Torque transmission device, drive system and motor vehicle

专利摘要:
The invention relates to a torque transmission device (10), a drive system with a torque transmission device (10) and a motor vehicle, wherein the torque transmission device (10) has a first input shaft (EW1), a Ravigneaux planetary gear set (PGS1 and PGS2) with a first planetary gear set (PGS1). with a first sun gear (1) and a second planetary gear set (PGS2) with a second and a third sun gear (S2, S3), a further gear set (WG), three disconnect clutches (C1, C2, C3), a first and a second brake device (B1, B2) and an output shaft (AW). The further gear set (WG) has a first and a second gear element (WH, WPT), wherein the first gear element (WH) is rotatably connected to the input shaft (EW1) and the second gear element (WPT) by means of the second separating clutch (C2) the first sun gear (S1) of the Ravigneaux planetary gear set (PGS1 and PGS2) is drehverbindbar and / or by means of the third separating clutch (C3) with the third sun gear (S3) 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 first braking device (B1) is designed for releasably fixing the second sun gear (S2) of Ravigneaux planetary gear set (PGS1 and PGS2) and the second braking device (B2) for releasably fixing the planet carrier (PT). The output shaft (AW) is rotatably connected to the ring gear (H2) of the Ravigneaux planetary gear set (PGS1 and PGS2). The torque transmitting device has a second input shaft (EW2) which is rotatably connected or drehverbindverbind with the first sun gear (S1) of the first planetary gear set (PGS1).
公开号:AT520219A4
申请号:T50763/2017
申请日:2017-09-12
公开日:2019-02-15
发明作者:Lichtenegger Stefan；Ing Ivan Andrasec Dipl
申请人:Avl List Gmbh；
IPC主号:

专利说明:

Summary
The invention relates to a torque transmission device (10), a drive system with a torque transmission device (10) and a motor vehicle, the torque transmission device (10) having a first input shaft (EW1), a Ravigneaux planetary gear set (PGS1 and PGS2) with a first planetary gear set (PGS1) with a first sun gear (1) and a second planetary gear set (PGS2) with a second and a third sun gear (S2, S3), a further gear set (WG), three clutch clutches (C1, C2, C3), a first and a second braking device (B1, B2) and an output shaft (AW). The further gear set (WG) has a first and a second gear element (WH, WPT), the first gear element (WH) being rotationally connected to the input shaft (EW1) and the second gear element (WPT) by means of the second separating clutch (C2) the first sun gear (S1) of the Ravigneaux planetary gear set (PGS1 and PGS2) can be rotatably connected and / or by means of the third clutch (C3) to the third sun gear (S3) 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) to the planet carrier (PT) of the Ravigneaux planetary gear set (PGS1 and PGS2), the first braking device (B1) is designed to releasably fix the second sun gear (S2) Ravigneaux planetary gear set (PGS1 and PGS2) and the second brake device (B2) for releasably fixing the planet carrier (PT). The output shaft (AW) is rotatably connected to the ring gear (H2) of the Ravigneaux planetary gear set (PGS1 and PGS2).
(Fig. 1a)
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-1 AVL List GmbH
September 12, 2017
Torque transmission device, drive system and motor vehicle
The present invention relates to a torque transmission device, preferably for a motor vehicle, in particular for a hybrid vehicle, the torque transmission device comprising a first input shaft, a first planetary gear set, a second planetary gear set, a further gear set, a first disconnect clutch, a second disconnect clutch, a third disconnect clutch, a first Has braking device, a second braking device and an output shaft.
Furthermore, the present invention relates to a drive system with at least a first drive motor, in particular an internal combustion engine, and a torque transmission device with a first input shaft, the first drive motor being rotatably connected or rotatably connectable to the first input shaft.
Furthermore, the invention relates to a motor vehicle, in particular a hybrid vehicle, with a drive system with a torque transmission device.
Torque transmission devices with an input shaft and an output shaft as well as two planetary gear sets and a further gear set and several switching elements in the form of separating clutches and / or braking devices are known in principle from the prior art, for example from DE 10 2015 222 594 A1, US Pat. No. 8,247,500 B2 WO 2014/063980 A1 or US 5,106,532.
The four aforementioned documents DE 10 2015 222 594 A1, US 8,247,500 B2, WO 2014/063980 A1 and US 5,106,532 each relate to the generic type
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-2 Torque transmission devices for a drive system with a primary drive and a primary drive shaft, in particular for motor vehicles. The torque transmission devices disclosed in the aforementioned documents each have two planetary gear sets, each of which forms a Ravigneaux planetary gear set, each of which is preceded by another gear in the form of a simple planetary gear set. Torque transmission devices with a Ravigneaux planetary gear set and an upstream, further planetary gear set are also referred to as so-called Lepelletier transmissions.
With the aid of a plurality of shifting elements in the form of separating clutches and / or braking devices, different gear stages can be shifted, whereby in addition to the primary drive, a secondary drive can also be coupled to the torque transmission device, in particular in such a way that, in addition to pure gear stages that can be driven by the primary drive, further, additional gear stages can be coupled Gear stages result in which a pure drive by means of the secondary drive is possible and / or a drive superimposed by means of the secondary drive, ie a so-called "boost" operation and / or a so-called ECVT operation (Electric Continuously Variable Transmission) can be implemented, in which torque and speed can be variably adjusted.
Depending on the arrangement and operative connection of the individual shifting elements to one another and depending on the operative connection with the individual transmission elements, different properties of the torque transmission device result.
In addition to a different number of available gear stages and possible gear ratios, depending on the arrangement and operative connection of the individual shifting elements, configurations with different installation space requirements and for different installation positions also result.
With regard to the installation position, a basic distinction is made between a transverse arrangement and a longitudinal arrangement, with a transverse arrangement the output shaft of a drive motor, for example an internal combustion engine, extending transversely to a direction of travel and / or a longitudinal axis of the motor vehicle, while in a longitudinal arrangement the output shaft of the drive motor extends in the direction of travel and / or in
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-3 extends along the longitudinal axis of the motor vehicle. That is to say, a torque transmission device designed for a transverse arrangement is designed to be connected to an output shaft of a drive motor extending transversely to the direction of travel and / or transversely to the longitudinal axis of the motor vehicle, while a torque transmission device designed for a longitudinal arrangement is designed to be connected to an in Driving direction and / or output shaft of a drive motor extending along the longitudinal axis of the motor vehicle to be connected.
If the installation position for a torque transmission device is specified, this and the available space in each case result in restrictions with regard to the possible spatial configuration of the torque transmission device, which are reconciled with the other requirements, such as the number and ratio of the individual gear steps and a permissible weight Need to become.
Against this background, it is therefore an object of the present invention to provide an improved torque transmission device, preferably a torque transmission device which is advantageous for a longitudinal arrangement and / or for a transverse arrangement in a motor vehicle, in particular a torque transmission device which is advantageous both for a longitudinal arrangement and for a transverse arrangement in a motor vehicle , Furthermore, it is an object of the invention to provide a corresponding drive system and a corresponding motor vehicle.
This object is achieved according to the invention 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 content of the description by express reference.
A torque transmission device according to the invention has a first input shaft, a first planetary gear set, a second planetary gear set, a further gear set, a first clutch, a second clutch, a third clutch, a first braking device, a second braking device, and an output shaft.
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The first planetary gear set of a torque transmission device according to the invention has as the first gear elements a first sun gear, at least one first planet gear that meshes with the first sun gear, and a planet carrier for rotatably supporting the at least one first planet gear.
The second planetary gear set of a torque transmission device according to the invention has, as second gear elements, a second sun gear, a third sun gear, at least one second planet gear and a ring gear, the at least one, second planet gear meshing with the second sun gear, with the third sun gear, with the ring gear and with one of the first planet gears and rotatably supported on the planet carrier.
The first planetary gear set and the second planetary gear set form a Ravigneaux planetary gear set, wherein the at least one, second planet gear of the second planetary gear set is preferably the axially longer planet gear compared to the at least one, first planet gear of the first planetary gear set.
The further gear set of a torque transmission device according to the invention has a first gear element and at least one second gear element, the first gear element of the further gear set being rotationally connected or rotationally connectable to the first input shaft.
The first separating clutch of a torque transmission device according to the invention is designed for the rotary connection of the first input shaft to the planet carrier.
The second separating clutch of a torque transmission device according to the invention is designed for the rotary connection of the second gear element of the further gear set to the first sun gear of the first planetary gear set and the third separating clutch is for the rotary connection of the second gear element of the further gear set to the third sun gear of the second planetary gear set. This means,
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The second gear element of the further gear set can be rotationally connected or separated from the first sun gear of the first planetary gear set via the second separating clutch and / or via the third separating clutch with the third sun gear of the second planetary gear set.
The first braking device of a torque transmission device according to the invention is designed to releasably fix the second sun gear of the second planetary gear set and the second braking device is designed to releasably fix the planet carrier.
The output shaft of a torque transmission device according to the invention is rotatably connected or rotatably connectable to the ring gear of the second planetary gear set.
The first input shaft of a torque transmission device according to the invention can preferably be rotatably connected to a first drive motor, in particular to an internal combustion engine.
The output shaft of a torque transmission device according to the invention is preferably rotatably connectable or rotatably connected to a drivable axle of a vehicle.
In the context of the invention, an input shaft is to be understood as a rotatably mounted component 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. The input shaft is preferably rotatably supported by a gear housing of the torque transmission device or is mounted in the gear housing.
In a torque transmission device according to the invention, at least one input shaft is preferably designed as a shaft and at least partially in a transmission housing that at least partially surrounds the torque transmission device
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6 supported and / or mounted in the gear housing and / or in particular at least partially led out of the gear housing.
An output shaft in the sense of the invention is a shaft or a gear element via which a mechanical power, in particular an output power, can be dissipated.
In a torque transmission device according to the invention, the output shaft is preferably designed as a shaft and at least partially supported by the transmission housing and / or mounted in the transmission housing and / or in particular at least partially led out of the transmission housing.
A planetary gear set in the sense of the invention is to be understood as a gear which serves to convert an input torque into an output torque and for this purpose has one or more gear elements, wherein a planetary gear according to the invention preferably has at least two gear elements, in particular at least one rotatably on a planet carrier supported planet gear and a sun gear and / or a ring gear, the at least one planet gear meshing with the sun gear and / or the ring gear. In principle, each transmission element can be acted upon by the input torque and the output torque can be tapped at each of the further transmission elements that are not acted upon by the input torque.
A disconnect clutch in the sense of 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 separating clutch, and in an open state in which a power flow between each with the disconnect clutch, in particular mechanically connected components, and therefore no torque can be transmitted via the disconnect clutch. For this purpose, a separating clutch preferably has at least two coupling parts, the two coupling parts separating in a closed state
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-7 coupling are rotatably connected to one another, preferably mechanically, in particular frictionally or positively, and in an open state they are independent of one another, in particular rotatable relative to one another.
At least one clutch of a torque transmission device according to the invention is preferably designed as a friction clutch, in particular as a multi-plate clutch.
A braking device in the sense of the invention is used for the releasable fixing of at least one component connected to the braking device in a rotationally fixed manner, in particular for the releasable fixing of at least one gear element, in particular for the releasable fixing of the respective associated gear element on a gear housing surrounding the torque transmission device. With the braking device activated, i.e. when the braking device is closed, the fixed gear element cannot be moved, thus preferably cannot rotate, and is therefore blocked in particular in its rotational movement. When the braking device is open, however, the gear element can preferably be moved in at least one of its intended degrees of freedom.
In the sense of the invention, a rotationally fixed connection is understood to mean a rotationally fixed connection between two elements or components. For the purposes of the invention, however, a rotationally connectable connection is understood to mean a connection between two components which can be both non-rotatable and detachable, for example a connection by means of a disconnect coupling, a non-rotatable connection being present when the disconnect coupling is closed and a released rotary connection when the disconnect coupling is open. That is to say, when the clutch is disengaged, the components connected by means of the clutch are rotatable relative to one another, but can be rotatably connected to one another by closing the clutch and can therefore be rotatably connected to one another.
Characterized in that the second planetary gear set has a third sun gear in addition to the second sun gear and thus two sun gears, wherein the second sun gear of the second planetary gear set can be releasably fixed by means of the first braking device and the third sun gear of the second planetary gear set by means of the third
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If the separating clutch can be rotationally connected to the second gear element of the further gear set, the individual elements of the torque transmission device can be arranged in a simple manner in such a way that a configuration which is particularly advantageous for a longitudinal arrangement of the torque transmission device results. In particular, this allows the first braking device to be spatially removed and / or detached from the second and / or third separating clutch, and thus a torque transmission device that is particularly advantageous for a longitudinal arrangement can be provided.
In particular, a torque transmission device which is advantageous for a longitudinal arrangement can be provided, which allows the setting of relatively many ratios with relatively few components, in particular with few shifting elements, in particular with a relatively small overlap area of the individual ratios and / or with particularly advantageous gradations.
With the aid of an additional transmission stage, in particular by means of a spur gear stage that is preferably rotationally connected or rotatable to the output shaft, preferably two-stage straight and / or helical gear stage, a transverse arrangement can also be implemented in a simple manner.
With a torque transmission device according to the invention, in particular with only five shift elements, in particular with three separating clutches and two braking devices, at least seven gear stages that can be driven by means of a first drive motor, in particular at least six gear stages for forward travel and at least one, can be realized in a manner that is particularly advantageous for a longitudinal arrangement Gear for a reverse drive.
In an advantageous embodiment of a torque transmission device according to the invention, the first sun gear of the first planetary gear set is arranged between the second sun gear and the third sun gear of the second planetary gear set, with respect to an axis of rotation of at least one of the second planet gears in the axial direction, i.e. in the longitudinal direction of the axis of rotation of one of the second planet gears.
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Preferably, the first sun gear of the first planetary gear set has a smaller pitch circle diameter than the second sun gear of the second planetary gear set and / or than the third sun gear of the second planetary gear set, the at least one first planet gear preferably having a larger pitch circle diameter than the at least one second planet gear ,
The second sun gear and the third sun gear of the second planetary gear set preferably have the same pitch circle diameter, in particular the same tooth geometry and / or the at least one second planet gear have a constant tooth geometry, in particular extending over its entire length.
In a further advantageous embodiment of a torque transmission device according to the invention, the third sun gear of the second planetary gear set is rotatably connected to a first hollow shaft, the first input shaft preferably being at least partially guided within the first hollow shaft, and in particular for establishing the rotary connection between the third sun gear of the second planetary gear set and the second gear element of the further gear set, the third clutch is rotatably connectable to the first hollow shaft.
In a further advantageous embodiment of a torque transmission device according to the invention, the first sun gear of the first planetary gear set is rotatably connected to a second hollow shaft, preferably the first hollow shaft and the first input shaft each being at least partially guided within the second hollow shaft, and in particular for establishing the rotary connection between the first Sun gear of the first planetary gear set and the second gear element of the further gear set, the second clutch is rotatably connected to the second hollow shaft. In particular, the first hollow shaft is at least partially guided within the second hollow shaft and the first input shaft is at least partially within the first hollow shaft.
In a further advantageous embodiment of a torque transmission device according to the invention, the second sun gear of the second planetary gear set is rotationally connected to a third hollow shaft, preferably within the third hollow shaft
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-10 the second hollow shaft, the first hollow shaft and the first input shaft are each guided at least partially, and in particular for fixing the second sun gear by means of the first braking device, the third hollow shaft can be fixed by means of the first braking device. In particular, the second hollow shaft is at least partially guided within the third hollow shaft and the first hollow shaft is at least partially within the second hollow shaft and the first input shaft is at least partially within the first hollow shaft.
In a further advantageous embodiment of a torque transmission device according to the invention, the further gear set has a planetary gear set or is a planetary gear set, preferably with a further sun gear, at least one further planet gear, which is rotatably supported on a further planet carrier, and in particular a further ring gear, the at least one , further planet gear of the planetary gear set of the further gear set preferably meshes with the further sun gear and / or the further ring gear of the planetary gear set of the further gear set.
Preferably, in a torque transmission device according to the invention, in particular if the further gear set is or has a planetary gear set, the further gear set is connected upstream of the Ravigneaux planetary gear set in the power flow direction, starting from the first input shaft, and together with the Ravigneaux planetary gear set forms a special Lepelletier gear unit in particular.
In a further advantageous embodiment of a torque transmission device according to the invention, the further ring gear of the planetary gear set of the further gear set forms the first gear element of the further gear set and the further planet carrier of the planetary gear set of the further gear set preferably the second gear element of the further gear set, in particular the further sun gear of the planetary gear set of the further gear set is set.
In particular, the further sun gear of the planetary gear set of the further gear set is fixed to a gear housing that at least partially surrounds the torque transmission device, i.e. not rotatably mounted. Preferably that is
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-11 further sun gear of the planetary gear set of the further gear set via a further shaft, in particular with the further sun gear rotatably connected shaft, fixed to the gear housing, wherein the further shaft can be a solid shaft or a further hollow shaft, depending on the application.
For the purposes of the invention, a sun shaft is understood to be a rotationally connected shaft with a sun wheel of a planetary gear set, in particular a solid shaft.
That in some applications it is more advantageous if the further sun gear of the further gear set is fixed in particular via a hollow shaft and in others if it is in particular via a solid shaft called a sun shaft, i.e. a massive wave is set.
In a further advantageous embodiment of a torque transmission device according to the invention, the torque transmission device has a fourth separating clutch, which is preferably designed to rotationally connect the first input shaft to the third sun gear of the second planetary gear set, the first input shaft being connected to the third sun gear by means of the fourth separating clutch, in particular via the first hollow shaft of the second planetary gear set is rotatably connectable. The additional, fourth separating clutch makes it easy to implement further gear stages. If the coupling of the first input shaft takes place via the first hollow shaft to the first sun gear of the first planetary gear set, the additional gear stages can be implemented 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 input shaft, the first sun gear of the first planetary gear set preferably being rotatably connected or rotatably connectable to the second input shaft, preferably via the second hollow shaft, in particular with a defined transmission ratio therebetween.
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In this case, the second input shaft is preferably designed to be rotationally connected to a second drive motor, in particular to an electrical machine that can be operated at least as a motor, in particular to an electrical machine that can also preferably be operated as a generator. As a result, the area of application of a torque transmission device according to the invention can be significantly increased.
In particular, an operation of a torque transmission device or a drive system according to the invention with a first drive motor and a second drive motor is possible in this way, in which both a pure drive by means of the first drive motor and / or a pure drive by means of the second drive motor and one of second drive motor superimposed drive of the first drive motor is possible.
In particular, with a torque transmission device according to the invention described above, in particular if the first drive motor is an internal combustion engine and the second drive motor is an electrical machine that can be operated at least as a motor, a so-called boost operation is possible in which the drive power generated by the first drive motor is generated with the aid of the second drive motor an additional torque can be superimposed if the speed is synchronous.
In this case, so-called E-CVT operation (Electric Continuously Variable Transmission operation) is also possible in at least one gear stage, in which torque and speed can be continuously adjusted in a defined operating range.
If the second drive motor can also be operated as a generator, in particular an electrical machine which can be operated as a motor and as a generator, the second drive motor can also be used in certain situations for recuperation to generate electrical energy, which is preferably stored in an electrical energy store, in particular a battery or the like. can be temporarily stored and / or can be transferred directly to an electrical consumer to supply it.
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-13If the second input shaft is connected to the first sun gear at a defined gear ratio, a particularly efficient operation of a drive system with an electric machine that can be operated as a motor can be achieved in some cases as a second drive motor, because with the gear ratio, a gear ratio can be selected appropriately Operation of the second drive motor in its optimal operating range, in particular in the range of its best possible efficiency, are made possible.
The transmission stage is preferably designed as a spur gear stage and in particular is formed by at least one gear wheel connected in a rotationally fixed manner to the second hollow shaft, in particular by a spur gear.
Furthermore, in at least one gear stage, a so-called charging operation is possible in which electrical energy can be generated when the vehicle is stationary. 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 torque being transmitted to the wheels.
In a further advantageous embodiment of a torque transmission device according to the invention, the second input shaft can be rotatably connected to the second gear element of the further gear set by means of the second clutch, in particular with a defined gear ratio therebetween, the second input shaft preferably being connectable to the further planet carrier of the planetary gear set of the further gear set. In particular, the second input shaft can be rotatably connected to the further planet carrier of the further planetary gear set by means of the second separating clutch.
In a further advantageous embodiment of a torque transmission device according to the invention, the first input shaft forms an input side of the torque transmission device and the output shaft is arranged coaxially with the first input shaft, the output shaft preferably forming an output side of the torque transmission device. This configuration is particularly advantageous for a longitudinal arrangement.
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In an alternative embodiment of a torque transmission device according to the invention, the first input shaft forms an input side of the torque transmission device and the output shaft is preferably arranged coaxially to the first input shaft, but does not form the output side, but is rotatably connected or rotatably connectable with a transmission stage, in particular with an at least 2-stage straight - And / or helical gear stage. The transmission stage preferably forms the output side of the torque transmission device. This configuration is particularly advantageous for a transverse arrangement.
For the purposes of the invention, an input side of a transmission, in particular the input side of the torque transmission device, is understood to mean an area and / or at least one component of the associated transmission and / or the associated torque transmission device, via which an output, in particular a drive output, on the respective associated transmission and / or the torque transmission device can be applied and / or introduced into it.
For the purposes of the invention, an output side of a transmission and / or a torque transmission device, in particular the output side of the torque transmission device, is understood to mean an area and / or at least one component via which the power applied to the associated transmission and / or the torque transmission device is dissipated can be.
The terms input side and output side are not to be understood as restricting space, i.e. the input side and the output side do not necessarily have to be on different sides of a transmission and / or a torque transmission device, but can also be arranged close to one another on one side.
In a further advantageous embodiment of a torque transmission device according to the invention, the output shaft of the torque transmission device is located in the region of an end of the torque transmission device facing away from the input side. In this case, the further gear set is preferably in the area
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-15 arranged on the input side and the second planetary gear set in particular in the region of the end of the torque transmission device facing away from the input side, preferably in the region of the output shaft, in particular together with the first separating clutch and / or the fourth separating clutch.
In an alternative, but also advantageous embodiment of a torque transmission device according to the invention, the output shaft of the torque transmission device is located in the region of the input side of the torque transmission device. In this case, the further transmission is preferably arranged in the region of an end of the torque transmission device facing away from the input side and the second planetary gear set is in particular in the region of the input side (and the output shaft).
In a torque transmission device according to the invention, at least the first separating clutch, in particular additionally also the fourth separating clutch, is arranged between the second planetary gear set and the output shaft, the fourth separating clutch being arranged in particular between the second planetary gear set and the first separating clutch.
In a torque transmission device according to the invention, the second separating clutch and the third separating clutch are preferably arranged at least partially in a common radial coupling plane, which extends perpendicular to the first input shaft. Alternatively, the second separating clutch and the third separating clutch can also be arranged in mutually different, in particular parallel, coupling radial planes, each of which extends perpendicular to the first input shaft.
The first braking device and the second braking device are preferably arranged at least partially in a common braking radial plane which extends perpendicular to the first input shaft. Alternatively, the first brake device and the second brake device can also be arranged in mutually different, in particular parallel, brake radial planes, which each extend perpendicular to the first input shaft.
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With reference to a longitudinal axis of the first input shaft, at least the second separating clutch and / or the third separating clutch is preferably arranged between the further gear set and the second planetary gear set.
In particular, there is at least one clutch radial plane and at least one brake radial plane between the further gear set and the second planetary gear set, with the common clutch radial plane of the second and third separating clutch and the common brake radial plane of the first and second brake devices preferably being between the further Gear set and the second planetary gear set.
Preferably, at least the second separating clutch and / or the third separating clutch, in particular their common clutch radial plane, is arranged between the further gear set and the first braking device and / or the second braking device, in particular their common braking radial plane.
Preferably, at least the first braking device and / or the second braking device, in particular their common radial brake plane, is arranged between at least the second clutch and / or the third clutch, in particular their common radial clutch plane, and the second planetary gear set.
A gear stage forms the output side of the torque transmission device, i.e. If the output shaft is rotatably connected or rotatably connectable to a transmission stage which forms the output side of the torque transmission device, the transmission stage, in particular its output side which forms the output side of the torque transmission device, can preferably be rotatably connected to the drivable axle of a motor vehicle, in particular to an associated axle drive.
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If a transmission stage forms the output side of the torque transmission device, the output side of the torque transmission device is preferably located laterally from the input side, in particular if the torque transmission device is provided for a transverse arrangement.
In an advantageous embodiment, the transmission stage of the output shaft is preferably connected downstream in the direction of power flow and preferably an at least 2-stage spur gear stage, in particular a straight and / or helical gear stage, preferably at least one axis of rotation of a first gear element of a first stage of the transmission stage being arranged coaxially to the output shaft and in particular an axis of rotation of a second gear element of the first stage parallel to the output shaft. A first gear element of a second stage of the transmission stage is preferably rotatably connected to the second gear element of the first stage. In particular, at least one gear element of the second stage of the transmission stage is arranged in a common gear element level with at least one gear element of the first planetary gear set of the Ravigneaux gear set.
In a further advantageous embodiment of a torque transmission device according to the invention, the torque transmission device is designed such that an axis of rotation of a second drive motor, in particular an electrical machine, can be arranged coaxially to the first input shaft or parallel to the first input shaft. The arrangement of the axis of rotation of the second drive motor coaxial with the first input shaft is generally particularly advantageous for a longitudinal arrangement, while the arrangement of the axis of rotation of the second drive motor parallel to the first input shaft is generally particularly advantageous for a transverse arrangement.
In particular, if a second drive motor can be arranged with its axis of rotation coaxial with the first input shaft, a torque transmission device according to the invention is preferably designed such that the second drive motor, in particular an electrical machine, can be arranged upstream of the gear sets in the direction of power flow, i.e. before the further gear set, the first planetary gear set and before the second planetary gear set of the torque transmission device, based on a power flow direction from the input side of the torque transmission device
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-18 starting, the enumeration of the gear sets made here not intended to restrict the sequence of the arrangement of the gear sets. The second input shaft is preferably at least partially a hollow shaft, in which in particular at least the first input shaft can be at least partially arranged and / or guided. This makes it possible to achieve a particularly advantageous configuration for a longitudinal arrangement.
If the second gear element of the further gear set, in particular the further sun gear, is fixed on the gear housing via a further shaft, the further shaft is preferably also at least partially arranged and / or guided within the second input shaft, the further shaft being in particular a hollow shaft. In this case, the first input shaft is preferably at least partially arranged and / or guided within the further shaft, i.e. within the further hollow shaft, so that as a result the further hollow shaft is at least partially arranged and / or guided within the second input shaft and the first input shaft at least partially within the further hollow shaft.
The second input shaft and / or the further hollow shaft and / or the first input shaft are particularly preferably arranged and / or guided within the second drive motor. That The second drive motor can preferably be arranged rotatably about the further hollow shaft and / or the input shaft, in particular together with the second input shaft.
However, a torque transmission device according to the invention can also be designed such that a second drive motor, in particular an electrical machine, can be arranged between the second planetary gear set and the further gear set, preferably with its axis of rotation coaxial with the first input shaft, in particular between the second and / or third separating clutch, in particular their common clutch radial plane, and the first and / or second braking device, in particular their common brake radial plane. In this case, the torque transmission device is preferably configured in this way and the second drive motor is configured in this way
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It can be arranged that at least the second hollow shaft, the first hollow shaft and the first input shaft are at least partially arranged and / or guided within the second drive motor or can be arranged and / or guided.
A torque transmission device according to the invention can also be designed such that a second drive motor, in particular an electrical machine, in the region of the end facing away from the input side according to the gear sets of the torque transmission device, i.e. can be arranged after the further gear set, the first planetary gear set and after the second planetary gear set, the enumeration of the gear sets made here not intended to restrict the sequence of the arrangement of the gear sets. The second drive motor can in particular likewise be arranged with its axis of rotation coaxial with the first input shaft and / or the output shaft and / or the further shaft, wherein preferably the output shaft and / or the further shaft can be arranged and / or guided at least partially within the second drive motor ,
Preferably, if the input side and output shaft of the torque transmission device are on the same side, the further gear set is arranged in the region of the end of the torque transmission device facing away from the input side and output shaft and the further shaft is designed in particular as a solid shaft and / or sun shaft and can be at least partially within the second Drive motor arranged and / or guided.
If the input side and output shaft of the torque transmission device are located on different sides and / or ends of the torque transmission device, the further gear set is preferably located in the area of the input side of the torque transmission device and the second planetary gear set is located in the area of the end of the torque transmission device facing away from the input side. In this case, the output shaft can preferably be arranged and / or guided at least partially within the second drive motor.
A torque transmission device according to the invention can also, in particular alternatively, be designed such that a second drive motor, in particular one
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-20 electrical machine, can be arranged laterally in the direction of power flow from the gear sets. especially with its axis of rotation parallel to the first input shaft. This results, in particular, in an embodiment of a torque transmission device according to the invention which is advantageous for a transverse arrangement in a motor vehicle.
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 has a second drive motor, in particular an electrical machine which can be operated at least as a motor, the torque transmission device preferably having a second input shaft and the second drive motor being rotatably connected or rotatably connectable to the second input shaft.
In a further advantageous embodiment of a drive system according to the invention, the second drive motor has an axis of rotation and the axis of rotation of the second drive motor is arranged coaxially with the first input shaft.
Alternatively, the axis of rotation of the second drive motor can also be arranged parallel to the first input shaft.
In a further advantageous embodiment of a drive system according to the invention, the second drive motor is arranged between the first drive motor and the torque transmission device, in particular between the first drive motor and the gear sets of the torque transmission device, based on a direction of power flow from the first drive motor to the torque transmission device.
Preferably, a drive system according to the invention additionally has a vibration damping device, in particular a vibration damping device designed to reduce torsional vibrations, preferably a dual-mass flywheel, the second drive motor being in particular in the direction of power flow from the first drive motor to the torque transmission device between the
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-21 vibration damping device and the torque transmission device is arranged, in particular between the dual-mass flywheel and an input side of the torque transmission device.
In a drive system according to the invention with a second drive motor, the second drive motor is preferably arranged in the power flow direction upstream of the gear sets of the torque transmission device, i.e. before the further gear set, the first planetary gear set and before the second planetary gear set of the torque transmission device, based on a power flow direction from the first drive motor to the torque transmission device. The enumeration of the gear sets made here is not intended to restrict the sequence of the arrangement of the gear sets at this point either.
The second drive motor is preferably arranged with its axis of rotation coaxial with the first input shaft. The second input shaft is preferably at least partially a hollow shaft, in which in particular at least the first input shaft is at least partially arranged and / or guided.
If the second gear element of the further gear set, in particular the further sun gear, is fixed on the gear housing via a further shaft, the further shaft is preferably also arranged and / or guided at least partially within the second input shaft, the further shaft being in particular a hollow shaft. In this case, the first input shaft is preferably at least partially arranged and / or guided within the further shaft, i.e. within the further hollow shaft, so that as a result the further hollow shaft is at least partially arranged and / or guided within the second input shaft and the first input shaft at least partially within the further hollow shaft.
The second input shaft and / or the further hollow shaft and / or the first input shaft are particularly preferably arranged and / or guided within the second drive motor. That The second drive motor is preferably rotatable about the further hollow shaft and / or the first input shaft, in particular together with the second input shaft.
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In a drive system according to the invention with a second drive motor, the second drive motor can also be arranged between the second planetary gear set and the further gear set, preferably with its axis of rotation coaxial with the first input shaft, in particular between the second and / or third separating clutch, in particular their common clutch. Radial plane, and the first and / or second braking device, in particular their common braking radial plane. In this case, the second drive motor is preferably arranged such that at least the second hollow shaft, the first hollow shaft and the first input shaft are each at least partially arranged and / or guided within the second drive motor.
In a drive system according to the invention with a second drive motor, the second drive motor can also be located in the region of the end facing away from the input side according to the gear sets of the torque transmission device, i.e. be arranged after the further gear set, the first planetary gear set and after the second planetary gear set, the enumeration of the gear sets made here also not intended to restrict the sequence of the arrangement of the gear sets. The second drive motor is in particular likewise arranged with its axis of rotation coaxial to the first input shaft and / or to the output shaft and / or to the further shaft, the output shaft and / or the further shaft preferably being arranged and / or guided at least partially within the second drive motor.
Preferably, if the input side and output shaft of the torque transmission device are on the same side, the further gear set is arranged in the region of the end of the torque transmission device facing away from the input side and the output shaft, and the further shaft is designed in particular as a solid shaft and / or sun shaft and is at least partially inside arranged and / or guided of the second drive motor.
If the input side and output shaft of the torque transmission device are located on different sides and / or ends of the torque transmission device, the further gear set is preferably in the area of the input side of the torque transmission device and the second planetary gear set is in the area
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-23 the end of the torque transmission device facing away from the input side. In this case, the output shaft is preferably arranged and / or guided at least partially within the second drive motor.
In an alternative embodiment of a drive system according to the invention, the second drive motor is arranged on the side of the torque transmission device, in particular on the side of the gear sets, in particular at the level of the further gear set.
A motor vehicle according to the invention is characterized in that it has a torque transmission device according to the invention, preferably a drive system according to the invention.
In a motor vehicle according to the invention, the output shaft of the torque transmission device is preferably rotatably connected or rotatably connectable to at least one drivable axle of the vehicle.
At least one spur gear of at least one spur gear stage of a torque transmission device according to the invention and / or of a drive system according to the invention is preferably designed as a spur gear with straight teeth. In some cases, however, it can be more advantageous if at least one spur gear is designed as a helical spur gear.
These and other features and advantages emerge from the claims and from the description and from the drawings, the individual features can be realized individually or in groups, in the form of sub-combinations in an embodiment of the invention and an advantageous and for can be a protective version.
Some of the features or properties mentioned relate both to a torque transmission device according to the invention and to a drive system according to the invention and a motor vehicle according to the invention. Some of these characteristics and characteristics
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Shafts are only described once, but apply independently of one another within the framework of technically possible configurations both for a torque transmission device according to the invention and for a drive system according to the invention and for a vehicle according to the invention.
The invention is explained in more detail below on the basis of non-restrictive exemplary embodiments, which are at least partially shown schematically in the figures. Components with the same function are provided with the same reference symbols. Show it:
Fig. 1a 1 shows a transmission plan 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 1 a shift table associated with the drive system according to the invention from FIG. 1 a with the possible switchable gear stages of the drive system from FIG. 1 a, Fig. 1c 1 shows a schematic illustration of an exemplary embodiment of an embodiment of an arrangement of the individual components of the drive system from FIG. Fig. 2a 1 shows a transmission plan 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. 2b 2 a shift table associated with the drive system according to the invention from FIG. 2 a with the possible switchable gear stages of the drive system from FIG. 2 a, Fig. 2c 2 shows a schematic illustration of an exemplary embodiment of an embodiment of an arrangement of the individual components of the drive system from FIG. 2a,
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Fig. 3a 1 shows a transmission plan 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. 3b 3 a shift table associated with the drive system according to the invention from FIG. 3 a with the possible switchable gear stages of the drive system from FIG. 3 a, Fig. 3c 3 shows a schematic illustration of a first exemplary embodiment of an embodiment of an arrangement of the individual components of the drive system from FIG. 3a, Fig. 4a 2 shows a transmission plan 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. 4b a shift table associated with the drive system according to the invention from Fig. 4a with the possible switchable gear stages of the drive system from Fig. 4a and Fig. 4c a schematic representation of an embodiment of an embodiment of an arrangement of the individual components of the drive system from FIG. 4a.
Fig. 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 which has a first drive motor ICE in the form of an internal combustion engine, as well as a first embodiment of a torque transmission device 10 according to the invention with a first input shaft EW1, which with the first drive motor ICE is rotatably connected.
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The torque transmission device 10 according to the invention has a first planetary gear set PGS1, a second planetary gear set PGS2, a further gear set WG, a first clutch clutch C1, a second clutch clutch C2, a third clutch clutch C3, a first brake device B1, a second brake device B2 and an output shaft AW , wherein the output shaft is rotatably connected to a drivable axis FD of a vehicle.
The first planetary gear set PGS1 has as the first gear elements a first sun gear S1, a plurality of first planet gears P1, which mesh with the first sun gear S1, and a planet carrier PT for rotatably supporting the first planet gears P1.
The second planetary gear set PGS2 has, as second gear elements, a second sun gear S2, a third sun gear S3, a second ring gear H2 and a plurality of planet gears P2, each with the second sun gear S2, the third sun gear S3, the second ring gear H2 and each with one of the Comb first planet gears P1 of the first planetary gear set PGS1, the second planet gears P2 also being rotatably supported on the planet carrier PT. That is, the second planet gears P2 of the second planetary gear set PGS2 are thus supported on the same planet carrier PT as the first planet gears P1 of the first planetary gear set PGS1, so that the first planetary gear set PGS1 and the second planetary gear set PGS2 form a Ravigneaux planetary gear set, which is not specified.
In this exemplary embodiment of a drive system 100 according to the invention or a torque transmission device 10 according to the invention, the further gear set WG is designed as a planetary gear set and has a further sun gear WS, a further planet carrier WPT, a further ring gear WH and further planet gears WP, the further sun gear WS on one the torque transmission device 10 is at least partially surrounding the transmission housing G and the further ring gear WH is connected in a rotationally fixed manner to the input shaft EW1 of the torque transmission device 10. By means of the second separating clutch C2, the further planet carrier WPT of the further gear set WG can be rotationally connected to the first sun gear S1 of the first planetary gear set PGS1 and / or by means of the
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-27th third clutch C3 with the third sun gear S3 of the second planetary gear set PGS2.
The first input shaft EW1 of the torque transmission device 10 can also be rotationally connected to the planet carrier PT of the Ravigneaux planetary gear set by means of the first separating clutch C1.
The second sun gear S2 of the second planetary gear set PGS2 can be releasably fixed by means of the existing first braking device B1, i.e. if necessary, be blocked in its rotational movement, and by means of the second braking device B2, the planet carrier PT of the Ravigneaux gear set can be detachably fixed on the gear housing G.
Drive power can be dissipated via the second ring gear H2 of the second planetary gear set PGS2, which is non-rotatably connected to the output shaft AW, in particular to a drivable axis FD which is non-rotatably connected to the output shaft AW.
For a particularly advantageous embodiment for a longitudinal arrangement of the drive system 100 according to the invention or the torque transmission device 10 according to the invention, the third sun gear S3 of the second planetary gear set PGS2 is rotatably connected to a first hollow shaft HW1, within which the first input shaft EW1 is at least partially arranged and guided.
Via this first hollow shaft HW1, the third sun gear S3 of the second planetary gear set PGS2 can also be rotatably connected to the further gear set WG, in particular to the further planet carrier WPT, with the aid of the third clutch C3.
For a particularly advantageous embodiment for a longitudinal arrangement of the drive system 100 according to the invention or the torque transmission device 10 according to the invention, the first sun gear S1 of the first planetary gear set PGS1 and the second sun gear S2 of the second planetary gear set PGS2 are each rotatably connected to a hollow shaft HW2 or HW3. The first sun gear is S1
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28 of the first planetary gear set PGS1 with a second hollow shaft HW2, via which it can also be rotationally connected to the further gear set WG, in particular the further planet carrier WPT of the further gear set WG, by means of the second separating clutch C2. The second sun gear S2 of the second planetary gear set PGS2 is rotatably connected to a third hollow shaft HW3, via which it can be detachably fixed to the gear housing G by means of the first braking device B1.
For a particularly advantageous embodiment for a longitudinal arrangement of the drive system 100 according to the invention or the torque transmission device 10 according to the invention, the second hollow shaft HW2 is at least partially arranged and guided within the third hollow shaft HW3 and the first hollow shaft HW1 at least partially within the second hollow shaft HW2 and the first input shaft EW1 at least partially within the first hollow shaft HW1.
In the torque transmission device 10 according to the invention shown in FIG. 1a, a drive power generated with the aid of the first drive motor ICE can be transmitted via the first input shaft EW1 either directly via the first clutch C1, i.e. without a translation in between, are transferred to the planet carrier PT of the Ravigneaux planetary gear set or indirectly, i.e. with a gear ratio in between, via the further gear set WG and via the first sun gear S1 and / or the third sun gear S3 into the Ravigneaux planetary gear set, from 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 of a vehicle. That In other words, a drive power generated by a first drive motor ICE can either be transmitted directly to the Ravigneaux planetary gear set, namely via the first input shaft EW1 and the first clutch C1, or via the upstream further gear set WG, in particular via the further ring gear WH and the other planet carrier WPT.
The torque transmission device 10 according to the invention shown in FIG. 1a or the drive system 100 according to the invention shown in FIG. 1a can be used
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-29 implement a total of seven different gear stages with the five shifting elements in the form of the three clutch clutches C1, C2 and C3, the first brake unit B1 and the second brake unit B2, six for forward travel (gear stages 1 to 6) and one for reverse driving (gear stage "R" ).
The shift table shown in FIG. 1b shows which of the shifting elements C1, C2, C3, B1 and B2 are to be actuated and how to shift one of the gear stages 1 to 6 or the gear stage “R”. An “X” means that the respective switching element is actuated, which corresponds to the closed state in the case of a clutch C1, C2, C3 and the blocked state in the case of a braking device B1, B2.
In a first gear stage 1, which occurs when the second clutch C2 is closed and the second brake device B2 is actuated, while the first clutch C1 and the third clutch C3 are open and the first brake device B1 is released, one of the first drive motor can ICE generated drive power via the input shaft EW1 and the further gear set WG, in particular via the further ring gear WH and the further planet carrier WPT, and via the second clutch C2 and the first sun gear S1 to the Ravigneaux planetary gear set, which consists of the first planetary gear set PGS1 and the second planetary gear set PGS2 is formed, which, due to the actuated second braking device B2, the drive power can be supported via the planet carrier PT of the Ravigneaux planetary gear set and thus via the second ring gear H2 and the output shaft AW which is rotatably connected to the second ring gear H2 can be discharged to the drivable axis FD.
If, on the other hand, the second brake device B2 is open and the first brake device B1 is actuated, gear stage 2 results, in which a drive power generated by the first drive motor ICE can also be transmitted to the Ravigneaux planetary gear set via the first input shaft EW1 and the further gear set WG in this case, the drive power can also be transmitted to the Ravigneaux planetary gear set via the second clutch C2 and the first sun gear S1. In this case, however, the drive power is supported by the second sun gear S2 defined by means of the first braking device B1 and can, as in the first
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-30th gear stage 1 are discharged to the drivable axis FD via the second ring gear H2 and the output shaft AW.
If, on the other hand, the second disconnect clutch C2 and the third disconnect clutch C3 are closed while the first disconnect clutch C1, the first brake device B1 and the second brake device B2 are open, gear stage 3 results, in which a drive power generated by the first drive motor ICE via the first input shaft EW1 and the further gear set WG, in particular via the further ring gear WH and the further planet carrier WPT, and via the second separating clutch C2 and the first sun gear S1 and also via the third separating clutch C3 and the third sun gear S3 can be introduced into the Ravigneaux planetary gear set. As with the previously described gear stages 1 and 2, the drive power can be dissipated via the second ring gear H2 and the output shaft AW.
If the first separating clutch C1 and the second separating clutch C2 are closed while the third separating clutch C3, the first braking device B1 and the second braking device B2 are both open, gear stage 4 results, in which a drive power generated by the first drive motor ICE on the one hand via the first Input shaft EW1 and the clutch C1 can be introduced into the Ravigneaux planetary gear set via the planet carrier PT and secondly via the first input shaft EW1, the further gear set WG and the second clutch C2 and the first sun gear S1. As with the previously described gear stages 1 and 2, the drive power can be dissipated via the second ring gear H2 and the output shaft AW.
Gear stage 5 results when the first clutch C1 and the third clutch C3 are closed and the second clutch C2 and the two braking devices B1 and B2 are open. In this case, a drive power generated by the first drive motor ICE can be introduced into the Ravigneaux planetary gear set on the one hand via the first input shaft EW1 and the first separating clutch C1 and the planet carrier PT and on the other hand via the first input shaft EW1, the further gear set WG and the third Separating clutch C3 and the third sun gear C3. As with the previously described gear stages 1 and 2, the drive power can be dissipated via the second ring gear H2 and the output shaft AW.
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-31 If only the first separating clutch C1 and the first braking device B1 are closed or actuated while the second separating clutch C2, the third separating clutch C3 and the second braking device are open, gear stage 6 results, in which a drive power generated by the first drive motor ICE only can be introduced into the Ravigneaux planetary gear set via the first input shaft EW1 and the first clutch C1 and the planet carrier PT. Due to the open clutches C2 and C3 in this gear stage 6, there is no power transmission from the further gear set WG to the Ravigneaux planetary gear set. Due to the closed first braking device B1, the second sun gear S2 is blocked in its rotational movement, so that a torque can be supported via the second sun gear S2 and the drive power generated by the first drive motor can be dissipated to the output shaft AW via the second ring gear H2.
The reverse gear R is obtained when the third clutch C3 and the second brake device B2 are closed and the other shift elements, in particular the first clutch C1, the second clutch C2 and the first brake device B1, are open. In this case, a drive power generated by the first drive motor ICE can only be introduced into the Ravigneaux gear set via the first input shaft EW1, the further gear set WG, the third clutch C3 and the third sun gear S3 and via the second ring gear H2 and the output shaft AW the drivable axis FD are removed. This results in a reversal of the direction of rotation and the drive power can be dissipated in the opposite direction of rotation, which enables reverse driving.
1c shows a schematic representation of an exemplary embodiment of an advantageous embodiment of an arrangement of the individual components of the drive system from FIG. 1a, which is particularly advantageous for a longitudinal arrangement. For the sake of clarity, the first planetary gear set PGS1 of the Ravigneaux gear set is only shown in the lower half and the second planetary gear set PGS2 only in the upper half of the figure.
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In the advantageous exemplary embodiment of an arrangement of the individual components of the drive system 100 according to the invention from FIG. 1 a with the torque transmission device 10 according to the invention from FIG. 1 a shown in FIG. 1 c, the first input shaft EW1 forms an input side E of the torque transmission device and the output shaft AW forms a Output side A of the torque transmission device 10, the first input shaft EW1 being rotatably connected or rotatably connectable to the first drive motor ICE, which is designed as an internal combustion engine, via a dual-mass flywheel ZMS, and the output shaft AW is arranged coaxially with the first input shaft EW1.
The output side A of the torque transmission device 10 is located in the region of an end of the torque transmission device 10 facing away from the input side E and the further gear set WG is arranged in the region of the input side E and the second planetary gear set PGS2 is located in the region of the end of the torque transmission device 10 facing away from the input side E Area of the output side A. This enables a compact arrangement to be achieved. The first clutch C1 is arranged between the second planetary gear set PGS2 and the output shaft AW.
For a particularly compact arrangement, the second clutch C2 and the third clutch C3 are arranged in a common clutch radial plane KR, which extends perpendicular to the first input shaft EW1, and the first brake device B1 and the second brake device B2 in a common brake radial plane BR , which also extends perpendicular to the first input shaft EW1.
The second clutch C2 and the third clutch C3 are arranged along a longitudinal axis of the first input shaft EW1 or its axis of rotation between the further gear set WG and the second planetary gear set PGS2. In particular, their common clutch radial plane KR and the common brake radial plane BR of the first and second brake devices B1 and B2 are located between the further gear set WG and the second planetary gear set PGS2, the common clutch radial plane KR between the further gear set WG and the common brake radial plane BR is arranged and the common brake
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-33Radial plane BR between the common clutch radial plane KR and the second planetary gear set PGS2.
2a shows a second exemplary embodiment of a drive system 200 according to the invention with a second exemplary embodiment of a torque transmission device 20 according to the invention, the torque transmission device 20 additionally having a fourth separating clutch C4 by way of the torque transmission device 10 from FIG. 1a, via which the first input shaft EW1 with the third sun gear S3 of the second planetary gear set PGS2 can be rotationally connected, in particular via the first hollow shaft HW1.
Due to the fourth clutch C4 additionally present compared to the torque transmission device 10 according to the invention from FIG. 1a, a total of three further mechanical gear stages can be shifted with the torque transmission device 20 according to the invention from FIG in Fig. 2b with "R2" and "4" and "6" designated gear steps, gear step R1 from Fig. 2b corresponds to gear step R from Fig. 1b and gear steps 1 to 3 from Fig. 2b to gear steps 1 to 3 from Fig. 1b, gear stage 5 from Fig. 2b gear stage 4 from Fig. 1b and gear stages 7 and 8 from Fig. 2b gear stages 5 and 6 from Fig. 1b, the respective gear stages each being the same combination of the switching states of the Individual switching elements C1 to C3 and B1 and B1 can be set and the same power flows result in these gear stages as in the corresponding gear stages described with reference to FIGS. 1a and 1b.
As can be seen from the shift table shown in FIG. 2b, the reverse gear R2 is set when the fourth clutch C4 and the second brake device B2 are open and the other shift elements, in particular the first clutch C1, the second clutch C2 and the third clutch C3 and the first brake device B1 are each open. In this case, a drive power generated by the first drive motor ICE can be directly via the first input shaft EW1 and the fourth clutch C4, i.e. without being routed through the additional gear set WG
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34, are introduced into the Ravigneaux gear set via the third sun gear S3, with torque support being provided via the second braking device B2 and the planet carrier PT of the Ravigneaux gear set, which leads to a reversal of the direction of rotation of the ring gear H2, which is connected in a rotationally fixed manner to the output shaft AW, as a result of which a drivable axis FD connected to the output shaft AW can be driven in the opposite direction, in this case in the reverse direction.
The additional gear step 4 resulting from the additional fourth clutch C4 is established when the second clutch C2 and the fourth clutch C4 are closed, while the first clutch C1, the third clutch C3 and the two braking devices B1 and B2 are open , In this case, a drive power generated by the first drive motor ICE can on the one hand via the first input shaft EW1, the further gear set WG, the second separating clutch C2, in particular via the second hollow shaft HW2, and the first sun gear S1 of the first planetary gear set PGS1 in the Ravigneaux Transmission set are initiated and on the other hand directly via the first input shaft EW1 and the fourth clutch C4 and the third sun gear S3, in particular also via the first hollow shaft HW1. Via the second ring gear H2, the drive power can be transmitted to the output shaft AW and can be dissipated from there to a drivable axis FD.
The third gear stage 6, which additionally arises on account of the additional fourth clutch C4, is established when the first clutch C1 and the fourth clutch C4 are closed and the other shifting elements in the form of the second clutch C2, the third clutch C3, the first braking device B1 and the second braking device B2 are each open. In this case, a drive power generated by the first drive motor ICE can be transmitted via the first input shaft EW1 on the one hand via the first clutch C1 to the planet carrier PT of the Ravigneaux gear set and on the other hand via the fourth clutch C4 and the third sun gear S3, in particular via the first hollow shaft HW1, and as drive power also via the second ring gear H2 and the output shaft AW to a drivable axis FD. paragraph
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-35Fig. 2c shows a schematic representation of an exemplary embodiment of an advantageous embodiment of an arrangement of the individual components of the drive system from FIG. 2a, the arrangement shown in FIG. 2c basically corresponding to the arrangement from FIG. 1c and comprising only the additional, fourth clutch C4.
In this case, the first separating clutch C1 and the fourth separating clutch C4 are arranged between the second planetary gear set PGS2 and the output shaft AW, the fourth separating clutch C4 being arranged between the second planetary gear set PGS2 and the first separating clutch C1.
3a shows a third exemplary embodiment of a drive system 300 according to the invention with a third exemplary embodiment of a torque transmission device 30 according to the invention, this exemplary embodiment of a drive system 300 according to the invention basically being constructed like the drive system 100 described in FIG. 1a or the torque transmission device 30 basically like the torque transmission device 10 Fig. 1a. The drive system 300 from FIG. 3a differs from the exemplary embodiment shown in FIG. 1a in that the torque transmission device 30 according to the invention shown in FIG. 3a additionally has a second input shaft EW2 and an additional transmission stage US and the drive system shown in FIG. 3a 300 in addition to the first exemplary embodiment of a drive system 100 according to the invention shown in FIG. 1a, a second drive motor EM.
In this exemplary embodiment, the second drive motor EM is formed by an electrical machine EM which can be operated as a motor and generator and which is connected in a rotationally fixed manner to the second input shaft EW2 of the torque transmission device 30, so that a drive power generated by the second drive motor EM inter alia directly via the second input shaft EW2, the transmission stage ÜS, the second hollow shaft HW2 and the first sun gear S1 of the first planetary gear set PGS1 can be introduced into the Ravigneaux planetary gear set.
Since the third exemplary embodiment of a torque transmission device 30 according to the invention shown in FIG. 3a is otherwise identical to that shown in FIG. 1a,
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3a, the torque transmission device 30 shown in FIG. 3a can also be used to shift the same, purely mechanical seven different gear stages R and 1 to 6, in particular each by the same combination of the switching states of the individual shifting elements C1 to C3 , B1 and B2, as can be seen from the associated shift table shown in FIG. 3b.
Due to the additionally existing electrical machine EM as the second drive motor EM, a torque generated by the second drive motor EM can, however, be superimposed in the aforementioned gear stages R and 1 to 6 with a corresponding operation of the second drive motor EM that is adapted to the speed of the second hollow shaft HW2 , so that a so-called “boosting” with the help of the electrical machine EM is possible in gear stages R and 1 to 6, which is symbolized by the expression “(+ EM)” in column 1 of the shift table in FIG. 3b.
Furthermore, the additional, second drive motor EM in the form of an electrical machine EM that can be operated as a motor and generator can provide two purely electrical drive gears EM1 and EM2 or two pure recuperation gears G1 and G2, which are set when the three separating clutches C1, C2 and C3 are open and only one of the two braking devices B1 or B2 is closed.
The first, purely electrical gear EM1 or the first purely regenerative gear G1 is established when the first to third clutch C1 to C3 are open and the second brake device B2 is actuated and the second, purely electrical gear EM2 or second purely regenerative gear G2 when the first to third clutch clutches C1 to C3 are open and the first brake device B1 is actuated.
In both cases, the first drive motor ICE is decoupled from the planet carrier PT due to the opened first clutch C1 and because of the opened second clutch C2 and the opened third clutch C3, no power can be supplied to the Ravigneaux planetary gear set via the first input shaft EW1 and the further gear set WG be introduced.
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In both purely electric gear stages EM1 and EM2, a drive power generated by the second drive motor EM can be transmitted to the first sun gear S1 of the first planetary gear set PGS1 via the second input shaft EW2, the transmission stage ÜS and the second hollow shaft HW2 and introduced into the Ravigneaux planetary gear set are, in the first purely electric gear EM1 the drive power introduced into the Ravigneaux planetary gear set is supported by the actuated second braking device B2 via the tarpaulin carrier PT of the Ravigneaux planetary gear set and as drive power via the second ring gear H2 and the output shaft AW to the drivable axle FD can be dissipated. In the second purely electrical gear stage EM2, on the other hand, the drive power is supported by the second sun gear S2 as a result of the actuated first braking device B1 and can be dissipated as drive power via the second ring gear H2 and the output shaft AW to the drivable axis FD.
In purely generator mode, i.e. when recuperating in gears G1 and G2, the power flow is exactly the opposite, i.e. A drive power generated on the axis FD, for example by rolling downhill, can be guided along the respective power paths described above to the electrical machine EM, which in this case can be used as a generator, and converted by means of this into electrical energy.
In addition to the two previously described, purely electrical or purely regenerative gears EM1 and EM2 or G1 and G2, the drive system 300 shown in FIG. 3a has two further gear stages, which are designated as E-CVT1 and E-CVT2 and in which both the first drive motor ICE and the second drive motor EM can each provide a drive power that can be superimposed to form a total drive power. In these two gear stages, the torque applied by means of the second drive motor EM can be changed by changing the speed and / or the direction of rotation of the rotor of the electric machine EM, so that a variable, in particular stepless transmission ratio can be set, which also gives the name to is the name of these gears, because CVT means Continuously Variable Transmission.
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These two gear stages E-CVT1 and E-CVT2 have the advantage that the first drive motor, especially if it is designed as an internal combustion engine ICE, as in the present case, can be operated within a preferred speed range, in particular in the area of its optimal efficiency that a particularly efficient operation of the drive system 300 with these two gear stages is possible.
The first gear stage with E-CVT 1 with infinitely variable speed results (see FIG. 2b) when the third clutch C3 is closed and the other shifting elements, in particular the first clutch C1, the second clutch C2, the first braking device B1 and the second brake device B2 are opened. In this case, a drive power generated by the first drive motor ICE can be introduced into the Ravigneaux gear set via the first input shaft EW1, the further gear set WG and the third clutch C3 and the third sun gear S3, in particular via the first hollow shaft HW1, and that from the second Drive motor EM generated drive power via the first sun gear S1. In the Ravigneaux planetary gear set, the drive power generated by the two drive motors ICE and EM is superimposed to form a total drive power and can be transferred to the drivable axis FD via the second ring gear H2 and the output shaft AW.
The second gear stage E-CVT2 with a continuously adjustable speed results when the first clutch C1 is closed and the second clutch C2, the third clutch C3, the first braking device B1 and the second braking device B2 are open. In this case, a drive power generated by the first drive motor ICE can be introduced into the Ravigneaux planetary gear set via the first separating clutch C1 and the planet carrier PT and the drive power generated by the second drive motor EM via the second input shaft EW2, the transmission stage ÜS and the second hollow shaft HW2 and the first sun gear S1, whereby the power components generated by the two drive motors ICE and EM are also superimposed in the Ravigneaux planetary gear set to form a total drive power and can be dissipated to the drivable axis FD via the second ring gear H2 and the output shaft AW.
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Furthermore, in the drive system 300 shown in FIG. 3a, a so-called charging operation “L” is possible in at least one gear stage, in this case in three gear stages L1 (P), L2 and L3 (P), in which the vehicle is at a standstill electrical energy can be generated, also called "charging in the stand". This can be advantageous in order to be able to increase a state of charge of the battery even when the vehicle is not in the ferry mode.
In the gear stages L1 (P) and L3 (P) shown in FIG. 3b, however, the drivable axle and / or the output shaft AW must be secured by means of a further switching element (P), in particular a locking device, for example by means of a parking brake prevent transmission of torque to the wheels. L1 (P) basically corresponds to the switching states E-CVT2 and L3 (P) corresponds to ECVT1, whereby the parking brake generates the drive power generated by the first drive motor ICE and introduced into the Ravigneaux planetary gear set via the locked axis FD and the second ring gear H2 is supported and thus discharged via the first sun gear S1, the second hollow shaft HW2, the transmission stage and the second input shaft EW2, which in this case serves as an output shaft, to the electrical machine EM, which in this case works as a generator.
In gear stage L2, charging operation without a parking lock is possible, in which gear stage, which occurs when the first clutch C1, the third clutch C3 and both braking devices B1 and B2 are open and only the second clutch C2 is closed. In this case, a drive power generated by the first drive motor ICE can be routed directly to the electrical machine EM via the first input shaft EW1, the further gear set WG and the second clutch C2 as well as via the transmission stage ÜS and the second input shaft EW2.
3c shows a schematic representation of an exemplary embodiment of an embodiment of an advantageous arrangement of the individual components of the drive system 300 from FIG. 3a, the output shaft AW being arranged on a side of the torque transmission device 30 facing away from the input side E and coaxial with the first input shaft EW1, and the second drive motor EM, especially the electrical one
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-40Machine EM based on a power flow from the first drive motor ICE to the torque transmission device 30, between the first drive motor ICE and the torque transmission device 30, in particular between the dual-mass flywheel ZMS and before the gear sets WG and PGS1 and PGS2.
For a particularly advantageous arrangement for a longitudinal arrangement, the second drive motor is arranged with its axis of rotation coaxial with the first input shaft EW1 and the second input shaft EW2 is at least partially a hollow shaft in which the first input shaft EW1 is at least partially arranged and guided.
The second gear element WPT of the further gear set, in particular the further sun gear WS, is fixed in favor of a particularly compact arrangement by means of a further shaft HWW on the gear housing G, the further shaft HWW also being arranged and guided at least partially within the second input shaft EW2 and a hollow shaft is. Furthermore, the first input shaft EW1 is arranged and guided at least partially within this further hollow shaft HWW, so that as a result the further hollow shaft HWW is at least partially arranged and guided within the second input shaft EW2 and the first input shaft EW1 at least partially within the further hollow shaft HWW.
Furthermore, the second input shaft EW2 and the further hollow shaft HWW and the first input shaft EW1 are at least partially arranged and guided within the second drive motor EM. That the second drive motor EM can be rotated, in particular together with the second input shaft EW2, about the further hollow shaft HWW and the first input shaft EW1.
As an alternative to the embodiment of a drive system 300 according to the invention shown in FIG. 3c, the second drive motor EM can be arranged with its axis of rotation parallel to the first input shaft EW1, in particular to the side or outside of the torque transmission device 30, for example at the level of the further gear set WG. This enables a shorter overall length in the longitudinal direction of the first input shaft EW1 to be achieved, which is particularly advantageous for a transverse arrangement.
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4a shows a fourth embodiment of a drive system 400 according to the invention with a fourth embodiment of a torque transmission device 40 according to the invention, this embodiment of a drive system 400 according to the invention having a fourth clutch C4 in addition to the torque transmission device 30 according to the invention previously described with reference to FIGS. 3a and 3b, Via which the first input shaft EW1 can be rotatably connected to the first hollow shaft HW1 and the third sun gear S3 of the second planetary gear set PGS2.
As can be seen from the associated shift table in FIG. 4b, with the torque transmission device 30 according to the invention shown in FIG. 4a and the drive system 400 according to the invention shown in FIG. 4a compared to the third exemplary embodiment of a drive system 300 according to the invention due to the fourth clutch C4 a further reverse gear R2 (gear step R1 corresponds to gear step R from Fig. 3b) two additional, purely mechanical gear steps (gear steps 4 and 6) are possible, in which a drive power generated only by the first drive motor ICE can be transmitted to the output shaft AW, all of which of these gear stages R1, R2 and 1 to 8, electrical boosting is also possible using the second drive motor EM.
As with the drive system 300, a purely electrical drive or a purely regenerative operation is possible in the drive system 400 from FIG. 4a in two gear stages EM1 and EM2 or G1 and G2.
The additional fourth separating clutch C4 of the drive system 400 from FIG. 4a, however, enables E-CVT operation in each case in three gear stages ECVT1, E-CVT2 and E-CVT3, that is to say in comparison with the drive system 300 from FIG. 3a. an additional E-CVT gear E-CVT3. In addition, a total of four instead of just three charge gear stages L1 (P), L2 (P), L3 and L4 (P) are possible.
The gear steps R1 and R2 and 1 to 8 basically correspond to the gear steps R1 and R2 and 1 to 8 from FIG. 2b, with more details on these gear steps
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-42 fen, in particular with regard to the individual power flows occurring in the respective gear stages, reference is made to the explanations in connection with FIGS. 2a and 2b.
The third, additional E-CVT gear E-CVT3 results when the fourth clutch C4 is closed and the other clutch C1, C2 and C3 and the two braking devices B1 and B2 are open. In this case, a drive power generated by the first drive motor ICE can be introduced into the Ravigneaux planetary gear set via the first input shaft EW1 and the fourth separating clutch C4 and the third sun gear S3, in particular via the first hollow shaft HW1, and in it with one from the second drive motor EM2 Drive power introduced into the Ravigneaux planetary gear set is superimposed on the second input shaft EW2, the transmission stage ÜS, the second hollow shaft HW2 and the first sun gear S1 and is discharged via the second ring gear H2 and the output shaft AW.
The additional charging gear stage L4, in which the axis FD must also be locked, results when the fourth clutch C4 is closed and the other shifting elements C1 to C3 and B1 and B2 are open. In this case, a drive power generated by the first drive motor ICE can be introduced into the Ravigneaux gear set via the first input shaft EW1, the fourth clutch C4, the first hollow shaft HW1 and the third sun gear S3 and via the first sun gear S1, the second hollow shaft HW2, the transmission stage ÜS and the second input shaft EW2 are fed to the second drive motor EM for charging an electrical energy store.
FIG. 4c shows a schematic illustration of an exemplary embodiment of an embodiment of an advantageous arrangement of the individual components of the drive system from FIG. 4a, this arrangement corresponding to a combination of the two arrangements from FIGS. 2c and 3c.
Accordingly, as an alternative to the embodiment of a drive system 400 according to the invention shown in FIG. 4c, the second drive motor EM can be arranged with its axis of rotation parallel to the first input shaft EW1, in particular laterally
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-43bzw. outside of the torque transmission device 30, for example at the level of the further gear set WG.
It should be noted that in all of the shift tables shown, the numbering of the individual gear stages only serves to clearly identify the individual gear stages in conjunction with the associated shift states of all shift elements and does not necessarily imply that the translation increases or decreases with increasing gear stage.
Depending on the design of the individual gear elements of a torque transmission device used, gear ratios can also arise for the individual gear stages, which, while maintaining the sequence of the gear stages in accordance with the shift table in conjunction with the respective combinations of the gear states of the individual gear elements assigned to the individual gear stages, result in a non-advantageous gear ratio step or which do not result in a meaningful translation level.
As is clear from the above explanations, a torque transmission device according to the invention represents a flexible starting basis with which a drive system with a wide variety of gear stages that can be configured almost as required can be provided in a simple manner.
A torque transmission device according to the invention enables in particular the provision of a drive system with at least four, up to 8 purely mechanical gear stages for forward travel and up to two reverse gears, in each of which a superimposition with a drive power generated by a second drive motor is possible, and with up to two purely electrical or regenerative gear stages, with up to three E-CVT gear stages and with up to four charging gear stages.
With the help of an additional transmission stage, not shown in the figures, in particular by means of a rotationally connected or rotatably connected to the output shaft AW
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44able, two-stage straight and / or helical toothed spur gear stage, all of the above-described embodiments 100, 200, 300 and 400 can be adapted in a simple manner for a transverse arrangement.
This can be achieved particularly easily by in each case following the output shaft AW in the power flow direction, a transmission stage which is rotatably connected or rotatably connectable to the output shaft AW and forms the output side of the torque transmission device, the transmission stage being in particular designed such that the output side of the torque transmission device located laterally from the entrance side.
A particularly simple configuration of a torque transmission device according to the invention and a drive system according to the invention suitable for a transverse arrangement is obtained if the transmission stage is designed as a 2-stage spur gear stage, in particular as a straight and / or helical spur gear stage, a first stage having two spur gears that are in engagement with one another and a second stage has at least one spur gear, a first spur gear of the first stage being rotatably connected to the output shaft AW and an axis of rotation of the first spur gear of the first stage being arranged coaxially with the output shaft AW and an axis of rotation of the second spur gear of the first stage parallel to the output shaft AW , The at least one spur gear of the second stage is preferably rotatably connected to the second spur gear of the first stage and can be rotationally connected to the drivable axle, in particular to the axle drive, in particular to the axle differential.
An arrangement which is particularly advantageous for a transverse arrangement results if the spur gear of the second stage is arranged in a common gear element plane with at least one gear element of the first planetary gear set PGS1 of the Ravigneaux gear set.
A particularly compact embodiment of a drive system according to the invention with a second drive motor results when the second drive motor EM with its
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Rotation axis is also arranged parallel to the first input shaft EW1, in particular to the side or outside of the torque transmission device, for example at the level of the further gear set WG.
Of course, a large number of modifications, in particular of structural modifications, are possible without departing from the content of the claims.
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-46-LIST OF REFERENCES 10, 20, 30, 40 Torque transmission device according to the invention 100, 200, 300, 400 drive system according to the invention Α Output side of the torque transmission device AW output shaft B1 first braking device B2 second braking device BR Brake radial plane C1 first disconnect clutch C2 second clutch C3 third clutch C4 fourth disconnect clutch e Input side of the torque transmission device EM second drive motor, electric machine EW1 first input shaft DR2 second input shaft FD drivable axis H2 ring gear HW1 first hollow shaft HW2 second hollow shaft HW3 third hollow shaft HWW further hollow shaft ICE first drive motor, internal combustion engine
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-47- KR Clutch radial plane P1 first planet wheel P2 second planet gear PGS1 first planetary gear set PGS2 second planetary gear set PT planet carrier S1 first sun gear S2 second sun gear S3 third sun gear excess sludge translation stage WG another gear set WH first gear element of the further gear set; another ring gear WPT second gear element of the further gear set; another planet carrier WS another sun gear ZMS Dual Mass Flywheel
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权利要求:
Claims (19)
[1]
claims
1. Torque transmission device (10, 20, 30, 40), preferably for a motor vehicle, in particular for a hybrid vehicle, the torque transmission device (10, 20, 30, 40) having:
a first input shaft (EW1), a first planetary gear set (PGS1), a second planetary gear set (PGS2), a further gear set (WG), a first clutch (C1), a second clutch (C2), a third clutch (C3), one first braking device (B1), a second braking device (B2), and an output shaft (AW), the first planetary gear set (PGS1) as first transmission elements having a first sun gear (S1), at least one first planet gear (P1) that is connected to the first sun gear (S1) meshes and has a planet carrier (PT) for rotatably supporting the at least one first planet gear (P1), the second planetary gear set (PGS2) as second gear elements, a second sun gear (S2), a third sun gear (S3), at least has a second planet gear (P2) and a ring gear (H2), the at least one, second planet gear (P2) with the second sun gear (S2), with the third sun gear (S3), with the ring gear (H2) and with one of the e rsten planet gears (P1) and rotatably supported on the planet carrier (PT), the further gear set (WG) having a first gear element (WH) and at least a second gear element (WPT), the first gear element (WH) of the further gear set ( WG) with the first input shaft (EW1) is rotatably connected or rotatably connectable, the first separating clutch (C1) being designed for the rotational connection of the first input shaft (EW1) with the planet carrier (PT),
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-49 whereby the second separating clutch (C2) is designed for the rotary connection of the second gear element (WPT) of the further gear set (WG) with the first sun gear (S1) of the first planetary gear set (PGS1), the third separating clutch (C3) being designed for the rotary connection of the second gear element (WPT) of the further gear set (WG) with the third sun gear (S3) of the second planetary gear set (PGS2), the first braking device (B1) being designed to releasably fix the second sun gear (S2) of the second planetary gear set (PGS2), wherein the second braking device (B2) is designed for releasably fixing the planet carrier (PT), and wherein the output shaft (AW) is rotatably connected or rotatably connectable to the ring gear (H2) of the second planetary gear set (PGS2).
[2]
2. 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 arranged between the second sun gear (S2) and the third sun gear (S3) of the second planetary gear set on an axis of rotation of one of the second planet gears (P2) in the axial direction.
[3]
3. Torque transmission device (10, 20, 30, 40) according to claim 1 or 2, wherein the third sun gear (S3) of the second planetary gear set (PGS2) is rotatably connected to a first hollow shaft (HW1), preferably within the first hollow shaft (HW1) the first input shaft (EW1) is at least partially arranged and / or guided, and in particular for establishing the rotary connection between the third sun gear (S3) and the second gear element (WPT) of the further gear set (WG) the third clutch (C3) with the first hollow shaft (HW1) is rotatably connectable.
[4]
Torque transmission device (10, 20, 30, 40) according to one of claims 1 to 3, wherein the first sun gear (S1) of the first planetary gear set (PGS1) is rotatably connected to a second hollow shaft (HW2), preferably the first hollow shaft (HW1) and the first input shaft (EW1) is arranged at least partially within the second hollow shaft (HW2) and / or
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[5]
5. Torque transmission device (10, 20, 30, 40) according to one of the claims
1 to 4, wherein the second sun gear (S2) of the second planetary gear set (PGS2) is rotatably connected to a third hollow shaft (HW3), preferably the second hollow shaft (HW2), the first hollow shaft (HW1) and the first input shaft (EW1) each are at least partially arranged and / or guided within the third hollow shaft (HW3), and in particular for fixing the second sun gear (S2) of the second planetary gear set (PGS2) by means of the first braking device (B1), the third hollow shaft (HW3) by means of the first braking device (B1) can be determined.
[6]
6. Torque transmission device (10, 20, 30, 40) according to one of the claims
1 to 5, the further gear set (WG) having a planetary gear set (WPG) with a further sun gear (WS), at least one further planet gear (WP) which is rotatably supported on a further planet carrier (WPT), and a further ring gear ( WH), the at least one further planet gear (WP) of the planetary gear set (WPG) of the further gear set meshing with the further sun gear (WS) and the further ring gear (WH) of the planetary gear set (WPG) of the further gear set (WG).
[7]
7. Torque transmission device (10, 20, 30, 40) according to claim 6, wherein the further ring gear (WH) of the planetary gear set (WPG) of the further gear set (WG), the first gear element (WH) of the further gear set
5 (WG) and preferably the further planet carrier (WPT) of the planetary gear set (WPG) forms the second gear element of the further gear set (WG), in particular the further sun gear (WS) of the planetary gear set (WPG) of the further gear set (WG) being fixed.
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[8]
8. Torque transmission device (20, 40) according to one of claims 1 to 7, wherein the torque transmission device (20, 30) has a fourth separating clutch (C4), which preferably for rotationally connecting the first input shaft (EW1) with the third sun gear (S3) second planetary gear set (PGS2), the first input shaft (EW1) can be rotatably connected to the third sun gear (S3) of the second planetary gear set (PGS2) by means of the fourth clutch (C4), in particular via the first hollow shaft (HW1).
[9]
9. torque transmission device (30, 40) according to one of claims 1 to 8, wherein the torque transmission device has a second input shaft (EW2) and the first sun gear (S1) of the first planetary gear set (PGS1) with the second input shaft (EW2) is rotatably connected or rotatably connectable , preferably via the second hollow shaft (HW2), in particular with a defined gear ratio (ÜS) in between.
[10]
10. torque transmission device (30, 40) according to claim 9, wherein the second input shaft (EW2) by means of the second clutch (C2) with the second gear element (WPT) of the further gear set (WG) is rotatably connectable, in particular with a defined gear ratio (ÜS) between.
[11]
11. Torque transmission device (10, 20, 30, 40) according to one of claims 1 to 10, wherein the first input shaft (EW1) forms an input side (E) of the torque transmission device (10, 20, 30, 40) and the output shaft (AW) is arranged coaxially to the first input shaft (EW1), the output shaft (AW) preferably forming an output side (A) of the torque transmission device (10, 20, 30, 40).
[12]
12. torque transmission device (10, 20, 30, 40) according to one of claims 1 to 11, wherein the output shaft (AW) of the torque transmission device (10, 20, 30, 40) in the region of an end facing away from the input side (E) Torque transmission device (10, 20, 30, 40) is located.
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[13]
13. Torque transmission device according to one of claims 1 to 11, wherein the output shaft (AW) of the torque transmission device is located in the region of the input side (E) of the torque transmission device.
[14]
14. Torque transmission device (10, 20, 30, 40) according to one of the claims
1 to 13, wherein the torque transmission device (10, 20, 30, 40) is designed such that an axis of rotation of a second drive motor (EM), in particular an electrical machine, coaxial to the first input shaft (EW1) or parallel to the first input shaft (EW1) can be arranged.
[15]
15. Drive system (100, 200, 300, 400) with at least a 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), the first drive motor (ICE) with the first input shaft (EW1) is rotatably connected or rotatably connectable, characterized in that the torque transmission device (10, 20, 30, 40) is designed according to one of claims 1 to 14.
[16]
16. Drive system (300, 400) according to claim 15, wherein the drive system (300, 400) has a second drive motor (EM), in particular an electrical machine (EM) which can be operated at least as a motor, the torque transmission device (30, 40) preferably one has second input shaft (EW2), and wherein the second drive motor (EM) with the second input shaft (EW2) is rotatably connected or rotatably connectable.
[17]
17. Drive system according to claim 15 or 16, wherein the second drive motor (EM) has an axis of rotation and the axis of rotation of the second drive motor is arranged coaxially to the first input shaft (EW1).
[18]
18. Drive system according to one of claims 15 to 17, wherein the second drive motor is arranged between the first drive motor (ICE) and the gear sets (WG, PGS1 and PGS2) of the torque transmission device,
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[19]
19. 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 one of the Is formed claims 1 to 14, wherein the drive system (100, 200, 300) is preferably designed according to one of claims 15 to 18.
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CX1 CQ X X £ X X COO X XX CXl OX X X XO X X X DT - CX1 CO CD
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BR 100 /
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200
LU
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CXI Cd X X X S XOX XXCOO X X X CXI O X X X X X O X X X X 2 CXI DT - CXI COm CD00
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Ο ΟΙ
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300
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CX1 Cd X XX£ X XX COO X XX X X CXl OX X X X X O X X X X X R (+ EM) 1 (+ EM) 2 (+ EM) 3 (+ EM) LLI 5 (+ EM) LLICD 0§LLI c T0 οίLLI H> OLLI E-CVT2 L1 (P) CX1 _1 a _1
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300
Ο
Ο σ
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400 ι ------------- 1 DGQ-1 Δ n
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CX1 Cd X X X X S XXX OX XX X X COO X X X X X CXl O X X X X X X O X X X X X X (ιλι3 +) ra R2 (+ EM) 1 (+ EM) 2 (+ EM) 3 (+ EM) 4 (+ EM) 5 (+ EM) LUCD 7 (+ EM) LU00 0§LU c T 0LU H> OLLI E-CVT2 E-CVT3L2 (P) CO_1 -1
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Ο
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06/27/2018
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New claims
1. Torque transmission device (10, 20, 30, 40), preferably for a motor vehicle, in particular for a hybrid vehicle, the torque transmission device (10, 20, 30, 40) having:
- a first input shaft (EW1),
- a second input shaft (EW2),
- a first planetary gear set (PGS1),
- a second planetary gear set (PGS2),
- another gear set (WG),
- a first separating clutch (C1),
- a second clutch (C2),
- a third clutch (C3),
a first braking device (B1),
- a second braking device (B2),
- 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 planet gear (P1), which meshes with the first sun gear (S1), and a planet carrier (PT) Rotationally supporting the at least one, first planet gear (P1), the second planetary gear set (PGS2) as second gear elements having a second sun gear (S2), at least one second planet gear (P2) and a ring gear (H2), the at least one, second planet gear (P2) with the second sun gear (S2), with the ring gear (H2) and with one of the first planet gears (P1) and rotatably supported on the planet carrier (PT), the further gear set (WG) being a first gear element ( WH) and at least one second gear element (WPT), the first gear element (WH) of the further gear set (WG) being rotatably connected or rotatably connectable to the first input shaft (EW1), the e rste separating clutch (C1) is designed for rotary connection of the first input shaft (EW1) with the planet carrier (PT),
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A 50763/2017
06/27/2018
PP31689AT wherein the second separating clutch (C2) is designed for the rotary connection of the second gear element (WPT) of the further gear set (WG) with the first sun gear (S1) of the first planetary gear set (PGS1), the first braking device (B1) for releasably fixing the second one Sun gear (S2) of the second planetary gear set (PGS2) is configured, wherein the second braking device (B2) is designed for releasably fixing the planet carrier (PT), and wherein the output shaft (AW) with the ring gear (H2) of the second planetary gear set (PGS2) is rotatably connected or rotatably connectable, characterized in that the second planetary gear set (PGS2) further has a third sun gear (S3), the at least one, second planet gear (P2) meshing with the third sun gear (S3), the third clutch (C3 ) is designed for the rotary connection of the second gear element (WPT) of the further gear set (WG) with the third sun gear (S3) of the z wide planetary gear set (PGS2), and the first sun gear (S1) of the first planetary gear set (PGS1) with the second input shaft (EW2) is rotatably connected or rotatably connectable.
2. 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 arranged between the second sun gear (S2) and the third sun gear (S3) of the second planetary gear set on an axis of rotation of one of the second planet gears (P2) in the axial direction.
3. Torque transmission device (10, 20, 30, 40) according to claim 1 or 2, wherein the third sun gear (S3) of the second planetary gear set (PGS2) is rotatably connected to a first hollow shaft (HW1), preferably within the first hollow shaft (HW1) the first input shaft (EW1) is at least partially arranged and / or guided, and in particular for establishing the rotary connection between the third sun gear (S3) and the second gear element (WPT) of the further gear set (WG) the third clutch (C3) with the first hollow shaft (HW1) is rotatably connectable.
68/72 [LAST CLAIMS]
A 50763/2017
06/27/2018
PP31689AT
4. Torque transmission device (10, 20, 30, 40) according to one of the claims
1 to 3, the first sun gear (S1) of the first planetary gear set (PGS1) being rotatably connected to a second hollow shaft (HW2), the first hollow shaft (HW1) and the first input shaft (EW1) preferably each being at least partially inside the second hollow shaft ( HW2) are arranged and / or guided, and in particular for establishing the rotary connection between the first sun gear (S1) of the first planetary gear set (PGS1) and the second gear element (WPT) of the further gear set (WG), the second clutch (C2) with the second hollow shaft (HW2) is rotatably connectable.
5. Torque transmission device (10, 20, 30, 40) according to one of the claims
1 to 4, wherein the second sun gear (S2) of the second planetary gear set (PGS2) is rotatably connected to a third hollow shaft (HW3), preferably the second hollow shaft (HW2), the first hollow shaft (HW1) and the first input shaft (EW1) each are at least partially arranged and / or guided within the third hollow shaft (HW3), and in particular for fixing the second sun gear (S2) of the second planetary gear set (PGS2) by means of the first braking device (B1), the third hollow shaft (HW3) by means of the first braking device (B1) can be determined.
6. Torque transmission device (10, 20, 30, 40) according to one of the claims
1 to 5, the further gear set (WG) having a planetary gear set (WPG) with a further sun gear (WS), at least one further planet gear (WP) which is rotatably supported on a further planet carrier (WPT), and a further ring gear ( WH), the at least one further planet gear (WP) of the planetary gear set (WPG) of the further gear set meshing with the further sun gear (WS) and the further ring gear (WH) of the planetary gear set (WPG) of the further gear set (WG).
7. Torque transmission device (10, 20, 30, 40) according to claim 6, wherein the further ring gear (WH) of the planetary gear set (WPG) of the further gear set (WG), the first gear element (WH) of the further gear set
5 (WG) and preferably the further planet carrier (WPT) of the planetary gear set (WPG) forms the second gear element of the further gear set
69/72 __________________________________________ [LAST CLAIMS **)
A 50763/2017
06/27/2018
PP31689AT (WG), whereby in particular the further sun gear (WS) of the planetary gear set (WPG) of the further gear set (WG) is fixed.
8. Torque transmission device (20, 40) according to one of claims 1 to 7, wherein the torque transmission device (20, 30) has a fourth separating clutch (C4), which preferably for rotationally connecting the first input shaft (EW1) with the third sun gear (S3) second planetary gear set (PGS2), the first input shaft (EW1) can be rotatably connected to the third sun gear (S3) of the second planetary gear set (PGS2) by means of the fourth clutch (C4), in particular via the first hollow shaft (HW1).
9. torque transmission device (30, 40) according to any one of claims 1 to 8, wherein the first sun gear (S1) of the first planetary gear set (PGS1) via the second hollow shaft (HW2), in particular with a defined gear ratio (ÜS) in between, with the second Input shaft (EW2) is rotatably connected or rotatably connectable.
10. torque transmission device (30, 40) according to claim 9, wherein the second input shaft (EW2) by means of the second clutch (C2) with the second gear element (WPT) of the further gear set (WG) is rotatably connectable, in particular with a defined gear ratio (ÜS) between.
11. Torque transmission device (10, 20, 30, 40) according to one of claims 1 to 10, wherein the first input shaft (EW1) forms an input side (E) of the torque transmission device (10, 20, 30, 40) and the output shaft (AW) is arranged coaxially to the first input shaft (EW1), the output shaft (AW) preferably forming an output side (A) of the torque transmission device (10, 20, 30, 40).
12. Torque transmission device (10, 20, 30, 40) according to one of the claims
1 to 11, the output shaft (AW) of the torque transmission device (10, 20, 30, 40) being located in the region of an end of the torque transmission device (10, 20, 30, 40) facing away from the input side (E).
70/72 [LAST CLAIMS]
A 50763/2017
06/27/2018
PP31689AT
13. Torque transmission device according to one of claims 1 to 11, wherein the output shaft (AW) of the torque transmission device is located in the region of the input side (E) of the torque transmission device.
14. Torque transmission device (10, 20, 30, 40) according to one of claims 1 to 13, wherein the torque transmission device (10, 20, 30, 40) is designed such that an axis of rotation of a second drive motor (EM), in particular an electrical machine , coaxial to the first input shaft (EW1) or parallel to the first input shaft (EW1) can be arranged.
15. Drive system (100, 200, 300, 400) with at least a 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), the first drive motor (ICE) with the first input shaft (EW1) is rotatably connected or rotatably connectable, characterized in that the torque transmission device (10, 20, 30, 40) is designed according to one of claims 1 to 14.
16. Drive system (300, 400) according to claim 15, wherein the drive system (300, 400) has a second drive motor (EM), in particular an electrical machine (EM) which can be operated at least as a motor, the torque transmission device (30, 40) preferably one has second input shaft (EW2), and wherein the second drive motor (EM) with the second input shaft (EW2) is rotatably connected or rotatably connectable.
17. Drive system according to claim 15 or 16, wherein the second drive motor (EM) has an axis of rotation and the axis of rotation of the second drive motor is arranged coaxially to the first input shaft (EW1).
18. Drive system according to one of claims 15 to 17, wherein the second drive motor is arranged between the first drive motor (ICE) and the gear sets (WG, PGS1 and PGS2) of the torque transmission device,
71/72 [LAST CLAIMS]
A 50763/2017
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PP31689AT related to a power flow direction from the first drive motor (ICE) to the torque transmission device.
19. 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 one of the Is formed claims 1 to 14, wherein the drive system (100, 200, 300) is preferably designed according to one of claims 15 to 18.
72/72 [LAST CLAIMS]

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同族专利:

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公开号 | 公开日

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WO2019051518A1|2019-03-21|

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AT520219B1|2019-02-15|

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法律状态:

优先权:

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申请号 | 申请日 | 专利标题

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ATA50763/2017A|AT520219B1|2017-09-12|2017-09-12|Torque transmission device, drive system and motor vehicle|ATA50763/2017A| AT520219B1|2017-09-12|2017-09-12|Torque transmission device, drive system and motor vehicle|

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PCT/AT2018/060203| WO2019051518A1|2017-09-12|2018-09-10|Torque transmission device, drive system, and motor vehicle|