• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a torque transmission device (10, 20, 30, 40, 50, 60), a drive system with a torque transmission device (10, 20, 30, 40, 50, 60) and a vehicle, wherein the torque transmission device (10, 20, 30 , 40, 50, 60) have a first input shaft (EW1), a Ravigneaux planetary gear set (PGS1 and PGS2), a further gear set (WG), three separating clutches (C1, C2, C3), a braking device (B1) and an output shaft ( AW). The further gear set (WG) has an input side and an output side, wherein the input side to the input shaft (EW1) is rotatably connected and the output side by means of the third separating clutch (C3) with the first sun gear (S1) of the Ravigneaux planetary gear set (PGS1 and PGS2 ) is drehverbindbar and / or by means of the second separating clutch (C2) with the second sun gear (S2) of the Ravigneaux planetary gear set (PGS1 and PGS2). The first separating clutch (C1) is designed for the rotary connection of the first input shaft (EW1) with the planet carrier (PT) of the Ravigneaux planetary gear set (PGS1 and PGS2), the braking device (B1) is designed for releasably fixing the second sun gear (S2) of the Ravigneaux Planetary gear set (PGS1 and PGS2) and the output shaft (AW) is rotatably connected to the second ring gear of Ravigneaux planetary gear set (PGS1 and PGS2).
    公开号:AT519487A1
    申请号:T50307/2017
    申请日:2017-04-13
    公开日:2018-07-15
    发明作者:Helmut Kassler Ing；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, 20, 30, 40, 50, 60), a drive system with a torque transmission device (10, 20, 30, 40, 50, 60) and a vehicle, the torque transmission device (10, 20, 30 , 40, 50, 60) a first input shaft (EW1), a Ravigneaux planetary gear set (PGS1 and PGS2), a further gear set (WG), three separating clutches (C1, C2, C3), a braking device (B1) and an output shaft ( AW). The further gear set (WG) has an input side and an output side, the input side being rotationally connected to the input shaft (EW1) and the output side by means of the third clutch (C3) with the first sun gear (S1) of the Ravigneaux planetary gear set (PGS1 and PGS2 ) is rotatably connectable and / or by means of the second clutch (C2) to the second sun gear (S2) of the Ravigneaux planetary gear set (PGS1 and PGS2). The first separating clutch (C1) is designed for the rotary connection of the first input shaft (EW1) to the planet carrier (PT) of the Ravigneaux planetary gear set (PGS1 and PGS2), the braking device (B1) is designed to releasably fix the second sun gear (S2) of the Ravigneaux Planetary gear set (PGS1 and PGS2) and the output shaft (AW) is rotatably connected to the second ring gear of the Ravigneaux planetary gear set (PGS1 and PGS2).
    (Fig. 2a) / 48
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    AVL List GmbH
    The torque transfer device
    The 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 clutch, a second clutch, a third clutch, and a first braking device and has an output shaft.
    The invention further 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 vehicle, in particular a motor 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 shifting elements in the form of separating clutches and / or braking devices are basically known from the prior art, for example from DE 10 2015 222 594 A1, US 8,246,500 B2 or WO 2014/063980 A1.
    The three aforementioned documents DE 10 2015 222 594 A1, US 8,246,500 B2 and WO 2014/063980 A1 each relate to generic torque transmission devices for a drive system with a primary drive and a primary drive 2/48
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    - 2 shaft, in particular for vehicles, the torque transmission devices disclosed in the aforementioned documents each having 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 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 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 CVT operation (Continuously Variable Transmission) can be implemented, in which the torque and speed can be variably adjusted.
    Depending on the arrangement and operative connection of the individual switching elements, i.e. of the individual separating clutches and braking devices, each other and in operative connection with the individual gear elements, there are different properties of the torque transmission device.
    Starting from this prior art, it is an object of the invention to provide an improved torque transmission device which is suitable for power split. Furthermore, it is an object of the invention to provide a corresponding drive system and a corresponding vehicle.
    This object is achieved 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.
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    - 3 A torque transmission device according to the invention has a first planetary gear set, which as a first gear elements a first. Sun gear, at least a 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 a second sun gear, a second ring gear and at least one second planet gear as second gear elements, wherein the at least one, second planet gear meshes with the second sun gear, the second ring gear and with one of the first planet gears and rotatably on the planet carrier is supported, in particular on the same planet carrier as the at least one first planet gear.
    The further gear set of a torque transmission device according to the invention has an input side and an output side, the input side of the further gear set being rotatably connected or rotatably connectable to the first input shaft and the output side of the further gear set being rotatably connectable to the first sun gear of the first planetary gear set by means of the third clutch and / or by means of the second clutch with the second sun gear of the second planetary gear set.
    The first separating clutch of a torque transmission device according to the invention is designed for the rotary connection of the first input shaft to the planet carrier and the first braking device is designed for releasably fixing the second sun gear of the second planetary gear set. The output shaft is rotatably connected or rotatably connectable to the second ring gear of the second planetary gear set.
    The first planetary gear set and the second planetary gear set form a Ravigneaux planetary gear set, which is preferably preceded by the further gear set in the power flow direction, starting from the first input shaft.
    The first input shaft of a torque transmission device according to the invention can preferably be rotatably connected to a first drive motor, in particular to an internal combustion engine.
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    - 4 The output shaft of a torque transmission device according to the invention is preferably rotatably or rotatably connected to a drivable axle of a vehicle.
    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.
    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 is at least partially supported in a transmission housing that at least partially surrounds the torque transmission device and / or is mounted in the transmission housing and / or in particular is at least partially led out of the transmission housing.
    An output shaft in the sense of the invention is a shaft or a transmission element, via which a mechanical power, in particular an output power, can be dissipated from the torque transmission device.
    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.
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    - 5 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 on one Planet carrier rotatably 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 being mechanically preferably rotationally connected to one another in a closed state of the separating clutch, in particular frictionally or positively, and in an open state independently of one another, in particular rotatably relative to one another.
    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 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 and therefore preferably cannot rotate and is therefore blocked in particular in its rotational movement. On the other hand, when the braking device is open, the gear element can preferably be moved in at least one of its intended degrees of freedom.
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    6 An input side of a transmission, in particular the input side of the further gear set, is understood to mean an area and / or at least one component of the associated transmission, via which power, in particular drive power, can be applied to the respective associated gear.
    An output side of a transmission, in particular the output side of the further transmission set, is to be understood in the sense of the invention in each case as an area and / or at least one component via which an output applied to the respectively associated transmission can be dissipated. 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, but can certainly be arranged close to one another on one side.
    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 loosened rotary connection when the disconnect coupling is open, i.e. When the disconnect clutch is open, the components connected by means of the disconnect clutch can rotate relative to one another, but can be rotatably connected to one another by closing the disconnect clutch and can therefore be rotatably connected to one another.
    With the above-described embodiment of a torque transmission device according to the invention, a torque transmission device can be provided in which as many translations as possible can be set with as few components as possible, in particular with the smallest possible overlap of the individual translations.
    With a torque transmission device according to the invention, at least five gears 7/48 that can be driven by means of a first drive motor can be driven, in particular with only four shifting elements, in particular with three separating clutches and only one braking device
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    - Realize 7 levels, especially in a particularly space-saving manner and with particularly advantageous levels of the individual ratios of the different gear levels.
    In an advantageous embodiment of a torque transmission device according to the invention, in particular in a particularly advantageous embodiment, the first sun gear of the first 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 rotational connection between the third sun clutch and the output side 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 further gear set has at least one first spur gear stage with at least a first spur gear and a second spur gear, the first spur gear preferably forming the input side of the further gear set and being rotatably connected or rotatably connectable to the first input shaft and to which second spur gear meshes. This makes it possible to provide a structurally particularly simple torque transmission device which has only little or no functional loss compared to a Lepelletier transmission, but is particularly cost-effective due to the configuration of the further transmission set as a spur gear stage instead of a planetary gear set.
    In a further advantageous embodiment of a torque transmission device according to the invention, the further gear set has a second spur gear stage with a third spur gear and a fourth spur gear, the third spur gear meshing with the fourth spur gear, the third spur gear preferably having an intermediate shaft with the second spur gear of the first spur gear stage is rotatably connected or rotatably connectable, and in particular the fourth spur gear forms the output side of the further gear set. As a result, the flexibility in the design of the torque transmission device, in particular with regard to the gradation of the individual gear ratios in the different gear stages, can be increased still further.
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    In a further advantageous embodiment of a torque transmission device according to the invention, in particular in a particularly space-saving embodiment, the fourth spur gear of the second spur gear stage can be rotatably connected or rotatably connected to a second hollow shaft, preferably the first input shaft and / or at least partially the inside of this second hollow shaft first hollow shaft is guided.
    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 first sun gear of the first planetary gear set, the first input shaft being connected to the first sun gear by means of the fourth separating clutch, in particular via the first hollow shaft of the first 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 braking device, the second braking device preferably being designed to releasably fix the planet carrier. As a result, at least one additional gear step can also be realized.
    In a further advantageous embodiment of a torque transmission device according to the invention, the first sun gear of the first planetary gear set is rotatably connected or rotatably connectable to a second input shaft, preferably via the first hollow shaft, in particular with a defined gear ratio in between.
    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
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    - 9 che is preferably also operable 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 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 second drive motor is used to boost the first drive motor generated drive power with appropriate speed synchronism, an additional torque can be superimposed.
    Furthermore, in at least one gear stage, so-called E-CVT operation (Electric - Continuously Variable Transmission operation) is possible, 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 that 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 energy store, in particular a battery or the like can be stored, and / or can be transferred directly to an electrical consumer to supply it.
    If the second input shaft is connected to the first sun gear at a defined gear ratio, particularly efficient operation of a drive system with an electric machine that can be operated as a motor can be achieved as the second drive motor in some cases, because with the gear ratio at / 48
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    Operation of the second drive motor in its optimal operating range, in particular in the range of its best possible efficiency, is made possible.
    The transmission stage is preferably designed as a spur gear stage and in particular is formed by at least one gear wheel that is non-rotatably connected to the first hollow shaft, in particular by a spur gear.
    Furthermore, so-called charging operation is possible in at least one gear stage, 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.
    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 at least one electrical machine which can be operated as a motor, the torque transmission device preferably having a second input shaft, and the second drive motor being in particular rotatably connected or rotatably connectable to the second input shaft. The second input shaft is preferably rotatably connected or rotatably connectable to the first sun gear of the first planetary gear set, in particular via the first hollow shaft, preferably with a defined gear ratio in between.
    A 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 an advantageous embodiment of a vehicle according to the invention, the output shaft of the torque transmission device is rotatably connected or rotatably connectable to at least one drivable axle of the vehicle.
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    At least one spur gear of at least one spur gear stage is preferably designed as a spur gear. In some cases, however, it can be more advantageous if at least one spur gear is designed as a helical toothed spur gear.
    Instead of at least one spur gear stage, a torque transmission device according to the invention in an advantageous embodiment can also have a further gear set with a different gear stage configuration. However, spur gear stages have the advantage that they are structurally particularly simple and therefore particularly cost-effective.
    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 vehicle according to the invention. Some of these features and properties are only described once, but apply independently of one another within the scope 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:
    1a shows a transmission plan of a first embodiment of a drive system according to the invention with a first embodiment of a torque transmission device according to the invention, / 48
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    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. 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. 3a 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. 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. 4a 1 shows a transmission plan of a fourth exemplary embodiment of a drive system according to the invention with a fourth exemplary embodiment of a torque transmission device according to the invention, Fig. 4b 4a shows a shift table associated with the drive system according to the invention with the possible switchable gear stages of the drive system from FIG. 4a, Fig. 5a 1 shows a transmission plan of a fifth exemplary embodiment of a drive system according to the invention with a fifth exemplary embodiment of a torque transmission device according to the invention,
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    5b shows a shift table associated with the drive system according to the invention from FIG. 5a with the possible switchable gear stages of the drive system from FIG. 5a,
    6a shows a transmission plan of a sixth embodiment of a drive system according to the invention with a sixth embodiment of a torque transmission device according to the invention and
    6b shows a shift table associated with the drive system according to the invention from FIG. 6a with the possible switchable gear stages of the drive system from FIG. 6a.
    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.
    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 and an output shaft AW, the output shaft having a drivable axis FD of a vehicle is rotatably connected, in this case with a drivable front axis FD.
    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 S1, a second ring gear H2 and a plurality of planet gears P2, each of which / 48
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    - 14 mesh with the second sun gear S2, the second ring gear H2 and in each case with one of the 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 addition, as already mentioned, the torque transmission device 10 according to the invention has a further gear set WG, which has an input side and an output side, the input side of the further gear set WG being rotationally connected to the first input shaft EW1 and the output side of the further gear set WG by means of the third Isolating clutch C3 can be rotationally connected to the first sun gear S1 of the first planetary gear set and / or by means of the second isolating clutch C2 to the second sun gear S2 of the second planetary gear set PGS2.
    The input shaft EW1 can also be rotatably connected to the planet carrier PT by means of the first clutch C1 which is also present, and the second sun gear S2 of the second planetary gear set PGS2 can be releasably fixed by means of the first brake device B1 which is also present. be blocked in its rotational movement if necessary.
    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 space-saving embodiment 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 is rotatably connected to a first hollow shaft HW1, within which the first input shaft is guided.
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    The first sun gear S1 of the first planetary gear set PGS1 can also be rotatably connected to the output side of the further gear set WG by means of the third clutch C3 via this first hollow shaft HW1.
    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 transmission WG is designed as a spur gear transmission with a first spur gear stage WGS1 and a second spur gear stage WGS2, the first spur gear stage WGS1 having a first spur gear Z1 and a second spur gear Z2, which with meshes with the first spur gear Z1, the first spur gear Z1 forming the input side of the further gear set WG and being rotationally connected to the first input shaft EW1.
    The second spur gear stage WGS2 of the further gear set WG has a third spur gear Z3 and a fourth spur gear Z4, in which case all spur gears Z1 to Z4 of the further gear set WG are designed as straight-toothed spur gears Z1 to Z4. The third spur gear Z3 of the second spur gear WGS2 meshes with the fourth spur gear Z4, the third spur gear Z3 via an intermediate shaft ZW with the second spur gear Z2 of the first spur gear WGS1, and the fourth spur gear Z4 forms the output side of the further gear set WG ,
    In order to enable a particularly space-saving design of the torque transmission device 10 according to the invention, in particular for a particularly space-saving arrangement of the further gear set WG within the torque transmission device 10 according to the invention, the fourth spur gear Z4 of the second spur gear stage WGS2 is rotatably connected to a second hollow shaft HW2, with inside the second hollow shaft HW2 the first input shaft EW1 and at least partially the first hollow shaft HW1 are guided.
    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 / 48
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    16 a translation in between to which planet carrier PT of the Ravigneaux planetary gear set is transmitted or indirectly, i.e. with a transmission in between, via the further gear set WG, via the first sun gear S1 and / or the second sun gear S2 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 rotates 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. The torque transmission device 10 according to the invention thus has a functionality similar to a so-called Lepelletier transmission, which likewise has a Ravigneaux planetary gear set, but which is preceded by a planetary gear set. The upstream connection of a further gear set WG, which is constructed as a spur gear stage, results in a structurally particularly simple construction and thus a particularly cost-effective torque transmission device 10.
    With 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, a total of five different gear stages can be provided with the four switching elements in the form of the three clutch clutches C1, C2 and C3 and the first braking device B1 realize, the shift table shown in Fig. 1b shows which shift elements C1, C2, C3 and B1 are each to be actuated to shift one of the gear stages 1 to 5. An “X” means that the respective switching element is actuated, which in the case of a disconnect clutch C1, C2, C3 corresponds to the closed state and, in the case of a braking device B1, to the blocked state.
    In a first gear stage 1, which occurs when the third clutch C3 is closed and the first brake device B1 is actuated while the first clutch C1 and the second clutch C2 are open, a drive power generated by the first drive motor ICE via the input shaft EW1 , continue on the / 48
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    17 first spur gear stage WGS1, in particular via the spur gears Z1 and Z2, and from there on via the second spur gear stage WGS2 (spur gears Z3 and Z4) and the third clutch C3 to the Ravigneaux planetary gear set, which consists of the first planetary gear set PGS1 and the second planetary gear set PGS2 is formed, are transmitted, the drive power being able to be supported via the second sun gear S2 due to the actuated first braking device B1 and thus being able to be dissipated to the drivable axis FD via the second ring gear H2 and via the output shaft AW rotatably connected to the second ring gear H2 ,
    If, on the other hand, the second clutch C2 and the third clutch C3 are closed while the first clutch C1 and the first braking device B1 are open, this results in gear stage 2 in which a drive power generated by the first drive motor ICE is likewise via the first input shaft EW1 and the others Gear set WG can be transferred to the Ravigneaux planetary gear set, in which case the drive power can be transferred to the first sun gear S1 via the third clutch C3 and the first hollow shaft HW1, as well as via the second clutch C2 and the second sun gear S2. As with the first gear, the drive power can be dissipated to the drivable axle via the second ring gear H2 and the output shaft AW.
    If, on the other hand, the first clutch C1 and the third clutch C3 are closed while the second clutch C2 and the first braking device B1 are open, gear stage 3 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 first Separating clutch C1 can be transferred to the planet carrier PT and introduced from there into the Ravigneaux planetary gear set. On the other hand, the drive power generated by the first drive motor ICE can be transmitted to the first sun gear S1 via the first input shaft EW1 and the further gear set WG and via the third separating clutch C3 and the first hollow shaft HW1 and can also be introduced from there into the Ravigneaux planetary gear set. As before, the drive power can be dissipated via the second ring gear H2 and the output shaft AW.
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    - 18 If the first clutch C1 and the second clutch C2 are closed while the third clutch C3 and the first braking device B1 are 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 Separating 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 separating clutch C2 and the second sun gear S2. The drive power is also dissipated via the second ring gear H2 and the output shaft AW.
    Gear stage 5 results when the first separating clutch C1 and the first braking device B1 are closed and the two separating clutches C2 and C3 are open. In this case, a drive power generated by the first drive motor ICE can only be introduced into the Ravigneaux planetary gear set via the first separating clutch C1 and the planet carrier PT. Due to the opened clutches C2 and C3, 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.
    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 differing from the torque transmission device 10 according to the invention shown in FIG. 1a in that the torque transmission device 20 according to the invention shown in FIG has additional gear ratio ÜS and a second input shaft EW2. Compared to the first exemplary embodiment of a drive system 100 according to the invention shown in FIG. 1a, the drive system 200 shown in FIG. 2a additionally has a second drive motor EM, which in this case is formed by an electrical machine EM which can be operated as a motor and generator and which is connected to the second Drive shaft EW2 of the torque transmission device 20 is connected in a rotationally fixed manner, so that a drive power generated by the second drive motor EM via the / 48th
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    - 19 second drive shaft EW2, the transmission stage ÜS, the first hollow shaft HW1 and the first sun gear S1 can be introduced into the Ravigneaux planetary gear set.
    Since the second exemplary embodiment of a torque transmission device 20 according to the invention shown in FIG. 2a is otherwise identical to the torque transmission device 10 according to the invention shown in FIG. 1a, the same five different gear stages 1 can also be used with the torque transmission device 20 according to the invention shown in FIG. 2a to 5 switch, in particular each by the same combination of the switching states of the individual switching elements C1 to C3 and B1, as can be seen from the associated switching table in Fig. 2b.
    Due to the additionally existing electrical machine EM as the second drive motor EM, a torque generated by the second drive motor EM can be superimposed in the aforementioned gear stages 1 to 5, however, with a corresponding operation of the second drive motor EM adapted to the speed of the first hollow shaft HW1 that in gear stages 1 to 5 a so-called “boosting” is possible with the help of the electrical machine EM, which is symbolized in each case by the expression “(+ EM)” in column 1 of the shift table in FIG. 2b.
    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 a purely electrical drive gear EM1, which is set when the three separating clutches C1, C2 and C3 are open and only the first braking device B1 closed is. In this case, the first drive motor ICE is decoupled from the planet carrier PT because of 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. The drive power generated by the second drive motor EM can be transmitted via the second input shaft EW2, the transmission stage ÜS and the first hollow shaft HW1 to the first sun gear S1 of the first planetary gear set PGS1 and introduced into the Ravigneaux planetary gear set. Due to the closed, first braking device B1, the / 48
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    - 20 drive power introduced into the Ravigneaux planetary gear set via the first sun gear S1 are supported via the second sun gear S2 of the second planetary gear set PGS2 and are dissipated as drive power via the second ring gear H2 and the output shaft AW to the drivable axis FD.
    In addition, there are two further gear stages, which are referred to as E-CVT1 and E-CVT2, in which both the first drive motor ICE and the second drive motor EM can each provide drive power, which can be superimposed to form a total drive power, whereby 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.
    These two gear stages E-CVT1 and E-CVT2 have the advantage that the first drive motor, particularly 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 range of its optimal efficiency, so that particularly efficient operation of the drive system 200 with these two gear stages becomes possible.
    The first gear stage with E-CVT1 with infinitely adjustable speed results (see FIG. 2b) when the second clutch C2 is closed, and the other shift elements, in particular the first clutch C1, the third clutch C3 and the first braking device B1, are always 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 further gear set WG and the second separating clutch C2 and the second sun gear S2, and the drive power generated by the second drive motor EM 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.
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    - 21 The second gear stage E-CVT2 with infinitely variable speed results when the first clutch C1 is closed and the second clutch C2, the third clutch C3 and the first brake device B1 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 first hollow shaft HW1 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.
    Furthermore, in at least one gear stage, a so-called charging operation L is possible in which electrical energy can be generated when the vehicle is at a standstill, also called “charging while stationary”. This can be advantageous in order to be able to increase a state of charge of the battery, even when the vehicle is not in the driving mode.
    In the gear stages L1 (P) and L2 (P) shown in Fig. 2b, the drivable axis and / or the output shaft AW must be secured by means of a further switching element (P), in particular a locking device or a parking brake, in order to transmit a To prevent torque on the wheels. L1 (P) corresponds to E-CVT 1 and L2 (P) corresponds to E-CVT 2.
    Charging operation without parking lock is possible in gear L3. When loading at the stand, however, the parking lock "P" must usually be engaged so that the vehicle cannot start to roll independently (e.g. on a slope).
    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, with this exemplary embodiment of a drive system 300 according to the invention likewise as in the exemplary embodiment / 48 shown in FIG. 1a
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    22 of a drive system 100 according to the invention, only a first drive motor ICE in the form of an internal combustion engine is present, which is rotatably connected to the first input shaft EW1.
    The torque transmission device 30 according to the invention shown in FIG. 3a likewise has, like the torque transmission device 10 according to the invention shown in FIG. 1a, in each case likewise only has a first input shaft EW1. In addition, however, the torque transmission device 30 according to the invention has a fourth separating clutch C4, via which the first input shaft EW1 can be rotatably connected to the first hollow shaft HW1, and a second braking device B2, by means of which the planet carrier PT can be releasably fixed, i.e. can be blocked in its rotational movement.
    The torque transmission device 30 according to the invention shown in FIG. 3a makes it possible to provide a drive system 300 with which it is additionally possible to reverse in relation to the drive system from FIG. 1a (see gear stage R in FIG. 3b). There are also two further gear steps 6 and 7 (see also FIG. 3b).
    As can be seen from the shift table shown in FIG. 3b, the reverse gear R is set when the second clutch C2 and the second brake device B2 are closed, while the other shift elements, in particular the first clutch C1, the third clutch C3 and the first braking device B1 are opened. 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, the further gear set WG, the second separating clutch C2 and the second sun gear S2, with a torque support being provided via the second braking device B2 leads to a reversal of the direction of rotation of the ring gear H2 non-rotatably connected to the output shaft AW, whereby a drivable axis FD connected to the output shaft AW can be driven in the opposite direction, in this case in the reverse direction.
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    23 The gear steps 2 to 4, 6 and 7 correspond to the gear steps 1 to 5 from FIG. 1b, reference being made in this regard to the explanations in connection with FIGS. 1a and 1b with regard to the power paths that arise.
    The gear stage 1 resulting from the additional, second brake device B2 arises when the third clutch C3 and the second brake device B2 are closed and the other shifting elements in the form of the first clutch C1, the second clutch C2, the fourth clutch C4 and of the first braking device B1 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, the further gear set WG, the third clutch C3, the first hollow shaft HW1 and the first sun gear S1 and via the closed, second braking device B2 are supported and transmitted as drive power via the second ring gear H2 to the output shaft AW and from there to a drivable axis FD.
    The gear stage 5 resulting from the additional, fourth clutch C4 occurs when the first clutch C1 and the fourth clutch C4 are closed and the other shift elements in the form of the second clutch C2, the third clutch C3, the first braking device B1 and second braking device B2 are 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 to the planet carrier PT via the first separating clutch C1 and introduced into the Ravigneaux planetary gear set via this and on the other hand via the fourth separating clutch C4, the first Hollow shaft HW1 and the first sun gear S1 and as drive power are also dissipated to a drivable axis FD via the second ring gear H2 and the output shaft AW.
    FIG. 4a shows a fourth exemplary embodiment of a drive system 400 according to the invention with a fourth exemplary embodiment of a torque transmission device 40 according to the invention, the torque transmission device 40 shown in FIG. 4a only being in the additionally available transmission stage ÜS and / 48
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    24 distinguishes the second input shaft EW2 from the torque transmission device 30 shown in FIG. 3a, analogously to the torque transmission device 20 shown in FIG. 2a compared to the torque transmission device 10 shown in FIG. 1a.
    The drive system 400 according to the invention shown in FIG. 4a likewise has, like the drive system 200 according to the invention shown in FIG. 2a, both a first drive motor ICE designed as an internal combustion engine ICE and a second drive motor EM, which is designed as a motor as well as a motor is also formed as a generator operable electrical machine EM and is rotatably connected to the second input shaft EW2.
    As can be seen from the associated shift table in FIG. 4b, with the torque transmission device 40 according to the invention shown in FIG. 4a or the drive system 400 according to the invention shown in FIG. 4a, in addition to a reverse gear R, a total of ten gear stages are possible, in which one of the first drive motors ICE generated drive power is transferable to the output shaft AW, wherein in all of these gear stages 1 to 10 and also in reverse gear R an electric boost using the second drive motor EM is possible. Furthermore, a purely electric drive is possible in two gear stages EM 1 and EM2, and E-CVT operation in two gear stages E-CVT1 and ECVT2.
    Gear stages 1 to 7 basically correspond to gear stages 1 to 7 from FIG. 3b, reference being made to the explanations in connection with FIGS. 3a and 3b for more detailed explanations, in particular with regard to the individual power flows which arise in the respective gear stages ,
    In gear stage 8, which occurs when the fourth clutch C4 and the first braking device B1 are closed while the other shifting elements C1 to C3 and B2 are open, a drive power generated by the first drive motor ICE can be generated via the first input shaft EW1 and the fourth Separating clutch C4 are transmitted to the first hollow shaft HW1 and are introduced from there via the first sun gear S1 into the Ravigneaux planetary gear set, the drive power being via the / 48
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    25 second sun gear S2, which is blocked with the aid of the first braking device B1, can be supported and can thus be removed via the second ring gear H2 and the output shaft AW.
    In gear 9, which occurs when the fourth clutch C4 and the second brake device B2 are closed while the other shifting elements C1 to C3 and B1 are open, a drive power generated by the first drive motor ICE can be applied to the first hollow shaft via the fourth clutch C4 HW1 are transmitted and from this are introduced into the Ravigneaux planetary gear set via the first sun gear S1 and are supported on the planet carrier PT, which is blocked with the aid of the second braking device B2. The drive power can also be dissipated via the second ring gear H2 and the output shaft AW.
    In gear stage 10, which occurs when the fourth clutch C4 and the second clutch C2 are closed while the other shifting elements C1, C3, C4, B1 and B2 are open, a drive power generated by the first drive motor ICE can be via the fourth clutch C4 are transmitted to the first hollow shaft HW1 and are introduced into the Ravigneaux planetary gear set via the first sun gear S1, as well as via the further gear set WG and the second clutch C2 and the second sun gear S2. The drive power can also be dissipated via the second ring gear H2 and the output shaft AW.
    As with the drive system 200 according to the invention explained with reference to FIG. 2a, the drive system 400 according to the invention shown in FIG. 4a enables the provision of two so-called E-CVT gear stages E-CVT1 and E-CVT2, in which a rotational speed of the axle that can be driven FD transferable drive power is infinitely adjustable, only the second clutch C2 having to be closed to set the first E-CVT gear E-CVT1, while the other shifting elements C1, C3, C4, B1 and B2 are each open. The second E-CVT gear E-CVT2, on the other hand, results when the first separating clutch C1 is closed and the other separating clutches C2, C3 and C4 and the two braking devices B1 and B2 are each open. The drive power can also be dissipated via the second ring gear H2 and the output shaft AW.
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    - 26 Likewise, purely electric driving, i.e. the complete decoupling of the first drive motor ICE from the output shaft AW and the generation of the drive power completely using the second drive motor EM, possible, in particular with two different gear stages EM1 and EM2, the first, purely electrically drivable gear stage EM1 resulting when the second braking device B2 is closed, while the other switching elements C1 to C4 and B1, ie in particular, all separating clutches C1 to C4 and the first braking device B1 are open.
    In this case, a drive power generated by the second drive motor EM can be introduced into the Ravigneaux planetary gear set via the second input shaft EW2, the transmission stage ÜS and the first hollow shaft HW1 and the first sun gear S1 and can be supported on the planet carrier PT which uses the second braking device B2 is set. The drive power can also be dissipated via the second ring gear H2 and the output shaft AW.
    The second, purely electrically drivable gear stage, EM2, however, results, like the gear stage EM1, in the drive system 200 according to the invention shown in FIG. 2a (see FIG. 2b), in which only the first braking device B1 is closed and the other switching elements C1 to C4 and the second brake device B2 are opened. The drive power generated by the second drive motor EM can also be transmitted, as in the gear stage EM1 from FIG. 2b via the second input shaft EW2, the transmission stage ÜS to the first hollow shaft HW1 and introduced by the latter via the first sun gear S1 into the Ravigneaux planetary gear set are, wherein the applied drive power can be supported on the second sun gear S2, which is fixed with the aid of the first braking device B1. The drive power can also be dissipated via the second ring gear H2 and the output shaft AW.
    It should be noted that in the shift table shown in FIG. 4b, the numbering of the individual gear stages 1 to 10 only serves and does not imply the unambiguous designation of the individual gear stages 1 to 10 in connection with the associated shift states of all shift elements C1 to C4 and B1 and B2 that the gear ratio increases or decreases with increasing gear.
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    - 27 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 gear stages 1 to 10 according to the shift table from FIG. 4b in conjunction with the respective combinations of the individual gear stages Switching states of the individual switching elements C1 to C4 and B1 and B2 lead to an advantageous translation step or which do not result in a meaningful translation step.
    In the present case, the gear elements of the torque transmission device 40 according to the invention are designed in such a way that there are meaningful or advantageous translations for the gear stages 1 to 7 and advantageous gradations between them. In this case, this results in gear ratios 8, 9 and 10, which are possible and switchable, but have no advantageous added value.
    In the present case, the transmission elements are designed in particular in such a way that a gear ratio of 4.17081 from the first drive motor ICE to the output shaft AW is set in gear stage 1 and 0.691057 in gear stage 7. However, this results in gear ratio 9 of 2.741935, which does not harmonize with gear levels 1 to 7 or does not blend in harmoniously between the individual gear levels 1 to 7, and therefore does not bring any meaningful added value.
    With differently designed gear elements, reasonable gear ratios in gear stages 8, 9 and 10 can be achieved. However, less advantageous or less usable translations will very likely arise in other gear stages.
    With the torque transmission device 40 according to the invention shown in FIG. 4a or the drive system 400 according to the invention shown in FIG. 4a, however, at least seven sensible gear stages can generally be implemented, in particular for gear stages 1 to 7 according to the shift table shown in FIG. 4b ,
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    - 28 i.e. effectively, the torque device 40 according to the invention shown in FIG. 4a has ten possible gear stages 1 to 10, in which a pure drive by means of the first drive motor ICE or a boost operation is possible, wherein at least seven sensible ratios can be achieved with these 10 gear stages , which in this case correspond to gear stages 1 to 7 due to the specific design of the individual gear elements.
    Because of the identical structure of the torque transmission device 30 according to the invention shown in FIG. 3a, this applies equally to the torque transmission device 30. However, only the advantageous gear stages 1 to 7 are shown in the associated shift table in FIG. 3b.
    Furthermore, in at least one gear stage in the transmission according to FIG. 4a, a so-called charging operation L is also possible, in which electrical energy can be generated when the vehicle is at a standstill, also called “charging while stationary”. This can be advantageous in order to be able to increase a state of charge of the battery, even when the vehicle is not in the driving mode.
    In the gear stages L1 (P) and L2 (P) shown in Fig. 4b, the drivable axis and / or the output shaft AW must be secured by means of a further switching element (P), in particular a locking device or a parking brake, in order to transmit a To prevent torque on the wheels. L1 (P) corresponds to E-CVT 1 and L2 (P) corresponds to E-CVT 2.
    Charging without a parking lock is possible in gear stages L3 and L4. When loading at the stand, however, the parking lock "P" must usually be engaged so that the vehicle cannot start to roll independently (e.g. on a slope).
    5a shows a fifth embodiment of a drive system 500 according to the invention with a fifth embodiment of a torque transmission device 50 according to the invention, the torque transmission device 50 being based on the torque transmission device 10 according to the invention shown in FIG. 1a, but additionally having a second braking device B2.
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    - 29 Due to the additional, second brake device B2 compared to the torque transmission device 10 according to the invention from FIG. 1a, two further mechanical gear stages can be shifted with the torque transmission device 50 according to the invention from FIG. 5a, namely those in FIG. 5b with “R” and “1” designated gear steps. The gear stages 2 to 6 from FIG. 5b correspond to the gear stages 1 to 5 from FIG. 1b, the gear stages 2 to 6 from FIG. 5b each being set by the same combination of the switching states of the individual switching elements C1 to C3 and B1 as in gears 1 to 5 from Fig. 1b.
    The reverse gear R is obtained (see FIG. 5b) when the second separating clutch C2 and the second braking device B2 are closed and the other shift elements, in particular the first separating clutch C1, the third separating clutch C3 and the first braking device B1, are each open are.
    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 second separating clutch C2 and the second sun gear S2 and via the second ring gear H2 and the output shaft AW to the drivable one Axis FD are discharged. This results in a reversal of the direction of rotation and the drive power is dissipated in the opposite direction of rotation, which enables reverse driving.
    The further, additional mechanical gear stage 1 is established when the third clutch C3 and the second brake device B2 are closed, while 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 also be introduced into the Ravigneaux gear set via the first input shaft EW1 and the further gear set WG, in this case, however, via the third clutch C3 and the first sun gear S1 and not as in reverse gear the second clutch C2 and the second sun gear S2. In this case it does not happen / 48
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    - 30 to a reversal of the direction of rotation. The drive power introduced into the Ravigneaux gear set can also be dissipated to the drivable axis FD via the second ring gear H2 and the output shaft AW.
    An extension of the torque transmission device 50 according to the invention by a fourth separating clutch C4 for rotationally connecting the first input shaft EW1 to the first sun gear S1 of the first planetary gear set PGS 1 leads to the torque transmission device 30 from FIG. 3a and thus to a further mechanical gear stage (cf. gear stage 5, 3b).
    6a shows a sixth exemplary embodiment of a drive system 600 according to the invention with a sixth exemplary embodiment of a torque transmission device 60 according to the invention, wherein the torque transmission device 60 is based on the torque transmission device 20 from FIG. 2a, but additionally has a second braking device B2 with which the planet carrier PT can be detachably fixed can.
    The additional, second braking device B2 likewise leads to the fact that with this embodiment of a torque transmission device 60 according to the invention, as in the fifth embodiment of a torque transmission device 50 according to the invention described above with reference to FIG. 5a, two additional mechanical gear stages, namely a reverse gear R and gear 1, 6b, which can be set in each case by the same combination of the switching states of the individual switching elements C1 to C3 and B1 and B2 and each lead to the same performance threads as in the torque transmission device 50 according to the invention from FIG. 5a (cf. switching tables from FIGS. 5b and 6b).
    In addition, the sixth exemplary embodiment of a drive system 600 according to the invention shown in FIG. 6 a has a further purely electrical drive gear due to the additional second braking device B2, which is designated EM1 in this case, while the drive gear designated EM2 from the shift table from / 48
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    - FIG. 6b corresponds to the purely electrical drive gear EM1 from FIG. 2b. The purely electrical gear stage EM1 results when the second braking device B2 is closed and the other shifting elements, in particular all three separating clutches C1 to
    C3 and the first braking device B1 are open.
    In this case, a drive power generated by the second drive motor EM can be introduced into the Ravigneaux gear set via the second input shaft EW2, the transmission stage ÜS and the first hollow shaft HW1 and the first sun gear S1 and via the second ring gear H2 and the output shaft AW to the drivable one Axis FD are discharged.
    An extension of the torque transmission device 60 according to the invention by a fourth separating clutch C4 for rotationally connecting the first input shaft EW1 to the first sun gear S1 of the first planetary gear set PGS 1 leads to the torque transmission device 40 from FIG. 4a and thus to four further mechanical gear stages (cf. gear stages 5 and 8 to 10, Fig. 4b).
    A torque transmission device according to the invention thus 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 five, up to ten purely mechanical gear stages, in each of which superimposition with a drive power generated by a second drive motor is possible, with a reverse gear, with up to two purely electrical gear stages, with up to two E-CVT gears and with up to three charging gears.
    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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    - 32 -LIST OF REFERENCE NUMBERS 10, 20, 30, 40, 50, 60 Torque transmission device according to the invention 100, 200, 300, 400,500, 600 drive system according to the invention
    AW output shaft B1 first braking device B2 second braking device C1 first clutch C2 second clutch C3 third clutch C4 fourth disconnect clutch EM second drive motor, electric machine EW1 first input shaft DR2 second input shaft FD drivable axis HW1 first hollow shaft HW2 second hollow shaft ICE first drive motor, internal combustion engine P1 first planet wheel P2 second planet gear PGS1 first planetary gear set PGS2 second planetary gear set PT planet carrier33/48
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    S1 first sun gear S2 second sun gear excess sludge translation stage WG another gear set WGS1 first spur gear stage WGS2 second spur gear stage
    Z1 first spur gear Z2 second spur gear Z3 third spur gear Z4 fourth spur gear ZW intermediate shaft
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    权利要求:
    Claims (12)
    [1]
    claims
    1. Torque transmission device (10, 20, 30, 40, 50, 60), preferably for a motor vehicle, in particular for a hybrid vehicle, the torque transmission device (10, 20, 30, 40, 50, 60) having:
    - a first input shaft (EW1),
    - a first planetary gear set (PGS1),
    - a second planetary gear set (PGS2),
    - another gear set (WG),
    - a first separating clutch (C1),
    - a second clutch (C2),
    - a third clutch (C3),
    a first braking device (B1),
    - And an output shaft (AW), wherein the first planetary gear set (PGS1) as first gear elements a first sun gear (S1), at least a first 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), a second ring gear (H2) and at least a second planet gear (P2), the at least one , second planet gear (P2) with the second sun gear (S2), the second ring gear (H2) and with one of the first planet gears (P1) meshes and is rotatably supported on the planet carrier (PT), the further gear set (WG) having an input side and has an output side, the input side of the further gear set (WG) being rotatably connected or rotatably connectable to the first input shaft (EW1) and the output side of the further gear set (W G) can be rotatably connected to the first sun gear (S1) of the first planetary gear set (PGS1) by means of the third clutch (C3) and can be rotationally connected to the second sun gear (S2) of the second planetary gear set (PGS2) by means of the second clutch (C2),
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    - 35, wherein the first separating clutch (C1) is designed for rotary connection of the first input shaft (EW1) to the planet carrier (PT), the first braking device (B1) being designed to releasably fix the second sun gear (S2) of the second planetary gear set (PGS2) , and wherein the output shaft (AW) with the second ring gear (H2) of the second planetary gear set (PGS2) is rotatably connected or rotatably connected.
    [2]
    2. Torque transmission device (10, 20, 30, 40, 50, 60) according to claim 1, wherein the first sun gear (S1) of the first planetary gear set (PGS1) is rotatably connected to a first hollow shaft (HW1), preferably within the first hollow shaft ( HW1) the first input shaft (EW1) is at least partially guided, and in particular for establishing the rotary connection between the first sun gear (S1) and the output side of the further gear set (WG) the third separating clutch (C3) can be rotatably connected to the first hollow shaft (HW1) is.
    [3]
    3. Torque transmission device (10, 20, 30, 40, 50, 60) according to claim 1 or 2, characterized in that the further gear set (WG) has at least one first spur gear stage (WGS1) with at least one first spur gear (Z1) and one second spur gear (Z2), the first spur gear (Z1) preferably forming the input side of the further gear set (WG) and being rotatably connected or rotatably connectable to the first input shaft (EW1) and meshing with the second spur gear (Z2).
    [4]
    4. Torque transmission device (10, 20, 30, 40, 50, 60) according to one of claims 1 to 3, characterized in that the further gear set (WG) has a second spur gear stage (WGS2) with a third spur gear (Z3) and a fourth Spur gear (Z4), the third spur gear (Z3) meshing with the fourth spur gear (Z4), preferably the third spur gear (Z3) via an intermediate shaft (ZW) with the second spur gear (Z2) of the first spur gear stage (WGS1) or is rotatably connectable, and in particular the fourth spur gear (Z4) forms the output side of the further gear set (WG).
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    [5]
    5. Torque transmission device (10, 20, 30, 40, 50, 60) according to claim 4, characterized in that the fourth spur gear (Z4) of the second spur gear stage (WGS2) with a second hollow shaft (HW2) is rotatably connected or rotatably connectable, preferably the first input shaft (EW1) and / or the first hollow shaft (HW1) is at least partially guided within the second hollow shaft (HW2).
    [6]
    6. Torque transmission device (30, 40) according to any one of claims 1 to 5, wherein the torque transmission device (30, 40) has a fourth clutch (C4), which preferably for rotationally connecting the first input shaft (EW1) with the first sun gear (S1) The first planetary gear set (PGS1) is configured, wherein the first input shaft (EW1) can be rotatably connected to the first sun gear (S1) of the first planetary gear set (PGS1) by means of the fourth clutch (C4), in particular via the first hollow shaft (HW1).
    [7]
    7. torque transmission device (30, 40, 50, 60) according to one of claims 1 to 6, wherein the torque transmission device (30, 40, 50, 60) has a second braking device (B2), the second braking device (B2) preferably for releasable Setting the planet carrier (PT) is designed.
    [8]
    8. torque transmission device (20, 40, 60) according to one of claims 1 to 7, wherein the first sun gear (S1) of the first planetary gear set (PGS1) with a second input shaft (EW2) is rotatably connected or rotatably connectable, preferably via the first hollow shaft (HW1 ), especially with a defined translation level (ÜS) in between.
    [9]
    9. Drive system (100, 200, 300, 400, 500, 600) with at least one first drive motor (ICE), in particular an internal combustion engine (ICE), and a torque transmission device (10, 20, 30, 40, 50, 60) with one first input shaft (EW1), wherein 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, 50, 60) according to any one of claims 1 to 8 is formed.
    37/48
    PP31480AT
    13/04/2017
    [10]
    10. Drive system (200, 400, 600) according to claim 9, characterized in that the drive system (200, 400, 600) 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 (20, 40, 60) preferably has a second input shaft (EW2), and the second drive motor (EM) in particular being rotatably connected or rotatably connectable to the second input shaft (EW2).
    [11]
    11. Motor vehicle, in particular hybrid vehicle, with a drive system (100, 200, 300, 400, 500, 600) with a torque transmission device (10, 20, 30, 40, 50, 60), characterized in that the torque transmission device (10, 20 , 30, 40, 50, 60) is designed according to one of claims 1 to 8, wherein the drive system (100, 200, 300, 400, 500, 600) is preferably designed according to claim 9 or 10.
    [12]
    12. Vehicle according to claim 11, characterized in that the output shaft (AW) of the torque transmission device (10, 20, 30, 40, 50, 60) with at least one drivable axis (FD) of the vehicle is rotatably connected or rotatably connectable.
    38/48
    PP31480AT
    1.9
    PGS1 PGS2
    EW1
    ICE
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    同族专利:
    公开号 | 公开日
    AT519486A1|2018-07-15|
    CN110234529A|2019-09-13|
    DE102016226090A1|2018-06-28|
    AT519487B1|2019-02-15|
    DE112017006505A5|2019-10-24|
    AT519486B1|2019-01-15|
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    DE102004028102A1|2003-06-12|2005-02-10|Honda Motor Co., Ltd.|Power transmission device for a hybrid vehicle|
    DE10346640A1|2003-10-08|2005-05-12|Zahnradfabrik Friedrichshafen|Powertrain for a hybrid vehicle|
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    JP4720898B2|2008-11-21|2011-07-13|トヨタ自動車株式会社|Hybrid drive device for vehicle|
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    CN102785564B|2012-08-24|2014-12-24|北京理工大学|Front-wheel-driven dual-mode four-gear hybrid drive device|
    AT513538B1|2012-10-22|2015-01-15|Avl List Gmbh|transmission|
    CN202986797U|2012-11-30|2013-06-12|长城汽车股份有限公司|Blending power device|
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    CN110816253B|2019-11-20|2021-02-02|奇瑞汽车股份有限公司|Gear ring-free planetary gear train hybrid power system|
    DE102019131572A1|2019-11-22|2021-05-27|Schaeffler Technologies AG & Co. KG|Gear unit with two planetary gear sets and a one-piece planetary gear carrier and a motor vehicle with such a gear unit|
    CN110884339A|2019-11-28|2020-03-17|北京航空航天大学|Multi-gear bit-string parallel type electromechanical coupling transmission device|
    CN110901367B|2019-11-28|2021-02-02|北京航空航天大学|Series-parallel electromechanical coupling transmission device|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    DE102016226090.1A|DE102016226090A1|2016-12-22|2016-12-22|The torque transfer device|PCT/EP2017/084025| WO2018115245A1|2016-12-22|2017-12-21|Torque-transmitting device, drive system, and motor vehicle|
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