DE102018200297A1 - Transmission for a motor vehicle - Google Patents

Abstract

The invention relates to a transmission (G) for a motor vehicle, comprising an electric machine (EM), a drive shaft (GW1), an output shaft (GWA), three planetary gear sets (P1, P2, P3) and six shifting elements (A, B, C, D, E, F), wherein by selectively operating the six switching elements (A, B, C, D, E, F) different gears switchable and also in interaction with the electric machine (EM) different operating modes are displayed, and drive train for a motor vehicle with such a transmission (G) and method of operating the same.

Description

The invention relates to a transmission for a motor vehicle, comprising an electric machine, a drive shaft, an output shaft, and a first planetary gear set, a second planetary gear set and a third planetary gear set, wherein the first, the second and the third planetary gear each have a first element, each a second Element and each have a third element, wherein the first element is formed by a respective sun gear of the respective planetary gear, wherein the second element in the case of a minus planetary gear set by a respective planetary land and in the case of a plus planetary gear set by a respective ring gear of the respective planetary gear set is formed, wherein the third element is formed in the case of a minus planetary gear set by the respective ring gear and in the case of a plus planetary gear set by the respective planetary gear of the respective planetary gear, wherein a first, a second, a third, a fourth, a fifth and a sixth switching element are provided by d he selective operation at least six gears between the drive shaft and the output shaft are represented, and wherein a rotor of the electric machine is connected to the drive shaft, the output shaft or at least one of the elements of the planetary gear sets.

In hybrid vehicles, transmissions are known which, in addition to a wheelset, also have one or more electric machines. The transmission is usually designed to be more continuous, d. H. There are several different ratios as gears between a drive shaft and an output shaft by operating corresponding switching elements switchable, this is preferably done automatically. Depending on the arrangement of the switching elements, these are clutches or brakes. The transmission is used to implement a traction power supply of a prime mover of the motor vehicle in terms of various criteria suitable. The gears of the transmission are usually used in conjunction with the at least one electric machine to represent a purely electric driving. Often, the at least one electric machine can also be incorporated in the transmission to display different modes of operation in different ways.

From the DE 10 2014 218 610 A1 goes out a gear that includes three planetary gear sets and an electric machine in addition to a drive shaft and an output shaft. Furthermore, in one variant, six switching elements are provided, via which different power flows from the drive shaft to the output shaft realized by showing different gears and also different engagements of the electric machine can be designed. Here, a purely electric driving can be represented by sole drive on the electric machine.

It is the object of the present invention to provide an alternative embodiment to the known from the prior art transmission for a motor vehicle, with which in a compact structure different operating modes can be displayed in a suitable manner.

This object is achieved on the basis of the preamble of claim 1 in conjunction with its characterizing features. The following dependent claims give each advantageous embodiments of the invention. A motor vehicle drive train is also subject matter of claim 10. Furthermore, the claims 11 and 12 each have a method for operating a transmission to the object.

According to the invention, a transmission comprises an electric machine, a drive shaft, an output shaft and a first planetary gear set, a second planetary gear set and a third planetary gear set. The planetary gear sets comprise a plurality of elements, each of the planetary gear sets in each case a first element, a second element and a respective third element are assigned. The first element is formed by a respective sun gear of the respective planetary gear set, while the second element is formed in the case of a minus planetary gear set by a respective planetary land and in the case of a plus planetary gear set by a respective ring gear of the respective planetary gear. The third element is in the case of a minus planetary gear set as a ring gear and in the case of a plus planetary gear set as a planetary web of the respective planetary gear set.

The planetary gear sets can, if it allows a connection of the elements, so in the context of the invention each present as a minus planetary gear set, wherein it is in the first element of each planetary gearset then a sun gear, wherein the second element of the respective planetary gear set is a planetary gear and the third element of the respective planetary gear set to a ring gear. A minus planetary set is composed in a manner known in principle to the person skilled in the art from the elements sun gear, planet carrier and ring gear, wherein the planet carrier at least one, but preferably several planet gears rotatably mounted, in detail each with both the sun gear, and comb the surrounding ring gear.

Alternatively, but one or more of the planetary gear sets, if it allows the connection of the respective elements, as a plus-planetary gear, wherein it is the first element of each planetary gear then a sun gear, in the second element of the respective planetary gear around Ring gear and the third element of each planetary gear set is a planetary land. In a plus-planetary gear set the elements sun gear, ring gear and planetary gear are also present, the latter at least one pair of planetary leads, in which one planetary gear with the inner sun gear and the other planet gear meshing with the surrounding ring gear, and the planet gears mesh with each other.

Where there is a connection of the individual elements, a minus planetary gear set can be converted into a plus-planetary gear set, in which case compared to the design as a minus planetary gear set the Hohlrad- and the Planetensteganbindung to swap with each other, and a Getriebestandübersetzung is to increase by one. Conversely, a plus planetary gear set could be replaced by a minus planetary gear set, if the connection of the elements of the transmission makes this possible. In this case, compared to the plus planetary gear set, the ring gear and the planet web connection would then also have to be exchanged with each other, as well as a transmission gear ratio reduced by one. Particularly preferably, however, all three planetary gear sets are present as minus planetary gear sets.

In addition, a first, a second, a third, a fourth, a fifth and a sixth switching element are provided by the selective actuation of six gears between the drive shaft and the output shaft can be represented. Particularly preferred can be formed by the gear ratio ago exactly six different gears between the drive shaft and the output shaft. Furthermore, the electric machine communicates with the drive shaft, with the output shaft or at least one of the elements of the planetary gear sets in combination.

For the purposes of the invention, a "shaft" is understood to mean a rotatable component of the transmission via which associated components of the transmission are non-rotatably connected to one another or via which such a connection is produced upon actuation of a corresponding switching element. The respective shaft can connect the components axially or radially or else both axially and radially. Thus, the respective shaft can also be present as an intermediate piece, via which a respective component is connected radially, for example.

By "axial" in the context of the invention is meant an orientation in the direction of a longitudinal central axis, along which the planetary gear sets are arranged coaxially to one another. By "radial" is then an orientation in the diameter direction of a shaft to understand, which lies on this longitudinal central axis.

Preferably, the output shaft of the transmission has a toothing, via which the output shaft is then operatively connected in the motor vehicle drive train with an axially parallel to the output shaft arranged differential gear. Here, the toothing is preferably provided at a connection point of the output shaft, said connection point of the output shaft is in particular axially in the region of one end of the transmission, on which a connection to the upstream prime mover producing connection point of the drive shaft is provided. This type of arrangement is particularly suitable for use in a motor vehicle with a transversely oriented to the direction of travel of the motor vehicle drive train.

Alternatively, an output of the transmission could in principle but also be provided on an opposite to a connection point of the drive shaft, axial end of the transmission. In this case, a connection point of the output shaft is then configured coaxially to a connection point of the drive shaft at an axial end of the output shaft, so that drive and output of the transmission are placed at opposite axial ends of the transmission. A gear designed in this way is suitable for use in a motor vehicle with a drive train aligned in the direction of travel of the motor vehicle. The drive shaft, and the output shaft are preferably coaxial with each other in the two aforementioned cases.

In the context of the invention, the planetary gear sets are preferably arranged axially following the connection point of the drive shaft in the order of the first planetary gearset, the second planetary gearset and the third planetary gearset. The planetary gear sets are preferably provided coaxially with the drive shaft and the output shaft.

The invention now includes the technical teaching that the first element of the first planetary gear set and the first element of the second planetary gear set are rotatably connected to each other and can be set together via the first switching element. Likewise, the first element of the third planetary gear set can be fixed by means of the second switching element. The output shaft is rotatably connected to the second element of the second planetary gear set and can be rotatably connected to the drive shaft via the third switching element in connection. Furthermore, the second element of the first planetary gear set, the third element of the second planetary gear set and the third element of the third planetary gear set are non-rotatably connected to each other and can together by means of the fourth switching element rotatably connected to the drive shaft. In addition, the third element of the first planetary gear and the second element of the third planetary gear are rotatably connected to each other and can be rotatably connected together via the fifth switching element with the drive shaft in connection, which is also rotatably connected by means of the sixth switching element with the first element of the third planetary gear set ,

In other words, in the transmission according to the invention, therefore, the output shaft is constantly rotatably connected to the second element of the second planetary, while the second element of the first planetary, the third element of the second planetary gear and the third element of the third planetary gear set permanently rotatably connected to each other , Likewise, the third element of the first planetary gear set and the second element of the third planetary gear set are permanently connected to each other in a rotationally fixed manner. Finally, the first element of the first planetary gear set is permanently non-rotatably in connection with the first element of the second planetary gear set.

By closing the first switching element, the first element of the first planetary gear set and the first element of the second planetary gear set are fixed together and prevented in the sequence of rotational movement, while an actuation of the second switching element pulls a setting of the first element of the third planetary by itself. The third switching element connects in the actuated state, the drive shaft and the output shaft rotatably with each other, whereas closing the fourth switching element results in a rotationally fixed connection of the drive shaft with the second element of the first planetary gear set, the third element of the second planetary gear set and also the third element of the third planetary gear set Has. The fifth switching element in the closed state, the drive shaft rotatably connected to the third element of the first planetary gear set and the second element of the third planetary, while an actuation of the sixth switching element pulls a rotationally fixed connection of the drive shaft with the first element of the third planetary gear after.

The third switching element, the fourth switching element, the fifth switching element and also the sixth switching element are in the form of clutches which, when actuated, adjust the components of the transmission which are directly connected thereto, if appropriate in their rotational movements, and then connect them to one another in a torque-proof manner. By contrast, the first switching element and also the second switching element are each designed as a brake, which fixes each of the directly adjoining component or the directly adjoining components upon actuation and prevents in the sequence of a rotational movement.

The first shifting element is preferably provided axially on a side of the first planetary gear set facing away from the second planetary gear set, while the second shifting element is arranged in particular axially on a side of the third planetary gearset facing away from the second planetary gearset. Furthermore, the third shift element, the fourth shift element, the fifth shift element and the sixth shift element are axially preferably provided between the second planetary gear set and the third planetary gear set, wherein in this case further preferably the third shift element is axially adjacent to the second planetary gear set and then axially first the fourth Switching element, then follow the fifth switching element and finally the sixth switching element.

A respective rotationally fixed connection of the rotatable components of the transmission is realized according to the invention preferably via one or more intermediate waves, which may also be present as a short intermediate pieces in spatially dense position of the components. In concrete terms, the components which are permanently connected to one another in a rotationally fixed manner can each be present either as individual components which are connected to one another in a torque-proof manner or also in one piece. In the second-mentioned case, the respective components and the possibly existing shaft are then formed by a common component, wherein this is especially realized just when the respective components are spatially close to each other in the transmission.

In the case of components of the transmission which are only connected to one another by actuation of a respective switching element, a connection is likewise preferably realized via one or more intermediate shafts.

A setting is carried out in particular by non-rotatable connection with a non-rotatable component of the transmission, which is preferably a permanently stationary component, preferably a housing of the transmission, a part of such a housing or a rotatably connected thereto component.

The term "connection" of the rotor of the electric machine with the drive shaft, the output shaft or at least one of the elements of the planetary gear sets is to be understood in the context of the invention such a connection that between the rotor of the electric machine and the rotatable or the components of the transmission a constant speed dependence prevails.

Overall, an inventive transmission is characterized by a compact design, low component loads, good gear efficiency and low losses.

According to one embodiment of the invention, the rotor of the electric machine is non-rotatably connected to the second element of the first planetary gear set, the third element of the second planetary gear set and the third element of the third planetary gear set, it being alternatively conceivable that the rotor of the electric machine with the second Element of the first planetary gear set, the third element of the second planetary gear set and the third element of the third planetary gear set via at least one translation stage is in communication.

The electric machine can either be arranged coaxially to the planetary gear sets or off-axis lying to these. In the former case, the rotor of the electric machine can either be directly rotatably connected to the second element of the first planetary, the third element of the second planetary and the third element of the third planetary or coupled via one or more intermediate gear ratios with these, the latter allows a more favorable design of the electric machine with higher speeds and lower torque. The at least one translation stage can be designed as a spur gear and / or as a planetary stage. In a coaxial arrangement of the electric machine, the planetary gear sets can also be further preferably at least partially disposed axially in the region of the electric machine and radially inwardly to this, so that the axial length of the transmission can be shortened.

If, however, the electric machine is provided offset in the axial direction with respect to the planetary gear sets, then a coupling takes place via one or more intermediate gear ratios and / or a traction drive. The one or more translation stages can also be realized in detail either as a spur gear or as a planetary stage. A traction drive may be either a belt drive or a chain drive. Even in the off-axis arrangement of the electric machine, the planetary gear sets can be placed at least partially axially at the height of the electric machine.

According to one embodiment of the invention, in particular in combination with the arrangement of the electric machine described above, six gears between the drive shaft and the output shaft result by selectively closing the six switching elements. Thus, a first gear between the drive shaft and the output shaft can be represented by operating the first and the sixth shift element, while a second gear between the drive shaft and the output shaft results by closing the first and the fifth shift element. A third speed is switched between the input shaft and the output shaft by operating the first shift element and the fourth shift element, whereas a fourth speed between the drive shaft and the output shaft results in a first variant by closing the first shift element and the third shift element.

In addition, the fourth gear can still in a second variant by operating the second and third switching element, in a third variant by closing the third and fourth switching element, in a fourth variant by operating the third and fifth switching element, in a fifth variant by closing the third and the sixth switching element, in a sixth variant by actuating the fourth and the fifth switching element, in a seventh variant by closing the fourth and the sixth switching element, in an eighth variant by actuating the fifth and the sixth switching element as well as in one ninth variant can be switched by closing the third switching element.

In the ninth variant already gives the fourth gear, since then the drive shaft and the output shaft are rotatably connected to each other. In this case, an electric machine connected to the second element of the first planetary gearset, the third element of the second planetary gearset and the third element of the third planetary gearset is decoupled in an advantageous manner, so that pure driving can be realized via the preceding drive machine and thus no-load losses of the electric machine can be avoided , However, in the first eight variants of the fourth gear, the electric machine is integrated so that hybrid functions can be displayed.

A fifth gear may be shifted between the input shaft and the output shaft by closing the second shift element and the fourth shift element, whereas a sixth gear between the input shaft and output shaft is provided by operating the second shift element and the fifth shift element.

With a suitable choice of stationary gear ratios of the planetary gear sets this is a suitable for the application in the field of a motor vehicle translation series realized. In this case, circuits between the gears can be realized, in which always only the state of two switching elements is to be varied by a to open the switching elements involved in the previous course and to close another switching element to represent the subsequent aisle. This then has the consequence that a shift between the courses can proceed very quickly.

When connecting the electric machine to the second element of the first planetary gear set, the third element of the second planetary gear set and the third element of the third planetary gear set also different operating modes can be realized in a simple manner:

Thus, a first gear between the rotor of the electric machine and the output shaft for a purely electric driving can be used, this first gear results by closing the first switching element. Thereby, the rotor of the electric machine is coupled via the second planetary gear set with the output shaft, wherein a translation of this first gear while a transmission of the third, effective between the drive shaft and the output shaft gear corresponds.

In addition, still a second gear between the rotor of the electric machine and the output shaft for a purely electric driving can be realized. In this case, to actuate this second gear, the second switching element is actuated, so that then the rotor of the electric machine is connected to the output shaft via all three planetary gear sets. A translation of this second, effective between the rotor of the electric machine and the output shaft gear corresponds to the translation of the fifth, effective between the drive shaft and the output shaft gear.

Starting from a purely electric driving in the first, between the rotor of the electric motor and the output shaft effective gear then the upstream prime mover in the first, effective between the drive shaft and the output shaft or in the second, between the drive shaft and the output shaft effective passage or in the third, between the drive shaft and the output shaft effective gear or in the first variant of the fourth, between the drive shaft and the output shaft effective gear each be started, since each of these also the first switching element is involved.

Likewise, from the second, between the rotor of the electric motor and the output shaft effective a commitment of the upstream engine in the second variant of the fourth, effective between the drive shaft and the output shaft gear, in the fifth, between the drive shaft and the output shaft effective gear as well as in the sixth between the drive shaft and the output shaft effective gear, since in these also the second switching element is also closed.

As a further mode of operation also a charging operation of an electrical energy storage can be realized by only the fourth switching element closed and thus a rotationally fixed connection of the drive shaft with the second element of the first planetary, the third element of the second planetary gear and the third element of the third planetary gear set and thus the electric machine is manufactured. In this case, the rotor of the electric machine rotatably connected to the second element of the first planetary, the third element of the second planetary gear set and the third element of the third planetary gear set as fast as the drive shaft. At the same time no frictional connection to the output shaft is made, so that the transmission is in a neutral position. Apart from a loading operation, this can also be used to start the preceding drive machine via the electric machine.

As a further operating mode can also be a start-up mode for reverse drive when driving on the drive shaft and thus the upstream prime mover can be realized. For this purpose, the sixth switching element is closed so that the prime mover drives via the first element of the third planetary gearset and at the same time the electric machine is supported on the second element of the first planetary gear set, on the third element of the second planetary gear set and on the third element of the third planetary gear set, while an output via the second element of the second planetary gear set takes place. The rotationally fixed connection between the first element of the first planetary gear set and the first element of the second planetary gear set and between the third element of the first planetary gear set and the second element of the third planetary gear set causes a coupling of the planetary gear sets. By supporting the torque via the electric machine while a start for reverse travel can be realized. Out of this start-up mode, the upstream drive machine can enter the first gear or the fifth variant or the seventh variant or the eighth variant of the fourth gear.

Furthermore, load circuits can be shown with traction support: when changing gear between the first, between the drive shaft and the output shaft effective gear and the second, effective between the drive shaft and output shaft gear, the pulling force can be supported with the first switching element closed via the electric machine, said Synchronization of the closing element to be closed via a speed control of upstream drive machine takes place. Alternatively, this can also be done by synchronized switching elements or by another, separate synchronization device, such as a transmission brake or another electric machine, which can be directly or indirectly operatively connected to the drive shaft. If, on the drive side, the drive shaft also provides a further switching element as a separating clutch, the inertial mass of the upstream drive machine can be decoupled during the synchronization. Similarly, switching between the second, between the drive shaft and the output shaft effective gear and the third, effective between the drive shaft and the output shaft gear and between the third, between the drive shaft and the output shaft effective gear and the first variant of the fourth, between the drive shaft and the output shaft effective gear to be realized with closed, first switching element.

Before a further upshift into the fifth, effective between the drive shaft and the output shaft gear then first must be switched between the first variant and the second variant of the fourth gear. Following this, then a gear change under load between the second variant of the fourth, between the drive shaft and the output shaft effective gear and the fifth, effective between the drive shaft and the output shaft gear with closed, second switching element take place, wherein the tensile force on the electric machine supported and a synchronization of the closing element to be closed by speed control of the upstream drive machine is realized. The same is also displayed in a gear change between the fifth, between the drive shaft and the output shaft effective gear and the sixth, effective between the drive shaft and the output shaft gear.

The transmission according to the invention can also be operated so that when driving a speed reduction of the electric machine is achieved. So can be driven first hybrid in the first variant of the fourth gear by the first switching element initially remains closed either by a torque-assisted via the electric machine circuit from third to fourth gear or after a states of the prime mover in the fourth gear. But now to lower a speed of the electric machine in fourth gear at higher speeds, can be switched from the first variant of the fourth gear in the second variant of the fourth gear, since the rotor of the electric machine has a lower speed than in the first variant of the fourth Ganges. This switching takes place while maintaining the tensile force on the upstream engine with closed, third switching element. First, the load-free, first switching element is initially designed and subsequently loaded the load-free, second switching element, wherein the rotational speed adjustment takes place by speed control of the electric machine.

In this case, no separate switching element is required to decouple the upstream drive machine, since the upstream drive machine in the second variant of the fourth, effective between the drive shaft and the output shaft gear can be decoupled by opening the third switching element. As a result, the second gear is then realized, which is effective between the rotor of the electric machine and the output shaft. In addition, the second variant of the fourth gear is required to switch under load in the fifth gear can. In addition, when the vehicle is slowing down a downshift from the fourth, effective between the drive shaft and the output shaft gear in the third, effective between the drive shaft and the output shaft gear to be prepared by first changed from the second variant in the first variant of the fourth gear and while the traction is obtained with the third switching element closed via the upstream drive machine. In the first variant of the fourth gear, in turn, the first switching element is then closed, which is required in order to support the traction over the electric machine in the course of the downshift from fourth to third gear.

In a further development of the invention, one or more switching elements are each realized as a form-locking switching element. In this case, the respective switching element is preferably designed either as a claw switching element or as a blocking synchronization.

Form-fitting switching elements have the advantage over non-positive switching elements that in the open state lower drag losses occur, so that it is possible to achieve a better efficiency of the transmission. In particular, in the transmission according to the invention all switching elements are realized as form-fitting switching elements, so that the lowest possible drag losses can be achieved.

However, it is also a conceivable variant of the invention that the first switching element is designed as a non-positive switching element, wherein this may be present concretely as a lamellar switching element. This has the advantage that from a loading operation with the fourth switching element closed, a starting or creeping of the motor vehicle by slipping closing of the first Switching element can be realized, wherein the first switching element acts as an integrated starting element. In this respect, a delay-free start from the loading operation can be displayed.

Alternatively or additionally, the second switching element can be designed as a non-positive switching element and here in particular as a lamellae switching element. Thereby, up-down and down-pull operations between the first gear operative between the rotor of the electric machine and the output shaft and the second gear operative between the rotor of the electric machine and the output shaft can be shown under load. In addition, if the first switching element is designed as a non-positive switching element, the two gears between the rotor of the electric machine and the output shaft are full load switchable, so it is high, Zugrück-, Schubhoch- and push downshifts possible.

If, in addition, a frictionally engaged separating clutch is provided between the upstream drive machine and the transmission, a tow start of the upstream drive machine can be represented from the two gears which are effective between the rotor of the electric machine and the output shaft.

According to a further embodiment of the invention, the third switching element and the fourth switching element are combined to form a pair of switching elements, which is associated with an actuating element. In this case, on the one hand the third switching element and on the other hand, the fourth switching element can be actuated via the actuating element from a neutral position. This has the advantage that this combination reduces the number of actuators and thus the production cost can be reduced. However, in this case, then not the third variant of the fourth, effective between the drive shaft and the output shaft gear can be realized, since this is the third switching element and the fourth switching element to operate simultaneously.

Alternatively or in addition to the aforementioned variant, the fifth switching element and the sixth switching element are combined to form a pair of switching elements, which is associated with an actuating element. About this actuator can be actuated from a neutral position on the one hand, the fifth switching element and on the other hand, the sixth switching element. As a result, the production cost can be reduced by an actuator for both switching elements can be used by combining the two switching elements to a pair of switching elements. However, in this case, then the eighth variant of the fourth, effective between the drive shaft and the output shaft gear are not shown, since this a simultaneous actuation of the fifth switching element and the sixth switching element is necessary.

Further alternatively or in addition to the two aforementioned variants, it is also conceivable within the scope of the invention to combine the first switching element and the second switching element to form a switching element pair. In this case, a common actuating element would then actuate the first switching element as well as the second switching element from a neutral position.

Particularly preferably, at least two aforementioned switching element pairs are realized, so that the four switching elements of the transmission can be actuated via two actuating elements. This makes it possible to realize a particularly low production cost.

In the context of the invention, the transmission can be preceded by a starting element, for example a hydrodynamic torque converter or a friction clutch. This starting element can then also be part of the transmission and serves to design a start-up process by enabling a slip speed between the drive machine, in particular designed as an internal combustion engine, and the drive shaft of the transmission. In this case, one of the switching elements of the transmission or the possibly existing separating clutch can be designed as such a starting element by being present as a friction switching element. In addition, a freewheel to the transmission housing or to another shaft can in principle be arranged on each shaft of the transmission.

The transmission according to the invention is in particular part of a motor vehicle drive train for a hybrid or electric vehicle and is then arranged between a designed as an internal combustion engine or as an electric machine prime mover of the motor vehicle and further, in the direction of power flow to drive wheels of the motor vehicle following components of the drive train. Here, the drive shaft of the transmission is either permanently non-rotatably coupled to a crankshaft of the internal combustion engine or the rotor shaft of the electric machine or connected via an intermediate separating clutch or a starting element with this, between a combustion engine and the transmission also a torsional vibration damper can be provided. On the output side, the transmission within the motor vehicle drive train is then preferably coupled to a differential gear of a drive axle of the motor vehicle, although here also a connection to a longitudinal differential may be present, via which a distribution takes place on a plurality of driven axles of the motor vehicle. The differential gear or the longitudinal differential can be arranged with the transmission in a common housing. Likewise, an optionally existing torsional vibration damper can also be integrated into this housing.

The fact that two components of the transmission are "connected" or "coupled" or "communicate with one another" means in the context of the invention a permanent coupling of these components, so that they can not rotate independently of one another. In this respect, no switching element is provided between these components, which may be elements of the planetary gear sets and / or shafts and / or a non-rotatable component of the transmission, but the corresponding components are coupled to each other with constant speed dependence.

If, by contrast, a switching element is provided between two components, then these components are not permanently coupled to one another, but a coupling is only made by actuating the intermediate switching element. In this case, an actuation of the switching element in the sense of the invention means that the relevant switching element is transferred into a closed state and, as a result, the components directly connected thereto, if necessary, in their rotational movements equal to one another. In the case of an embodiment of the relevant switching element as a form-locking switching element on this directly rotatably interconnected components are running at the same speed, while in the case of a non-positive switching element can also exist after pressing desselbigen speed differences between the components. This intentional or unwanted state is still referred to in the context of the invention as a rotationally fixed connection of the respective components via the switching element.

The invention is not limited to the specified combination of the features of the main claim or the claims dependent thereon. It also results in ways to combine individual features, even if they emerge from the claims, the following description of preferred embodiments of the invention or directly from the drawings. The reference of the claims to the drawings by use of reference numerals is not intended to limit the scope of the claims.

• 1 eine schematische Ansicht eines Kraftfahrzeugantriebsstranges;
• 2 bis 7 jeweils eine schematische Ansicht je eines Getriebes, wie es jeweils bei dem Kraftfahrzeugantriebsstrang aus 1 zur Anwendung kommen kann;
• 8 ein beispielhaftes Schaltschema der Getriebe aus den 2 bis 7; und
• 9 bis 14 jeweils eine schematische Darstellung je einer Abwandlungsmöglichkeit der Getriebe aus den 2 bis 7.

Advantageous embodiments of the invention, which are explained below, are shown in the drawings. It shows:

• 1 a schematic view of a motor vehicle drive train;
• 2 to 7 in each case a schematic view of each of a transmission, as is the case in each case in the motor vehicle drive train 1 can be used;
• 8th an exemplary circuit diagram of the transmission of the 2 to 7 ; and
• 9 to 14 in each case a schematic representation depending on a modification possibility of the transmission from the 2 to 7 ,

1 shows a schematic view of a motor vehicle drive train of a hybrid vehicle, wherein in the motor vehicle drive train, an internal combustion engine VKM via an intermediate torsional vibration damper TS with a gear G connected is. The transmission G on the output side is a differential gear AG downstream, via which a drive power on drive wheels DW a drive axle of the motor vehicle is distributed. The gear G and the torsional vibration damper TS are doing in a common housing of the transmission G arranged, in which then the differential gear AG can be integrated. As well as in 1 it can be seen, are the internal combustion engine VKM , the torsional vibration damper TS , The gear G and also the differential gear AG aligned transversely to a direction of travel of the motor vehicle.

Out 2 is a schematic representation of the transmission G according to a first embodiment of the invention. As can be seen, the gearbox sits down G from a wheelset RS and an electric machine EM together, in common in the housing of the transmission G are arranged. The wheelset RS includes three planetary gear sets P1 . P2 and P3 where each of the planetary gear sets P1 . P2 and P3 one first element each E11 or. E12 or. E13 , a second element each E21 or. E22 or. E23 and a third element each E31 or. E32 or. E33 having. The respective first element E11 or. E12 or. E13 is in each case by a respective sun gear of the respective planetary gear set P1 or. P2 or. P3 formed while the respective second element E21 or. E22 or. E23 of the respective planetary gear set P1 or. P2 or. P3 than ever a planetary bridge and the respective third element E31 or. E32 or. E33 of the respective planetary gear set P1 or. P2 or. P3 than ever a ring gear is present.

In the present case, so are the first planetary gear P1 , the second planetary gear set P2 and also the third planetary gear set P3 each as a minus planetary gear set, whose respective planetary web at least one planetary gear rotatably mounted, which both with the respective radially inner sun gear, as well as the respective radial surrounding ring gear is in meshing engagement. But are particularly preferred in the first planetary gear P1 , at the second planetary gear set P2 and also at the third planetary gear set P3 each provided a plurality of planet gears.

If it allows the connection, the first planetary gear set could P1 , the second planetary gear set P2 and the third planetary gear set P3 in each case also be designed as a plus-planetary gear set, wherein in comparison to the execution as a minus planetary gear set then the respective second element E21 or. E22 or. E23 through the respective ring gear and the respective third element E31 or. E32 or. E33 formed by the respective planet web and also a respective transmission gear ratio must be increased by one. In the case of a plus planetary gear set, the planet carrier then rotatably supports at least one pair of planetary gears, whose planet gears mesh with the radially inner sun gear and a planet gear mesh with the radially surrounding ring gear, and the planet gears intermesh.

As in 2 can be seen, includes the gearbox G a total of six switching elements in the form of a first switching element A , a second switching element B , a third switching element C , a fourth switching element D , a fifth switching element e and a sixth switching element F , Here are the switching elements A . B . C . D . e and F each designed as a form-fitting switching elements and are preferably before as claw switching elements. In addition, the third switching element C , the fourth switching element D , the fifth switching element e and the sixth switching element F each designed as clutches, while the first switching element A and the second switching element B as brakes.

The first element E11 of the first planetary gear set P1 and the first element E12 of the second planetary gear set P2 are constantly connected to each other in a rotationally fixed manner and can together via the first switching element A on a non-rotatable component GG be set, which in particular is the transmission housing of the transmission G or part of the transmission housing. On the non-rotatable component GG can also be the first element E13 of the third planetary gear set P3 be set, for which purpose the second switching element B to close. An output shaft GWA of the transmission G permanently rotationally fixed with the second element E22 of the second planetary gear set P2 connected and can by means of the third switching element C rotationally fixed with a drive shaft LV1 of the transmission G be associated.

As well as out 2 shows are the second element E21 of the first planetary gear set P1 , the third element E32 of the second planetary gear set P2 and the third element E33 of the third planetary gear set P3 constantly rotatably connected to each other and are also permanently non-rotatable with a rotor R the electric machine EM in connection, whose stator S constantly on the non-rotatable component GG is fixed. In addition, the second element E21 of the first planetary gear set P1 , the third element E32 of the second planetary gear set P2 and the third element E33 of the third planetary gear set P3 by closing the fourth switching element D rotatably with the drive shaft LV1 be associated, which accordingly also a rotationally fixed connection of the rotor R the electric machine EM with the drive shaft LV1 entails. Further, the third element E31 of the first planetary gear set P1 and the second element E23 of the third planetary gear set P3 rotatably connected to each other and can together via the fifth switching element e rotatably with the drive shaft LV1 be associated. Finally, the drive shaft LV1 still on the sixth switching element F non-rotatable with the first element E13 of the third planetary gear set P3 get connected.

Both the drive shaft LV1 , as well as the output shaft GWA each form one connection point Level 1-A or. GWA-A out, with the connection point Level 1-A in the motor vehicle drive train 1 a connection to the internal combustion engine VKM serves while the gearbox G at the junction GWA-A with the following differential gear AG connected is. The connection point LV1 - A the drive shaft LV1 is at one axial end of the transmission G designed, with the connection point GWA-A the output shaft GWA is located at the same axial end and this transverse to the junction Level 1-A the drive shaft LV1 is aligned. In addition, the drive shaft LV1 and the output shaft GWA arranged coaxially to each other.

The planetary gear sets P1 . P2 and P3 are also coaxial with the drive shaft LV1 and the output shaft GWA , pointing to the junction LV1 - A the drive shaft LV1 axially following in the order of the first planetary gear set P1 , second planetary gear set P2 and finally third planetary gear set P3 are arranged. Likewise, the electric machine is EM coaxial with the planetary gear sets P1 . P2 and P3 and thus also the drive shaft LV1 and the output shaft GWA placed, the electric machine EM while axially on a second planetary gear P2 remote side of the first planetary gear set P1 is provided.

As well as in 2 can be seen, is the first switching element A axially on a second planetary gear set P2 remote side of the first planetary gear set P1 arranged, the first switching element A specifically axially between the electric machine EM and the first planetary gear set P1 lies. The second switching element B is axially on a second planetary gear set P2 remote side of the third planetary gear set P3 intended. By contrast, the third switching element C , the fourth switching element D , the fifth switching element e and also the sixth switching element F axially between the second planetary gear set P2 and the third planetary gear set P3 arranged, wherein the third switching element C axially adjacent to the second planetary gear set P2 is and then then axially first, the fourth switching element D , then the fifth switching element e and finally the sixth switching element F consequences.

The third switching element C and the fourth switching element D are axially adjacent to each other and placed radially at the same height and have a common actuating element, via which from a neutral position, on the one hand, the third switching element C and on the other hand, the fourth switching element D can be operated. In this respect, the third switching element C and the fourth switching element D to a pair of switching elements SP1 summarized.

Likewise, the fifth switching element e and the sixth switching element F axially immediately adjacent to each other and arranged radially substantially at the same height and to a switching element pair SP2 summarized by the fifth switching element e and the sixth switching element F a common actuating element is assigned, via which from a neutral position on the one hand, the fifth switching element e and on the other hand, the sixth switching element F can be operated.

3 shows a schematic representation of a transmission G according to a second embodiment of the invention. This embodiment possibility can in the motor vehicle powertrain in 1 come into application and corresponds largely to the variant 2 , It is different, however, that the first switching element A is now designed as a non-positive switching element, wherein the first switching element A this is preferably present as a lamellar switching element. In other respects the possibility of design corresponds to 3 according to the variant 2 so that reference is made to what has been described.

Further, go out 4 a schematic view of a transmission G according to a third embodiment of the invention, as they are also in the motor vehicle drive train in 1 Application can be found. This embodiment corresponds essentially to the variant 2 , with the difference that now the second switching element B is designed as a non-positive switching element and concretely exists as a lamellar switching element. Axial is the second switching element B between the connection point Level 1-A the drive shaft LV1 and the connection point GWA-A the output shaft GWA intended. Otherwise, the embodiment corresponds to 4 according to the variant 2 so that reference is made to what has been described.

In addition shows 5 a schematic representation of a transmission G according to a fourth embodiment of the invention. This can also in the motor vehicle powertrain in 1 come to the application, the design option largely according to the variant 2 equivalent. In contrast, both are now the first switching element A as well as the second switching element B realized as non-positive switching elements, wherein the switching elements A and B each present as a lamellae switching elements. Again, the second switching element B while axially between the connection point Level 1-A the drive shaft LV1 and the connection point GWA-A the output shaft GWA intended. Incidentally, the possibility of design according to 5 otherwise the variant 2 so that reference is made to what has been described.

Out 6 is a schematic view of a transmission G according to a fifth embodiment of the invention, as also in the motor vehicle drive train in 1 Application can be found. This embodiment corresponds essentially to the variant 2 , In contrast, now the third switching element C and the fourth switching element D no longer combined to form a switching element pair. In this respect, the third switching element C and the fourth switching element D be operated independently. Otherwise, the embodiment corresponds to 6 according to the variant 2 so that reference is made to what has been described.

7 shows a schematic representation of a transmission G according to a sixth embodiment of the invention, which also essentially according to the embodiment 2 equivalent. In this case, this embodiment possibility in the motor vehicle drive train in 1 come to the application and differs from the embodiment according to 2 in that the fifth switching element e and the sixth switching element F no longer combined to form a switching element pair. Accordingly, the fifth switching element e and the sixth switching element F be operated independently. Otherwise, the embodiment corresponds to 7 according to the variant 2 so that reference is made to what has been described.

In 8th is an exemplary circuit diagram for the transmission G from the 2 to 7 tabulated. As can be seen, this case between the drive shaft LV1 and the output shaft GWA a total of six courses 1 to 6 be realized, where in the columns of the circuit diagram with a X is in each case marked, which of the switching elements A to F in which of the corridors 1 to 6 each is closed.

As in 8th recognizable, becomes a first gear 1 between the drive shaft LV1 and the output shaft GWA by actuating the first switching element A and the sixth switching element F connected. Furthermore, there is a second gear 2 between the drive shaft LV1 and the output shaft GWA by closing the first switching element A and the fifth switching element e while a third gear 3 between the drive shaft LV1 and the output shaft GWA by actuating the first switching element A and the fourth switching element D is pictured.

A fourth gear between the drive shaft LV1 and the output shaft GWA is in a first variant 4.1 by actuating the first switching element A and the third switching element C switched, with the fourth gear also still in a second variant 4.2 by actuating the second switching element B and the third switching element C , in a third variant 4.3 by closing the third switching element C and the fourth switching element D , in a fourth variant 4.4 by actuating the third switching element C and the fifth switching element e , in a fifth variant 4.5 by closing the third switching element C and the sixth switching element F , in a sixth variant 4.6 by actuating the fourth switching element D and the fifth switching element e , in a seventh variant 4.7 by closing the fourth switching element D and the sixth switching element F , in an eighth variant 4.8 by actuating the fifth switching element e and the sixth switching element F as well as in a ninth variant 4.9 by closing the third switching element C results.

While in the first eight variants 4.1 to 4.8 the electric machine EM each is involved, so that hybrid with simultaneous use of the internal combustion engine VKM can be driven is the electric machine EM in the case of the last variant 4.9 decoupled. This can zero load losses of the electric machine EM be avoided while the drive shaft LV1 over the third switching element C directly against rotation with the output shaft GWA connected is. The third variant 4.3 can also only with the variant after 6 be realized, in which a simultaneous actuation of the third switching element C and the fourth switching element D is possible. In addition, the eighth variant 4.8 only with the transmission G to 7 be switched because only here a simultaneous actuation of the fifth switching element e and the sixth switching element F can take place.

In addition, a fifth gear 5 between the drive shaft LV1 and the output shaft GWA by closing the second switching element B and the fourth switching element D whereas there is a sixth gear 6 by actuating the second switching element B and the fifth switching element e results.

Although the switching elements A to F Each designed as a form-locking switching elements, a shift between the first gear 1 and second gear 2 be realized under load, as in each case the first switching element A is involved. Similarly, a gear change between the second gear 2 and third gear 3 as well as between the third gear 3 and the first variant 4.1 take place of the fourth gear under load, since also here in each case the first switching element A closed is. In fourth gear must then before a further upshift into fifth gear 5 between the variants 4.1 and 4.2 be changed, the internal combustion engine VKM in this case, the tensile force on the closed third switching element C maintains and between the first switching element A and the second switching element B is changed.

After a change in the variant 4.2 of the fourth gear can then under load between the second variant 4.2 the fourth gear and the fifth gear 5 , and also between the fifth gear 5 and the sixth gear 6 be changed under load, since in each case the second switching element B is involved. A synchronization in the circuits can in each case by an appropriate regulation of the upstream internal combustion engine VKM take place, so that the respective switching element to be interpreted load-free and the closing element to be closed below can be closed without load.

The gears G from the 2 to 7 can also in other operating modes with the aid of the electric machine EM operated: so can a purely electric driving in a first gear E1 take place, which between the rotor R the electric machine EM and the output shaft GWA is effective and to the representation of the first switching element A is to be converted into a closed state. This will be the rotor R over the second planetary gear set P2 with the output shaft GWA coupled, the translation of the first gear E1 the translation of the third, between the drive shaft LV1 and the output shaft GWA effective gear 3 equivalent.

Advantageously, starting from the first gear E1 in each case a states of the internal combustion engine VKM in the first gear 1 , in second gear 2 in the third gear 3 and also in the first variant 4.1 be made of the fourth gear, as well as in each of these gears each of the first switching element A closed is. In this respect, it is possible to move quickly from purely electric driving to driving via the internal combustion engine or hybrid driving.

In addition, still between the rotor R the electric machine EM and the output shaft GWA a second course E2 are shown, for the representation of the second switching element B to close. This will cause the output shaft GWA over all three planetary gear sets P1 to P3 with the rotor R the electric machine EM coupled. A translation of this passage E2 corresponds to the translation of the fifth gear 5 between the drive shaft LV1 and the output shaft GWA ,

Starting from second gear E2 can be a start of the internal combustion engine VKM in the second variant 4.2 the fourth gear, in the fifth gear 5 and in the sixth gear 6 be executed, as in each case the second switching element B is involved. As a result, it is also possible here to move quickly from driving purely by electricity into driving via the internal combustion engine or hybrid driving.

Furthermore, by closing the fourth switching element, the one charging or starting function can be realized. Because in the closed state of the fourth switching element D are the second element E21 of the first planetary gear set P1 , the third element E32 of the second planetary gear set P2 and the third element E33 of the third planetary gear set P3 and therefore also the rotor R the electric machine EM directly against rotation with the drive shaft LV1 connected and thus with the internal combustion engine VKM , At the same time, however, there is no frictional connection to the output shaft GWA , where the rotor R while turning as fast as the drive shaft LV1 , In generator operation of the electric machine EM can be an electrical energy storage via the internal combustion engine VKM be charged while in the electric motor operation of the electric machine EM starting the internal combustion engine VKM over the electric machine EM is feasible.

Another operating mode can also be a start-up function for reversing EDA-R be realized. For this purpose, the sixth switching element F close, causing over the drive shaft LV1 by means of the first element E13 of the third planetary gear set P3 is driven while the electric machine EM on the second element E21 of the first planetary gear set P1 , on the third element E32 of the second planetary gear set P2 and at the third element E33 of the third planetary gear set P3 the torque of the internal combustion engine VKM can support. An output then takes place via the second element E22 of the second planetary gear set P2 on the output shaft GWA , where the first element E11 of the first planetary gear set P1 and the first element E12 of the second planetary gear set P2 as well as the third element E31 of the first planetary gear set P1 and the second element E23 of the third planetary gear set P3 here the planetary gear sets P1 to P3 pair with each other. As a result, a start for reversing can be displayed.

In addition, still a speed reduction of the electric machine EM be designed in mechanical or hybrid operation: after a via the electric machine EM third-speed torque-assisted shift 3 in the fourth gear or after a Zustart the internal combustion engine VKM in the fourth gear results in a hybrid driving in the first variant 4.1 of the fourth gear. To the speed of the electric machine EM Lowering in fourth gear at higher speeds, can from the first variant 4.1 the fourth gear in the second variant 4.2 be switched, in which the rotor R has a lower speed. This switching takes place while maintaining the traction over the internal combustion engine VKM when closed, third switching element C , This is then the load-free, first switching element A designed and also load-free, second switching element B inserted, the speed adjustment in each case by speed control of the electric machine EM he follows.

Switching to the second variant 4.2 also has the advantage that the internal combustion engine VKM by opening the third switching element C can be decoupled at any time without the presence of an additional clutch, while the electric machine EM the vehicle drives or brakes. Furthermore, the second variant 4.2 the fourth gear needed to load a fifth gear 5 to be able to realize. In addition, when the vehicle slows down a shift from fourth gear to third gear 3 be prepared by first of the second variant 4.2 in the first variant 4.1 is changed while the internal combustion engine VKM the tensile force when the third switching element is closed C receives. In the first variant 4.1 the fourth gear is then again the first switching element A closed, which is needed to switch back from fourth gear to third gear 3 the tensile force on the electric machine EM to support.

At the transmissions G out 3 and 5 may also due to the execution of the first switching element A as non-positive switching element additionally in the charging operation described above, a start on the first switching element A be realized by this in the generator operation of the electric machine EM is closed slipping. Accordingly, the first switching element functions A in this case as an integrated starting element, so that a delay-free starting from the loading operation out is possible.

At the transmissions G from the 4 and 5 in which the second switching element B is present as a non-positive switching element, is a switching between the gears E1 and E2 also at least partial load switchable. So can look at the variant 4 High and low train downshifts between gears E1 and E2 each carried out under load. Is then also also the first switching element A realized as non-positive switching element, as in the transmission G out 5 the case is, then in addition to the special charging operation also circuits between the gears E1 and E2 be designed fully load switchable. In this case, then train up, Zugrück-, Schubhoch- and push downshifts under load can be displayed.

Finally show the 9 to 14 Modifications of the transmission G from the 2 to 7 , These modification options relate to other possibilities of integration of the electric machine EM , So is in 9 the electric machine EM not coaxial with the respective - not shown in detail here - wheelset RS of the transmission G placed but arranged off-axis. A connection is made via a spur gear SRS made up of a first spur gear SR1 and a second spur gear SR2 composed. The first spur gear SR1 is part of the respective wheelset RS on the second element E21 of the first planetary gear set P1 , the third element E32 of the second planetary gear set P2 and the third element E33 of the third planetary gear set P3 tethered. The spur gear SR1 then stands with the spur gear SR2 in tooth engagement, which rotatably on an input shaft EW of the electric machine EM is placed inside the electric machine EM the connection to the - not shown here - rotor of the electric machine EM manufactures.

Even with the possibility of modification 10 is the electric machine EM off-set to the respective wheelset RS of the respective transmission G placed. Unlike the previous variant 9 is a connection but not via a spur gear, but via a traction drive ZT performed. This traction drive ZT can be configured as a belt or chain drive. On the side of the respective wheelset RS is the traction drive ZT then on the second element E21 of the first planetary gear set P1 , the third element E32 of the second planetary gear set P2 and the third element E33 of the third planetary gear set P3 tethered. About the traction mechanism drive ZT This will then be a coupling to an input shaft EW of the electric machine EM made, in turn, within the electric machine EM makes a connection to the rotor of the electric machine.

In case of modification possibility 11 is an integration of the off-axis to the respective wheelset RS placed electric machine EM about a planetary stage PS and a spur gear stage SRS realized. Here is the planetary stage PS the wheelset RS downstream, with the output side of the planetary stage PS then the spur gear SRS is provided, via which the connection to the electric machine EM is made. The planetary stage PS is made up of a ring gear HO , a planetary bridge PT and a sun wheel SO together, the planetary bridge PT at least one planetary gear PR rotatably mounted, which leads both to the sun gear SO as well as the ring gear HO is in meshing.

The present is the planetary bridge PT on the part of the respective wheelset RS on the second element E21 of the first planetary gear set P1 , the third element E32 of the second planetary gear set P2 and the third element E33 of the third planetary gear set P3 tethered. In contrast, the ring gear HO permanently on the non-rotatable component GG fixed while the sun gear SO rotatably with a first spur gear SR1 the spur gear stage SRS connected is. The first spur gear SR1 then combs with a second spur gear SR2 the spur gear stage SRS , which rotatably on an input shaft EW the electric machine EM is provided. In this case, the electric machine EM So on the part of the wheelset RS connected via two gear ratios.

Even with the possibility of modification 12 is an integration of the electric machine EM from the wheelset RS about a planetary stage PS and a spur gear stage SRS performed. The Abwandlungsmöglichkeit largely corresponds to the variant 11 , with the difference that at the planetary stage PS now the sun wheel SO on the non-rotatable component GG is set while the ring gear HO rotatably with the first spur gear SR1 the spur gear stage SRS connected is. Specifically, are the ring gear HO and the first spur gear SR1 preferably integrally formed by the ring gear HO is equipped with a toothing on an outer circumference. Otherwise, the possibility of modification corresponds to 12 otherwise the variant 11 so that reference is made to what has been described.

Further shows 13 Another modification of the transmission G from the 2 to 7 , whereby also here an integration of the electric machine EM via a spur gear SRS and a planetary stage PS is made. Unlike the previous variant 12 follows the wheelset RS but first the spur gear stage SRS while the planetary stage PS in the power flow between spur gear SRS and electric machine EM is provided. The planetary stage PS also includes the elements ring gear again HO , Planetary bridge PT and sun gear SO , where the planetary bridge PT several planet wheels PR1 and PR2 rotatably mounted, each with both the sun gear SO as well as the ring gear HO in mesh.

As in 13 can be seen, is a first spur gear SR1 the spur gear stage SRS on the part of the respective wheelset RS rotatably connected, with this connection thereby to the second element E21 of the first planetary gear set P1 , the third element E32 of the second planetary gear set P2 and the third element E33 of the third planetary gear set P3 is done. The first spur gear SR1 meshes with a second spur gear SR2 the spur gear stage SRS , which rotatably with the planet web PT the planetary stage PS connected is. The ring gear HO is permanently on the non-rotatable component GG fixed while the sun gear SO rotatably on an input shaft EW the electric machine EM is provided.

Finally shows 14 Another modification of the transmission G from the 2 to 7 , this modification possibility essentially according to the previous variant 13 equivalent. The only difference is that now the sun wheel SO the planetary stage PS permanently on the non-rotatable component GG is set while the ring gear HO the planetary stage PS rotatably with the input shaft EW of the electric machine EM connected is. Otherwise, the possibility of modification corresponds to 14 otherwise the variant 13 so that reference is made to what has been described.

The execution of the second switching element B and / or the first switching element A according to the 3 or. 4 or. 5 can in an analogous manner in the other variants after the 6 and 7 Find application.

By means of the embodiments according to the invention, a transmission with a compact design and with good efficiency can be realized.

LIST OF REFERENCE NUMBERS

G

transmission

RS

wheelset

GG

Non-rotating component

P1

First planetary gear set

E11

First element of the first planetary gear set

E21

Second element of the first planetary gear set

E31

Third element of the first planetary gear set

P2

Second planetary gear set

E12

First element of the second planetary gear set

E22

Second element of the second planetary gear set

E32

Third element of the second planetary gear set

P3

Third planetary gear set

E13

First element of the third planetary gear set

E23

Second element of the third planetary gear set

E33

Third element of the third planetary gear set

A

First switching element

B

Second switching element

C

Third switching element

D

Fourth switching element

e

Fifth switching element

F

Sixth switching element

SP1

Switching element pair

SP2

Switching element pair

1

First course

2

Second gear

3

Third gear

4.1

Fourth gear

4.2

Fourth gear

4.3

Fourth gear

4.4

Fourth gear

4.5

Fourth gear

4.6

Fourth gear

4.7

Fourth gear

4.8

Fourth gear

4.9

Fourth gear

5

Fifth gear

6

Sixth gear

E1

first course

E2

second gear

EDA-R

Start-up mode for reversing

LV1

drive shaft

Level 1-A

junction

GWA

output shaft

GWA-A

junction

EM

electric machine

S

stator

R

rotor

SRS

spur gear

SR1

spur gear

SR2

spur gear

PS

planetary stage

HO

ring gear

PT

planet spider

PR

planet

PR1

planet

PR2

planet

SO

sun

ZT

traction drive

VKM

Internal combustion engine

TS

torsional vibration damper

AG

differential gear

DW

drive wheels

QUOTES INCLUDE IN THE DESCRIPTION

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

Cited patent literature

• DE 102014218610 A1 [0003]

Claims (12)

Transmission (G) for a motor vehicle, comprising an electric machine (EM), a drive shaft (GW1), an output shaft (GWA), and a first planetary gear set (P1), a second planetary gear set (P2) and a third planetary gear set (P3) the first, the second and the third planetary gear set (P1, P2, P3) each have a first element (E11, E12, E13), a second element (E21, E22, E23) and a third element (E31, E32, E33 ), wherein the first element (E11, E12, E13) is formed by a respective sun gear of the respective planetary gear set (P1, P2, P3), wherein the second element (E21, E22, E23) in the case of a minus planetary gear set by each a planetary land and in the case of a plus planetary gear set by a respective ring gear of the respective planetary gear set (P1, P2, P3) is formed, wherein the third element (E31, E32, E33) in the case of a minus planetary gear set by the respective ring gear and in the case a plus-planetary gear set through the respective planetary ridge of the respective Planetenradsa tts (P1, P2, P3), wherein a first (A), a second (B), a third (C), a fourth (D), a fifth (E) and a sixth switching element (F) are provided , by the selective operation of at least six gears between the drive shaft (GW1) and the output shaft (GWA) are represented, and wherein a rotor (R) of the electric machine (EM) on the drive shaft (GW1), the output shaft (GWA) or at least one the elements (E11, E12, E13, E21, E22, E23, E31, E32, E33) of the planetary gear sets (P1, P2, P3) is connected, characterized in that - the first element (E11) of the first planetary gear set (P1) and the first element (E12) of the second planetary gear set (P2) rotatably connected to each other and together via the first switching element (A) can be fixed, - that the first element (E13) of the third planetary gear set (P3) by means of the second switching element (B) can be fixed is, - that the output shaft (GWA) rotatably with the second element (E22) of the second plan etenradsatzes (P2) connected and via the third switching element (C) rotationally fixed to the drive shaft (GW1) is connectable, - that the second element (E21) of the first planetary gear set (P1), the third element (E32) of the second planetary gear set ( P2) and the third element (E33) of the third planetary gear set (P3) rotatably connected to each other and together by means of the fourth switching element (D) rotationally fixed to the drive shaft (GW1) are connectable, - that the third element (E31) of the first planetary gear set (P1) and the second element (E23) of the third planetary gear set (P3) rotatably connected to each other and together via the fifth switching element (E) rotatably connected to the drive shaft (GW1) are brought into connection, - and that the drive shaft (GW1) by means of sixth shift element (F) rotatably connected to the first element (E13) of the third planetary gear set (P3) is connectable. Transmission (G) to Claim 1 , characterized in that the rotor (R) of the electric machine (EM) rotatably with the second element (E21) of the first planetary gear set (P1), the third element (E32) of the second planetary gear set (P2) and the third element (E33) of the third planetary gear set (P3) is connected or via at least one translation stage with the second element (E21) of the first planetary gear set (P1), the third element (E32) of the second planetary gear set (P2) and the third element (E33) of the third planetary gear set (P3 ). Transmission (G) to Claim 1 or 2 , characterized in that by selectively closing the six switching elements (A, B, C, D, E, F) - a first gear (1) between the drive shaft (GW1) and the output shaft (GWA) by operating the first (A ) and the sixth shift element (F), - a second gear (2) between the drive shaft (GW1) and the output shaft (GWA) by closing the first (A) and the fifth shift element (E), - a third gear (3) between the drive shaft (GW1) and the output shaft (GWA) by actuating the first (A) and the fourth shift element (D), - a fourth gear between the drive shaft (GW1) and the output shaft (GWA) in a first variant (4.1) by closing the first (A) and the third switching element (C), in a second variant (4.2) by closing the second (B) and the third switching element (C), in a third variant (4.3) by actuating the third (C ) and the fourth switching element (D), in a fourth variant (4.4) by closing the third (C) and the fifth switching element (E), in a fifth variant (4.5) by operating the third (C) and the sixth switching element (F), in a sixth variant (4.6) by closing the fourth (D) and fifth switching element (E), in a seventh variant (4.7) by operating the fourth (D) and the sixth switching element (F), in an eighth variant (4.8) by closing the fifth (E) and the sixth switching element (F) and in a ninth variant (4.9) by actuating the third switching element (C), - a fifth gear (5) by actuating the second (B) and the fourth switching element (D), - and a sixth gear (6) by closing the second (B) and the fifth switching element (E). Transmission (G) to Claim 2 , characterized in that a first gear (E1) between the rotor (R) of the electric machine (EM) and the output shaft (GWA) by closing the first switching element (A) and a second gear (E2) between the rotor (R) of the electric machine (EM) and the output shaft (GWA) Actuating the second switching element (B) yields. Transmission (G) according to one of the preceding claims, characterized in that one or more of the switching elements (A, B, C, D, E, F) are each realized as a form-locking switching element. Transmission (G) according to one of the preceding claims, characterized in that the first switching element (A) and / or the second switching element (B) is designed as a non-positive switching element. Transmission (G) according to one of the preceding claims, characterized in that the third switching element (C) and the fourth switching element (D) are combined to form a pair of switching elements (SP1), which is associated with an actuating element, wherein via the actuating element from a neutral position on the one hand, the third switching element (C) and on the other hand, the fourth switching element (D) is actuated. Transmission (G) according to one of the preceding claims, characterized in that the fifth switching element (E) and the sixth switching element (F) to a pair of switching elements (SP2) are combined, which is associated with an actuating element, wherein via the actuating element from a neutral position on the one hand, the fifth switching element (E) and on the other hand, the sixth switching element (F) is actuated. Transmission according to one of the preceding claims, characterized in that the first switching element and the second switching element are combined to form a pair of switching elements, which is associated with an actuating element, via the actuating element from a neutral position on the one hand, the first switching element and on the other hand the second switching element is actuated. Motor vehicle drive train for a hybrid or electric vehicle, comprising a transmission (G) after one or more of the Claims 1 to 9 , Method for operating a transmission (G) after Claim 2 , characterized in that only a fourth switching element (D) is closed to represent a charging operation or a starting operation. Method for operating a transmission (G) after Claim 2 , characterized in that the sixth switching element (F) is closed to represent a start-up mode for reverse drive when driven via the drive shaft (GW1).

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