a simple way more grades. If the coupling of the first input shaft takes place via the first hollow shaft with the first sun gear of the first planetary gear set, the additional gear steps can be realized in a particularly space-saving manner.

In a further advantageous embodiment of a torque transmission device according to the invention, the torque transmission device has a second brake device, wherein the second brake device is preferably designed for releasably securing the planet carrier. As a result, at least one additional, additional gear ratio can also be realized.

In a further advantageous embodiment of a torque transmission device according to the invention, the first sun gear of the first planetary gear set with a second input shaft is rotatably connected or drehverbindbar, preferably via the first hollow shaft, in particular with a defined translation stage in between.

In this case, the second input shaft is preferably designed to be rotatably connected to a second drive motor, in particular to an electric machine that can be operated as a motor, in particular with an electric machine, which is preferably additionally operable as a generator. As a result, the range of application of a torque transmission device according to the invention can be appreciably increased.

In particular, in this way an operation of a torque transmission device according to the invention or a drive system with a first drive motor and a second drive motor possible, in which both a pure drive means of the first drive motor and / or a pure drive means of the second drive motor and a from second drive motor superimposed drive of the first drive motor possible.

In particular, with a previously described torque transmission device according to the invention, in particular when the first drive motor is an internal combustion engine and the second drive motor is an electric machine that can be operated as a motor, a so-called boost operation is possible in which the first drive motor is driven by the second drive motor generated drive power can be superimposed with appropriate speed synchrony an additional torque.

Further, in at least one gear stage in this case, a so-called E-CVT operation is possible (Electric - Continuously variable transmission operation), in which torque and speed are continuously adjustable in a defined operating range.

If the second drive motor can also be operated as a generator, in particular an electric machine which can be operated as a motor and as a generator, the second drive motor can also be used for recuperation in certain situations to generate electrical energy, which is preferably present in an energy store, in particular a battery or the like can be stored, and / or can be transmitted to supply an electrical consumer directly to this.

If the second input shaft is connected to the first sun gear with a defined gear ratio, in some cases a particularly efficient operation of a drive system with an electric machine that can be operated as a motor can be achieved as the second drive motor, because with the aid of the gear ratio step, operation can be appropriately selected the second drive motor in its optimum operating range, in particular in the range of its best possible efficiency, are made possible.

The translation stage is preferably designed as a spur gear and in particular by at least one rotatably connected to the first hollow shaft gear formed, in particular by a spur gear.

Furthermore, in at least one gear stage in this case, a so-called charging operation is possible in which electrical energy can be generated when the vehicle is at a standstill. For this purpose, it may be necessary that a locking device of the drivable axle is provided as a further switching element in order to prevent a transmission of a torque to the wheels.

A drive system according to the invention is characterized in that it has a torque transmission device according to the invention.

In an advantageous embodiment of a drive system according to the invention, the drive system to a second drive motor, in particular at least one operable as a motor electric machine, wherein the torque transmitting device preferably has a second input shaft, and wherein the second drive motor in particular rotatably connected or drehverbindbar with the second input shaft. Preferably, the second input shaft is rotatably connected to the first sun gear of the first planetary gear set or drehverbindbar, in particular via the first hollow shaft, preferably with a defined translation stage in between.

An inventive vehicle is characterized in that it comprises a torque transmission device according to the invention, preferably a drive system according to the invention.

In an advantageous embodiment of a vehicle according to the invention, the output shaft of the torque transmission device with at least one drivable axle of the vehicle is rotatably connected or drehverbindbar.

Preferably, at least one spur gear of at least one spur gear stage is designed as a straight-toothed spur gear. In some cases, however, it may be more advantageous if at least one spur gear is designed as a helical spur gear.

Instead of at least one spur gear, a torque transmission device according to the invention in an advantageous embodiment may also have a further gear set with a different gear stage design. However, spur gears have the advantage that they are structurally particularly simple and therefore particularly cost-effective.

These and other features and advantages will become apparent from the claims and from the description also from the drawings, wherein the individual features may be implemented alone or in each case in the form of sub-combinations in an embodiment of the invention and an advantageous as well as for can represent protectable design.

Some of the features mentioned or properties relate both to a torque transmission device according to the invention and to a drive system according to the invention and to a vehicle according to the invention. Some of these features and properties are described only once, but apply independently in the context of technically possible embodiments both for a torque transmission device according to the invention as well as for an inventive drive system and for a vehicle according to the invention.

• 1a einen Getriebeplan eines ersten Ausführungsbeispiels eines erfindungsgemäßen Antriebssystems mit einem ersten Ausführungsbeispiel einer erfindungsgemäßen Drehmomentübertragungsvorrichtung,
• 1b eine zum erfindungsgemäßen Antriebssystem aus 1a zugehörige Schalttabelle mit den möglichen, schaltbaren Gangstufen des Antriebssystems aus 1a,
• 2a einen Getriebeplan eines zweiten Ausführungsbeispiels eines erfindungsgemäßen Antriebssystems mit einem zweiten Ausführungsbeispiel einer erfindungsgemäßen Drehmomentübertragungsvorrichtung,
• 2b eine zum erfindungsgemäßen Antriebssystem aus 2a zugehörige Schalttabelle mit den möglichen, schaltbaren Gangstufen des Antriebssystems aus 2a,
• 3a einen Getriebeplan eines dritten Ausführungsbeispiels eines erfindungsgemäßen Antriebssystems mit einem dritten Ausführungsbeispiel einer erfindungsgemäßen Drehmomentübertragungsvorrichtung,
• 3b eine zum erfindungsgemäßen Antriebssystem aus 3a zugehörige Schalttabelle mit den möglichen, schaltbaren Gangstufen des Antriebssystems aus 3a,
• 4a einen Getriebeplan eines vierten Ausführungsbeispiels eines erfindungsgemäßen Antriebssystems mit einem vierten Ausführungsbeispiel einer erfindungsgemäßen Drehmomentübertragungsvorrichtung und
• 4b eine zum erfindungsgemäßen Antriebssystem aus 4a zugehörige Schalttabelle mit den möglichen, schaltbaren Gangstufen des Antriebssystems aus 4a.

The invention will be explained in more detail below with reference to non-limiting exemplary embodiments, which are shown at least partially schematically in the figures. In this case, components with the same function are provided with the same reference numerals. Show it:

• 1a FIG. 2 shows a transmission diagram of a first exemplary embodiment of a drive system according to the invention with a first exemplary embodiment of a torque transmission device according to the invention, FIG.
• 1b a to the drive system of the invention 1a associated switching table with the possible, switchable gear ratios of the drive system off 1a .
• 2a FIG. 2 shows a transmission diagram of a second exemplary embodiment of a drive system according to the invention with a second exemplary embodiment of a torque transmission device according to the invention, FIG.
• 2 B a to the drive system of the invention 2a associated switching table with the possible, switchable gear ratios of the drive system off 2a .
• 3a FIG. 2 shows a transmission diagram of a third exemplary embodiment of a drive system according to the invention with a third exemplary embodiment of a torque transmission device according to the invention, FIG.
• 3b a to the drive system of the invention 3a associated switching table with the possible, switchable gear ratios of the drive system off 3a .
• 4a a transmission diagram of a fourth embodiment of a drive system according to the invention with a fourth embodiment of a torque transmission device according to the invention and
• 4b a to the drive system of the invention 4a associated switching table with the possible, switchable gear ratios of the drive system off 4a ,

1a shows a first embodiment of a drive system 100 according to the invention, which is designed in particular for use in a motor vehicle and the first drive motor ICE in the form of an internal combustion engine as a first embodiment of a torque transmission device according to the invention 10 with a first input shaft EW1 , which with the first drive motor ICE is rotationally connected.

The torque transmission device according to the invention 10 has a first planetary gear set PGS1 , a second planetary gear set PGS2 , another gear set WG , a first disconnect clutch C1 , a second disconnect clutch C2 , a third disconnect clutch C3 , a first braking device B1 and an output shaft AW on, with the output shaft with a driven axle FD a vehicle is rotatably connected, in this case with a drivable front axle FD ,

The first planetary gear set PGS1 has as first gear elements a first sun gear S1 , several first planet gears P1 , which with the first sun wheel S1 comb, and a planet carrier PT for rotatably supporting the first planet gears P1 on.

The second planetary gear set PGS2 has as second gear elements a second sun gear S1 , a second ring gear H2 and a plurality of planet gears P2 on, each with the second sun gear S2 , the second ring gear H2 and each with one of the first planet gears P1 of the first planetary gear set PGS1 comb, the second planetary gears P2 also rotatably on the planet carrier PT are supported. That is, the second planet gears P2 of the second planetary gear set PGS2 are thus on the same planet carrier PT supported, like the first planet gears P1 of the first planetary gear set PGS1 , so the first planetary gear set PGS1 and the second planetary gear set PGS2 form an unspecified Ravigneaux planetary gear set.

In addition, the torque transmission device according to the invention 10 , as already mentioned, another set of gears WG on, which has an input side and an output side, wherein the input side of the further gear set WG with the first input shaft EW1 is drehverbunden and the output side of the other gear set WG by means of the third separating clutch C3 with the first sun gear S1 of the first planetary gear set can be rotatably connected and / or by means of the second separating clutch C2 with the second sun gear S2 of the second planetary gear set PGS2 ,

By means of the first available separating clutch C1 can the input shaft EW1 with the planet carrier PT be rotationally connected and by means of the first brake device also available B1 can the second sun gear S2 of the second planetary gear set PGS2 be set releasably, ie blocked if necessary in its rotational movement.

About the second ring gear H2 of the second planetary gear set PGS2 , which rotatably with the output shaft AW is connected, a drive power can be dissipated, in particular to one with the output shaft AW rotatably connected drivable axle FD ,

For a particularly space-saving design of the drive system according to the invention 100 or the torque transmission device according to the invention 10 is the first sun wheel S1 of the first planetary gear set rotatably connected to a first hollow shaft HW1, within which the first input shaft is guided.

About this first hollow shaft HW1 can also be the first sun S1 of the first planetary gear set PGS1 using the third disconnect clutch C3 with the output side of the other gear set WG be connected.

In this embodiment of a drive system according to the invention 100 or a torque transmission device according to the invention 10 is the further gear WG designed as a spur gear with a first spur gear WGS1 and a second spur gear WGS2 , wherein the first spur gear WGS1 a first spur gear Z1 and a second spur gear Z2 having, which with the first spur gear Z1 meshes with the first spur gear Z1 the input side of the other gear set WG forms and with the first input shaft EW1 is rotationally connected.

The second spur gear WGS2 the further gear set WG has a third spur gear Z3 and a fourth spur gear Z4 on, in which case all the spur gears Z1 to Z4 of the further gear set WG as straight-toothed spur gears Z1 to Z4 are formed. The third spur gear Z3 the second spur gear WGS2 combs with the fourth spur gear Z4 , wherein the third spur gear Z3 over an intermediate shaft ZW with the second spur gear Z2 the first spur gear WGS1 is rotatably connected, and wherein the fourth spur gear Z4 the output side of the other gear set WG forms.

To a particularly space-saving design of the torque transmission device according to the invention 10 to allow, in particular for a particularly space-saving arrangement of the other gear set WG within the torque transmission device according to the invention 10 , is the fourth spur gear Z4 the second spur gear WGS2 with a second hollow shaft HW2 rotatably connected, wherein within the second hollow shaft HW2 the first input shaft EW1 and at least partially the first hollow shaft HW1 are guided.

At the in 1a shown, torque transmission device according to the invention 10 can one using the first drive motor ICE generated drive power via the first input shaft EW1 either via the first disconnect clutch C1 directly, ie without a translation in between, on the planet carrier PT the Ravigneaux planetary gear set or indirectly, ie with a translation in between, on the other gear set WG , about the first sun wheel S1 and / or the second sun gear S2 be introduced into the Ravigneaux planetary gear set, of which the drive power via the second ring gear H2 of the second planetary gear set PGS2 , which rotatably with the output shaft AW is connected to a drivable axle FD a vehicle can be removed.

In other words, that one of a first drive motor ICE generated drive power either directly, namely via the first input shaft EW1 and the first disconnect clutch C1 , can be transmitted to the Ravigneaux planetary gear set or via the upstream, further gear set WG , Thus, the torque transmission device according to the invention 10 a similar functionality as a so-called Lepelletier gear, which also has a Ravigneaux planetary gear set, but which is preceded by a planetary gear set. By the upstream of another gear set WG , which is constructed as spur gear, results in a structurally particularly simple construction and thus a particularly cost-effective torque transmission device 10 ,

With the in 1a shown, torque transmission device according to the invention 10 or in 1a illustrated, drive system according to the invention 100 , can be used with the existing four switching elements in the form of the three separating clutches C1, C2 and C3 and the first braking device B1 realize a total of five different gears, with the in 1b shown switching table shows which switching elements C1 . C2 . C3 and B1 to be operated in each case by one of the gear stages 1 to 5 to switch. An "X" means that the respective switching elements is actuated, which in the case of a disconnect clutch C1 . C2 . C3 respectively corresponds to the closed state and a braking device B1 the blocked state.

In a first gear 1, which adjusts when the third clutch C3 is closed and the first brake device B1 is actuated while the first disconnect clutch C1 and the second disconnect clutch C2 can be opened, one of the first drive motor ICE generated drive power via the input shaft EW1 , continue over the first spur gear WGS1 , in particular via the spur gears Z1 and Z2 , and from there on the second spur gear WGS2 (Spur gears Z3 and Z4 ) and the third separating clutch C3 to the Ravigneaux planetary gear set, which from the first planetary gear set PGS1 and the second planetary gear set PGS2 is formed to be transmitted, wherein due to the actuated first brake device B1 the drive power via the second sun gear S2 can be supported and thus via the second ring gear H2 and via the rotatably connected to the second ring gear H2 output shaft AW to the driven axle FD can be dissipated.

Are however the second separating clutch C2 and the third disconnect clutch C3 closed while the first disconnect clutch C1 and the first brake device B1 are open, there is the gear ratio 2, in which one of the first drive motor ICE generated drive power also via the first input shaft EW1 and the other gear set WG can be transmitted to the radio planetary gear set, in which case the drive power via both the third separating clutch C3 and the first hollow shaft HW1 on the first sun wheel S1 can be transmitted, as well as the second separating clutch C2 and the second sun wheel S2 , As with the first gear, the drive power via the second ring gear H2 and the output shaft AW be discharged to the drivable axle.

Are however the first separating clutch C1 and the third disconnect clutch C3 closed while the second disconnect clutch C2 and the first brake device B1 are open, results in grade 3, in which one from the first drive motor ICE generated drive power on the one hand via the first input shaft EW1 and the first disconnect clutch C1 on the planet carrier PT transferred from there and can be introduced into the Ravigneaux planetary gear set. On the other hand, that of the first drive motor ICE generated drive power via the first input shaft EW1 and the other gear set WG and over the third disconnect clutch C3 and the first hollow shaft HW1 on the first sun gear S1 be transferred from there also in the Ravigneaux planetary gear set. As before, the drive power via the second ring gear H2 and the output shaft AW be dissipated.

Are the first disconnect clutch C1 and the second disconnect clutch C2 closed while the third disconnect clutch C3 and the first brake device B1 are open, results in gear 4, in which one of the first drive motor ICE generated drive power on the one hand via the first input shaft EW1 and the disconnect clutch C1 over the planet carrier PT can be introduced into the Ravigneaux planetary gear set and the other via the first input shaft EW1 , the other transmission set WG and the second disconnect clutch C2 and the second sun wheel S2 , The dissipation of the drive power also takes place via the second ring gear H2 and the output shaft AW ,

Gear stage 5 results when the first clutch C1 and the first brake device B1 are closed and the two disconnect couplings C2 and C3 each are open. In this case, one of the first drive motor ICE generated drive power only via the first disconnect clutch C1 and the planet carrier PT be introduced into the Ravigneaux planetary gear set. Due to the open couplings C2 and C3 no power is transmitted from the other gear set WG in the Ravigneaux planetary gear set. Due to the closed first brake device B1, the second sun gear S2 blocked in its rotational motion, leaving over the second sun gear S2 a torque can be supported and the drive power generated by the first drive motor via the second ring gear H2 can be dissipated to the output shaft AW.

2a shows a second embodiment of a drive system according to the invention 200 with a second embodiment of a torque transmission device according to the invention 20 , wherein the torque transmission device 20 in it from the in 1a illustrated torque transmission device according to the invention 10 differentiates that in 2a illustrated, torque transmission device according to the invention 20 an additional translation level excess sludge and a second input shaft DR2 having. This in 2a illustrated drive system 200 points opposite to in 1a illustrated first embodiment of a drive system according to the invention 100 in addition a second drive motor EM on, which in this case by an operable as a motor and generator electric machine EM is formed, with the second drive shaft DR2 the torque transmission device 20 rotatably connected, so that a drive power generated by the second drive motor EM via the second drive shaft DR2 , the translation stage ÜS, the first hollow shaft HW1 and the first sun wheel S1 can be initiated in the Ravigneaux planetary gear set.

Since that in 2a illustrated, a second embodiment of a torque transmission device according to the invention 20 otherwise identical to the one in 1a shown, torque transmission device according to the invention 10 is formed, can be with the in 2a shown, torque transmission device according to the invention 20 also the same five different gear ratios 1 to 5 switch, in particular in each case by the same combination of the switching states of the individual switching elements C1 to C3 and B1 , as indicated by the corresponding switching table in 2 B is recognizable.

Due to the additional electrical machine EM as a second drive motor EM can in the aforementioned ratios 1 to 5, however, at a corresponding, in each case to the rotational speed of the first hollow shaft HW1 adapted operation of the second drive motor EM , one from the second drive motor EM are superimposed torque generated so that in the gear stages 1 to 5 each a so-called "boosting" using the electric machine EM what is possible by the expression ,, (+ EM ) "In column 1 of the switching table in 2 B is symbolized.

Furthermore, by the additional, second drive motor EM in the form of an operable as a motor and generator electric machine EM a purely electric drive EM1 be provided, which adjusts when the three disconnect couplings C1 . C2 and C3 are open and only the first brake device B1 closed is. In this case, the first drive motor ICE due to the opened first disconnect clutch C1 from the planet carrier PT decoupled and due to the opened second disconnect clutch C2 and the opened third disconnect clutch C3 furthermore, no power can be transmitted through the first input shaft EW1 and the other gear set WG be introduced into the Ravigneaux planetary gear set. The drive power generated by the second drive motor EM can thereby via the second input shaft DR2 , the translation level excess sludge as well as the first hollow shaft HW1 to the first sun wheel S1 of the first planetary gear set PGS1 be transferred and introduced via this in the Ravigneaux planetary gear set. Due to the closed, first braking device B1 can the over the first sun gear S1 in the Ravigneaux planetary gear set introduced drive power via the second sun gear S2 of the second planetary gear set PGS2 be supported and as drive power via the second ring gear H2 and the output shaft AW to the driven axle FD be dissipated.

In addition, there are two further gear stages, which are referred to as E-CVT1 and E-CVT2, in which both the first drive motor ICE as well as the second drive motor EM can each provide a drive power, which can be superimposed to a total drive power, wherein in these two Gear steps each by changing the speed and / or the direction of rotation of the rotor of the electric machine EM that by means of the second drive motor EM applied torque can be changed, so that as a result, a variable, in particular continuously variable ratio, can be set, which is also eponymous for the designation of these grades, because CVT means continuously variable transmission.

These two gear stages E-CVT1 and E-CVT2 have the advantage that the first drive motor, in particular, if this as an internal combustion engine ICE is designed as in the present case, can be operated within a preferred speed range, in particular in the range of its optimum efficiency, so that a particularly efficient operation of the drive system 200 with these two gear steps becomes possible.

The first gear with E-CVT1 with infinitely variable speed results here (see 2 B ) when the second disconnect clutch C2 is closed, and the other switching elements, in particular the first disconnect clutch C1 , the third separating clutch C3 and the first brake device B1 , each are open. In this case, one of the first drive motor ICE generated drive power via the first input shaft EW1 , the other transmission set WG as well as the second separating clutch C2 and the second sun wheel S2 be introduced into the Ravigneaux gear set and the second drive motor EM generated drive power via the first sun gear S1 , In the Ravigneaux planetary gear set are those of the two drive motors ICE and EM generated drive power superimposed on a total drive power and can via the second ring gear H2 and the output shaft AW to the driven axle FD be dissipated.

The second gear E-CVT2 with continuously variable speed results when the first clutch C1 is closed and the second disconnect clutch C2 , the third separating clutch C3 and the first brake device B1 each are open. In this case, one of the first drive motor ICE generated drive power through the first disconnect clutch C1 and the planet carrier PT be introduced into the Ravigneaux planetary gear set and the second drive motor EM generated drive power via the second input shaft DR2 , the translation level excess sludge and the first hollow shaft HW1 and the first sun gear S1 , where by the two drive motors ICE and EM generated power components are also each superimposed in the Ravigneaux planetary gear set to a total drive power and the second ring gear H2 and the output shaft AW to the driven axle FD can be dissipated.

Furthermore, in at least one gear stage in this case, a so-called charging operation L is possible, in which electrical energy can be generated when the vehicle is at a standstill, also called "charging while stationary". This can be advantageous in order to be able to increase a state of charge of the battery, even if the vehicle is not in driving operation.

In the in 2 B shown gear stages L1 (P) and L2 (P) must the drivable axle and / or the output shaft AW by means of a further switching element (P), in particular a locking device or a parking brake, be secured to prevent transmission of torque to the wheels. L1 (P) corresponds to E-CVT 1 and L2 (P) corresponds to E-CVT 2.

In gear ratio L3 a charging operation without parking lock is possible. When loading on the stand, however, usually the parking lock "P" must be inserted so that the vehicle can not start to roll independently (for example: on a slope).

3a shows a third embodiment of a drive system 300 according to the invention with a third embodiment of a torque transmission device according to the invention 30 , wherein in this embodiment of a drive system according to the invention 300 likewise, like the one in 1a illustrated embodiment of a drive system according to the invention 100 , only a first drive motor ICE is present in the form of an internal combustion engine, which with the first input shaft EW1 is rotationally connected.

In the 3a illustrated, torque transmission device according to the invention 30 also shows how the in 1a shown, torque transmission device 10 according to the invention, in each case also only a first input shaft EW1 on. In addition, the torque transmission device according to the invention 30 however, a fourth disconnect clutch C4 on, over which the first input shaft EW1 with the first hollow shaft HW1 can be rotationally connected and a second braking device B2, by means of which the planet carrier PT can be set releasably, that can be blocked in its rotational movement.

In the 3a illustrated, torque transmission device according to the invention 30 enables the provision of a drive system 300 , with which in addition to the drive system 1a reversing is possible (see gear ratio R in 3b ). Furthermore, there are two more grades 6 and 7 (see also 3b ).

As from the in 3b associated shift table is visible, the reverse gear R, when the second disconnect clutch C2 and the second brake device B2 are closed while the other switching elements, in particular the first disconnect clutch C1 , the third separating clutch C3 and the first brake device B1, are opened. In this case, one of the first drive motor ICE generated drive power via the first input shaft EW1 , the other transmission set WG , the second disconnect clutch C2 and the second sun wheel S2 be introduced into the Ravigneaux planetary gear set, via the second brake device B2 a torque support takes place, which leads to a reversal of the direction of rotation with the output shaft AW rotatably connected ring gear H2 leads, creating one with the output shaft AW connected, drivable axle FD in the opposite direction, in this case in the reverse direction, can be driven.

The gear stages 2 to 4, 6 and 7 correspond to the gear stages 1 to 5 1b , with regard to the adjusting power paths in this regard to the statements in connection with the 1a and 1b is referenced.

The due to the additionally existing, second braking device B2 resulting gear ratio 1 adjusts when the third disconnect clutch C3 and the second brake device B2 be closed and the other switching elements in the form of the first disconnect clutch C1 , the second disconnect clutch C2 , the fourth disconnect clutch C4 and the first brake device B1 are open. In this case, one of the first drive motor ICE generated drive power via the first input shaft EW1 , the other transmission set WG , the third separating clutch C3 , the first hollow shaft HW1 and the first sun wheel S1 introduced into the Ravigneaux planetary gear set and the closed, second braking device B2 be supported and as drive power via the second ring gear H2 to the output shaft AW transferred and from this to a drivable axle FD be dissipated.

Due to the additional, fourth clutch C4 resulting gear 5 turns when the first clutch C1 and the fourth separating clutch C4 are closed and the other switching elements in the form of the second separating clutch C2 , the third disconnect clutch C3 , the first braking device B1 and the second brake device B2 are open. In this case, one of the first drive motor ICE generated drive power via the first input shaft EW1 on the one hand via the first separating clutch C1 on the planet carrier PT be transmitted and introduced via this in the Ravigneaux planetary gear set and on the other via the fourth separating clutch C4 , the first hollow shaft HW1 and the first sun wheel S1 and as drive power also via the second ring gear H2 and the output shaft AW to a drivable axle FD be dissipated.

4a shows a fourth embodiment of a drive system 400 according to the invention with a fourth embodiment of a torque transmission device according to the invention 40 , where the in 4a illustrated torque transmitting device 40 only in the additionally existing translation stage excess sludge and the second input shaft DR2 from the in 3a illustrated torque transmitting device 30 differs, analogous to that in 2a illustrated torque transmitting device 20 opposite to the 1a illustrated torque transmitting device 10 ,

This in 4a shown, drive system according to the invention 400 also shows how the in 2a shown, drive system according to the invention 200 , both a first, as an internal combustion engine ICE trained drive motor ICE on and a second drive motor EM powered by an electric motor operable as both a motor and a generator EM is formed and rotatably connected to the second input shaft EW2.

As from the associated switching table in 4b to be recognized with the in 4a illustrated torque transmission device according to the invention 40 or in 4a illustrated, drive system according to the invention 400 in addition to a reverse gear R a total of ten gear ratios possible in which a drive power generated by the first drive motor ICE to the output shaft AW is transferable, wherein in all of these gear ratios 1 to 10 and also in reverse gear R each electrical boosting using the second drive motor EM is possible. It also has two gears EM 1 and EM2 a purely electric drive possible and in two gear ratios E-CVT1 and E-CVT2 each E-CVT operation.

The gear ratios 1 to 7 basically correspond to the gear ratios 1 to 7 3b , for further details, in particular with regard to the individual, setting in the respective gear levels power flows, the comments in connection with the 3a and 3b is referenced.

In gear 8, which adjusts when the fourth clutch C4 and the first brake device B1 are closed while the remaining switching elements C1 to C3 and B2 can be opened, one of the first drive motor ICE generated drive power via the first input shaft EW1 and the fourth separating clutch C4 on the first hollow shaft HW1 be transmitted and from this on the first sun S1 be introduced into the Ravigneaux planetary gear set, the drive power through the second sun gear S2 , which by means of the first braking device B1 is blocked, can be supported and thus on the second ring gear H2 and the output shaft AW can be dissipated.

In gear 9, which sets when the fourth clutch C4 and the second brake device B2 are closed while the remaining switching elements C1 to C3 and B1 can be opened, one of the first drive motor ICE generated drive power via the fourth separating clutch C4 on the first hollow shaft HW1 be transmitted and from this on the first sun S1 be introduced into the Ravigneaux planetary gear set and the planet carrier PT supported by means of the second braking device B2 is blocked. The drive power can also via the second ring gear H2 and the output shaft AW be dissipated.

In gear 10 , which adjusts when the fourth separating clutch C4 and the second disconnect clutch C2 are closed while the remaining switching elements C1 . C3 . C4 , B1 and B2 may be one of the first drive motor ICE generated drive power via the fourth separating clutch C4 on the first hollow shaft HW1 be transmitted and from this both on the first sun gear S1 be introduced into the Ravigneaux planetary gear set, as well as on the other gear set WG and the second disconnect clutch C2 and the second sun wheel S2 , The drive power can also via the second ring gear H2 and the output shaft AW be dissipated.

As with the basis of 2a explained drive system according to the invention 200 allows that in 4a shown, drive system according to the invention 400 the provision of two so-called E-CVT gear ratios E-CVT1 and E-CVT2, in which a rotational speed of the to a drivable axle FD transferable drive power is infinitely adjustable, wherein for setting the first E-CVT gear E-CVT1 only the second separating clutch C2 must be closed while the remaining switching elements C1 . C3 . C4 . B1 and B2 each are open. The second E-CVT gear E-CVT2, however, results when the first clutch C1 is closed and the remaining disconnect couplings C2 . C3 and C4 as well as the two brake devices B1 and B2 each are open. The drive power can also via the second ring gear H2 and the output shaft AW be dissipated.

Likewise, purely electric driving, ie the complete decoupling of the first drive motor ICE from the output shaft AW and the generation of drive power completely by means of the second drive motor EM , possible, in particular with two different gear stages EM1 and EM2, wherein the first, purely electrically driven gear stage EM1 results when the second brake device B2 is closed while the remaining switching elements C1 to C4 and B1 , ie in particular all disconnect couplings C1 to C4 and the first brake device B1 are open.

In this case, one of the second drive motor EM generated drive power via the second input shaft DR2 , the translation level excess sludge and the first hollow shaft HW1 and the first sun wheel S1 be introduced into the Ravigneaux planetary gear set and the planet carrier PT supported by means of the second braking device B2 is fixed. The drive power can also via the second ring gear H2 and the output shaft AW be dissipated.

The second, purely electrically driven gear, EM2, however, results, as already the gear stage EM1 at the in 2a illustrated, drive system 200 according to the invention (see 2 B ), in which only the first braking device B1 is closed and the other switching elements C1 to C4 and the second brake device B2 be opened. The second drive motor EM generated drive power can also, as in the gear stage EM1 off 2 B over the second input shaft DR2 , the translation level excess sludge on the first hollow shaft HW1 be transmitted and from this on the first sun S1 be introduced into the Ravigneaux planetary gear set, the applied drive power on the second sun S2 , which by means of the first braking device B1 is fixed, can be supported. The drive power can also via the second ring gear H2 and the output shaft AW be dissipated.

It should be noted that at the in 4b shown switching table the numbering of the individual gear stages 1 to 10 only the unique name of the individual gear stages 1 to 10 in conjunction with the associated switching states of all switching elements C1 to C4 and B1 and B2 serves and does not imply that the ratio increases or decreases steadily with increasing gear.

Depending on the configuration of the individual transmission elements of a torque transmission device used can also gear ratios arise for the individual gear ratios, which while maintaining the order of the gear ratios 1 to 10 according to the switching table 4b in conjunction with the respective, the individual gear ratios associated combinations of the switching states of the individual switching elements C1 to C4 and B1 and B2 lead to a non-advantageous translation jump or which do not give meaningful translation stage.

In the present case, the transmission elements of the torque transmission device according to the invention 40 designed such that there are meaningful or advantageous translations for the gear ratios 1 to 7 and advantageous gradations between them. This results in this case for the gear ratios 8, 9 and 10 respectively translations, which are indeed possible and switchable, but have no advantageous added value.

In the present case, the transmission elements are in particular designed such that in gear ratio 1, a translation from the first drive motor ICE to the output shaft AW of 4,17081 sets and in gear 7 of 0,691057. However, this results in gear 9, however, a translation of 2.741935, which thus does not harmoniously follow the gears 1 to 7 or not harmoniously fits between the individual grades 1 to 7, and thus brings no meaningful added value.

With differently designed transmission elements can be quite reasonable translations in the gears 8, 9 and 10 can be achieved. However, then in other grades are likely to arise less advantageous or less useful translations.

With the in 4a shown, torque transmission device according to the invention 40 or in 4a illustrated, drive system according to the invention 400 As a rule, however, at least seven useful gear steps can be realized, in particular for the gear steps 1 to 7 according to the 4b shown switching table.

That means the in 4a illustrated torque device 40 according to the invention ten possible gear ratios 1 to 10, in which a pure drive means of the first drive motor ICE or a boost operation is possible, with at least seven meaningful translations can be achieved with these 10 gear ratios, which correspond to the gear stages 1 to 7 in this case due to the specific configuration of the individual transmission elements.

Due to the same structure of the in 3a shown, torque transmission device according to the invention 30 this applies to the torque transmission device 30 just like that. In the associated switching table in 3b However, only the advantageous ratios 1 to 7 are shown.

Furthermore, in at least one gear stage in the transmission after 4a also a so-called charging operation L possible, in which at standstill of the vehicle electrical energy can be generated, also called "charging in the state"". This can be advantageous in order to be able to increase a state of charge of the battery, even if the vehicle is not in driving operation.

In the in 4b shown gear stages L1 (P) and L2 (P) must the drivable axle and / or the output shaft AW by means of a further switching element (P), in particular a locking device or a parking brake, be secured to prevent transmission of torque to the wheels. L1 (P) corresponds to E-CVT 1 and L2 (P) corresponds to E-CVT 2.

In the gear ratios L3 and L4 a charging operation without parking lock is possible. When loading on the stand, however, usually the parking lock "P" must be inserted so that the vehicle can not start to roll independently (for example: on a slope).

Of course, a variety of modifications, in particular of structural modifications possible without departing from the content of the claims.

LIST OF REFERENCE NUMBERS

10, 20, 30, 40

Torque transmission device according to the invention

100, 200, 300, 400

Drive system according to the invention

AW

output shaft

B1

first braking device

B2

second braking device

C1

first disconnect clutch

C2

second separating clutch

C3

third disconnect clutch

C4

fourth separating clutch

EM

second drive motor, electric machine

EW1

first input shaft

DR2

second input shaft

FD

drivable axle

HW1

first hollow shaft

HW2

second hollow shaft

ICE

first drive motor, internal combustion engine

P1

first planetary wheel

P2

second planetary gear

PGS1

first planetary gear set

PGS2

second planetary gear set

PT

Planetenräger

S1

first sun gear

S2

second sun wheel

excess sludge

translation stage

WG

additional gear set

WGS1

first spur gear

WGS2

second spur gear

Z1

first spur gear

Z2

second spur gear

Z3

third spur gear

Z4

fourth spur gear

ZW

intermediate shaft

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 102015222594 A1 [0004, 0005]
• US 8246500 B2 [0004, 0005]
• WO 2014/063980 A1 [0004, 0005]

Claims (12)

Torque transmission device (10, 20, 30, 40), preferably for a motor vehicle, in particular for a hybrid vehicle, wherein the torque transmission device (10, 20, 30, 40) comprises: a first input shaft (EW1), a first planetary gear set (PGS1), a second planetary gear set (PGS2), another gear set (WG), a first separating clutch (C1), a second separating clutch (C2), a third separating clutch (C3), a first braking device (B1), - and an output shaft (AW), wherein the first planetary gear set (PGS1) as first gear elements, a first sun gear (S1), at least a first planetary gear (P1), which meshes with the first sun gear (S1), and a planet carrier (PT) for rotatably supporting the at least one, first planetary gear (P1), the second planetary gear set (PGS2) having as second gear elements a second sun gear (S2), a second ring gear (H2) and at least one second planet gear (P2), the at least one second planet gear (P2) being connected to the second sun gear (S2) , the second ring gear (H2) and with one of the first planet gears (P1) meshes and is rotatably supported on the planet carrier (PT), wherein the further gear set (WG) has an input side and an output side, wherein the input side of the further gear set (WG) with the first input shaft (EW1) is rotatably connected or drehverbindbar and the output side of the further gear set (WG) by means of the third separating clutch (C3) with the first sun gear (S1) of the first planetary gear set (PGS1) is drehverbindbar and by means of the second separating clutch (C2) with the second sun gear (S2) of the second planetary gear set (PGS2) is drehverbindbar, wherein the first separating clutch (C1) is configured for rotational connection the first input shaft (EW1) with the planet carrier (PT), wherein the first brake device (B1) for releasably fixing the second sun gear (S2) of the second planetary gear set (PGS2) is configured, and wherein the output shaft (AW) with the second ring gear (H2) of the second planetary gear set (PGS2) is rotatably connected or drehverbindbar. Torque transmission device (10, 20, 30, 40) according to Claim 1 wherein the first sun gear (S1) of the first planetary gear set (PGS1) is rotatably connected to a first hollow shaft (HW1), wherein preferably within the first hollow shaft (HW1), the first input shaft (EW1) is at least partially guided, and wherein in particular for producing the Rotary connection between the first sun gear (S1) and the output side of the further gear set (WG), the third separating clutch (C3) with the first hollow shaft (HW1) is drehverbindbar. Torque transmission device (10, 20, 30, 40) according to Claim 1 or 2 , characterized in that the further gear set (WG) at least a first spur gear (WGS1) having at least a first spur gear (Z1) and a second spur gear (Z2), wherein preferably the first spur gear (Z1), the input side of the further gear set (WG ) and rotatably connected to the first input shaft (EW1) or is drehverbindbar and with the second spur gear (Z2) meshes. Torque transmission device (10, 20, 30, 40) according to at least one of the preceding claims, characterized in that the further gear set (WG) has a second spur gear (WGS2) with a third spur gear (Z3) and a fourth spur gear (Z4), wherein the third spur gear (Z3) meshes with the fourth spur gear (Z4), wherein preferably the third spur gear (Z3) is rotatably connected or rotationally connectable via an intermediate shaft (ZW) to the second spur gear (Z2) of the first spur gear (WGS1), and in particular the fourth spur gear (Z4) forms the output side of the further gear set (WG). Torque transmission device (10, 20, 30, 40) according to Claim 4 , characterized in that the fourth spur gear (Z4) of the second spur gear (WGS2) with a second hollow shaft (HW2) is rotatably connected or drehverbindbar, wherein preferably within the second hollow shaft (HW2), the first input shaft (EW1) and / or the first hollow shaft (HW1) is at least partially guided. Torque transmission device (30, 40) according to at least one of the preceding claims, wherein the torque transmission device (30, 40) has a fourth separating clutch (C4), which is preferably for rotationally connecting the first input shaft (EW1) to the first sun gear (S1) of the first planetary gear set (C4). PGS1) is configured, wherein the first input shaft (EW1) by means of the fourth separating clutch (C4) in particular via the first hollow shaft (HW1) with the first sun gear (S1) of the first planetary gear set (PGS1) is drehverbindbar. Torque transmission device (30, 40) according to at least one of the preceding claims, wherein the torque transmission device (30, 40) comprises a second brake device (B2), wherein the second brake device (B2) is preferably designed for releasably securing the planet carrier (PT). Torque transmission device (20, 40) according to at least one of the aforementioned Claims, wherein the first sun gear (S1) of the first planetary gear set (PGS1) with a second input shaft (EW2) is rotatably connected or drehverbindbar, preferably via the first hollow shaft (HW1), in particular with a defined translation stage (ÜS) in between. Drive system (100, 200, 300, 400) with at least one first drive motor (ICE), in particular an internal combustion engine (ICE), and a torque transmission device (10, 20, 30, 40) with a first input shaft (EW1), wherein the first drive motor (ICE) with the first input shaft (EW1) is rotatably connected or drehverbindbar, characterized in that the torque transmission device (10, 20, 30, 40) after at least one of Claims 1 to 8th is trained. Drive system (200, 400) after Claim 9 , characterized in that the drive system (200, 400) comprises a second drive motor (EM), in particular an electric machine (EM) operable at least as a motor, wherein the torque transmission device (20, 40) preferably has a second input shaft (EW2), and wherein the second drive motor (EM) in particular with the second input shaft (EW2) is rotatably connected or drehverbindverbind. Motor vehicle, in particular hybrid vehicle, with a drive system (100, 200, 300, 400) with a torque transmission device (10, 20, 30, 40), characterized in that the torque transmission device (10, 20, 30, 40) according to at least one of Claims 1 to 8th is formed, wherein the drive system (100, 200, 300, 400) preferably after Claim 9 or 10 is trained. Vehicle after Claim 11 , characterized in that the output shaft (AW) of the torque transmitting device (10, 20, 30, 40) with at least one drivable axle (FD) of the vehicle is rotatably connected or drehverbindverbind.

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