DE102017206811A1 - Transmission for a motor vehicle - Google Patents

Abstract

The invention relates to a transmission (G) for a motor vehicle, wherein the transmission (G) comprises a drive shaft (GW1), an output shaft (GW2), four planetary gear sets (P1, P2, P3, P4) and six shift elements (K1, B1, K2 , K3, K4, B2), wherein by selectively operating the six switching elements (K1, B1, K2, K3, K4, B2) ten forward gears and one reverse gear between the drive shaft (GW1) and the output shaft (GW2) 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 and an output shaft, and a first, a second, a third and a fourth planetary gear, wherein the planetary gear sets each comprise a plurality of elements, wherein a first, a second, a third, a fourth , A fifth and a sixth switching element are provided by the selective actuation different power flow guides on the planetary gear sets under different gears between drive shaft and output shaft can be displayed.

In the present case, a transmission is thus a multi-speed transmission, d. H. There are several different ratios as gears between the drive shaft and the output shaft of the transmission by operating corresponding switching elements switchable, this is preferably done automatically. Depending on the arrangement of the switching elements, these are clutches or brakes. Such transmissions are mainly used in motor vehicles to implement a traction power supply of a prime mover of the respective motor vehicle in terms of various criteria suitable.

From the WO 2015/029481 A1 goes out a gearbox which comprises four planetary gear sets, each composed of several elements in the form of one sun gear, one planet web and one ring gear each. In addition, six switching elements are provided, through the selective actuation of different gears between a drive shaft and an output shaft of the transmission can be displayed. Overall, ten forward gears, and a reverse gear between the drive shaft and the output shaft can be switched.

It is the object of the present invention to provide an alternative embodiment to the transmission known from the prior art with at least ten forward gears and one reverse gear.

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, in which a transmission according to the invention is used, is the subject matter of claim 15.

According to the invention, a transmission comprises a drive shaft and an output shaft, and a first, a second, a third and a fourth planetary gear set. The planetary gear sets each comprise a plurality of elements and serve to guide a flow of power from the drive shaft to the output shaft. Further, six switching elements are provided, through the selective actuation of different power flow guides on the planetary gear sets under different gears between drive shaft and output shaft can be displayed.

In the context of the invention, a "shaft" is understood to mean a rotatable component of the transmission via which each associated components of the transmission are connected to one another in an axially and / or rotationally fixed manner or via which such a connection can be produced upon actuation of a corresponding switching element. 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 an axis along which the planetary gear sets are arranged coaxially to one another. The term "radial" is understood to mean an orientation in the diameter direction of a shaft lying on the axis.

The planetary gear sets are preferably arranged in the axial direction in the order of the first planetary gearset, the second planetary gearset, the third planetary gearset, and the fourth planetary gearset. In principle, however, another arrangement could also be made within the scope of the invention.

The invention now includes the technical teaching that the drive shaft is rotatably connected to the third element of the first planetary gear set and can be rotatably connected via the first switching element with the first element of the fourth planetary gear in combination. Furthermore, the first element of the first planetary gear set is fixed to a rotationally fixed component, whereas the second element of the first planetary gear set is non-rotatably in communication with the first element of the second planetary gear set. The third element of the second planetary gear set can be fixed on the one hand by means of the second switching element to a non-rotatable component and the other via the third switching element rotatably connected to the first element of the fourth planetary gear set, with which the second element of the second planetary gear by means of the fourth switching element rotationally fixed in Connection can be brought.

Furthermore, the third element of the fourth planetary gear set is rotatably connected to the output shaft, whereas the second element of the fourth planetary gear via the fifth switching element rotatably connected to the drive shaft in combination can be brought. Finally, in the third planetary gear set, there is a first coupling of the first element of the third planetary gear set with a non-rotatable component, a second coupling of the second element of the third planetary gear set with the second element of the fourth planetary gear set, and a third coupling of the third element of the third planetary gear set with the second Element of the second planetary gear set. Of these couplings are two couplings as permanent non-rotatable compounds before, while the remaining coupling a rotationally fixed connection by means of the sixth switching element can be produced.

In other words, in the transmission according to the invention, therefore, the drive shaft is permanently non-rotatably connected to the third element of the first planetary gear set, whose second element is permanently non-rotatably connected to the first element of the second planetary gear set. Furthermore, the first element of the first planetary gear set is permanently fixed to a non-rotatable component, whereas the third element of the fourth planetary gear set is constantly rotatably connected to the output shaft.

Upon actuation of the first switching element, the drive shaft is rotatably connected to the first element of the fourth planetary gear set, while the second switching element fixed in the closed state, the third element of the second planetary gear set on a rotationally fixed component. The third element of the second planetary gear set can also be rotatably connected via the third switching element to the first element of the fourth planetary gear set, which also in the closed state of the fourth switching element rotatably connected to the second element of the second planetary gear set. In contrast, the fifth switching element in the actuated state, the second element of the fourth planetary gear set and the drive shaft rotatably connected to each other.

In the case of the third planetary gear set there are three couplings of the elements of the third planetary gear set in the transmission according to the invention. 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, there is a second coupling to the second element of the fourth planetary gear set. A third coupling is then present in the form of the third element of the third planetary gear set with the third element of the second planetary gear set. Two of the three aforementioned couplings are realized as permanent non-rotatable connections, while the remaining coupling is present as a compound that is made non-rotatably only by closing the sixth switching element.

For the purposes of the invention, a "coupling" is to be understood as meaning a connection which either consists of a permanently non-rotatable connection or is made non-rotatable only by actuating a respective switching element.

The non-rotatable components of the transmission according to the invention are permanently stationary components of the transmission, preferably a transmission housing or a part of such a transmission housing or a permanently connected to the transmission housing component. The first element of the first planetary gear set is permanently fixed to a rotationally fixed component and is thus constantly prevented from rotating. Likewise, the third element of the second planetary gear set can be stopped by closing the second switching element on the same or a further rotationally fixed component and thus then its rotational movement can be prevented.

In the transmission according to the invention, the second switching element is designed as a brake which brakes when driven the respective rotatable component or the rotatably interconnected, rotatable components of the transmission to a standstill and fixed to a non-rotatable component. In contrast, the first, the third, the fourth and the fifth switching element are in the form of clutches which, when actuated, each match the respective rotatable components of the transmission in their rotational movements and subsequently connect them to one another in a rotationally fixed manner. The sixth switching element can be designed either as a brake or as a clutch, depending on the connection to be made.

Preferably, the first switching element is provided together with the fifth switching element axially on a side facing away from a connection point of the drive shaft side of the fourth planetary gear, wherein the first switching element and the fifth switching element axially axially adjacent to each other and radially substantially at the same height. Therefore, the first switching element and the fifth switching element could possibly be supplied via a common supply line. More preferably, the first switching element and the fifth switching element are placed radially in the region of the third element of the fourth planetary gear set.

Furthermore, the second switching element is arranged in particular axially between the first planetary gear set and the second planetary gear set and in this case lies axially immediately adjacent to the second planetary gear set and radially surrounding this. The third switching element and the fourth Switching element are preferably provided axially immediately adjacent to each other between the second planetary gear and the third planetary gear, wherein the third switching element is axially between the second planetary gear and the fourth switching element and is disposed radially inwardly of the fourth switching element. Due to this spatial arrangement, therefore, a common supply of the third and the fourth switching element could be realized.

A respective rotationally fixed connection of the rotatable elements of the planetary gear sets according to the invention preferably realized via one or more intermediate waves, which may be present in a spatially dense position of the element as a short axial and / or radial spacers. Specifically, the permanently non-rotatably interconnected elements of the planetary gear sets can each be present either as non-rotatably interconnected individual components or in one piece. In the second-mentioned case, the respective elements and the optionally existing shaft are then formed by a common component, wherein this is realized in particular just when the respective elements in the transmission are spatially close to each other.

In the case of elements of the planetary gear sets, which are connected to one another in a rotationally fixed manner only by actuation of a respective switching element, a connection via one or even several intermediate shafts is likewise realized.

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

According to one embodiment of the invention, the second element of the fourth planetary gear set is non-rotatably connected to the second element of the third planetary gear set, the third element is non-rotatably connected to the second element of the second planetary gear set. In addition, the first element of the third planetary gear set can be fixed via the sixth switching element on a rotationally fixed component.

In this case, therefore, the second element of the third planetary gear set is constantly rotatably connected to the second element of the fourth planetary gear set and can also be rotatably connected together with this via the fifth switching element with the drive shaft in connection. Further, the third element of the third planetary gear set is permanently non-rotatably connected to the second element of the second planetary gear set, while the first element of the third planetary gear set is fixed in the closed state of the sixth switching element to a rotationally fixed component. The sixth switching element is preferably arranged axially between the third planetary gear set and the fourth planetary gear set and radially surrounding these.

According to an alternative embodiment of the invention, the second element of the second planetary gear set is rotatably connected to the third element of the third planetary gear set, whose first element is fixed to a non-rotatable component. In addition, the second element of the third planetary gear set can be rotatably connected via the sixth switching element with the second element of the fourth planetary gear in combination.

In this variant, the first element of the third planetary gear set is permanently fixed to a rotationally fixed component and is thus permanently prevented from rotating, whereas the third element of the third planetary gear set and the second element of the second planetary gear set are constantly rotatably connected with each other. On the other hand, the second element of the third planetary gear set is connected in a rotationally fixed manner to the second element of the fourth planetary gear set only by closing the sixth switching element. The sixth switching element is preferably provided axially between the second planetary gear set and the third planetary gear set and is more preferably axially between the fourth switching element and the third planetary gear set. Due to this spatial arrangement, therefore, a common supply of the third switching element, the fourth switching element and the sixth switching element could be realized. Radially, the sixth switching element is preferably arranged in the region of the second element of the third planetary gear set.

According to a further alternative embodiment of the invention, the second element of the fourth planetary gear set is non-rotatably connected to the second element of the third planetary gear set, whose first element is fixed to a rotationally fixed component. Further, the third element of the third planetary gear set can be rotatably connected via the sixth switching element with the second element of the second planetary gear in combination.

In this case, the first element of the third planetary gear set is permanently shut down on a rotationally fixed component, so that a rotational movement of the first element of the third planetary gear set is permanently prevented. The second element of the third planetary gear set and the second element of the fourth planetary gear set are permanently connected to each other in a rotationally fixed manner and can together via the fifth Switching element rotatably connected to the drive shaft in connection. In contrast, the third element of the third planetary gear set is connected by closing the sixth switching element rotationally fixed to the second element of the second planetary gear set. The sixth shifting element lies axially preferably in the wheel plane of the third planetary gear set, ie substantially at the same axial height, and is arranged radially surrounding this.

In the aforementioned variants of a transmission according to the invention ten forward gears, and a reverse gear can be realized by selectively closing each of three switching elements. In this case, a first forward gear is switched by operating the second, the fourth and the sixth switching element, while a second forward gear is formed by closing the second, the third and the sixth switching element. Further, a third forward speed results by operating the third, fourth and sixth shift elements, whereas a fourth forward speed is switchable by operating the first, third and sixth shift elements. Further, a fifth forward speed can be represented by closing the first, the fourth and the sixth shift element, wherein the fourth, the fifth and the sixth shift element are to be actuated for the circuit of a sixth forward gear.

Furthermore, a seventh forward gear in a first variant results by actuating the first, the fourth and the fifth shifting element. A seventh forward gear can also in a second variant by closing the first, second and fifth switching element, in a third variant by operating the first, the fifth and the sixth switching element, and in a fourth variant by closing the first, the third and the fifth switching element to be switched. An eighth forward speed is obtained by operating the third, fourth and fifth shift elements, whereas a ninth forward speed can be switched by operating the second, fourth and fifth shift elements. Finally, for the circuit of a tenth forward gear to close the second, the third and the fifth switching element. A reverse gear is obtained by operating the first, the second and the sixth switching 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. For a sequential shift of the forward gears according to their order is, except for the second, the third and the fourth variant of the seventh forward gear, always to vary the state of two switching elements by opening one of the preceding elements involved in the forward gear and another To close switching element for displaying the subsequent forward gear is. This then has the consequence that a shift between the courses can proceed very quickly.

Advantageously, in the transmission according to the invention, a reverse gear for a drive via the drive machine upstream of the transmission can be realized. This can be realized as an alternative or in addition to an arrangement of an electric machine in the transmission, in order to be able to realize a reverse drive of the motor vehicle in case of failure of the electric machine.

In a further development of the invention, an additional gear can be switched by actuating the third, the fifth and the sixth switching element. Also, this additional gear can be represented in the individual aforementioned variants of a transmission according to the invention, the additional gear, however, does not fit well in the translation series.

It is a further embodiment of the invention that the respective planetary gear is present as a minus planetary gear, wherein it is at the respective first element of each planetary gear to a respective sun gear at the respective second element of the respective planetary gear around a respective planet web and at the respective third element of the respective planetary gear set is a respective 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 carries at least one but preferably a plurality of planetary gears which in each case mesh with both the sun gear and the surrounding ring gear , Of the four planetary gear sets then one or more planetary gear sets are designed as such minus planetary gear sets. Particularly preferably, however, the first, the third and the fourth planetary gear set are present as minus planetary gear sets, which makes it possible to realize a particularly compact construction.

Alternatively or in addition thereto, the respective planetary gear set is in the form of a positive planetary gear set, wherein the respective first element of the respective planetary gear set is a respective sun gear, the respective second element of the respective planetary gear set is a respective ring gear and the respective third element of the respective planetary gear set is about a respective planetary land. In a plus-planetary gear set, the elements sun gear, ring gear and planet web are also present, the latter leading at least one pair of planetary gears, in which the a planetary gear with the inner sun gear and the other planet gear with the surrounding ring gear is in meshing engagement, and the planetary gears mesh with each other. In the transmission according to the invention, one or more planetary gear sets may be designed as such plus planetary gear sets. In particular, the second planetary gear set is designed as a plus planetary gear set.

Where there is a connection of the individual elements, a minus planetary gear set can be converted into a plus-planetary gear set, then compared to the execution as a minus planetary gear set the Hohlrad- and the Planetensteganbindung to exchange each other, and a respective 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 respective gearbox ratio reduced by one. Preferably, in the transmission according to the invention, however, the first, the third and the fourth planetary gear set are designed as minus planetary gear sets, while the second planetary gear set is present as a plus-planetary gear set.

In a further development of the invention, one or more switching elements are each realized as non-positive switching elements. Non-positive switching elements have the advantage that they can be switched under load, so that a change between the courses without interruption of traction is enforceable. But particularly preferably, the sixth switching element is designed as a form-locking switching element, such as a dog clutch or lock synchronization. Because the sixth switching element is involved in the representation of the first to sixth forward gear, so that ultimately takes place only an opening in the course of a successive upshift. A form-fitting switching element has the advantage over a non-positive switching element that only slight drag torques occur in the opened state, so that a higher efficiency can be realized.

According to a further embodiment of the invention, the second element of the first planetary gear set and the first element of the second planetary gear set are rotatably coupled to a power take-off. In this case, the transmission according to the invention is thus equipped with a power take-off, via which a drive of ancillary units or the like can take place. More preferably, the power take-off is axially between the first planetary gear set and the second planetary gear set. Alternatively, a power take-off can also be connected in a rotationally fixed manner to the drive shaft.

In a further development of the invention, the drive shaft and the output shaft are coaxial with each other and each form a connection point, wherein the connection point of the drive shaft and the connection point of the output shaft are at opposite axial ends. This type of arrangement is particularly suitable for use in a motor vehicle with an aligned in the direction of travel of the motor vehicle drive train. Alternatively, the connection point of the output shaft but also be aligned transversely to the junction of the drive shaft to realize a structure which is suitable for a transversely oriented to the direction of travel of the motor vehicle drive train. In this case, the connection point of the output shaft may be formed by a toothing, which meshes with a toothing of a shaft arranged axially parallel to the drive shaft. The axle differential of a drive axle can then be arranged on this shaft.

In a further development of the invention, an electric machine is provided whose rotor is rotatably coupled to one of the rotatable components of the transmission. Preferably, then a stator of the electric machine is rotatably connected to a non-rotatable component of the transmission. In addition, the electric machine can in this case in particular be operated by an electric motor and / or as a generator in order to realize different functions. Preferably, a purely electric driving, a boosting via the electric machine, a deceleration and recuperation and / or a synchronization in the transmission via the electric machine can be performed. The rotor of the electric machine can be coaxial with the respective component or be arranged off-axis to this, then in the latter case, a coupling via one or more intermediate gear ratios, for example in the form of spur gears, or a traction drive, such as a chain drive, be realized can.

Preferably, however, the rotor of the electric machine is rotatably coupled to the drive shaft, whereby a purely electric driving of the motor vehicle is represented in a suitable manner. More preferably, one or more of the switching elements are used as internal starting elements for electric driving. For this purpose, in particular, the second switching element or the sixth switching element, since these are each closed both in reverse, as well as in the first two forward gears are. As a further alternative, however, a separate starting clutch can be used, which is positioned between the electric machine and the gear set.

For purely electric driving one of the gears in the transmission is switched, in which Forward gears while a reverse drive of the motor vehicle is realized by an opposite rotational movement is initiated via the electric machine, whereby the reverse movement of the motor vehicle takes place in the ratio of the respective forward gear. As a result, the gear ratios of the forward gears can be used for both the electric forward and the reverse electric drive. The rotor of the electric machine could be apart from the drive shaft also connected to one of the other, rotatable components of the transmission.

According to a further embodiment possibility of the invention, which is realized in particular in combination with the aforementioned arrangement of an electric machine, in addition, a separating clutch is provided, via which the drive shaft with a connecting shaft rotatably connected. The connecting shaft then serves within a motor vehicle drive train of the connection to the drive machine. The provision of the separating clutch has the advantage that in the course of purely electric driving a connection to the drive machine can be interrupted, so that they are not dragged. The separating clutch is preferably designed as a non-positive switching element, such as a multi-disc clutch, but may also be present as a positive switching element, such as a dog clutch or lock synchronization.

In general, the transmission can in principle 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 allowing a slip speed between the 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 and is then arranged between a drive motor of the motor vehicle designed in particular as an internal combustion engine and further components of the drive train following in the direction of power flow to drive wheels of the motor vehicle. Here, the drive shaft of the transmission is either permanently non-rotatably coupled to a crankshaft of the internal combustion engine or connected via an intermediate disconnect clutch or a starting element with this, between the engine and 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 an axle drive 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 axle or the longitudinal differential can be arranged with the transmission in a common housing. Likewise, a torsional vibration damper can also be integrated into this housing.

The fact that two components of the transmission are non-rotatably "connected" or "coupled" or "communicate with one another" means in the sense of the invention a permanent connection of these components, so that they can not rotate independently of one another. In this respect, no switching element is provided between these components, in which it may be elements of the planetary gear sets or shafts or a non-rotatable component of the transmission, but the corresponding components are rigidly coupled together.

However, if a switching element is provided between two components of the transmission, then these components are not permanently rotatably coupled to each other, but a rotationally fixed coupling is made only by pressing 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 coupled to it 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. There are also possibilities, individual features, also as far as they emerge from the claims, the following description of preferred embodiments of the invention or directly from the drawings, to each other combine. 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, in welchem ein erfindungsgemäßes Getriebe zur Anwendung kommt;
• 2 eine schematische Ansicht eines Getriebes entsprechend einer ersten Ausführungsform der Erfindung;
• 3 eine schematische Darstellung eines Getriebes gemäß einer zweiten Ausgestaltungsmöglichkeit der Erfindung;
• 4 eine schematische Ansicht eines Getriebes entsprechend einer dritten Ausführungsform der Erfindung;
• 5 eine schematische Darstellung eines Getriebes gemäß einer vierten Ausgestaltungsmöglichkeit der Erfindung;
• 6 eine schematische Ansicht eines Getriebes entsprechend einer fünften Ausführungsform der Erfindung; und
• 7 ein beispielhaftes Schaltschema der Getriebe aus den 2 bis 6.

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, in which a transmission according to the invention is used;
• 2 a schematic view of a transmission according to a first embodiment of the invention;
• 3 a schematic representation of a transmission according to a second embodiment of the invention;
• 4 a schematic view of a transmission according to a third embodiment of the invention;
• 5 a schematic representation of a transmission according to a fourth embodiment of the invention;
• 6 a schematic view of a transmission according to a fifth embodiment of the invention; and
• 7 an exemplary circuit diagram of the transmission of the 2 to 6 ,

1 shows a schematic view of a motor vehicle drive train, in which 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 an axle drive 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 summarized in a common gearbox housing, in which then the axle drive 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 axle drive AG aligned in the 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 transmission includes G 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 , Each of the planetary gear sets P1 . P2 . P3 and P4 each has a first element 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 always by a sun gear of the respective planetary gear set P1 respectively. P2 respectively. P3 respectively. P4 formed while the respective second element E21 respectively. E23 respectively. E24 at the planetary gear sets P1 . P3 and P4 each as a planetary bridge is present. The remaining third element E31 respectively. E33 respectively. E34 is then by a respective ring gear of the respective planetary gear set P1 respectively. P3 respectively. P4 educated. On the other hand, in the case of the second planetary gear set P2 at the second element E22 around a ring gear and the third element E32 around a planetary bridge.

The planetary gear sets P1 . P3 and P4 In the present case, these are each designed as negative planetary gear sets, in which the respective planetary web, but preferably a plurality of planet gears rotatably mounted, which are in mesh with the radially inner sun gear and also with the surrounding ring gear in detail. In contrast, the second planetary gear set P2 as plus planetary gear set, in which the planet carrier carries at least one pair of planetary gears of the planetary gears with the radially inner sun gear and a planet gear with the radially surrounding ring gear meshing, as well as meshing the planetary gears of the pair of wheels.

Where it allows the connection, but one or more of the planetary gear sets P1 . P3 and P4 be executed as plus planetary gear sets. In comparison to a respective version as a minus planetary gear set would then for the transfer to a plus-planetary gear set the respective second element E21 respectively. E23 respectively. E24 through the respective ring gear and the respective third element E31 respectively. E33 respectively. E34 formed by the respective planet web and also a respective transmission gear ratio can be increased by one. Conversely, could also be the second planetary gear P2 be implemented as a minus planetary gear set, if it allows the connection of the elements. It would have compared to the execution as plus planetary gear set the second element E22 through the planetary bridge and the third element E32 formed by the ring gear and the Getriebestandübersetzung be reduced by one.

In the present case are the first planetary gear set P1 , the second planetary gear set P2 , the third planetary gear set P3 and the fourth planetary gear set P4 axially in the order of the first planetary gear set P1 , second planetary gear set P2 , third planetary gear set P3 and fourth planetary gear set P4 between a connection point Level 1-A a drive shaft LV1 and a connection point GW2-A an output shaft GW2 arranged.

The connection point Level 1-A and the connection point GW2-A are coaxial with each other at opposite axial ends of the transmission G intended. The connection point serves this purpose Level 1-A in the motor vehicle drive train 1 a connection to the internal combustion engine VKM while the gearbox G at the junction GW2-A with the following axle drive AG connected is.

As in 2 can be seen, includes the gearbox G a total of six switching elements in the form of a first switching element K1 , a second switching element B1 , a third switching element K2 , a fourth switching element K3 , a fifth switching element K4 and a sixth switching element B2 , Here are the switching elements K1 . B1 . K2 . K3 . K4 and B2 each designed as non-positive switching elements and are preferably before as lamella switching elements. In addition, the first switching element K1 , the third switching element K2 , the fourth switching element K3 and the fifth switching element K4 designed here as couplings, while the second switching element B1 and the sixth switching element B2 as brakes.

The present is the first element E11 of the first planetary gear set P1 permanently on a non-rotatable component GG stated, which is in particular a transmission housing of the transmission G or a part of such a transmission housing is. The second element E21 of the first planetary gear set P1 is constantly rotatable with the first element E12 of the second planetary gear set P2 in connection while the third element E31 of the first planetary gear set P1 permanently non-rotatable with the drive shaft LV1 connected is.

As well as in 2 it can be seen, the drive shaft LV1 on the one hand on the first switching element K1 with the first element E14 of the fourth planetary gear set P4 rotatably connected, and on the other by closing the fifth switching element K4 rotatably with the second element E24 of the fourth planetary gear set P4 and the second element E23 of the third planetary gear set P3 be associated. The second element E24 of the fourth planetary gear set P4 and the second element E23 of the third planetary gear set P3 are permanently connected to each other in a non-rotatable manner.

Apart from the connectivity with the drive shaft LV1 can be the first element E14 of the fourth planetary gear set P4 on the one hand via the third switching element K2 with the third element E32 of the second planetary gear set P2 , as well as the other by operating the fourth switching element K3 rotatably with the second element E22 of the second planetary gear set P2 and the third element E33 of the third planetary gear set P3 get connected. Here are the second element E22 of the second planetary gear set P2 and the third element E33 of the third planetary gear set P3 permanently rotatably connected with each other.

Furthermore, there is the third element E32 of the second planetary gear set P2 by actuating the second switching element B1 on the non-rotatable component GG be fixed, on which also the first element E13 of the third planetary gear set P3 in the closed state of the sixth switching element B2 is shut down. Finally, there is the third element E34 of the fourth planetary gear set P4 rotatably with the output shaft GW2 connected.

As in 2 can be seen, is the first switching element K1 together with the fifth switching element K4 axially on one of the connection points Level 1-A the drive shaft LV1 remote side of the fourth planetary gear set P4 provided, wherein the first switching element K1 and the fifth switching element K4 axially adjacent to each other and radially substantially at the same height and in the region of the third element E34 of the fourth planetary gear set P4 are placed. The second switching element B1 however, lies axially between the first planetary gear P1 and the second planetary gear set P2 and is disposed radially surrounding these.

Furthermore, the third switching element K2 and the fourth switching element K3 axially between the second planetary gear set P2 and the third planetary gear set P3 provided, wherein the third switching element K2 while axially between the second planetary gear P2 and the fourth switching element K3 is located radially inwardly of the fourth switching element K3 is placed. The fourth switching element is located radially at the level of the second element E22 of the second planetary gear set P2 and the third element E33 of the third planetary gear set P3 whereas the third switching element K2 radially in the region of the third element E32 of the second planetary gear set P2 is provided. Finally, there is the sixth switching element B2 axially between the third planetary gear set P3 and the fourth planetary gear set P4 and provided radially surrounding these.

In addition, goes out 3 a schematic representation of a transmission G according to a second embodiment of the invention, which in this case essentially according to the previous variant 2 equivalent. The only difference is that in addition a power take-off PTO is provided, which rotatably with the second element E21 of the first planetary gear set P1 and the first element E12 of the second planetary gear set P2 connected is. Axial is the power take-off PTO between the first planetary gear set P1 and the second planetary gear set P2 , Otherwise, the embodiment corresponds to 3 the previous variant 2 so that reference is made to what has been described.

4 shows a schematic view of a transmission G according to a third embodiment of the invention. Again, this design option corresponds again largely to the variant 2 , in contrast to the first element E13 of the third planetary gear set P3 now permanently on the non-rotating component GG is fixed and thus constantly prevented from rotating. There is also the second element E23 of the third planetary gear set P3 no longer permanently rotatable with the second element E24 of the fourth planetary gear set P4 in conjunction, but a non-rotatable connection is only by closing a sixth switching element K5 made, which is designed as a clutch. Axial is the sixth switching element K5 while between the fourth switching element K3 and the third planetary gear set P3 and is thus axially immediately adjacent to the fourth switching element K3 and to the third switching element K2 placed. In addition, the sixth switching element K5 radially in the region of the second element E23 of the third planetary gear set P3 intended. Otherwise, the design option corresponds to 4 according to the variant 2 so that reference is made to what has been described.

Furthermore goes out 5 a schematic representation of a transmission G according to a fourth embodiment of the invention, which also largely according to the Ausgestaltungsmöglichkeit 2 equivalent. It is different, however, that the first element E13 of the third planetary gear set P3 permanently on the non-rotatable component GG is fixed and accordingly can not perform any rotational movement. By contrast, the third element E33 of the third planetary gear set P3 not permanently rotatable with the second element E22 of the second planetary gear set P2 connected, but a non-rotatable connection is only by closing a sixth switching element K5 produced. The sixth switching element K5 is designed as a clutch and axially in the wheel plane of the third planetary gear set P3 placed. Accordingly, the sixth switching element lies K5 axially substantially at the height of the third planetary gear set P3 , and radially surrounding this. Otherwise, the embodiment corresponds to 5 according to the variant 2 so that reference is made to what has been described.

Finally shows 6 a schematic representation of a transmission G according to a fifth embodiment of the invention. This embodiment corresponds essentially to the variant 2 , in contrast, in addition to an electric machine EM is provided, whose stator S on the non-rotatable component GG is fixed while a rotor R the electric machine EM rotatably with the drive shaft LV1 connected is. Furthermore, the drive shaft LV1 at the junction Level 1-A via an intermediate separating clutch K0 , which is designed here as a lamellae switching element, with a connecting shaft AT rotatably connected, which in turn connected to a crankshaft of the internal combustion engine VKM by means of the intermediate torsional vibration damper TS connected is. Due to the rotationally fixed connection of the rotor R with the drive shaft LV1 is the electric machine EM coaxial with the drive shaft LV1 placed.

About the electric machine EM In this case, a purely electric driving can be realized, in which case the separating clutch K0 is opened to the drive shaft LV1 from the connection shaft AT to decouple and the internal combustion engine VKM not to lug. Otherwise, the embodiment corresponds to 6 according to the variant 2 so that reference is made to what has been described.

In 7 is an exemplary circuit diagram for the transmission G from the 2 to 6 tabulated. As can be seen, in each case a total of ten forward gears 1 to 10 , as well as a reverse gear R1 be realized, which is marked in the columns of the circuit diagram with an X respectively, which of the switching elements K1 . B1 . K2 . K3 . K4 and B2 respectively. K5 in which of the forward gears 1 to 10 and the reverse gear R1 each is closed. In each of the forward gears 1 to 10 and the reverse gear R1 are each three of the switching elements K1 . B1 . K2 . K3 . K4 and B2 respectively. K5 closed, with a successive circuit of the forward gears 1 to 10 , except for a seventh forward gear 7.2 , a seventh forward gear 7.3 and a seventh forward gear 7.4 to open one of the involved switching elements and to close another switching element in the following.

As in 7 can be seen, is a first forward gear 1 by actuating the second switching element B1 , the fourth switching element K3 and the sixth switching element B2 respectively. K5 switched, starting from this, a second forward gear 2 is formed by the fourth switching element K3 opened and in the following the third switching element K2 is closed. Furthermore, a third forward gear 3 switched by starting from the second forward gear 2 the second switching element B1 opened and the fourth switching element K3 closed becomes. Based on this results then a fourth forward gear 4 by opening the fourth switching element K3 and closing the first switching element K1 , This results in a fifth forward gear 5 by opening the third switching element K2 and actuating the fourth switching element K4 , starting from this in a sixth forward gear 6 is switched by the first switching element K1 opened and the fifth switching element K4 is closed.

To shift to a seventh forward gear 7.1 is then the sixth switching element B2 respectively. K5 to open and the first switching element K1 close. Alternatively, but also the seventh forward gear 7.2 by actuating the first switching element K1 , the second switching element B1 and the fifth switching element K4 be switched. In addition, as a further alternative, the seventh forward gear 7.3 by closing the first switching element K1 , the fifth switching element K4 and the sixth switching element B2 respectively. K5 , as well as further alternatively the seventh forward gear 7.4 by actuating the first switching element K1 , the third switching element K2 and the fifth switching element K4 being represented.

Furthermore, there is an eighth forward gear 8th by the third switching element K2 , the fourth switching element K3 and the fifth switching element K4 be operated. To further upshift into a ninth forward gear 9 is the third switching element below K2 to open and the second switching element B1 close. Furthermore, the ninth forward gear 9 in a tenth forward gear 10 switched by the fourth switching element K3 in an unactuated state and then the third switching element K2 is transferred to an actuated state.

The first reverse R1 , in which a reverse drive of the motor vehicle even when driven by the internal combustion engine VKM can be realized, however, by closing the first switching element K1 , the second switching element B1 and the sixth switching element B2 respectively. K5 connected. In the transmissions go out of the 2 to 6 can also have an additional gear Z1 are shown, which, however, not good in the translation series of the respective transmission G fits. This results in this additional gear Z1 by closing the third switching element K2 , the fifth switching element K4 and the sixth switching element B2 respectively. K5 ,

As in the 2 to 6 is shown, is the sixth switching element B2 respectively. K5 designed as non-positive switching element. However, the sixth switching element could B2 respectively. K5 Also be realized as a form-locking switching element, such as locking synchronization or as a claw switching element.

Furthermore, the gears can also G according to the embodiments of 3 to 5 analogous to the variant according to 6 be hybridized. In addition, a power take-off PTO analogous to that in 3 also shown in the embodiments according to the 4 to 6 will be realized.

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

LIST OF REFERENCE NUMBERS

G

transmission

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

K1

First switching element

B1

Second switching element

K2

Third switching element

K3

Fourth switching element

K4

Fifth switching element

B2

Sixth switching element

K5

Sixth switching element

1

First forward

2

Second forward speed

3

Third forward

4

Fourth forward

5

Fifth forward speed

6

Sixth forward

7.1

Seventh forward

7.2

Seventh forward

7.3

Seventh forward

7.4

Seventh forward

8th

Eighth forward

9

Ninth forward

10

Tenth forward

R1

reverse gear

Z1

additional transition

LV1

drive shaft

Level 1-A

junction

GW2

output shaft

GW2-A

junction

EM

electric machine

S

stator

R

rotor

AT

connecting shaft

K0

separating clutch

PTO

PTO

VKM

Internal combustion engine

TS

torsional vibration damper

AG

transaxles

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

• WO 2015/029481 A1 [0003]

Claims (15)

A transmission (G) for a motor vehicle, comprising a drive shaft (GW1) and an output shaft (GW2), and a first (P1), a second (P2), a third (P3) and a fourth planetary gear set (P4), wherein the planetary gear sets (P1, P2, P3, P4) each comprise a plurality of elements (E11, E12, E13, E14, E21, E22, E23, E24, E31, E32, E33, E34), wherein a first (K1), a second (B1 ), a third (K2), a fourth (K3), a fifth (K4) and a sixth switching element (B2; K5) are provided, by their selective actuation different power flow guides on the planetary gear sets (P1, P2, P3, P4) Circuit of different gears (1 to 10, R1) between the drive shaft (GW1) and output shaft (GW2) are represented, characterized in that the drive shaft (GW1) rotatably connected to the third element (E31) of the first planetary gear set (P1) and via the first switching element (K1) rotatably with the first element (E14) of the fourth planetary gear set (P4) in Ver can be brought - that the first element (E11) of the first planetary gear set (P1) is fixed to a non-rotatable component (GG), whereas the second element (E21) of the first planetary gear set (P1) rotatably with the first element (E12) of second planetary gear set (P2) is in connection, - that the third element (E32) of the second planetary gear set (P2) by means of the second switching element (B1) on a non-rotatable component (GG) can be fixed and on the other via the third switching element (K2) rotatably connected to the first element (E14) of the fourth planetary gear set (P4) is connectable, with which the second element (E22) of the second planetary gear set (P2) by means of the fourth switching element (K3) rotatably connected in connection, - that the third element (E14) E34) of the fourth planetary gear set (P4) rotatably connected to the output shaft (GW2), whereas the second element (E24) of the fourth planetary gear set (P4) via the fifth switching element (K4) rotationally fixed with d in the third planetary gear set (P3), a first coupling of the first element (E13) of the third planetary gear set (P3) with a non-rotatable component (GG), a second coupling of the second element (G3) E23) of the third planetary gear set (P3) with the second element (E24) of the fourth planetary gear set (P4), and a third coupling of the third element (E33) of the third planetary gear set (P3) with the second element (E22) of the second planetary gear set (P2 ), wherein of these couplings two couplings exist as permanent non-rotatable connections, while in the remaining coupling a rotationally fixed connection by means of the sixth switching element (B2; K5) can be produced. Transmission (G) to Claim 1 , characterized in that the second element (E24) of the fourth planetary gear set (P4) is non-rotatably connected to the second element (E23) of the third planetary gear set (P3), the third element (E33) rotatably connected to the second element (E22) of the second Planetary gear set (P2) is in communication, wherein the first element (E13) of the third planetary gear set (P3) via the sixth switching element (B2) on a rotationally fixed component (GG) can be fixed. Transmission (G) to Claim 1 characterized in that the second element (E22) of the second planetary gear set (P2) is non-rotatably connected to the third element (E33) of the third planetary gear set (P3) whose first element (E13) is fixed to a non-rotatable component (GG), wherein the second element (E23) of the third planetary gear set (P3) via the sixth switching element (K5) rotatably connected to the second element (E24) of the fourth planetary gear set (P4) is connectable. Transmission (G) to Claim 1 characterized in that the second element (E24) of the fourth planetary gear set (P4) is non-rotatably connected to the second element (E23) of the third planetary gear set (P3) whose first element (E13) is fixed to a non-rotatable component (GG), wherein the third element (E33) of the third planetary gear set (P3) via the sixth switching element (K5) rotatably connected to the second element (E22) of the second planetary gear set (P2) is brought into connection. Transmission (G) according to one of the preceding claims, characterized in that a first forward gear (1) by operating the second (B1), the fourth (K3) and the sixth switching element (B2, K5), a second forward gear (2) by Actuating the second (B1), the third (K2) and the sixth shifting element (B2; K5), a third forward speed (3) by actuating the third (K2), the fourth (K3) and the sixth shifting element (B2; K5) a fourth forward speed (4) by operating the first (K1), the third (K2) and the sixth shifting element (B2; K5), a fifth forward speed (5) by operating the first (K1), the fourth (K3) and a sixth forward gear (6) by operating the fourth (K3), the fifth (K4) and the sixth shifting element (B2; K5), a seventh forward gear (7.1) by operating the first (K1 ), the fourth (K3) and the fifth switching element (K4) or (7.2) by actuating the first (K1), the zw Eiten (B1) and the fifth switching element (K4) or (7.3) by operating the first (K1), the fifth (K4) and the sixth switching element (B2; K5) or (7.4) by operating the first (K1), the third (K2) and the fifth shifting element (K4), an eighth forward speed (8) by operating the third (K2), the fourth (K3) and the fifth shifting element (K4), a ninth forward gear (9) by operating the second (B1), the fourth (K3) and the fifth switching element (K4), a tenth forward gear (10) by operating the second (B1), the third (K2) and the fifth switching element (K4) , a reverse gear (R1) is switchable by operating the first (K1), the second (B1) and the sixth shifting element (B2; K5). Transmission (G) according to one of the preceding claims, characterized in that an additional gear (Z1) can be switched by actuating the third (K2), the fifth (K4) and the sixth shifting element (B2; K5). Transmission (G) according to one of the preceding claims, characterized in that the respective planetary gear set (P1, P3, P4) is present as a minus planetary gear set, wherein it is at the respective first element (E11, E13, E14) of the respective planetary gear set (P1 , P3, P4) about a respective sun gear, at the respective second element (E21, E23, E24) of the respective planetary gear set (P1, P3, P4) about a respective planet web and at the respective third element (E31, E33, E34) of respective planetary gear set (P1, P3, P4) is a respective ring gear. Transmission (G) according to one of the preceding claims, characterized in that the respective planetary gear set (P2) is present as a plus-planetary gear, wherein it is in the respective first element (E12) of the respective planetary gear set (P2) to a respective sun gear, wherein respective second element (E22) of the respective planetary gear set (P2) is a respective ring gear and the respective third element (E32) of the respective planetary gear set (P2) is a respective planet gear. Transmission (G) according to one of the preceding claims, characterized in that one or more switching elements (K1, B1, K2, K3, K4, B2, K1, B1, K2, K3, K4, K5) are each realized as non-positive switching element. Transmission according to one of the preceding claims, characterized in that the sixth switching element is realized as a form-locking switching element. Transmission (G) according to one of the preceding claims, characterized in that the drive shaft (GW1) and the output shaft (GW2) are coaxial with each other and each form a connection point (GW1-A, GW2-A), wherein the connection point (GW1- A) of the drive shaft (GW1) and the connection point (GW2-A) of the output shaft (GW2) lie at opposite axial ends. Transmission (G) according to one of the preceding claims, characterized in that the second element (E21) of the first planetary gear set (P1) and the first element (E12) of the second planetary gear set (P2) are rotatably coupled to a PTO (PTO). Transmission (G) according to one of the preceding claims, characterized in that an electric machine (EM) is provided, whose rotor (R) is coupled to a rotatable component. Transmission (G) according to one of the preceding claims, characterized in that in addition a separating clutch (K0) is provided, via which the drive shaft (GW1) with a connecting shaft (AN) is rotatably connected. Motor vehicle drive train, comprising a transmission (G) after one or more of the Claims 1 to 14 ,

Images