DE102018207990A1 - Transmission for a motor vehicle - Google Patents

Abstract

The invention relates to a transmission (G) for a motor vehicle, comprising a drive shaft (GW1), an output shaft (GWA), four planetary gear sets (P1, P2, P3, P4) and at least five shift elements (A, B, C, D, E ), wherein by selectively operating the at least five switching elements (A, B, C, D, E) different gears are switchable, and drive train for a motor vehicle with such a transmission (G).

Description

The invention relates to a transmission for a motor vehicle, comprising a drive shaft, an output shaft, and a first planetary gear set, a second planetary gear set, a third planetary gear set and a fourth planetary gear set, the planetary gear sets each comprising a plurality of elements, wherein a first, a second, a third , a fourth and a fifth switching element are provided, through the selective actuation of different gears between the drive shaft and the output shaft can be displayed. Furthermore, the invention relates to a motor vehicle drive train, in which an aforementioned transmission is used.

In motor vehicles multi-speed transmissions are known in which several different ratios can be switched as gears between a drive shaft and an output shaft by operating corresponding switching elements, and 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. In transmissions for hybrid vehicles, an aforementioned transmission is often combined with one or more electric machines, the gears of the transmission are then also used to represent a purely electric driving.

From the DE 10 2016 206 895 A1 goes out a motor vehicle drive train, in which a prime mover is connected to a transmission. In one variant, the transmission comprises four planetary gear sets and five shifting elements, through the selective actuation of which different power flows from a drive shaft to an output shaft of the transmission can be realized by displaying different gears. A total of six forward gears and one reverse gear can be switched.

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, which is characterized by a compact design and a simple structure.

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 the subject of claim 14.

According to the invention, a transmission comprises a drive shaft, an output shaft and a first planetary gear set, a second planetary gear set, a third planetary gear set and a fourth planetary gear set. The planetary gear sets comprise several elements, wherein each of the planetary gear sets preferably has a respective first element, a second element and a third element each. In addition, a first, a second, a third, a fourth and a fifth switching element are provided by the selective actuation of different gears between the drive shaft and the output shaft can be represented. Particularly preferably, six different forward gears and two reverse gears can be formed from the transmission ratio.

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.

The invention now includes the technical teaching that the drive shaft rotatably connected to the first element of the first planetary gear set and the output shaft rotatably connected to the second element of the second planetary gear set. The third element of the first planetary gear set and the first element of the second planetary gear set are rotatably connected to each other. The third element of the third planetary gear set and the first element of the fourth planetary gear set are rotatably connected to each other and rotatably connected by means of the first switching element with the third element of the second planetary gear set.

The third element of the second planetary gear set can be fixed by means of the second switching element. The third element of the third planetary gear set can by means of the third switching element with the second element of the second Planetenradsatzes are rotatably connected. The fourth switching element is arranged such that always two of the three elements of the first planetary gear set by means of the fourth switching element for blocking the third planetary gear set are rotatably connected,

In the third planetary gear set, there is a first coupling of the first element of the third planetary gear set with a stationary component and a second coupling of the second element of the third planetary gear set with the first element of the first planetary gear set, of which these two couplings is a permanent non-rotatable connection while at the remaining coupling a rotationally fixed connection by means of the fifth switching element can be produced.

In other words, therefore, the third element of the first planetary gear set and the first element of the second planetary gear set are permanently connected to each other in a rotationally fixed manner. In addition, the third element of the third planetary gear set and the first element of the fourth planetary gear set are permanently connected to each other in a rotationally fixed manner. In addition, the second element of the first planetary gear is constantly rotatably connected to the second element of the fourth planetary gear set. The second element of the second planetary gear set is permanently non-rotatably connected to the output shaft, whereas, on the other hand, the first element of the first planetary gear set is permanently connected in a rotationally fixed manner to the drive shaft.

By closing or actuating the first switching element, the third element of the third planetary gear set and the first element of the fourth planetary gear set are rotatably connected to the third element of the second planetary gear set. By closing or actuating the second switching element, the third element of the second planetary gear set is fixed and prevented in the sequence of a rotational movement. The third switching element connects in the actuated state, the second element of the second planetary gear set and the third element of the fourth planetary gear rotatably with each other.

With regard to the third planetary gear set there are in the transmission according to the invention a total of two couplings of the elements of the third planetary gear set. Thus, a first coupling in the form of the first element of the third planetary gear set with a rotationally fixed component is present, while in the case of the second element of the third planetary gear set, a second coupling with the first element of the first planetary gear set and the drive shaft of the transmission. One of the two aforementioned couplings is realized as a permanent non-rotatable connection, while the remaining coupling is present as a connection, which is made non-rotatably only by closing the fifth switching element.

For the purposes of the invention, a "coupling" in the third planetary gear set is therefore to be understood as meaning a connection which either exists as a permanent connection or is made non-rotatable only by actuating the fifth switching element.

If the first planetary gear set is blocked, the gear ratio is always one regardless of the number of teeth. In other words, the planetary gear is running as a block. There are three ways to lock the first planetary gear according to the invention by means of the fourth switching element, that is to connect two elements of the third planetary gear rotatably together.

• - das erste Element mit dem zweiten Element oder
• - das erste Element mit dem dritten Element oder
• - das zweite Element mit dem dritten Element des dritten Planetenradsatzes drehfest miteinander verbinden.

The third switching element can either

• the first element with the second element or
• - the first element with the third element or
• - Connect the second element with the third element of the third planetary gear rotatably together.

In the case of the transmission according to the invention, the second shifting element is in the form of a brake which, in each case in the closed state, fixes the respectively adjoining component or the adjoining components in each case and subsequently prevents them from rotating

On the other hand, the first, third and fourth shifting elements are in the form of a clutch which, when actuated, in each case adjust the components of the transmission which directly adjoin it, if appropriate, in their rotational movements and subsequently connect them to one another in a rotationally fixed manner.

The fifth switching element is designed depending on the coupling to be produced in the third planetary gear either as a brake or as a clutch.

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 realized in particular when the respective components are spatially close together 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.

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

According to an embodiment of the invention, by selectively closing the five switching elements six gears between the drive shaft and the output shaft. Thus, a first gear between the drive shaft and the output shaft can be represented by operating the second, the third and the fifth switching element. A first variant of the second gear between the drive shaft and the output shaft is represented by operating the second, the third and the fourth switching element. A second variant of the second forward gear between the drive shaft and the output shaft is formed by operating the second, the fourth and the fifth switching element, where, however, a third variant of the second gear between the drive shaft and the output shaft by closing the first, the second and the fourth switching element results. Further, the third speed between the drive shaft and the output shaft is switched by operating the third, the fourth and the fifth shift element, while a fourth speed between the drive shaft and the output shaft results by closing the first, the third and the fourth shift element. In addition, the fifth gear is formed between the input shaft and the output shaft by operating the first, the fourth and the fifth shifting element, whereas the sixth gear between the input shaft and the output shaft is formed by closing the first, third and fifth shifting elements.

With a suitable choice of stationary gear ratios of the planetary gear sets suitable for the application in the field of a motor vehicle translation series is 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 one of the switching elements involved in the previous course to open and another switching element to represent the subsequent course is to close. This then has the consequence that a shift between the courses can proceed very quickly.

In a further development of the invention results in a first reverse gear between the drive shaft and the output shaft by closing the first, second and third switching element. In the transmission according to the invention, transmission ratios can thus advantageously also be represented, in which a reverse drive of a motor vehicle can be realized by initiating a constant rotary motion via an upstream drive machine.

According to one embodiment of the invention, the second element of the third planetary gear set is non-rotatably connected to the first element of the first planetary gear set, whereas where the first element of the third planetary gear set can be fixed via the fifth switching element. In this embodiment, therefore, the second element of the third planetary gear set and the first element of the first planetary gear set are constantly rotatably connected to each other, while the first element of the third planetary gear set fixed by closing the fifth switching element and subsequently prevented from rotating. In this case, the fifth switching element is thus designed as a brake.

According to an alternative embodiment of this invention, the first element of the third planetary gear set is fixed, whereas, on the other hand, the second element of the third planetary gear by means of the fifth switching element rotatably connected to the first element of the first planetary gear set. In this case, therefore, the first element of the third planetary gear set is constantly fixed and is thus permanently prevented from rotating, while the second element of the third planetary gear set is not rotatably brought by pressing the fifth switching element with the first element of the first planetary gear in combination. The fifth switching element is then designed as a clutch.

According to a further embodiment of the invention, the first element of the third planetary gear set by means of the fourth switching element rotationally fixed to the third element of the first Planetary gear set are connected. In this case, by operating the fourth switching element, the first and third elements of the third planetary gear set rotatably connected to each other, whereby the first planetary gear set is blocked.

According to an alternative embodiment for this purpose, the second element of the first planetary gear set can be non-rotatably connected by means of the fourth switching element with the first element of the first planetary gear set. In this case, by operating the fourth switching element, the first and second elements of the first planetary gear set rotatably connected to each other, whereby the first planetary gear is blocked.

According to an alternative embodiment, the second element of the first planetary gear set can be connected by means of the fourth switching element rotationally fixed to the third element of the first planetary gear set. In this case, by operating the fourth switching element, the second and third elements of the first planetary gear set rotatably connected to each other, whereby the first planetary gear is blocked.

It is a further advantageous embodiment of the invention that the first planetary gear set and the second planetary gear set are arranged together in a wheel plane. In other words, therefore, the first planetary gear set and the second planetary gear set are substantially at the same axial height, wherein the first planetary gear set is preferably arranged radially inwardly of the second planetary gear set. More preferably, the third element of the first planetary gear set and the first element of the second planetary gear set are preferably integrally formed.

According to an alternative embodiment of the invention that is alternative to the aforementioned embodiment, but is preferably complementary, the third planetary gear set and the fourth planetary gear set are arranged together in a gear plane. In this case, the third planetary gearset and the fourth planetary gearset are then essentially at the same axial height, in which case, in particular, the third planetary gearset is provided radially inward of the fourth planetary gearset. In this case, the third element of the third planetary gear set and the first element of the fourth planetary gear set are also preferably embodied in one piece.

For the purposes of the invention, preferably both aforementioned variants are used together, so that the four planetary gear sets are provided in two gear planes, whereby a particularly compact axial construction can be realized.

According to a further embodiment of the invention, an electric machine is additionally provided, whose rotor is non-rotatably connected to the drive shaft or is permanently coupled to the drive shaft via at least one transmission stage. In principle, the electric machine can either be arranged coaxially with the planetary gear sets or offset in an axial direction with respect to these. In the former case, the rotor of the electric machine either directly rotatably connected to the drive shaft or be coupled via one or more intermediate gear ratios with the drive shaft, the latter allows a cheaper 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 the case of a coaxial arrangement of the electric machine, the planetary gear sets can furthermore preferably be arranged at least partially axially in the region of the electric machine and radially inward to the latter, 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.

The integration of an electric machine, a transmission can be created, which is suitable for use in a hybrid or electric vehicle. Because due to the connection of the electric machine with the drive shaft, the representable ratios of the transmission, so both the six gears, and the two reverse gears, can be used for a purely electric driving. In this case, a forward or reverse travel of the motor vehicle can be represented for each initiated rotary movement of the electric machine.

In the gearbox individual switching elements can be used as starting elements, which are then closed slipping in the course of a startup. For this purpose, in particular the second switching element are suitable both for forward and for reverse or the fifth switching element for reversing and the fourth switching element for forward drive. Alternatively, however, it is also possible to position a separate starting clutch between the electric machine and the gear set.

When using an aforementioned transmission in a motor vehicle drive train with a designed as an internal combustion engine drive also starting the upstream engine via the electric machine by switching a neutral gear in the transmission can be realized, the electric machine is to operate this as an electric motor. In addition, a charging of an electrical energy storage be realized by operating the gear provided in the electric machine is operated as a generator and driven by the upstream drive machine.

In a further development of the invention and in particular in combination of the arrangement of an electric machine described above, a sixth switching element is also provided, via which the drive shaft can be rotatably connected to a connecting shaft. This connecting shaft then establishes the connection to an upstream drive machine in a drive train. About the sixth switching element, the drive shaft can then be separated from the upstream drive machine, so that when providing an electric machine in the transmission a purely electric driving without entrainment of the upstream drive machine can be displayed.

According to a further embodiment of the invention, one or more switching elements are each realized as non-positive switching element. Here, the respective switching element is preferably designed as a lamellar switching element. Non-positive switching elements have the advantage over positive switching elements that they can be transferred under load in a closed state. However, it is within the scope of the invention also conceivable to carry out one or more switching elements as a form-locking switching elements. Because interlocking switching elements have the advantage that they have a lower drag torque in an open state, as non-positive switching elements. For an embodiment as a form-locking switching element in the present case, in particular the second switching element is suitable, since this is involved only in the representation of the first gear, the three variants of the second gear and the reverse gear.

The drive shaft and the output shaft according to the invention are arranged in particular coaxially to each other. Preferably, the output shaft of the transmission in this case 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.

In particular, then follow the planetary gear sets on the connection points of the drive shaft and the output shaft axially in the order of the first planetary and second planetary and third planetary and fourth planetary, preferably the first planetary gear and the second planetary gear here then in a wheel plane and the third planetary gear and the fourth planetary gear set are placed in a wheel plane. In the case of the shifting elements, the third shifting element preferably lies axially between the first planetary gear set and the second planetary gear set on the one hand and the third planetary gear set and the fourth planetary gear set on the other hand, wherein the second shifting element is further preferably arranged axially between the second planetary gear set on the one hand and the fourth planetary gear set on the other hand.

By contrast, the fourth switching element is provided axially on a side facing the connection points of the drive shaft and the output shaft side of the first and second planetary gear set.

The first switching element is provided axially on a side facing away from the connection points of the drive shaft and the output shaft side of the third and the fourth planetary gear set.

The fifth switching element is axially provided on a side facing away from the connection points of the third and the fourth planetary gear set, while in a design as a clutch axially between the first planetary gear set and the second planetary gear set on the one hand and the third planetary gear set and the fourth planetary gear set on the other is placed, more preferably axially between the first planetary gear on the one hand and the third planetary gear set on the other.

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 also coaxial with each other here.

In this case, preferably followed axially on the connection point of the drive shaft, the third third Planetary gear and the fourth planetary gear and then the first planetary gear and the second planetary gear, the third planetary gear and the fourth planetary gear are here again in particular in a gear plane and the first planetary gear and the second planetary are provided in a gear plane.

The first switching element is preferably provided on one of the connection point of the drive shaft facing side of the third planetary gear set and the fourth planetary gear set.

Furthermore, the fourth switching element is preferably provided on one of the connection point of the output shaft facing side of the first planetary gear set and the second planetary gear set.

Furthermore, the third shifting element is arranged axially between the third planetary gear set and the fourth planetary gear set on the one hand and the first planetary gear set and the second planetary gear set on the other hand, preferably axially between the fourth planetary gear set on the one hand and the second planetary gear set on the other hand.

Depending on the coupling of the third planetary gearset, the fifth shifting element is provided axially on one side of the third planetary gearset and the fourth planetary gearset facing the drive shaft or the fourth shifting element is axially between the third planetary gearset and the fourth planetary gearset on the one hand and the first planetary gearset and the second planetary gearset On the other hand arranged planetary gear set, particularly preferably axially between the third planetary gear set on the one hand and the first planetary gear set on the other. In the first case, the first element of the third planetary gear set by means of the executed as a brake fifth switching element can be fixed. In the second case, the fifth switching element is designed as a clutch and the first element of the third planetary gear set constantly fixed.

The planetary gear sets can, if it allows a connection of the elements, in the context of the invention each present as a minus planetary gear set, wherein it is a sun gear at the first element of the respective planetary gear, at the second element of each planetary gear set and a planet third element of the respective planetary gear is 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 planetary gears rotatably mounted, in each case with both the sun gear, and the combing the surrounding ring gear.

Alternatively, but one or more planetary gear sets, if it allows the connection of the respective elements, as a plus-planetary gear, wherein it is the first element of the respective planetary gear then a sun gear, in the second element of the respective planetary gear around a ring gear and the third element of the respective 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 four planetary gear sets are present as minus planetary gear sets.

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 designed in particular as an internal combustion engine and the first drive shaft of the transmission. In this case, one of the switching elements of the transmission 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 and is then preferably arranged between an engine of the motor vehicle designed as an internal combustion engine and further components of the drive train following in the direction of force flow to drive wheels of the motor vehicle. Here, the drive shaft of the transmission is either permanently rotatably coupled to a crankshaft of the internal combustion engine or over an intermediate separating clutch or a starting element with this connectable, wherein between the internal 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 entsprechend einer ersten Ausführungsform;
• 2 bis 7 je eine schematische Darstellung jeweils eines Getriebes, wie es jeweils bei dem Kraftfahrzeugantriebsstrang aus 1 zur Anwendung kommen kann;
• 8 eine schematische Ansicht eines Kraftfahrzeugantriebsstranges gemäß einer zweiten Ausführungsform;
• 9 bis 12 je eine schematische Darstellung jeweils eines Getriebes, wie es jeweils bei dem Kraftfahrzeugantriebsstrang aus 8 zur Anwendung kommen kann; und
• 13 ein beispielhaftes Schaltschema der Getriebe aus den 2 bis 7 und 9 bis 12.

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 according to a first embodiment;
• 2 to 7 each a schematic representation of each of a transmission, as is the case in each case in the motor vehicle drive train 1 can be used;
• 8th a schematic view of a motor vehicle drive train according to a second embodiment;
• 9 to 12 each a schematic representation of each of a transmission, as is the case in each case in the motor vehicle drive train 8th can be used; and
• 13 an exemplary circuit diagram of the transmission of the 2 to 7 and 9 to 12 ,

1 shows a schematic view of a motor vehicle drive train of a motor vehicle according to a first embodiment, 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 together, which four planetary gear sets P1 . P2 . P3 and P4 includes. In this case, each of the planetary gear sets P1 . P2 . P3 and P4 one first element each E11 respectively. E12 respectively. E13 respectively. E14 , a second element each E21 respectively. E22 respectively. E23 respectively. E24 and a third element each E31 respectively. E32 respectively. E33 respectively. E34 on. The respective first element E11 respectively. E12 respectively. E13 respectively. E14 is in each case by a respective sun gear of the respective planetary gear set P1 respectively. P2 respectively. P3 respectively. P4 formed while the respective second element E21 respectively. E22 respectively. E23 respectively. E24 of the respective planetary gear set P1 respectively. P2 respectively. P3 respectively. P4 than ever a planetary bridge and the respective third element E31 respectively. E32 respectively. E33 respectively. E34 of the respective planetary gear set P1 respectively. P2 respectively. P3 respectively. P4 than ever a ring gear is present.

In the present case, so are the first planetary gear P1 , the second planetary gear set P2 , the third planetary gear set P3 and also the fourth planetary gear set P4 each as a minus planetary gear set, the respective planetary web at least one planetary rotatably mounted, which is in meshing with both the respective radially inner sun gear, and the respective radially surrounding ring gear. But especially preferred are the planetary gear sets P1 . P2 . P3 and P4 each provided a plurality of planet gears.

If it allows the connection, could one or more of the planetary gear sets P1 . P2 . P3 and P4 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 respectively. E22 respectively. E23 respectively. E24 through the respective ring gear and the respective third element E31 respectively. E32 respectively. E33 respectively. E34 formed by the respective planet web and also a respective transmission gear ratio must be increased by one. In a positive planetary gear set, the planetary bridge then rotatably supports at least one pair of planetary, of the planetary gears a planetary gear with the radially inner sun gear and a planet gear meshing with the radially surrounding ring gear, and the planet gears mesh with each other.

As in 2 can be seen, includes the gearbox G a total of five 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 and a fifth switching element e , Here are the switching elements A . C . D and e each designed as non-positive switching elements and are preferably before as lamella switching elements. The second switching element B is designed as a positive switching element and is preferably present as a claw or as a synchronization. In addition, the second switching element B , the fifth switching element e executed as brakes, while the first switching element A , the third switching element C and the fourth switching element D present as couplings.

The third element E31 of the first planetary gear set E11 and the first element E12 of the second planetary gear set P2 are permanently connected with each other The third element E33 of the third planetary gear set P3 and the first element E14 of the fourth planetary gear set P4 are permanently connected with each other The second element E21 of the first planetary gear set P1 is permanent with the second element E24 of the fourth planetary gear set P4 rotatably connected. Further, the first element E11 of the first planetary gear set P1 and the second element E23 of the third planetary gear set P3 permanently rotatably connected to each other and stand together constantly with a drive shaft LV1 of the transmission G in connection. In addition, the second element E22 of the second planetary gear set P2 permanently rotationally fixed with an output shaft GWA rotatably connected.

As well as in 2 It can be seen, the third element E33 of the third planetary gear set and the first element E14 of the fourth planetary gear set P4 together with the third element E32 of the second planetary gear set via the first switching element A rotatably connected to each other. The third element E32 of the second planetary gear set P2 can via the second switching element B on a non-rotatable component GG be set, which is preferably a Gebriebegehäuse the transmission G or part of the transmission housing. Furthermore, the third element E34 of the fourth planetary gear set P4 by means of the third switching element C with the second element E22 of the second planetary gear set and thus with the output shaft GWA rotatably connected. The fourth switching element D locks the first planetary gear set, by pressing the same, the first element E11 and the third element E31 of the first planetary gear set P1 rotatably connected. The first element E13 of the third planetary gear set P3 can by actuation of the fifth switching element e on the non-rotatable component GG be fixed.

In the present case are the first planetary gear set P1 and the second planetary gear set P2 arranged together in a wheel plane by the first planetary gear set P1 and the second planetary gear set P2 axially substantially at the same height and the first planetary gear set P1 in this case radially inward of the second planetary gear set P2 is provided. Particularly preferred are also the third element E31 of the first planetary gear set P1 and the first element E12 of the second planetary gear set P2 carried out in one piece, for example by the third element E31 of the first planetary gear set P1 forming ring gear is equipped on an outer periphery with an additional toothing, via which the sun gear in the form of the first element E12 of the second planetary gear set P2 is formed.

Likewise, the third planetary gear set P3 and the fourth planetary gear set P4 placed together in a wheel plane, the third planetary gear set P3 and the fourth planetary gear set P4 axially substantially at the same height and the third planetary gear P3 radially inward of the fourth planetary gear set P4 is arranged. Here are the third element E33 of the third planetary gear set P3 and the first element E14 of the fourth planetary gear set P4 in particular carried out in one piece by both the ring gear of the third planetary gear set on a component P3 forming teeth, as well as the sun gear of the fourth planetary gear set P4 forming toothing are configured.

Both the drive shaft LV1 , as well as the output shaft GWA each form one connection point Level 1-A respectively. 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 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 and P2 are also coaxial with the drive shaft LV1 and the output shaft GWA , pointing to the junction Level 1-A the drive shaft LV1 axially in the order of the first planetary gear set P1 and second planetary gear set P2 as well as third planetary gear set P3 and fourth planetary gear set P4 consequences.

As well as out 2 shows, are the first switching element A and the fifth switching element e axially on a first planetary gear set P1 and the second planetary gear set P2 remote side of the third planetary gear set P3 and the fourth planetary gear set P4 intended. In contrast, the third switching element lies C axially between the first planetary gear set P1 and the second planetary gear set P2 on the one hand and the third planetary gear set on the other P3 and the fourth planetary gear set P4 arranged on the other hand, in which case the third switching element C axially between the second planetary gear set P2 and the fourth planetary gear set P4 is placed. The fourth switching element D however, is axially on a third planetary gear P3 and the fourth planetary gear set P4 remote side of the first planetary gear set P1 and the second planetary gear set P2 intended.

Further shows 3 a schematic representation of a transmission according to a second embodiment of the invention, as also in the motor vehicle drive train in 1 can be used. In this case, this embodiment substantially corresponds to the previous variant 2 , in contrast to the fourth switching element D now the first element E11 with the second element E21 of the first planetary gear set can connect to each other. Is the switching element D activated, the first planetary gear set is locked. In this embodiment, it is therefore a first Verblockungsvariante the embodiment according to 2 , Otherwise, the embodiment corresponds to 3 according to the variant 2 so that reference is made to what has been described.

Out 4 is a schematic view of a transmission according to a third embodiment possibility of the invention, this embodiment also largely as far as the variant 2 equivalent. This Ausgestaltungsmöglichkeit can in the motor vehicle powertrain in 1 Find application. Different compared to the variant 2 Here is that the fourth switching element D now the second element E21 with the third element E31 of the first planetary gear set P1 rotatably connect with each other. If the fourth switching element is activated, the first planetary gear set is locked. In the embodiment according to 4 So it is a further Verblockungsvariante the embodiment according to 2 , Otherwise, the embodiment corresponds to 4 according to the variant 2 so that reference is made to what has been described.

Out 5 is a schematic view of a transmission G according to a fourth embodiment of the invention, this embodiment also largely according to the variant 2 equivalent. This embodiment can also in the motor vehicle drive train in 1 Find application. In contrast to 2 is the first element E13 of the third planetary gear set P3 constantly on the non-rotatable component GG set. In addition, the second element is available E23 of the third planetary gear set P3 not permanently rotatable with the first element E11 of the first planetary gear set P1 and the drive shaft LV1 of the transmission G in conjunction, but a non-rotatable connection is only by closing a fifth switching element e produced. The case designed as a clutch fifth switching element e is axially between the first planetary gear set P1 and the second planetary gear set P2 on the one hand and the third planetary gear set on the other P3 and the fourth planetary gear set P4 provided on the other hand and lies concretely axially between the third switching element on the one hand and the third planetary gear set P3 and fourth planetary gear set P4 on the other hand, as well as radially inwardly of the third switching element C , Otherwise, the embodiment corresponds to 5 according to the variant 2 so that reference is made to what has been described.

6 shows a schematic representation of a transmission G according to a fifth embodiment of the invention. This embodiment corresponds essentially to the variant 2 and may be in the motor vehicle powertrain in 1 come into use. Unlike the variant after 2 is with the transmission G next to the wheelset RS , which analogous to the variant according to 2 is designed, in addition to an electric machine EM provided which coaxial with the drive shaft LV1 and also the output shaft GWA and thus also the planetary gear sets P1 . P2 . P3 and P4 is arranged. A rotor R the electric machine EM is non-rotatable with the drive shaft LV1 connected while a stator S the electric machine EM constantly on the non-rotatable component GG is fixed. In addition, the gearbox has G still via a sixth switching element K0 , which is designed as a non-positive switching element in the form of a lamellar switching element and when actuated the drive shaft LV1 at their junction Level 1-A non-rotatable with a connection shaft ON combines. The connection shaft ON is then off within the motor vehicle powertrain 1 rotatably with the upstream internal combustion engine VKM connected. Otherwise, the design option corresponds to 6 according to the variant 2 so that reference is made to what has been described.

Further, go out 7 a schematic view of a transmission G according to a sixth embodiment of the invention, as far as possible the previous variant 6 equivalent. This Ausgestaltungsmöglichkeit can in the motor vehicle powertrain in 1 Application, whereby they differ from the variant 6 now differs in that an electric machine EM not coaxial to the drive shaft LV1 and the output shaft GWA is provided lying, but is offset in relation to these is placed. In this case, a connection of a - not shown here - rotor of the electric machine EM 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 non-rotatable with the drive shaft LV1 connected and meshes with the second spur gear SR2 , which rotatably on an input shaft EW the electric machine EM is placed. The input shaft EW then puts inside the electric machine EM a non-rotatable connection to the rotor ago. The electric machine EM covers axially with the Planetenradsätzen P1 to P4 and also essentially with the switching elements A . B . C . D and e , so that a compact axial structure is realized. Otherwise, the variant corresponds to 6 the embodiment according to 6 so that reference is made to what has been described.

Further shows 8th a schematic representation of a motor vehicle drive train of a motor vehicle according to a second embodiment possibility. In this case, this motor vehicle drive train includes an internal combustion engine VKM , the output side via an intermediate torsional vibration damper TS with a gear G connected is. The gear G in turn stands on a driven side with a subsequent axle drive AG in connection, via which a drive power to drive wheels DW a drive axle of the motor vehicle is distributed. Again, there are the gears G and the torsional vibration damper TS in a common housing of the transmission G arranged, in which also the differential gear AG can be integrated. In addition, the internal combustion engine VKM , the torsional vibration damper TS , The gear G and also the differential gear AG aligned in the direction of travel of the motor vehicle transmission.

Out 9 is a schematic view of a transmission G according to a seventh embodiment of the invention, as in the motor vehicle drive train 8th can be used. This includes the gearbox G a wheelset RS , which consists of four planetary gear sets P1 . P2 . P3 and P4 composed. In addition, the wheel set points RS of the transmission G five switching elements A . B . C . D and e on, which are each designed as a lamellae switching elements. elements E11 . E21 . E31 . E12 . E22 . E32 . E13 . E23 . E33 . E14 . E24 and E34 the planetary gear sets P1 to P4 are analogous to that 2 Described interconnected or be about the switching elements A . B . C . D and e analogous to that 2 Connected described. Different compared to the variant 2 is now that connection points Level 1-A and GWA-A the drive shaft LV1 and the output shaft GWA at opposite axial ends of the transmission G are provided to the respective connection within the motor vehicle drive train 8th to be able to produce. In the axial direction then follow on the junction Level 1-A the drive shaft LV1 first the third planetary gear set P3 and the fourth planetary gear set P4 in a wheel plane and only in the episode of the first planetary gear set P1 and the second planetary gear set P2 in another wheel plane. The switching elements A to e are analogous to that too 2 Described arranged. For the rest, the embodiment corresponds to 9 of the Variant after 2 so that reference is made to what has been described.

10 shows a schematic representation of a transmission G according to an eighth embodiment of the invention, as far as possible the previous variant 9 corresponds and also in the motor vehicle powertrain in 8th can be used. Different compared to the variant 9 is now that the first element E13 of the third planetary gear set P3 constantly on the non-rotatable component GG is fixed. In addition, the second element stands E23 of the third planetary gear set P3 not permanently rotatable with the first element E11 of the first planetary gear set P1 and thus the drive shaft AW1 in connection, but a non-rotatable connection is only by closing a fifth switching element e produced. The fifth switching element e is here designed as a clutch and is located axially between the third planetary gear and the fourth planetary gear P3 respectively. P4 on the one hand and the first planetary gear set P1 and the second planetary gear set P2 on the other hand. Otherwise, the embodiment corresponds to 10 according to the variant 9 so that reference is made to what has been described.

Out 11 is a schematic representation of a transmission G according to an eighth embodiment of the invention. This embodiment corresponds essentially to the variant 9 and may be in the motor vehicle powertrain in 8th come into use. Unlike the variant after 9 is with the transmission G next to the wheelset RS which is the wheelset RS according to the variant 9 corresponds, in addition still an electrical machine EM provided coaxially with the drive shaft LV1 and also the output shaft GWA and thus also the planetary gear sets P1 . P2 . P3 and P4 is arranged. A rotor R the electric machine EM is non-rotatable with the drive shaft LV1 connected while a stator S the electric machine EM constantly on the non-rotatable component GG is fixed. Also, in the transmission G still a sixth switching element K0 provided, which is designed as a non-positive switching element and this concretely as a lamellae switching element and when actuated the drive shaft LV1 at their junction Level 1-A non-rotatable with a connection shaft ON combines. The connection shaft ON is then off within the motor vehicle powertrain 8th rotatably with the upstream internal combustion engine VKM connected. Otherwise, the design option corresponds to 11 according to the variant 9 so that reference is made to what has been described.

Finally shows 12 a schematic view of a transmission G according to a ninth embodiment of the invention, as far as possible the previous variant 11 equivalent. This Ausgestaltungsmöglichkeit can in the motor vehicle powertrain in 8th Application, whereby they differ from the variant 11 now differs in that an electric machine EM not coaxial to the drive shaft LV1 and the output shaft GWA is provided lying, but is offset in relation to these is placed. In this case, a connection of a - not shown here - rotor of the electric machine EM 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 non-rotatable with the drive shaft LV1 connected and meshes with the second spur gear SR2 , which rotatably on an input shaft EW the electric machine EM is placed. The input shaft EW then puts inside the electric machine EM a rotationally fixed connection to the rotor R ago. The electric machine EM covers axially with the Planetenradsätzen P1 to P4 and also essentially with the switching elements A . B . C . D and e , so that a compact axial structure is realized. Otherwise, the variant corresponds to 12 the embodiment according to 11 so that reference is made to what has been described.

In 13 is an exemplary circuit diagram for the transmission of the 2 to 7 and 9 to 12 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 as forward gears and a reverse gear R1 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 e in which of the corridors 1 to 6 such as R1 each is closed. For the second gear 2 exist three variants, namely variant 2.1 , Variant 2.2 and variant 2.3 ,

As in 13 It can be seen, a first gear between the drive shaft LV1 and the output shaft GWA by actuating the second switching element B of the third switching element C and the fifth switching element e connected. Furthermore, a second gear between the drive shaft LV1 and the output shaft GWA in the first variant 2.1 by closing the second switching element B , the third switching element C and the fourth switching element D educated. In the second variant 2.2 becomes the second gear between the drive shaft LV1 and the output shaft GWA by closing the second switching element B , the fourth switching element D and the fifth switching element e educated. In the third variant 2.3 becomes the second gear between the drive shaft LV1 and the output shaft GWA by closing the first switching element A , the second switching element B and the fourth switching element D educated.

A third gear 3 between the drive shaft LV1 and the output shaft GWA is closed by closing the third switching element C , the fourth switching element D and the fifth switching element e switched while a fourth gear 4 between the drive shaft LV1 and the output shaft GWA by actuating the first switching element A , the third switching element C and the fourth switching element D results. Furthermore, a fifth gear 5 between the drive shaft LV1 and the output shaft GWA by closing the first switching element A , the fourth switching element D and the fifth switching element e switched, where, however, a sixth gear 6 between the drive shaft LV1 and the output shaft GWA by actuating the first switching element A , the third switching element C and the fifth switching element e results.

The first reverse R1 is closed by closing the first switching element A , the second switching element B and the third switching element C connected.

In the variants of the 6 . 7 . 11 and 12 can the aisles 1 to 6 such as R1 also for a purely electric driving on the respective electric machine EM be used. It can be in the hallways 1 to 6 also in each case a reverse drive by initiating an opposite rotational movement via the electric machine EM being represented. So that in purely electric driving not the upstream internal combustion engine VKM is also entrained, is also in each case the sixth switching element K0 to open to the upstream internal combustion engine VKM decouple. Is in the variants of the 6 . 7 . 11 and 12 none of the gears 1 to 6 such as R1 in the respective transmission G switched, so can in electromotive operation of the respective electric machine EM also starting the upstream internal combustion engine VKM when the sixth switching element is closed K0 be performed. Will the electric machine EM however, operated as a generator, so can then closed sixth switching element K0 a charging operation for charging an electrical energy storage via the electric machine EM in the course of a drive via the internal combustion engine VKM will be realized.

At this point it should be noted that in the above variants, the second switching element B can also be designed as a non-positive switching element. In addition, it is clarified that the coupling variant according to 5 with each individual Verlockungsvariante according to the 2 to 4 can be combined. In addition, it should be noted that the Verblockungsvarianten according to the 3 and 4 may be implemented in analogous application of the above in the standard construction and not only in the front transverse construction.

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

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

P4

Fourth planetary gear set

E14

First element of the fourth planetary gear set

E24

Second element of the fourth planetary gear set

E34

Third element of the fourth planetary gear set

A

First switching element

B

Second switching element

C

Third switching element

D

Fourth switching element

e

Fifth switching element

K0

Sixth switching element

1

First course

2

Second gear

3

Third gear

4

Fourth gear

5

Fifth gear

6

Sixth gear

R1

First reverse

R2

Second reverse

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

EW

input shaft

ON

connecting shaft

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 102016206895 A1 [0003]

Claims (14)

Transmission (G) for a motor vehicle, comprising a drive shaft (GW1), an output shaft (GWA), a first planetary gear set (P1), a second planetary gear set (P2), a third planetary gear set (P3) and a fourth planetary gear set (P4), wherein the planetary gear sets (P1, P2, P3, P4) each comprise a plurality of elements (E11, E21, E31, E12, E22, E32, E13, E23, E33, E14, E24, E34), wherein a first (A), a second (B), a third (C), a fourth (D) and a fifth switching element (E) are provided, through the selective actuation of different gears between the drive shaft (GW1) and the output shaft (GWA) can be represented, characterized - That the drive shaft (GW1) rotatably connected to the first element (E11) of the first planetary gear set (P1), - that the output shaft (GWA) rotatably connected to the second element (22) of the second planetary gear set (P2), - that the third element (E31) of the first planetary gear set (P1) and the first element nt (E12) of the second planetary gear set (P2) are rotatably connected to each other, - that the third element (33) of the third planetary gear set (P3) and the first element (E14) of the fourth planetary gear set (P4) are rotatably connected to each other and by means of the first Switching element (A) with the third element (E32) of the second planetary gear set are rotatably connected, - that the third element (E32) of the second planetary gear set (P2) by means of the second switching element (B) can be fixed, - that the third element (E33) of the third planetary gear set (P3) by means of the third switching element (C) with the second element (E22) of the second planetary gear set (P2) rotatably connected, - that the fourth switching element (D) is arranged such that always two of the three elements (E11 , E21, E31) of the first planetary gear set (P1) by means of the fourth switching element (D K1) for blocking the third planetary gear set (P3) are rotatably connected, - that in the third planetary gear set (P3) e Ine first coupling of the first element (E13) of the third planetary gear set (P3) with a stationary component (GG) and a second coupling of the second element (E23) of the third planetary gear set (P3) with the first element (E11) of the first planetary gear set (P1 ), wherein of these two couplings as a permanent rotationally fixed connection is present, while in the remaining coupling a rotationally fixed connection by means of the fifth switching element (E) can be produced. Transmission (G) to Claim 1 wherein, by selectively closing the five switching elements (A, B, C, D, E) - a first gear (1) between the drive shaft (GW1) and the output shaft (GWA) by operating the second (B), the third ( C) and the fifth switching element (E), - a second gear between the drive shaft (GW1) and the output shaft (GWA) in a first variant (2.1) by closing the second (B), the third (C) and the fourth switching element (D) and in a second variant (2.2) by actuating the second (B), the fourth (D) and the fifth switching element (E) and in a third variant (2.3) by operating the first (A), the second ( B) and the fourth shift element (D), - a third gear (3) between the drive shaft (GW1) and the output shaft (GWA) by closing the third (C), the fourth (D) and the fifth shift element (E), - A fourth gear (4) between the drive shaft (GW1) and the output shaft (GWA) by operating the first (A), the third (C) u a fourth gear (5) between the drive shaft (GW1) and the output shaft (GWA) by operating the first (A), the fourth (D) and the fifth switching element (E), - as well as the fourth switching element (D) a sixth gear (6) between the input shaft (GW1) and the output shaft (GWA) by closing the first (A), the third (C) and the fifth shifting element (E). Transmission (G) to Claim 1 or 2 wherein a first reverse gear (R1) between the drive shaft (GW1) and the output shaft (GWA) results by closing the first (A), the second (B) and the third shift element (C). Transmission (G) according to one of Claims 1 to 3 wherein the second element (E23) of the third planetary gear set (P3) is non-rotatably connected to the first element (E11) of the first planetary gear set (P1), whereas the first element (E13) of the third planetary gear set (P3) is connected via the fifth switching element (E ) can be fixed. Transmission (G) according to one of Claims 1 to 3 wherein the first element (E11) of the third planetary gear set (P3) is fixed, whereas the second element (E23) of the third planetary gear set (P3) by means of the fifth switching element (E) rotatably with the first element (E11) of the first planetary gear set (P1 ) is connectable. Transmission (G) according to one of the preceding claims, wherein the first planetary gear set (P1) and the second planetary gear set (P2) are arranged together in a gear plane. Transmission (G) according to one of the preceding claims, wherein the third planetary gear set (P3) and the fourth planetary gear set (P4) are arranged together in a gear plane. Transmission (G) according to one of the preceding claims, wherein in addition an electric machine (EM) is provided, the rotor (R) rotatably connected to the drive shaft (GW1) or coupled via at least one translation stage with the drive shaft (GW1). Transmission (G) according to one of the preceding claims, wherein in addition a sixth switching element (K0) is provided, via which the drive shaft (GW1) rotatably connected to a connection shaft (AN) can be connected. Transmission (G) according to one of the preceding claims, wherein the drive shaft (GW1) and the output shaft (GWA) are provided coaxially with each other, wherein connection points (GW1-A, GWA-A) of the drive shaft (GW1) and the output shaft (GWA) lie on the same axial end. Transmission (G) according to one of Claims 1 to 9 wherein the drive shaft (GW1) and the output shaft (GWA) are provided coaxially with each other, wherein connection points (GW1-A, GWA-A) of the drive shaft (GW1) and the output shaft (GWA) are formed at opposite axial ends. Transmission (G) according to one of the preceding claims, wherein the respective planetary gear set (P1, P2, P3, P4) is present as a minus planetary gear set, wherein it is at the respective first element (E11, E12, E13, E14) of the respective planetary gear set ( P1, P2, P3, P4) about a respective sun gear, at the respective second element (E21, E22, E23, E24) of the respective planetary gear set (P1, P2, P3, P4) about a respective planet web and at the respective third element ( E31, E32, E33, E34) of the respective planetary gear set (P1, P2, P3, P4) is a respective ring gear. Transmission according to one of the preceding claims, wherein the respective planetary gear set is present as a plus-planetary gear, wherein it is at the respective first element of each planetary gear set to a respective sun gear at the respective second element of the respective planetary gear around a respective ring gear and at the respective third Element of each planetary gear set is about a respective planetary web. Motor vehicle drive train, comprising a transmission (G) after one or more of the Claims 1 to 13 ,

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