DE102017206801A1 - 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 (B1, K1, K2 , B2, K3, K4), wherein by selectively operating the six shift elements (B1, K1, K2, B2, K3, K4) ten forward gears and two reverse gears between the drive shaft (GW1) and the output shaft (GW2) are switchable, as well 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 a drive shaft, and a first, a second, a third and a fourth planetary gear set, wherein the planetary gear sets each comprise a plurality of elements, wherein the first element of the respective planetary gear set is formed by a sun gear , wherein the second element of the respective planetary gear set in the case of a minus planetary gear set is formed by a land and in the case of a plus planetary gear set by a ring gear, wherein the third element of the respective planetary gear set in the case of a minus planetary gear set through the ring gear and in the case Plus planetary gear set is formed by the web, wherein a first, a second, a third, a fourth, a fifth and a sixth switching element are provided, wherein by selective actuation of three of the switching elements different power flow guides on the planetary gear sets under different Gän ge between drive shaft and output shaft are represented, wherein the drive shaft is rotatably connected to the second element of the second planetary gear set, the first element via the first switching element on a non-rotatable component fixable and the third member is rotatably connected to the first element of the third planetary, wherein the drive shaft also by means of the second switching element rotatably connected to the first element of the fourth planetary gear in conjunction is further connected via the third switching element rotatably connected to the third element of the third planetary, with the second element of the fourth planetary gear set is rotatably connected to the output shaft and wherein in the first planetary gear set, a first coupling of the first element of the first planetary gear set with the first element of the second planetary gear set, a second coupling of the second element of the first planetary gear set with the third Ele ment of the fourth planetary gear set, as well as a third coupling of the third element of the first planetary gear set with a non-rotatable component, of these couplings two couplings exist as permanent non-rotatable connections, while in the remaining coupling a rotationally fixed connection by means of the fourth switching element can be produced.

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 US 8,545,362 B1 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 known from the prior art transmission with ten forward gears and at least 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 also the subject of claim 12.

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" is meant in the context of the invention, an orientation in the direction of an axis along which the Planetenradsätze coaxial with each other are arranged horizontally. The term "radial" is understood to mean an orientation in the diameter direction of a shaft lying on the axis.

The planetary gear sets can each, if it allows the connection of the elements, be designed either as a minus planetary gear set or as plus planetary gear set. In the case of a minus planetary gear set, the respective first element of the respective planetary gear set is a respective sun gear, in the respective second element of the respective planetary gear set about a respective planetary land and the respective third element of the respective planetary gear around a respective ring gear. A minus planetary set is thus 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 a plurality of planet gears, which in detail each with both the sun gear and the surrounding ring gear comb.

By contrast, in the case of a positive planetary gear set, the respective first element of the respective planetary gear set is a respective sun gear, in the respective second element of the respective planetary gear set a respective ring gear and in the respective third element of the respective planetary gear set about a respective planet 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.

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.

In the transmission according to the invention, the drive shaft is non-rotatably connected to the second element of the second planetary gear set, the first element via the first switching element can be fixed to a non-rotatable component and the third element is rotatably connected to the first element of the third planetary gear set. The drive shaft can also be rotatably connected by means of the second switching element with the first element of the fourth planetary gear in conjunction, which is further rotatably connected via the third switching element with the third element of the third planetary gear set. Furthermore, the second element of the fourth planetary gear set is rotatably connected to the output shaft, whereas in the first planetary gear set, a first coupling of the first element of the first planetary gear set with the first element of the second planetary gear set, a second coupling of the second element of the first planetary gear set with the third element of the fourth planetary gear set, as well as a third coupling of the third element of the first planetary gear set with a non-rotatable component. Of these couplings are then two couplings as permanent non-rotatable compounds before, while the remaining coupling a rotationally fixed connection can be made by means of the fourth switching element.

The non-rotatable component of the transmission according to the invention is a permanently stationary component of the transmission, preferably a transmission housing or a part of such a transmission housing. In this case, the first element of the second planetary gear set fixed by closing the first switching element on the rotationally fixed component and thus prevented in the sequence of a rotational movement. The rotationally fixed components can be one and the same component, as well as various components, for example different housing parts.

The invention includes the technical teaching that the third element of the fourth planetary gear is rotatably connected to the second element of the third planetary gear, the third element via the fifth switching element rotationally fixed to the second element of the fourth planetary gear set can be associated. Furthermore, the first element of the third planetary gear set and the third element of the second planetary gear set can be connected together in a rotationally fixed manner by means of the sixth shifting element to the first element of the fourth planetary gearset.

In other words, in the transmission according to the invention, the drive shaft is permanently connected non-rotatably to the second element of the second planetary gear set, whose third element is permanently non-rotatably connected to the first element of the third planetary gear set. Likewise, the second element of the third planetary gear set and the third element of the fourth planetary gear set are permanently connected to each other in a rotationally fixed manner, whereas the second element of the fourth planetary gear set is permanently non-rotatably connected to the output shaft.

By closing the first switching element, the first element of the second planetary gear set is fixed to a rotationally fixed component, while the actuation of the second switching element a rotationally fixed connection of the drive shaft with the pulls first element of the fourth planetary gear by itself. The first element of the fourth planetary gear set can also be rotatably connected by closing the third switching element with the third element of the third planetary, which also in the closed state of the fifth switching element rotationally fixed to the second element of the fourth planetary gear and thus the output shaft is in communication. Finally, an actuation of the sixth switching element has a rotationally fixed connection of the first element of the fourth planetary gear set with the first element of the third planetary gear set and the third element of the second planetary gear set to the sequence.

In the case of the first planetary gear set there are three couplings of the elements of the first planetary gear set in the transmission according to the invention. Thus, a first coupling in the form of the first element of the first planetary gear set with the first element of the second planetary gear set is present, while in the case of the second element of the first planetary gear set, a second coupling to the third element of the fourth planetary gear set. A third coupling is then present in the form of the third element of the first planetary gear set with a rotationally fixed component. 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.

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

Preferably, the first switching element is provided axially on one of a connection point of the drive shaft facing side of the first planetary gear set and lies radially surrounding the first planetary gear set. On the other hand, the second switching element, the third switching element, the fifth switching element and the sixth switching element are placed axially in particular between the third planetary gear set and the fourth planetary gear set, wherein further preferably in the axial direction, an arrangement sixth switching element, second switching element, third switching element and fifth switching element between the third planetary gear set and the fourth planetary gear set is selected. Further, while the second switching element and the sixth switching element are axially adjacent to each other and substantially at the same radial height, while also the third switching element and the fifth switching element are axially juxtaposed and radially placed at the same height. Due to this placement, in each case a common supply of the second switching element and the sixth switching element and / or the third switching element and the fifth switching element could be realized via a respective common supply line.

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 first element of the second planetary gear set is non-rotatably connected to the first element of the first planetary gear set, the second member rotatably connected to the second element of the third planetary gear set and the third element of the fourth planetary gear set, wherein the third element of the first Planetary gear set can be fixed by means of the fourth switching element on a non-rotatable component.

In this case, therefore, the first element of the first planetary gear set is permanently non-rotatably in connection with the first element of the second planetary gear set and can be fixed together with this via the first switching element on a non-rotatable component. The second element of the first planetary gearset, however, is constantly non-rotatably connected to the second element of the third planetary gear set and the third element of the fourth planetary gear set, whereas the third element of the first planetary gearset can be fixed via the fourth switching element on a non-rotatable component and thus with actuation of the fourth Switching element is prevented from rotating. The fourth switching element is in this case preferably arranged in the gear plane of the first planetary gear set and thus lies axially substantially at the height of and radially surrounding the first planetary gear set.

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

In this variant, therefore, the third element of the first planetary gear set is permanently fixed to a rotationally fixed component and is thus permanently prevented from rotating. In addition, the second element of the first planetary gear set is permanently non-rotatably connected to the second element of the third planetary gear set and the third element of the fourth planetary gear set, whereas in the case of the first element of the first planetary gear set a rotationally fixed connection to the first element of the second planetary gear set only with actuation of the fourth switching element will be produced. In this case, the fourth switching element is placed in particular axially on one of a connection point of the drive shaft facing side of the first planetary gear set and lies axially between the first switching element and the first planetary gear. Radially, the fourth switching element is preferably provided between the second element and the third element of the first planetary gear set.

According to a further alternative embodiment of the invention, the first element of the second planetary gear set is rotatably connected to the first element of the first planetary gear, whose third element is fixed to a non-rotatable component, wherein the second element of the first planetary gear by means of the fourth switching element rotationally fixed to the second element of the third planetary gear set and the third element of the fourth planetary gear set can be brought into connection.

In this case, therefore, the third element of the first planetary gear set is permanently fixed to a rotationally fixed component and is thus constantly prevented from rotating, whereas the first element of the first planetary gear set permanently rotatably connected to the first element of the second planetary gear in conjunction and together with this can also be fixed to a non-rotatable component by closing the first switching element. The second element of the first planetary gear set is connected by closing the fourth switching element rotationally fixed to the second element of the third planetary gear set and the third element of the fourth planetary gear set, wherein the fourth switching element is preferably arranged axially between the first planetary gear set and the second planetary gear set and radially surrounding lies to the two planetary gear sets.

In the aforementioned variants of a transmission according to the invention ten forward gears, and two reverse gears can be realized by selectively closing three switching elements. In this case, a first forward gear is switched by operating the first, the second and the fourth switching element, while a second forward gear is formed by closing the first, the fourth and the sixth switching element. Furthermore, a third forward gear results by actuating the second, the fourth and the sixth shift element, whereas a fourth forward gear in a first variant can be shifted by actuating the fourth, the fifth and the sixth shift element. Alternatively, a fourth forward gear in a second variant can also be switched by closing the third, the fourth and the fifth shift element or, alternatively, in a third variant by actuating the third, the fourth and the sixth shift element.

Further, a fifth forward speed can be represented by closing the second, the fourth and the fifth shift element, wherein the sixth, the third and the fourth 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 second, the third and the fifth shifting element, the seventh forward gear alternatively also in a second variant by closing the second, the fifth and the sixth shifting element or, alternatively, in one third variant can be switched by actuating the second, the third and the sixth switching element.

An eighth forward speed is switchable by operating the first, second and third shift elements, while a ninth forward speed may be switched by operating the first, second and fifth shift elements. For the circuit of a tenth forward gear, the first, the third and the fifth switching element are to be closed in a first variant. Alternatively, a tenth forward gear in a second variant can also be switched by closing the first, the fifth and the sixth shifting element or, alternatively, in a third variant by actuating the first, the third and the sixth shifting element.

Further, a first reverse gear results by operating the first, the third and the fourth shift element, while a second reverse gear is switched upon closing of the first, the fourth and the fifth shift element.

With a suitable choice of stationary gear ratios of the planetary gear sets this is a suitable for the application in the field of a motor vehicle translation series realized. For a sequential shift of the forward gears according to their order is, with the exception of the second and third variant of the fourth forward gear, the second variant of the seventh forward gear and the third variant of the tenth forward gear, always to vary the state of each two switching elements by one of To open the switching elements involved in the previous forward gear and to close another 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 two reverse gears can be realized for a drive via the drive machine upstream of the transmission. 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.

According to one embodiment of the invention, the planetary gear sets are all designed as minus planetary gear sets. Where there is a connection of the individual elements, but also one or more of the minus planetary gear sets can each be converted into a plus-planetary gear set, in which case compared to the execution as a minus planetary gear set the Hohlrad- and the Planetensteganbindung with each other, as well as a respective transmission gear ratio is to increase by one. As already mentioned, but preferably all planetary gear sets are realized as minus planetary gear sets.

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 fourth switching element is designed as a form-locking switching element, such as a jaw clutch or lock synchronization. Because the fourth 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 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 be operated in particular by an electric motor and / or a generator in order to realize different functions. In particular, 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 first switching element or the fourth switching element, since these are closed both in the reverse gears, 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 is engaged in the transmission, wherein in the 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, the hereby directly rotatably connected to each other components under run 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, 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; und
• 6 ein beispielhaftes Schaltschema der Getriebe aus den 2 bis 5.

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; and
• 6 an exemplary circuit diagram of the transmission of the 2 to 5 ,

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. E22 respectively. E23 respectively. E24 at the planetary gear sets P1 . P2 . P3 and P4 each as a planetary bridge is present. The still remaining, third element E31 or E32 or E33 or E34 is then by a respective ring gear of the respective planetary gear set P1 respectively. P2 respectively. P3 respectively. P4 educated.

The planetary gear sets P1 . P2 . 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.

Where it allows the connection, but one or more of the planetary gear sets P1 . P2 . P3 and P4 be executed as plus planetary gear sets. In the case of a plus planetary gear set, the planet carrier then carries at least one pair of planetary gears, whose planet gears mesh with the radially inner sun gear and a planetary gear with the radially surrounding ring gear, and the planetary gears of the pair of wheels intermesh with one another. 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. 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 can be increased 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 one junction 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 B1 , a second switching element K1 , a third switching element K2 , a fourth switching element B2 , a fifth switching element K3 and a sixth switching element K4 , Here are the switching elements B1 . K1 . K2 . B2 . K3 and K4 each designed as non-positive switching elements and are preferably before as lamella switching elements. In addition, the second switching element K1 , the third switching element K2 , the fifth switching element K3 and the sixth switching element K4 designed here as couplings, while the first switching element B1 and the fourth switching element B2 as brakes.

Present are the first element E11 of the first planetary gear set P1 and the first element E12 of the second planetary gear set P2 rotatably connected to each other and can together via the first switching element B1 on a non-rotatable component GG be set, 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 permanently non-rotatable with the second element E23 of the third planetary gear set P3 and the third element E34 of the fourth planetary gear set P4 in connection.

As well as in 2 it can be seen, is the second element E22 of the second planetary gear set P2 rotatably with the drive shaft LV1 connected, which also has the second switching element K1 non-rotatable with the first element E14 of the fourth planetary gear set P4 get connected. In addition to the rotationally fixed connectivity with the drive shaft LV1 can be the first element E14 of the fourth planetary gear set P4 also still on the one hand via the third switching element K2 non-rotatable with the third element E33 of the third planetary gear set P3 , and on the other hand by means of the sixth switching element K4 non-rotatable with the first element E13 of the third planetary gear set P3 and the third element E32 of the second planetary gear set P2 be associated. The first element E13 of the third planetary gear set P3 and the third element E32 of the second planetary gear set P2 are permanently connected to each other in a non-rotatable manner.

In 2 is also to recognize that the third element E31 of the first planetary gear set P1 by means of the fourth switching element B2 on a non-rotatable component GG can be fixed. Furthermore, still the third element E33 of the third planetary gear set P3 by actuating the fifth switching element K3 rotatably with the second element E24 of the fourth planetary gear set P4 be brought into connection, which permanently rotatably with the output shaft GW2 connected is. Accordingly, upon actuation of the fifth switching element K3 through the non-rotatable connection of the third element E33 of the third planetary gear set P3 with the second element E24 of the fourth planetary gear set P4 also a non-rotatable connection of the third element E33 of the third planetary gear set P3 to the output shaft GW2 produced.

The first switching element B1 lies axially on one of the connection point Level 1-A facing side of the first planetary gear set P1 and is radially surrounding the first planetary gear set P1 intended. In contrast, the fourth switching element lies B2 in the wheel plane of the first planetary gear set P1 and is thus substantially at the same axial height, as well as radially surrounding the first planetary gear set P1 placed.

In 2 It can also be seen that the second switching element K1 , the third switching element K2 , the fifth switching element K3 and the sixth switching element K4 axially between the third planetary gear set P3 and the fourth planetary gear set P4 are arranged. Specifically, the sixth switching element is located K4 while axially adjacent to the third planetary gear P3 , whereupon axially the second switching element K1 , then the third switching element K2 and finally the fifth switching element K3 consequences. In this case, the sixth switching element K4 and the second switching element K1 axially juxtaposed directly and radially arranged substantially at the same height. Likewise, the third switching element K2 and the fifth switching element K3 axially immediately adjacent to each other and provided radially at substantially the same height. Due to this spatial arrangement could present a common supply of the sixth switching element K4 and the second switching element K1 on the one hand, as well as the third switching element K2 and the fifth switching element K3 On the other hand be realized on each a common supply line.

In addition, goes out 3 a schematic representation of a transmission G according to a second embodiment of the invention, which thereby substantially the previous Variant after 2 equivalent. Unlike the variant after 2 is the third element in this case E31 of the first planetary gear set P1 permanently on a non-rotatable component GG fixed and is accordingly prevented from constantly rotating. Furthermore, the first element E11 of the first planetary gear set P1 now not permanently rotatable with the first element E12 of the second planetary gear set P2 connected, but a non-rotatable connection is only by pressing a fourth switching element K5 produced. The fourth switching element K5 is designed as a clutch and is located axially between the first switching element B1 and the first planetary gear set P1 , as well as radially between the third element E31 and the second element E21 of the first planetary gear set P1 , 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 third element E31 of the first planetary gear set P1 constantly on a non-rotatable component GG is fixed and accordingly is permanently prevented from rotating. It is also different that the second element E21 of the first planetary gear set P1 no longer permanently rotatable with the second element E23 of the third planetary gear set P3 and the third element E34 of the fourth planetary gear set P4 is connected, but a non-rotatable connection only by closing a fourth switching element K5 will be produced. This fourth switching element K5 is axially between the first planetary gear P1 and the second planetary gear set P2 provided and lies radially surrounding the two Planetenradsätzen P1 and P2 , Otherwise, the design option corresponds to 4 according to the variant 2 so that reference is made to what has been described.

Finally shows 5 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 a 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 their 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 5 according to the variant 2 so that reference is made to what has been described.

In 6 is an exemplary circuit diagram for the transmission G from the 2 to 5 tabulated. As can be seen, in each case a total of ten forward gears 1 to 10.3 , as well as two reverse gears R1 and R2 be realized, which is marked in the columns of the circuit diagram with an X respectively, which of the switching elements B1 . K1 . K2 . B2 respectively. K5 . K3 and K4 in which of the forward gears 1 to 10.3 and the reverse gears R1 and R2 each is closed. In each of the forward gears 1 to 10.3 and the reverse gears R1 and R2 are each three of the switching elements B1 . K1 . K2 . B2 respectively. K5 . K3 and K4 closed, with a successive circuit of the forward gears 1 to 10.3 , with the exception of the forward gears 4.2 and 4.3 . 7.2 , such as 10.3 to open one of the involved switching elements and to close another switching element in the following.

As in 6 can be seen, is a first forward gear 1 by actuating the first switching element B1 , the second switching element K1 and the fourth switching element B2 respectively. K5 switched, starting from this, a second forward gear 2 is formed by the second switching element K1 opened and in the following the sixth switching element K4 is closed. Furthermore, a third forward gear 3 switched by starting from the second forward gear 2 the first switching element B1 opened and the second switching element K1 is closed. Based on this results in a first variant, a fourth forward gear 4.1 by opening the second switching element K1 and closing the fifth switching element K3 , Alternatively, but also a fourth forward gear 4.2 by closing the third switching element K2 , the fourth switching element B2 respectively. K5 and the fifth switching element K3 switched, as well as a fourth forward gear 4.3 by actuating the third switching element K2 , the fourth switching element B2 respectively. K5 and the sixth switching element K4 being represented.

This results in a fifth forward gear 5 by actuating the second switching element K1 , the fourth switching element B2 respectively. K5 and the fifth switching element K3 , starting from this in a sixth forward gear 6 is switched by the fifth switching element K3 opened and the third switching element K2 is closed. To shift to a seventh forward gear 7.1 is then the fourth switching element B2 respectively. K5 to open and the fifth switching element K3 close. Alternatively, but also a seventh forward gear 7.2 by actuating the second switching element K1 , the fifth switching element K3 and the sixth switching element K4 shown, and further alternatively a seventh forward gear 7.3 by closing the second switching element K1 , the third switching element K2 and the sixth switching element K4 being represented.

Furthermore, there is an eighth forward gear 8th by the first switching element B1 , the second switching element K1 and the third switching element K2 be operated.

To further upshift into a ninth forward gear 9 is the third switching element below K2 to open and the fifth switching element K3 close. Furthermore, the ninth forward gear 9 in a tenth forward gear 10.1 switched by the second switching element K1 in an unactuated state and then the third switching element K2 is transferred to an actuated state. Alternatively, but also a tenth forward gear 10.2 by closing the first switching element B1 , the fifth switching element K3 and the sixth switching element K4 switched, as well as alternatively a tenth forward gear 10.3 by actuating the first switching element B1 , the third switching element K2 and the sixth switching element K4 being represented.

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 B1 , the third switching element K2 and the fourth switching element B2 respectively. K5 connected. In contrast, there is the second reverse gear R2 by actuating the first switching element B1 , the fourth switching element B2 respectively. K5 and the fifth switching element K3 ,

As in the 2 to 5 is shown, is the fourth switching element B2 respectively. K5 designed as non-positive switching element. However, the fourth 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 and 4 analogous to the variant according to 5 be hybridized.

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

B1

First switching element

K1

Second switching element

K2

Third switching element

B2

Fourth switching element

K5

Fourth switching element

K3

Fifth switching element

K4

Sixth switching element

1

First forward

2

Second forward speed

3

Third forward

4.1

Fourth forward

4.2

Fourth forward

4.3

Fourth forward

5

Fifth forward speed

6

Sixth forward

7.1

Seventh forward

7.2

Seventh forward

7.3

Seventh forward

8th

Eighth forward

9

Ninth forward

10.1

Tenth forward

10.2

Tenth forward

10.3

Tenth forward

R1

First reverse

R2

Second reverse

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

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

• US 8545362 B1 [0003]

Claims (12)

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), the first element (E11, E12, E13, E14) of the respective planetary gear set (P1, P2, P3, P4) is formed by a sun gear, wherein the second element (E21, E22, E23, E24) of the respective planetary gear set (P1, P2, P3, P4) in the case of a minus Planet set by a bridge and in the case of a plus-planetary gear set is formed by a ring gear, wherein the third element (E31, E32, E33, E34) of the respective planetary gear set (P1, P2, P3, P4) in the case of a minus planetary gear set through the Ring gear and in the case of a plus planetary gear set is formed by the web, wherein a first (B1), a second (K1), a third (K2), a fourth (B2; K5), an f fifth (K3) and a sixth switching element (K4) are provided, wherein by selective actuation of three of the switching elements (B1, K1, K2, B2, K3, K4; B1, K1, K2, K5, K3, K4) different power flow guides on the planetary gear sets (P1, P2, P3, P4) with switching different gears (1 to 10.3, R1 and R2) between the drive shaft (GW1) and output shaft (GW2) represented are -, wherein the drive shaft (GW1) rotatably connected to the second element (E22) of the second planetary gear set (P2) whose first element (E12) via the first switching element (B1) on a non-rotatable component (GG) can be fixed and the third Element (E32) rotatably connected to the first element (E13) of the third planetary gear set (P3), - wherein the drive shaft (GW1) also by means of the second switching element (K1) rotationally fixed to the first element (E14) of the fourth planetary gear set (P4) can be brought into connection, which is further rotatably connected via the third switching element (K2) with the third element (E33) of the third planetary gear set (P3), - wherein the second element (E24) of the fourth planetary gear set (P4) rotatably connected to the Output shaft (GW2) is connected, and - wherein in the first planetary gear set (P1) a first coupling of the first element (E11) of the first planetary gear set (P1) with the first element (E12) of the second planetary gear set (P2), a second coupling of second element (E21) of the first planetary gear set (P1) with the third element (E34) of the fourth planetary gear set (P4), and a third coupling of the third element (E31) of the first planetary gear set (P1) with a non-rotatable component (GG), wherein from these couplings two couplings exist as permanent non-rotatable connections, while in the remaining coupling a rotationally fixed connection by means of the fourth switching element (B2; K5) can be produced, characterized in that the third element (E34) of the fourth planetary gear set (P4) rotatably connected to the second element (E23) of the third planetary gear set (P3), the third element (E33) via the fifth switching element (K3 ) rotatably connected to the second element (E24) of the fourth planetary gear set (P4) is brought into connection, and that the first element (E13) of the third planetary gear set (P3) and the third element (E32) of the second planetary gear set (P2) together rotationally fixed means of the sixth switching element (K4) with the first element (E14) of the fourth planetary gear set (P4) are connectable. Transmission (G) to Claim 1 , characterized in that the first element (E12) of the second planetary gear set (P2) is non-rotatably connected to the first element (E11) of the first planetary gear set (P1), the second element (E21) rotatably connected to the second element (E23) of the third Planetary gear set (P3) and the third element (E34) of the fourth planetary gear set (P4) is in communication, wherein the third element (E31) of the first planetary gear set (P1) by means of the fourth switching element (B2) on a rotationally fixed component (GG) can be fixed , Transmission (G) to Claim 1 , characterized in that the second element (E23) of the third planetary gear set (P3) and the third element (E34) of the fourth planetary gear set (P4) are non-rotatably in communication with the second element (E21) of the first planetary gear set (P1), the third Element (E31) is fixed to a non-rotatable component (GG), wherein the first element (E11) of the first planetary gear set (P1) by means of the fourth switching element (K5) rotatably connected to the first element (E12) of the second planetary gear set (P2) is connectable , Transmission (G) to Claim 1 characterized in that the first element (E12) of the second planetary gear set (P2) is non-rotatably connected to the first element (E11) of the first planetary gear set (P1) whose third element (E31) is fixed to a non-rotatable component (GG), wherein the second element (E21) of the first planetary gear set (P1) by means of the fourth switching element (K5) rotatably connected to the second element (E23) of the third planetary gear set (P3) and the third element (E34) of the fourth planetary gear set (P4) in combination is. Transmission (G) according to one of the preceding claims, characterized in that a first forward gear (1) by pressing the first (B1), the second (K1) and the fourth switching element (B2; K5), a second forward gear (2) by Actuate the first (B1), the fourth (B2; K5) and the a sixth forward gear (K4), a third forward gear (3) by operating the second (K1), the fourth (B2; K5) and the sixth shifting element (K4), a fourth forward gear (4.1) by actuating the fourth (B2; K5) , the fifth (K3) and the sixth switching element (K4) or (4.2) by actuating the third (K2), the fourth (B2; K5) and the fifth switching element (K3) or (4.3) by actuating the third (K2) , the fourth (B2; K5) and the sixth shifting element (K4), a fifth forward speed (5) by operating the second (K1), the fourth (B2; K5) and the fifth shifting element (K3), a sixth forward speed (6th) ) by operating the second (K1), the third (K2) and the fourth shift element (B2; K5), a seventh forward gear (7.1) by operating the second (K1), the third (K2) and the fifth shift element (K3) or (7.2) by operating the second (K1), the fifth (K3) and the sixth switching element (K4) or (7.3) by actuating the second (K1), the third (K2) and the sixth shifting element (K4), an eighth forward speed (8) by operating the first (B1), second (K1) and third shifting elements (K2), a ninth forward speed (9) by operating the first (B1), the second (K1) and the fifth switching element (K3), a tenth forward gear (10.1) by actuating the first (B1), the third (K2) and the fifth switching element (K3) or (10.2 ) by actuating the first (B1), the fifth (K3) and the sixth switching element (K4) or (10.3) by actuating the first (B1), the third (K2) and the sixth switching element (K4), a first reverse ( R1) by operating the first (B1), the third (K2) and the fourth switching element (B2; K5), and a second reverse gear (R2) by switching the first (B1), the fourth (B2, K5) and the fifth switching element (K3) is switchable. Transmission (G) according to one of the preceding claims, characterized in that the planetary gear sets (P1, P2, P3, P4) are designed as minus planetary gear sets. Transmission (G) according to one of the preceding claims, characterized in that one or more switching elements (B1, K1, K2, B2, K3, K4, B1, K1, K2, K5, K3, K4) are each realized as non-positive switching element. Transmission according to one of the preceding claims, characterized in that the fourth switching element is realized as a positive 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 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 11 ,

Images