DE102017206826A1 - 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, K2, B1 , B2, K3, K4), wherein by selectively operating the six switching elements (K1, K2, B1, B2, K3, K4) ten forward gears and two reverse gears 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 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 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 non-rotatably connected to the second element of the third planetary gear set, whose first element is non-rotatably in communication with the third element of the second planetary gear set and the first element of the fourth planetary gear set. Furthermore, the third element of the third planetary gear set can be non-rotatably connected to the first element of the second planetary gear set via the first switching element and to the output shaft by means of the second switching element, which is also non-rotatably connected to the second element of the fourth planetary gear set. Furthermore, the second element of the second planetary gear set can be fixed via the third switching element to a rotationally fixed component. The third element of the fourth planetary gear set can also be non-rotatably connected by means of the fourth switching element with a rotationally fixed component. The second planetary gear set can be locked via the fifth switching element, while in the first planetary gear set, a first coupling of the first element of the first planetary gear set with a rotationally fixed component, a second coupling of the second element of the first planetary gear set with the first element of the second planetary gear set, and a third coupling of the third element of the first planetary gear set with the drive shaft. Of these couplings are two couplings as permanent non-rotatable connections before, while the remaining coupling a rotationally fixed connection can be made by means of the sixth switching element.

In other words, in the transmission according to the invention, the third element of the second planetary gear set permanently rotatably connected to the first element of the third planetary gear set and the first element of the fourth planetary gear set, whereas the second element of the third planetary gear set is constantly rotatably connected to the drive shaft in communication. The output shaft, however, is permanently connected non-rotatably to the second element of the fourth planetary gear set.

Upon actuation of the first switching element, the third element of the third planetary gear set is rotatably connected to the first element of the second planetary gear in conjunction, while closing the second switching element pulls a rotationally fixed connection of the third element of the third planetary gear set with the output shaft. The third switching element sets the second element of the second planetary gear set when actuated on a rotationally fixed component. The third element of the fourth planetary gear set can also be stopped at a non-rotatable component in the closed state of the fourth switching element. On the other hand causes the fifth switching element in the closed state blocking the second planetary gear set.

The non-rotatable component of the transmission according to the invention is a permanently stationary component of the transmission, preferably a transmission housing, a component connected to the transmission housing or a part of such a transmission housing. The non-rotatable component does not necessarily have to be one and the same component. For rotationally fixed setting of a transmission component, the components can also be connected to different rotationally fixed components.

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 a rotationally fixed component is present, while in the case of the second element of the first planetary gear set, a second coupling to the first element of the second planetary gear set. A third coupling is then present in the form of the third element of the first planetary gear set with the drive shaft. 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 third and the fourth switching element are designed as brakes, which decelerate the respective rotatable component of the transmission to a standstill when driving and fix it on a non-rotatable component. In contrast, the first, the second and the fifth switching element are in the form of clutches, which in use in each case match the respective rotatable components of the transmission in their rotational movements and subsequently connect them to one another in a rotationally fixed manner.

Preferably, the first switching element is placed together with the second switching element and the fifth switching element axially between the second planetary gear set and the third planetary gear set, wherein the fifth switching element is further axially adjacent to the second planetary gear and then then axially first, the first switching element and then the second Follow switching element. In particular, the first switching element and the fifth switching element lie axially next to each other, so that a common supply via a common supply line would be conceivable here.

The third switching element is arranged axially in particular between the first planetary gear set and the second planetary gear set and provided radially surrounding these. In contrast, the fourth switching element is preferably placed in the gear plane of the fourth planetary gear set and thus lies axially substantially at the height of and radially surrounding the fourth planetary gear set.

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 case, the respective elements and the possibly existing wave formed by a common component, which is especially just realized 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 each other in a rotationally fixed manner only by actuation of a respective switching element, a connection is likewise preferably realized via one or more intermediate waves.

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 drive shaft is non-rotatably connected to the third element of the first planetary gear set, whose first element is fixed to the rotationally fixed component. The second element of the first planetary gear set can be rotatably connected via the sixth switching element with the first element of the second planetary gear set.

In this case, therefore, the first element of the first planetary gear set is permanently fixed to the rotationally fixed component and is thus permanently prevented from rotating. Furthermore, the third element of the first planetary gear set and the drive shaft are permanently non-rotatably connected to each other, whereas in the second element of the first planetary gear set a rotationally fixed connection to the first element of the second planetary gear set is made only with the closing of the sixth switching element. The designed as a coupling sixth switching element is preferably provided axially between the first planetary gear and the second planetary gear and is in this case more preferably adjacent to the third switching element. In this respect, a common supply of these two switching elements could possibly be realized here.

According to an alternative embodiment of this invention, the first element of the second planetary gear set is non-rotatably connected to the second element of the first planetary gear set, the third element is rotatably connected to the drive shaft in connection. Furthermore, the first element of the first planetary gear set can be fixed by means of the sixth switching element on the rotationally fixed component.

In this variant, therefore, the drive shaft and the third element of the first planetary gear set are permanently connected to each other in a rotationally fixed manner, while the second element of the first planetary gear set and the first element of the second planetary gear set are permanently connected to each other in a rotationally fixed manner. By contrast, the first element of the first planetary gear set is fixed only by pressing the sixth switching element on the rotationally fixed component and thus prevented from rotating. The sixth switching element designed as a brake is in this case provided in particular axially on a side of the first planetary gearset facing a connection point of the drive shaft and in this case lies preferably radially surrounding the first planetary gearset.

According to a further alternative embodiment of the invention, the first element of the second planetary gear set is rotatably connected to the second element of the first planetary gear set, whose first element is fixed to the rotationally fixed component. In contrast, the third element of the first planetary gear set can be rotatably connected to the drive shaft via the sixth switching element in connection.

In this case, therefore, the first element of the first planetary gear set is permanently fixed to the rotationally fixed component and is thus permanently prevented from rotating, while the second element of the first planetary gear set and the first element of the second planetary gear are constantly rotatably connected with each other. On the other hand, the third element of the first planetary gear set is not connected to the drive shaft until the sixth switching element is closed, wherein the sixth shifting element is present as a clutch and is preferably provided axially between the first planetary gear set and the second planetary gear set. More preferably, the sixth switching element is provided axially adjacent to the first planetary gear set and is radially in the region of the third element of the first planetary gear set.

In a further development of the invention, a blocking of the second planetary gear set is achieved by the fifth switching element, when actuated, connecting the first element and the third element of the second planetary gear set to one another in a rotationally fixed manner. Alternatively, the blocking may also be caused by non-rotatably connecting the first element and the second element of the second planetary gear set via the fifth switching element or, alternatively, by non-rotatably connecting the second element and the third element of the second planetary gear set via the fifth switching element. In all three cases, a blocking of the second planetary gear set is achieved.

In the 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 by pressing the fourth, the fifth and the sixth switching element while a second forward speed is formed by closing the first, fourth and fifth switching elements. Furthermore, a third forward gear results by actuating the first, the fourth and the sixth shift element, whereas a fourth forward gear in a first variant can be shifted by actuating the first, the second and the fourth shift element. Alternatively, a fourth forward gear but also in a second variant by closing the second, third and fourth switching element, in a third variant by operating the second, the fourth and the sixth switching element or in a fourth variant by closing the second, the be switched fourth and fifth switching element.

Further, a fifth forward speed can be represented by closing the first, the second and the sixth shift element, wherein the first, the second and the fifth shift element are to be operated for the circuit of a sixth forward gear. In addition, a seventh forward gear results by actuating the second, the fifth and the sixth shifting element, while an eighth forward gear can be shifted by actuating the second, the third and the fifth shifting element. In contrast, a ninth forward gear can be switched by operating the second, the third and the sixth switching element, whereas for the circuit of a tenth forward gear to close the first, the second and the third switching element.

In addition, a first reverse gear results by actuating the third, the fourth and the sixth shifting element, while a second reverse gear is engaged when the first, the third and the fourth shifting element are closed.

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 variant and the fourth variant of the fourth forward gear always to vary the state of two switching elements by opening one of the preceding forward gear involved switching elements and another switching element for Presentation of the subsequent forward gear is close. 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.

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 at least one, but preferably several planetary gears leads, in each case both with the sun gear, as well as the surrounding ring gear comb. 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 second and the fourth planetary gear set are present as minus planetary gear sets, whereby a particularly compact design can be realized.

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 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. In the transmission according to the invention, one or more planetary gear sets may be designed as such plus planetary gear sets. But particularly preferably, the third 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. As already mentioned, however, the first, the second and the fourth planetary gear set are preferably designed as minus planetary gear sets, whereas the third planetary gearset is present as a plus planetary gearset.

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 fourth 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, the element of the first planetary gear set is non-rotatably connected to a power take-off in the first planetary gear set in the connection rotatably on the sixth switching element. In this case, therefore, the element of the first planetary gear set, which is connected non-rotatably connected only by pressing the sixth switching element, permanently connected non-rotatably connected to a power take-off, via which a drive can take place of ancillaries. Alternatively, a power take-off but also before the gear set lying rotatably connected to the drive 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 the 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. 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 fourth switching element or the sixth switching element, since these are closed in both a reverse gear, as well as in the first forward gear are suitable. 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, a separating clutch is also 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. 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;
• 6 eine schematische Ansicht eines Getriebes entsprechend einer fünften Ausführungsform der Erfindung;
• 7 eine schematische Darstellung eines Getriebes gemäß einer sechsten Ausgestaltungsmöglichkeit der Erfindung;
• 8 eine schematische Ansicht eines Getriebes entsprechend einer siebten Ausführungsform der Erfindung; und
• 9 ein beispielhaftes Schaltschema der Getriebe aus den 2 bis 8.

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;
• 7 a schematic representation of a transmission according to a sixth embodiment of the invention;
• 8th a schematic view of a transmission according to a seventh embodiment of the invention; and
• 9 an exemplary circuit diagram of the transmission of the 2 to 8th ,

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. E24 at the planetary gear sets P1 . P2 and P4 each as a planetary bridge is present. The remaining third element E31 respectively. E32 respectively. E34 is then by a respective ring gear of the respective planetary gear set P1 respectively. P2 respectively. P4 educated. On the other hand, it is the second element E23 of the third planetary gear set P3 around the ring gear, while the third element E33 of the third planetary gear set P3 designed as a planetary bridge.

The planetary gear sets P1 . P2 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. On the other hand lies the third planetary gear set P3 as a plus planetary gear set, the planetary gear carries at least one pair of planetary, of the planetary gears of the at least one pair of planetary gears with the radially inner sun gear and a planetary gear with the radially surrounding ring gear meshing, and the planetary gears of the Planetenradpaares mesh with each other.

Where it allows the connection, but one or more of the planetary gear sets P1 . P2 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. E22 respectively. E24 through the respective ring gear and the respective third element E31 respectively. E32 respectively. E34 formed by the respective planet web and also a respective transmission gear ratio can be increased by one. Likewise could also the third planetary gear set P3 , if it allows the connection of the elements, be designed as a minus planetary gear set, in which case compared to the design as a plus-planetary gear set the second element E23 through the planetary bridge and the third element E33 to form by the ring gear as well as to reduce a gearbox ratio by one would be.

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 shape a first switching element K1 , a second switching element K2 , a third switching element B1 , a fourth switching element B2 , a fifth switching element K3 and a sixth switching element K4 , Here are the switching elements K1 . K2 . B1 . B2 . K3 and K4 each designed as non-positive switching elements and are preferably before as lamella switching elements. In addition, the third switching element B1 and the fourth switching element B2 in the present case designed as brakes, while the first switching element K1 , the second switching element K2 , the fifth switching element K3 and the sixth switching element K4 present as couplings.

The present is the first element E11 of the first planetary gear set P1 constantly on a non-rotatable component GG fixed, which is preferably a transmission housing of the transmission G or a part of such a transmission housing is. Furthermore, the third element stands E31 of the first planetary gear set P1 permanently non-rotatable with the drive shaft LV1 in conjunction, which also constantly rotatably with the second element E23 of the third planetary gear set P3 connected is.

As well as in 2 It can be seen, the second element E21 of the first planetary gear set P1 via the sixth switching element K4 non-rotatable with the first element E12 of the second planetary gear set P2 in addition, by operating the first switching element K1 non-rotatable with the third element E33 of the third planetary gear set P3 can be connected. Apart from that, the third element E33 of the third planetary gear set P3 still on the second switching element K2 rotatably with the output shaft GW2 are connected, the permanent rotation with the second element E24 of the fourth planetary gear set P4 communicates.

Furthermore, the second element E22 of the second planetary gear set P2 by actuating the third switching element B1 on the non-rotatable component GG be fixed while the third element E32 of the second planetary gear set P2 Constantly rotatable with the first element E13 of the third planetary gear set P3 and the first element E14 of the fourth planetary gear set P4 communicates. The third element E34 of the fourth planetary gear set P4 can by means of the fourth switching element B2 on the non-rotatable component GG fixed and thus prevented from rotating. Finally, when the fifth switching element is actuated K3 the first element E12 of the second planetary gear set P2 and the third element E32 of the second planetary gear set P2 rotatably connected to each other, which is a blocking of the second planetary gear set P2 entails.

As well as in 2 can be seen, are the first switching element K1 , the second switching element K2 and the fifth switching element K3 axially between the second planetary gear set P2 and the third planetary gear set P3 arranged, in which case the fifth switching element K3 axially immediately adjacent to the second planetary gear set P2 is and then then axially first, the first switching element K1 and then the second switching element K2 consequences. Radial is the fifth switching element K3 surrounding the second planetary gear set P2 provided, wherein the first switching element K1 while radially inwardly displaced thereto is placed, while the second switching element K2 also radially inside this and in the region of the third element E33 of the third planetary gear set P3 is arranged.

The third switching element B1 is in common with the sixth switching element K4 axially between the first planetary gear set P1 and the second planetary gear set P2 provided, wherein the third switching element B1 while axially between the sixth switching element K4 and the second planetary gear set P2 lies. Both the third switching element B1 , as well as the sixth switching element K4 are radially surrounding the first planetary gear set P1 and to the second planetary gear set P2 placed. Finally, the fourth switching element is still B2 in the wheel plane of the fourth planetary gear set P4 provided and is thus axially substantially at the height of the fourth planetary gear set P4 and radially surrounding this.

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 now additionally a power take-off PTO is provided, via which a drive of ancillaries is possible. The power take-off PTO is rotatably with the second element E21 of the first planetary gear set P1 connected. Axial is the power take-off PTO between the first planetary gear set P1 and the sixth switching element K4 , 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, now a blocking of the second planetary gear set P2 is achieved by the fifth switching element K3 when pressed, the first element E12 of the second planetary gear set P2 and the second element E22 of the second planetary gear set P2 rotatably connected. In this case, the fifth switching element K3 radially in the region of the second element E22 of the second planetary gear set P2 placed. 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 again largely the variant 2 equivalent. It is different, however, that the fifth switching element K3 now in the actuated state, the second element E22 of the second planetary gear set P2 and the third element E32 of the second planetary gear set P2 rotatably connected together and thereby the blocking of the second planetary gear set P2 causes. In this case, the fifth switching element K3 radially outboard of the second planetary gear set P2 intended. Otherwise, the embodiment corresponds to 5 according to the variant 2 so that reference is made to what has been described.

6 shows a schematic view of a transmission G according to a fifth embodiment of the invention, which also essentially according to the embodiment 2 equivalent. Unlike the variant after 2 But now is the second element E21 of the first planetary gear set P1 permanently rotatable with the first element E12 of the second planetary gear set P2 whereas the first element E11 of the first planetary gear set P1 no longer permanently on the non-rotatable component GG is set, but a setting only by closing a sixth switching element B3 is done. The sixth switching element B3 is designed as a brake and is located axially on one of the connection point Level 1-A the drive shaft GW 1 facing side of the first planetary gear set P1 , Radial is the sixth switching element B3 surrounding the first planetary gear set P1 intended. Otherwise, the design option corresponds to 6 according to the variant 2 so that reference is made to what has been described.

Further, go out 7 a schematic representation of a transmission G according to a sixth embodiment of the invention. This embodiment also largely corresponds to the variant 2 , in contrast to the second element E21 of the first planetary gear set P1 now permanently rotatable with the first element E12 of the second planetary gear set P2 connected is. Furthermore, there is the third element E31 of the first planetary gear set P1 now no longer permanently rotatable with the drive shaft LV1 in conjunction, but a non-rotatable connection is only by closing a sixth switching element K4 produced. The sixth switching element K4 is designed as a clutch and is located axially between the first planetary gear P1 and the second planetary gear set P2 , wherein the sixth switching element K4 while axially immediately adjacent to the first planetary gear P1 provided and radially in the region of the third element E31 of the first planetary gear set P1 is placed. Otherwise, the embodiment corresponds to 7 according to the variant 2 so that reference is made to what has been described.

Finally shows 8th a schematic representation of a transmission G according to a seventh embodiment of the invention. This embodiment also essentially corresponds 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 8th according to the variant 2 so that reference is made to what has been described.

In 9 is an exemplary circuit diagram for the transmission G from the 2 to 8th tabulated. As can be seen, in each case a total of ten forward gears 1 to 10 , 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 K1 . K2 . B1 . B2 . K3 and K4 respectively. B3 in which of the forward gears 1 to 10 and the reverse gears R1 and R2 each is closed. In each of the forward gears 1 to 10 and the reverse gears R1 and R2 are each three of the switching elements K1 . K2 . B1 . B2 . K3 and K4 respectively. B3 closed, with a successive circuit of the forward gears 1 to 10 , except for a fourth forward gear 4.2 and one fourth forward gear 4.4 to open one of the involved switching elements and to close another switching element in the following.

As in 9 can be seen, is a first forward gear 1 by actuating the fourth switching element B2 , the fifth switching element K3 and the sixth switching element K4 respectively. B3 switched, starting from this, a second forward gear 2 is formed by the sixth switching element K4 respectively. B3 opened and in the following the first switching element K1 is closed. Furthermore, starting from the second forward gear 2 a third forward speed 3 switched by the fifth switching element K3 opened and the sixth switching element K4 respectively. B3 is closed. Based on this results then a fourth forward gear 4.1 by opening the sixth switching element K4 respectively. B3 and closing the second switching element K2 , Alternatively, but also a fourth forward gear 4.2 be represented by the second switching element K2 , the third switching element B1 and the fourth switching element B2 be operated. There is also a fourth forward gear 4.3 by closing the second switching element K2 , the fourth switching element B2 and the sixth switching element K4 respectively. B3 switchable, as well as a fourth forward gear 4.4 by actuating the second switching element K2 , the fourth switching element B2 and the fifth switching element K3 represented. Preference is given to the fourth forward gear 4.1 or 4.3 , to switch, since in both cases, only the switching state of two switching elements is to change for switching.

This results in a fifth forward gear 5 by actuating the first switching element K1 , the second switching element K2 and the sixth switching element K4 respectively. B3 , starting from this in a sixth forward gear 6 is switched by the sixth switching element K4 respectively. B3 opened and the fifth switching element K3 is closed. To shift to a seventh forward gear 7 is then the first switching element in the following K1 to open and the sixth switching element K4 respectively. B3 close. Furthermore, starting from the seventh forward gear 7 an eighth forward gear 8th by the sixth switching element K4 respectively. B3 opened again and the third switching element B1 is pressed. To further upshift into a ninth forward gear 9 is the fifth switching element below K3 to open and the sixth switching element K4 respectively. B3 close. Furthermore, the ninth forward gear 9 in a tenth forward gear 10 switched by the sixth switching element K4 respectively. B3 in an unactuated state and then the first switching element K1 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 third switching element B1 , the fourth switching element B2 and the sixth switching element K4 respectively. B3 connected. In contrast, there is the second reverse gear R2 by actuating the first switching element K1 , the third switching element B1 and the fourth switching element B2 ,

As in the 2 to 8th is shown, is the fourth switching element B2 designed as non-positive switching element. However, the fourth switching element could B2 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 7 analogous to the variant according to 8th be hybridized. In addition, also a power take-off PTO in the embodiments of the 4 to 8th be realized accordingly.

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

K2

Second switching element

B1

Third switching element

B2

Fourth switching element

K3

Fifth switching element

K4

Sixth switching element

B3

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

4.4

Fourth forward

5

Fifth forward speed

6

Sixth forward

7

Seventh forward

8th

Eighth forward

9

Ninth forward

10

Tenth forward

R1

First reverse

R2

Second reverse

LV1

drive shaft

Level 1-A

junction

GW2

output shaft

GW2-A

junction

PTO

PTO

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

• 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 (K2 ), a third (B1), a fourth (B2), a fifth (K3) and a sixth switching element (K4; B3) 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 and R2) between the drive shaft (GW1) and output shaft (GW2) are represented, characterized in that the drive shaft (GW1) rotatably connected to the second element (E23) of the third planetary gear set (P3) is, whose first element (E13) rotationally fixed to the third element (E32) of the second planetary gear set (P2) and the first element (E14) of the fourth planetary gear set (P4) is connected, - that the third element (E33) of the third planetary gear set (P3) on the one hand via the first switching element (K1) rotationally fixed to the first element (E12) of the second planetary gear set (P2) and on the other by means of the second switching element (K2) rotatably connected to the output shaft (GW2) is also rotatably connected to the second element (E24) of the fourth planetary gear set (P4), - that the second element (E22 ) of the second planetary gear set (P2) via the third switching element (B1) on a non-rotatable component (GG) can be fixed, and the third element (E34) of the fourth planetary gear set (P4) by means of the fourth switching element (B2) also rotatably with a non-rotatable component (GG) is connectable, - that the second planetary gear set (P2) via the fifth switching element (K3) is blockable, - and that in the first planetary gear set (P1) a first coupling of the first element ( E11) of the first planetary gear set (P1) with a rotationally fixed component (GG), a second coupling of the second element (E21) of the first planetary gear set (P1) with the first element (E12) of the second planetary gear set (P2), and a third coupling of third element (E31) of the first planetary gear set (P1) with the drive shaft (GW1), of these couplings two couplings as permanent non-rotatable connections, while the remaining coupling a rotationally fixed connection by means of the sixth switching element (K4; B3) can be produced. Transmission (G) to Claim 1 , characterized in that the drive shaft (GW1) is non-rotatably connected to the third element (E31) of the first planetary gear set (P1) whose first element (E11) is fixed to a non-rotatable component (GG), the second element (E21) of the first planetary gear set (P1) via the sixth switching element (K4) 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 second element (E21) of the first planetary gear set (P1) whose third element (E31) is non-rotatably in communication with the drive shaft (GW1) , wherein the first element (E11) of the first planetary gear set (P1) by means of the sixth switching element (B3) on a non-rotatable component (GG) can be fixed. 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 second element (E21) of the first planetary gear set (P1) whose first element (E11) is fixed to a non-rotatable component (GG), wherein the third element (E31) of the first planetary gear set (P1) via the sixth switching element (K4) rotatably connected to the drive shaft (GW1) is brought into connection. Transmission (G) according to one of the preceding claims, characterized in that the fifth switching element (K3) when actuated the first element (E12) and the third element (E32) of the second planetary gear set (P2) or the first element (E12) and the second element (E22) of the second planetary gear set (P2) or the second element (E22) and the third element (E32) of the second planetary gear set (P2) rotatably connected to each other. Transmission (G) according to one of the preceding claims, characterized in that a first forward gear (1) by actuating the fourth (B2), the fifth (K3) and the sixth switching element (K4, B3), a second forward gear (2) by Actuating the first (K1), fourth (B2) and fifth switching elements (K3), a third forward speed (3) by operating the first (K1), fourth (B2) and sixth switching elements (K4; B3) fourth forward gear (4.1) by operating the first (K1), the second (K2) and the fourth switching element (B2) or (4.2) by operating the second (K2), the third (B1) and the fourth switching element (B2) or (4.3) by actuating the second (K2), the fourth (B2) and the sixth switching element (K4; B3) or (4.4) by actuating the second (K2), the fourth (B2) and the fifth switching element (K3), a fifth forward speed (5) by operating the first (K1), the second (K2) and the sixth switching element (K4; B3), e in sixth forward gear (6) by operating the first (K1), the second (K2) and the fifth switching element (K3), a seventh forward gear (7) by operating the second (K2), the fifth (K3) and the sixth shifting element (K4; B3), an eighth forward speed (8) by operating the second (K2), third (B1) and fifth shifting element (K3), a ninth forward speed (9) by operating the second (K2), third (B1) and sixth shifting elements (K4; B3), a tenth forward speed (10) by operating the first (K1), second (K2) and third (B1) switching elements, a first reverse (R1) by operating the third (B1), fourth (B2) and sixth (K4; B3) switching elements, and a second one Reverse gear (R2) by operating the first (K1), the third (B1) and the fourth switching element (B2) is switchable. Transmission (G) according to one of the preceding claims, characterized in that the respective planetary gear set (P1, P2, P4) is present as a minus planetary gear set, wherein it is at the respective first element (E11, E12, E14) of the respective planetary gear set (P1 , P2, P4) about a respective sun gear, at the respective second element (E21, E22, E24) of the respective planetary gear set (P1, P2, P4) about a respective planet web and at the respective third element (E31, E32, E34) of respective planetary gear set (P1, P2, P4) is a respective ring gear. Transmission (G) according to one of the preceding claims, characterized in that the respective planetary gear set (P3) is present as a plus-planetary gear set, wherein it is in the respective first element (E13) of the respective planetary gear set (P3) to a respective sun gear, wherein respective second element (E23) of the respective planetary gear set (P3) is a respective ring gear and the respective third element (E33) of the respective planetary gear set (P3) is a respective planet gear. Transmission (G) according to one of the preceding claims, characterized in that one or more switching elements (K1, K2, B1, B2, K3, K4, K1, K2, B1, B2, K3, B3) 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 in the first planetary gear set (P1) in the over the sixth switching element (K4) rotatably to be produced compound, the element of the first planetary gear set (P1) is rotatably connected 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 ,

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