DE102017206800A1 - 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 , K3, B2, K4), wherein by selectively operating the six switching elements (B1, K1, K2, K3, B2, 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 US 8,545,362 B3 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 power flow 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 invention now includes the technical teaching that the second element of the first planetary gearset and the third element of the third planetary gear rotatably connected to each other and fixed on the one to the first switching element to a non-rotatable component, and on the other by means of the second switching element rotatably connected to the drive shaft can be, which is non-rotatably in communication with the third element of the second planetary gear set. In addition, the first element of the first planetary gearset is fixed to a rotationally fixed component, whereas the third element of the first planetary gear on the one hand via the third switching element rotationally fixed to the second element of the third planetary gear set and on the other by means of the fourth switching element rotationally fixed to the second element of the second planetary gear set can be associated.

Further, the second element of the third planetary gear set can be fixed via the fifth switching element to a rotationally fixed component, whereas the first element of the third planetary gear set is rotatably connected to the first element of the second planetary gear set. The latter can also be blocked by means of the sixth switching element. Finally, the second element of the fourth planetary gear set is rotatably connected to the output shaft, whereas of the first element of the fourth planetary gear set and the third element of the fourth planetary gear set rotatably with the second element of the second Planetenradsatzes and one rotatably connected to the second element of the third planetary gear in conjunction.

In other words, in the transmission according to the invention, therefore, the first element of the first planetary gear set is permanently fixed to a non-rotatable component and is thus constantly prevented from rotating. Further, the second element of the first planetary gear set is permanently non-rotatably connected to the third element of the third planetary gear set in connection, the first element is permanently rotatably connected to the first element of the second planetary gear set. The drive shaft is permanently connected in a rotationally fixed manner to the third element of the second planetary gear set, whereas the output shaft is permanently non-rotatably connected to the second element of the fourth planetary gear set.

In the fourth planetary gear set, either the first element of the fourth planetary gear set or the third element of the fourth planetary gear set permanently rotatably connected to the second element of the second planetary gear set, while the third element of the fourth planetary or the first element of the fourth planetary gear constantly rotatably with the second element of third planetary gear set communicates.

Upon actuation of the first switching element, the second element of the first planetary gearset and the third element of the third planetary gear set are fixed together on a non-rotatable component, while the second switching element in the closed state, the second element of the first planetary gear set and the third element of the third planetary gear set rotatably together with the Drive shaft connects. Upon actuation of the third switching element, the third element of the first planetary gearset is non-rotatably connected to the second element of the third planetary gear set, wherein the third element of the first planetary gear set can also be rotatably connected via the fourth switching element with the second element of the second planetary gear in combination. The second element of the third planetary gear set can also be set by closing the fifth switching element a non-rotatable component and thus prevented from rotating. Finally, even the sixth switching element in the closed state ensures a blocking of the second planetary gear set.

The non-rotatable components of the transmission according to the invention are permanently stationary components of the transmission, preferably a transmission housing or a part of such a transmission housing. By no means does it have to be a one and the same component in the non-rotatable component. The switching elements may also connect the elements of the planetary gear sets to various individual non-rotatable components, such as components attached to the transmission housing. The first element of the first planetary gear set is permanently fixed to a rotationally fixed component and is thus constantly prevented from rotating. In contrast, the second element of the first planetary gear and the third element of the third planetary gear set are stopped only by pressing the first switching element, and the second element of the third planetary gear set and either the third element or the first element of the fourth planetary gear set by closing the fifth switching element.

In the transmission according to the invention, the first and the fifth switching element are designed as brakes, which decelerate when driving the rotatably connected to each other, rotatable components of the transmission to a standstill and set to a non-rotatable component. By contrast, the second, the third, the fourth and the sixth switching element are in the form of clutches which, when actuated, each match the respective rotatable components of the transmission in their rotational movements and subsequently connect them to one another in a rotationally fixed manner.

Preferably, the first switching element is placed substantially axially at the height of the first planetary gear set and radially surrounding this, while the second switching element and the sixth switching element are provided axially in particular on a side facing the junction of the drive shaft side of the second planetary gear set. Furthermore, the third shift element and the fourth shift element are preferably arranged axially between the second planetary gear set and the third planetary gear set and are preferably located axially next to one another, whereby the fourth shift element is provided between the second planetary gear set and the third shift element. Radially, the third switching element and the fourth switching element are in particular substantially at the same height. By contrast, the fifth shifting element is preferably placed axially on one side of the fourth planetary gearset facing the connection point of the drive shaft and radially surrounding it.

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 either rotationally fixed 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 fourth planetary gear set is rotatably connected to the second element of the second planetary gear set, whereas the third element of the fourth planetary gear set is non-rotatably in communication with the second element of the third planetary gear set. Alternatively, the first member of the fourth planetary gear set is rotatably connected to the second element of the third planetary gear in conjunction, whereas the third element of the fourth planetary gear set is rotatably connected to the second element of the second planetary gear set.

In a further development of the invention, a blocking of the second planetary gear set is achieved by the sixth switching element, when actuated, connecting the second element and the third element of the second planetary gear set or, alternatively, the first element and the second element of the second planetary gear set to one another in a rotationally fixed manner. In both cases, the blocking of the second planetary gear set is realized.

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

Further, a seventh forward speed is obtained by operating the second and sixth shift elements, while an eighth forward speed is switchable by operating the second and fourth shift elements. In contrast, a ninth forward gear can be switched by operating the second and the third switching element, whereas for the circuit of a tenth forward gear, the third and the fourth switching element are to be closed.

Further, a first reverse gear results by operating the first and the fourth shift element, while a second reverse gear is switched upon closing of the second 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, except for the third variant of the second 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 displaying the subsequent forward gear to 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 made in a manner known to those skilled in the art the elements sun gear, planetary gear and ring gear together, the planetary web at least one but preferably more planetary gears leads, which mesh in detail each with both the sun gear, as well as the surrounding ring gear. Of the four planetary gear sets then one or more planetary gear sets are designed as such minus planetary gear sets.

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.

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. In a first variant of the invention, all planetary gear sets are available as minus planetary gear sets, whereby a compact construction can be realized. Alternatively, however, in a second variant of the fourth planetary gear set is designed as a plus-planetary gear set, while the first, the second and the third planetary gear are each present as a minus planetary gear set.

According to one embodiment of the invention, the planetary gear sets are arranged axially in the order first, second, third and fourth planetary gear set. Alternatively, however, a structure may be selected in which the planetary gear sets are arranged axially in the order second, third, first and fourth planetary gear set.

In a further development of the invention, one or more switching elements are each realized as non-positive switching elements. Non-positive switching elements have the advantage that they can be switched under load, so that a change between the courses without interruption of traction is enforceable. But particularly preferably, the fifth switching element is designed as a form-locking switching element, such as a jaw clutch or lock synchronization. For the fifth switching element is involved in the circuit of the first forward gear and one of the two reverse gears, so that a closing of the fifth switching element is to take place at a standstill of the motor vehicle. 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 electric motor and / or 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, in the latter case then a coupling via one or more intermediate gear ratios, for example in shape of spur gears, or a traction mechanism, such as a chain drive, can be realized.

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 fifth switching element is suitable, since this is closed both in a reverse gear, as well as in the first forward gear. 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-fitting Switching element over here directly rotatably connected to each other 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;
• 9 eine schematische Darstellung eines Getriebes gemäß einer achten Ausgestaltungsmöglichkeit der Erfindung;
• 10 eine schematische Ansicht eines Getriebes entsprechend einer neunten Ausführungsform der Erfindung;
• 11 eine schematische Darstellung eines Getriebes gemäß einer zehnten Ausgestaltungsmöglichkeit der Erfindung;
• 12 eine schematische Ansicht eines Getriebes entsprechend einer elften Ausführungsform der Erfindung;
• 13 eine schematische Darstellung eines Getriebes gemäß einer zwölften Ausgestaltungsmöglichkeit der Erfindung;
• 14 eine schematische Ansicht eines Getriebes entsprechend einer dreizehnten Ausführungsform der Erfindung; und
• 15 ein beispielhaftes Schaltschema der Getriebe aus den 2 bis 14.

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;
• 9 a schematic representation of a transmission according to an eighth embodiment of the invention;
• 10 a schematic view of a transmission according to a ninth embodiment of the invention;
• 11 a schematic representation of a transmission according to a tenth embodiment of the invention;
• 12 a schematic view of a transmission according to an eleventh embodiment of the invention;
• 13 a schematic representation of a transmission according to a twelfth embodiment of the invention;
• 14 a schematic view of a transmission according to a thirteenth embodiment of the invention; and
• 15 an exemplary circuit diagram of the transmission of the 2 to 14 ,

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 remaining third element E31 respectively. E32 respectively. E33 respectively. 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 a connection point Level 1-A a drive shaft LV1 and a connection point GW2-A an output shaft GW2 arranged.

The connection points Level 1-A and 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 K3 , a fifth switching element B2 and a sixth switching element K4 , Here are the switching elements B1 . K1 . K2 . K3 . B2 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 fourth switching element K3 and the sixth switching element K4 designed here as couplings, while the first switching element B1 and the fifth switching element B2 as brakes.

The present is the first element E11 of the first planetary gear set P1 permanently on a non-rotatable component GG stated, which is the transmission case of the transmission G or may act as part of the transmission housing. The second element E21 of the first planetary gear set P1 is constantly rotatable with the third element E33 of the third planetary gear set P3 connected and can together with this on the one hand over the first switching element B1 on the non-rotatable component GG set, and on the other by closing the second switching element K1 rotatably with the drive shaft LV1 get connected. Furthermore, the third element E31 of the first planetary gear set P1 over the third switching element K2 rotatably with the second element E23 of the third planetary gear set P3 and the third element E34 of the fourth planetary gear set P4 be associated in addition, which also together on the fifth switching element B2 can be fixed to the non-rotatable component.

The third element E31 of the first planetary gear set P1 can also use the fourth switching element K3 rotatably with the second element E22 of the second planetary gear set P2 and the first element E14 of the fourth planetary gear set P4 be connected, which are permanently rotatably connected with each other. Further, also the first element E12 of the second planetary gear set P2 and the first element E13 of the third planetary gear set P3 permanently rotatably connected.

As well as in 2 can be seen, stands the drive shaft LV1 non-rotatable with the third element E32 of the second planetary gear set P2 in connection, whereas the output shaft GW2 Constantly rotatable with the second element E24 of the fourth planetary gear set P4 connected is. Finally, by closing the sixth switching element K4 a blocking of the second planetary gear set P2 be achieved by the sixth switching element K4 when closed, the third element E32 and the second element E22 of the second planetary gear set P2 rotatably connected.

The first switching element B1 is axially substantially at the height of the first planetary gear set P1 and is provided radially surrounding this. The second switching element K1 and the sixth switching element K4 are axially between the first planetary gear set P1 and the second planetary gear set P2 arranged, wherein the second switching element K1 while axially adjacent to the first planetary gear P1 and the sixth switching element K4 axially adjacent to the second planetary gear set P2 lies. Radial are the second switching element K1 and the sixth switching element K4 essentially at the same level and in the area of the third elements E31 and E32 of the first planetary gear set P1 and the second planetary gear set P2 intended.

Furthermore, in 2 to realize that the third switching element K2 and the fourth switching element K3 axially between the second planetary gear set P2 and the third planetary gear set P3 are arranged and axially adjacent to each other. Radial are the third switching element K2 and the fourth switching element K3 essentially at the same level and in the area of the third elements E32 and E33 of the second planetary gear set P2 and the third planetary gear set P3 intended. Finally, the fifth switching element B2 axially between the third planetary gear set P3 and the fourth planetary gear set P4 placed and arranged radially surrounding these.

In addition, goes out 3 a schematic representation of a transmission G according to a second embodiment of the invention, which in this case essentially according to the previous variant 2 equivalent. The only difference is that a blocking of the second planetary gear set P2 now by the rotationally fixed connection of the second element E22 and the first element E12 of the second planetary gear set P2 by means of the sixth switching element K4 is brought about. The sixth switching element K4 is compared to the variant after 2 now arranged radially further inboard and lies in the region of the second element E22 of the second planetary gear set P2 , Otherwise, the embodiment corresponds to 3 the previous variant 2 so that reference is made to what has been described.

4 shows a schematic view of a transmission G according to a third embodiment of the invention. Again, this design option corresponds again largely to the variant 2 , in contrast to the planetary gear set P1 . P2 . P3 and P4 are arranged in the axial direction otherwise. So now lies the second planetary gear set P2 axially adjacent to the junction Level 1-A the drive shaft LV1 , being on the second planetary gear set P2 then first the third planetary gear set P3 , then the first planetary gear set P1 and finally the fourth planetary gear set P4 consequences. The latter is then still axially adjacent to the junction GW2-A the output shaft GW2 ,

Due to the different arrangement of the planetary gear set P1 to P4 are also the switching elements partially placed differently. So are the second switching element K1 and the sixth switching element K4 axially on one of the connection points Level 1-A facing side of the second planetary gear set P2 provided, wherein the sixth switching element K4 while axially between the second switching element K1 and the second planetary gear set P2 is located and radially inwardly of the second switching element K1 is arranged. The first switching element B1 is axially substantially at the height of the first planetary gear set P1 and radially surrounding it, while the fifth switching element B2 axially between the first planetary gear set P1 and the fourth planetary gear set P4 and is placed radially adjacent to these. In contrast, the third switching element lie K2 and the fourth switching element K3 still axially between the second planetary gear set P2 and the third planetary gear set P3 , Also otherwise corresponds to the possibility of design 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, as far as possible the previous embodiment possibility 4 equivalent. It is different, however, that the sixth switching element K4 , as with the variant 3 , now a blocking of the second planetary gear set P2 causes by the sixth switching element K4 when closed, the second element E22 and the first element E12 of the second planetary gear set P2 rotatably connected. In this case, the sixth switching element K4 axially still between the second switching element K1 and the second planetary gear set P2 but now it is radially in the region of the second element E22 of the second planetary gear set P2 lies. Otherwise, the embodiment corresponds to 5 according to the variant 4 so that reference is made to what has been described.

6 shows a schematic representation of a transmission G according to a fifth embodiment of the invention. This embodiment largely corresponds to the variant 2 , in contrast to the first element E14 of the fourth planetary gear set P4 now permanently rotatable with the second element E23 of the third planetary gear set P3 is connected and together with this on the one hand by means of the third switching element K2 non-rotatable with the third element E31 of the first planetary gear set P1 connected, as well as the other via the fifth switching element B2 on the non-rotatable component GG can be fixed. On the other hand, the third element stands E34 of the fourth planetary gear set P4 now permanently rotatable with the second element E22 of the second planetary gear set P2 in connection, wherein via the fourth switching element K3 a common rotationally fixed connection of the third element of the fourth planetary gear set P4 and the second element E22 of the second planetary gear P2 with the third element E31 of the first planetary gear set P1 can be produced. Otherwise, the embodiment corresponds to 6 according to the variant 2 so that reference is made to what has been described.

In addition, goes out 7 a schematic view of a transmission according to a sixth embodiment of the invention, which largely the immediately preceding variant 6 equivalent. The only difference is that in this case a blocking of the second planetary gear set P2 via the sixth switching element K4 is caused by the sixth switching element K4 when closed, the second element E22 and the first element E12 of the second planetary gear set P2 rotatably connected. Due to the changed function, the sixth switching element is located K4 compared to the variant after 6 now radially further inside in the area of the second element E22 of the second planetary gear set P2 , Otherwise, the design option corresponds to 7 the previous variant 6 so that reference is made to what has been described.

In 8th is a schematic representation of a transmission G illustrated according to a seventh embodiment of the invention, which is essentially the variant according to 2 equivalent. Unlike the variant after 2 in this case, however, becomes the second element E24 of the fourth planetary gear set P4 through the ring gear and the third element E34 of the fourth planetary gear set P4 formed by the planetary bridge. The fourth planetary gear set P4 In this case, it is designed as a positive tarpaulin set. Otherwise, the embodiment corresponds to 8th according to the variant 2 so that reference is made to what has been described.

In addition shows 9 a schematic view of a transmission G according to an eighth embodiment of the invention, this embodiment as far as possible of the previous variant 8th equivalent. It is different, however, that in this case, as in the variant after 3 , a blocking of the second planetary gear set P2 is caused by the sixth switching element K4 in the actuated state, the first element E12 and the second element E22 of the second planetary gear set P2 rotatably connected. Otherwise, the embodiment corresponds to 9 according to the variant 8th so that reference is made to what has been described.

In 10 is a schematic representation of a transmission G to see according to a ninth embodiment of the invention. This embodiment corresponds essentially to the variant 4 , as well as the planetary gear sets P1 to P4 in the axial direction in the order second planetary gear set P2 , third planetary gear set P3 , first planetary gear set P1 and fourth planetary gear set P4 are arranged. Only difference compared to the variant after 4 is that the second element E24 of the fourth planetary gear set P4 through the ring gear and the third element E34 of the fourth planetary gear set P4 formed by the planetary bridge, so that the fourth planetary gear set P4 accordingly exists as a plus-planetary gear set. Otherwise, the design option corresponds to 10 according to the variant 4 so that reference is made to what has been described.

In addition, goes out 11 a schematic view of a transmission G according to a tenth embodiment of the invention, which largely as the variant described immediately above 10 equivalent. It is different that on the sixth switching element K4 a blocking of the second planetary gear set P2 can be caused by the sixth switching element K4 when closed, the first element E12 and the second element E22 of the second planetary gear set P2 rotatably connected. Due to the changed function is the sixth switching element K4 now radially further inside in the area of the second element E22 of the second planetary gear set P2 , Incidentally, the possibility of design according to 11 otherwise the variant 10 so that reference is made to what has been described.

12 shows a schematic representation of a transmission G according to an eleventh embodiment of the invention. This corresponds largely to the variant 6 , in contrast to the second element E24 of the fourth planetary gear set P4 now through the ring gear and the third element E34 of the fourth planetary gear set P4 now formed by the planetary ridge. Also in the present case is therefore the fourth planetary gear P4 designed as a plus planetary set. Otherwise, the design option corresponds to 12 according to the variant 6 so that reference is made to what has been described.

Furthermore goes out 13 a schematic view of a transmission G according to a twelfth embodiment of the invention, the case of essentially the variant described immediately above 12 equivalent. The only difference is again here that the sixth switching element K4 in this case, a blocking of the second planetary gear set P2 causes by in the closed state of the sixth switching element K4 the second element E22 and the first element E12 of the second planetary gear set P2 rotatably connected to each other. Compared to the variant 12 is the sixth switching element K4 placed radially further inside and is located in the region of the second element E22 of the second planetary gear set P2 , Otherwise, the embodiment corresponds to 13 according to the variant 12 so that reference is made to what has been described.

Finally shows 14 a schematic representation of a transmission G according to a thirteenth embodiment of the invention. This embodiment corresponds essentially to the variant 2 , in contrast, in addition to an electric machine EM is provided, whose stator S on the non-rotatable component GG is fixed while a rotor R the electric machine EM rotatably with the drive shaft LV1 connected is. Furthermore, the drive shaft LV1 at 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 14 according to the variant 2 so that reference is made to what has been described.

In 15 is an exemplary circuit diagram for the transmission G from the 2 to 14 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 B1 . K1 . K2 . K3 . B2 and K4 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 two of the switching elements B1 . K1 . K2 . K3 . B2 and K4 closed, with a successive circuit of the forward gears 1 to 10 , except for a second forward gear 2.3 to open one of the involved switching elements and to close another switching element in the following.

As in 15 can be seen, is a first forward gear 1 by actuating the fourth switching element K3 and the fifth switching element B2 switched, starting from this, a second forward gear 2.1 is formed by the fourth switching element K3 opened and in the following the third switching element K2 is closed. Alternatively, but also a second forward gear 2.2 by actuating the first switching element B1 and the fifth switching element B2 or alternatively, a second forward gear 2.3 by closing the first switching element B1 and the third switching element K2 be formed.

Furthermore, a third forward gear 3 switched by the fifth switching element B2 and the sixth switching element K4 getting closed. Based on this results then a fourth forward gear 4 by opening the fifth switching element B2 and closing the first switching element B1 , This results in a fifth forward gear 5 by opening the first switching element B1 and actuating the third switching element K2 , starting from this in a sixth forward gear 6 is switched by the third switching element K2 opened and the fourth switching element K3 is closed. To shift to a seventh forward gear 7 is then the fourth switching element K3 to open again and the second switching element K1 close.

Furthermore, starting from the seventh forward gear 7 an eighth forward gear 8th by the sixth switching element K4 opened and the fourth switching element K3 is pressed. To further upshift into a ninth forward gear 9 is the fourth switching element below K3 open again and the third switching element K2 close. Furthermore, the ninth forward gear 9 in a tenth forward gear 10 switched by the second switching element K1 in an unactuated state and then the fourth switching element K3 is transferred to an actuated state.

The first reverse R1 , in which a reverse drive of the motor vehicle even when driven by the internal combustion engine VKM can be realized, however, by closing the first switching element B1 and the fourth switching element K3 connected. In contrast, there is the second reverse gear R2 by actuating the second switching element K1 and the fifth switching element B2 ,

As in the 2 to 14 is shown, is the fifth switching element B2 designed as non-positive switching element. However, the 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 13 analogous to the variant according to 14 be hybridized. In addition, the different connection of the elements can also E24 and E34 of the fourth planetary gear set P4 with the changed arrangement of the planetary gear sets P1 to P4 be combined in the axial direction.

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

K3

Fourth switching element

B2

Fifth switching element

K4

Sixth switching element

1

First forward

2.1

Second forward speed

2.2

Second forward speed

2.3

Second forward speed

3

Third forward

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

EM

electric machine

S

stator

R

rotor

AT

connecting shaft

K0

separating clutch

PTO

PTO

VKM

Internal combustion engine

TS

torsional vibration damper

AG

transaxles

DW

drive wheels

QUOTES INCLUDE IN THE DESCRIPTION

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

Cited patent literature

• US 8545362 B3 [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 (B1), a second (K1 ), a third (K2), a fourth (K3), a fifth (B2) and a sixth switching element (K4) are provided by their selective actuation different power flow guides on the planetary gear sets (P1, P2, P3, P4) under different circuit Gears (1 to 10, R1 and R2) between the drive shaft (GW1) and output shaft (GW2) are represented, characterized in that - the second element (E21) of the first planetary gear set (P1) and the third element (E33) of the third planetary gear set (P3) rotatably connected to each other and on the one hand via the first switching element (B1) on a rotationally fixed Component (GG) can be fixed, and on the other by means of the second switching element (K1) rotatably connected to the drive shaft (GW1) are connected, which in rotation with the third element (E32) of the second planetary gear set (P2) is in communication - that the first element (E11) of the first planetary gear set (P1) on a non - rotatable component (GG) is fixed, whereas the third element (E31) of the first planetary gear set (P1) on the one hand via the third switching element (K2) rotationally fixed to the second element (E23) of third planetary gear set (P3) and on the other by means of the fourth switching element (K3) rotatably connected to the second element (E22) of the second planetary gear set (P2) is brought into connection, - that the second element (E23) of the third planetary gear set (P3) also via the fifth shift element (B2) can be fixed to a non-rotatable component (GG), whereas the first element (E13) of the third planetary gear set (P3) is rotationally fixed to the first element (E12) of the second plane tenradsatzes (P2) is connected, - that the second planetary gear set (P2) by means of the sixth switching element (K4) is lockable, and that the second element (E24) of the fourth planetary gear set (P4) rotatably connected to the output shaft (GW2), whereas, of the first element (E14) of the fourth planetary gear set (P4) and the third element (E34) of the fourth planetary gear set (P4), one non-rotatably connected to the second element (E22) of the second planetary gear set (P2) and one non-rotatable with the second element (E4) E23) of the third planetary gear set (P3) is in communication. Transmission (G) to Claim 1 , characterized in that the first element (E14) of the fourth planetary gear set (P4) is non-rotatably connected to the second element (E22) of the second planetary gear set (P2), whereas 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) is in communication. Transmission (G) to Claim 1 , characterized in that the first element (E14) of the fourth planetary gear set (P4) rotatably with the second element (E23) of the third planetary gear set (P3) is in communication, whereas the third element (E34) of the fourth planetary gear set (P4) rotatably with the second element (E22) of the second planetary gear set (P2) is connected. Transmission (G) according to one of Claims 1 to 3 , characterized in that the sixth switching element (K4) when actuated, the second element (E22) 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) 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 (K3) and the fifth switching element (B2), a second forward gear (2.1) by operating the third (K2) and fifth switching element (B2) or (2.2) by operating the first (B1) and the fifth switching element (B2) or (2.3) by operating the first (B1) and third switching element (K2), a third forward gear (3) by pressing a fifth forward gear (4) by operating the first (B1) and the sixth shifting element (K4), a fifth forward gear (5) by operating the third (K2) and the sixth Shift element (K4), a sixth forward speed (6) by operating the fourth (K3) and the sixth shifting element (K4), a seventh forward speed (7) by operating the second (K1) and the sixth shifting element (K4), an eighth forward speed (8) by Be operating the second (K1) and fourth shifting elements (K3), a ninth forward gear (9) by operating the second (K1) and third shifting elements (K2), a tenth forward gear (10) by operating the third (K2) and fourth shift element (K3), a first reverse gear (R1) by operating the first (B1) and the fourth shift element (K3), and a second reverse gear (R2) by operating the second (K1) and the fifth shift element (B2) is switchable , Transmission (G) according to one of the preceding claims, characterized in that the respective planetary gear set (P1, P2, P3, P4) is present as a minus planetary gear set, wherein it is at the respective first element (E11, E12, E13, E14) of respective planetary gear set (P1, P2, P3, P4) about a respective sun gear at the respective second Element (E21, E22, E23, E24) of the respective planetary gear set (P1, P2, P3, P4) about a respective planet web and at the respective third element (E31, E32, E33, E34) of the respective planetary gear set (P1, P2, P3 , P4) is a respective ring gear. Transmission (G) according to one of the preceding claims, characterized in that the respective planetary gear set (P4) is present as a plus-planetary gear, wherein it is the respective first element (E14) of the respective planetary gear set (P4) to a respective sun gear, wherein respective second element (E24) of the respective planetary gear set (P4) is a respective ring gear and the respective third element (E34) of the respective planetary gear set (P4) is a respective planet gear. Transmission (G) according to one of the preceding claims, characterized in that the planetary gear sets (P1, P2, P3, P4) arranged axially in the order of first (P1), second (P2), third (P3) and fourth planetary gear set (P4) are. Transmission (G) according to one of Claims 1 to 7 , characterized in that the planetary gear sets (P1, P2, P3, P4) are arranged axially in the order of the second (P2), third (P3), first (P1) and fourth planetary gear sets (P4). Transmission (G) according to one of the preceding claims, characterized in that one or more switching elements (B1, K1, K2, K3, B2, K4) are each realized as a force-locking switching element. Transmission according to one of the preceding claims, characterized in that the fifth switching element is realized as a form-locking switching element. Transmission (G) according to one of the preceding claims, characterized in that the drive shaft (GW1) and the output shaft (GW2) are coaxial with each other and each form a connection point (GW1-A, GW2-A), wherein the connection point (GW1- A) of the drive shaft (GW1) and the connection point (GW2-A) of the output shaft (GW2) lie at opposite axial ends. Transmission (G) according to one of the preceding claims, characterized in that 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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