DE102017206829A1 - 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), five planetary gear sets (P1, P2, P3, P4, P5) and seven shift elements (B1, B2 , K1, K2, B3, B4, K3), wherein by selectively operating the seven shift elements (B1, B2, K1, K2, B3, B4, K3) fourteen forward gears and two reverse gears between the drive shaft (GW1) and the output shaft ( GW2) are switchable, as well as powertrain 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, a fourth and a fifth planetary gear, wherein the Planetenradsätze each comprise a plurality of elements, wherein a first, a second, a third , Fourth, fifth, sixth and seventh switching elements are provided, through the selective actuation of which different power flow guides can be represented via the planetary gear sets while shifting different gears between drive shaft and output shaft.

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 DE 101 15 995 A1 goes out a gearbox comprising five planetary gear sets, each composed of several elements in the form of one sun gear, one planetary land and one ring gear each. In addition, seven switching elements are provided, through the selective actuation of different gears between a drive shaft and an output shaft of the transmission can be represented. A total of fifteen forward gears, and a reverse gear between the drive shaft and the output shaft can be switched.

It is the object of the present invention to provide an alternative embodiment to the transmission known from the prior art with at least ten forward gears and 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 14.

According to the invention, a transmission comprises a drive shaft and an output shaft, and a first, a second, a third, a fourth and a fifth 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. Furthermore, seven switching elements are provided, through the selective actuation of different power flow guides on the planetary gear trains under different gears between drive shaft and output shaft are 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, the fourth planetary gearset, and the fifth 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 first element of the first planetary gear set can be fixed via the first switching element to a rotationally fixed component or a housing part, wherein the first element of the second planetary gear set by means of the second switching element is rotatably fixable. In addition, the first element of the second planetary gear set can be rotatably connected via the third switching element to the drive shaft, which is non-rotatably connected to the first element of the third planetary gear set and by means of the fourth switching element rotationally fixed to the second element of the second planetary gear set and the third element of the first Planetenradsatzes is connectable. The second element of the second planetary gear set and the third element of the first planetary gear set are rotatably connected to each other and can be fixed together on the fifth switching element on the rotationally fixed component.

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

In other words, in the transmission according to the invention thus the drive shaft permanently rotatably connected to the first element of the third planetary gear set, while the output shaft is constantly rotatably connected to the second element of the fourth planetary gear in combination. In addition, the second element of the first planetary, the third element of the third planetary and the first element of the fourth planetary gear set are permanently connected to each other, whereas the third element of the first planetary gear set and the second element of the second planetary gear set constantly rotatably in communication with each other. Finally, even the third element of the second planetary gear set and the second element of the third planetary gear set are permanently connected to each other in a rotationally fixed manner.

Upon actuation of the first switching element, the first element of the first planetary gearset is fixed to a rotationally fixed component and thus prevented from rotating, with this also the first element of the second planetary gear set is shut down in the closed state of the second switching element. By contrast, the first element of the second planetary gear set is rotatably connected upon actuation of the third switching element to the drive shaft, which is also rotatably connected in the closed state of the fourth switching element with the second element of the second planetary gear set and the third element of the first planetary gear set. The third element of the first planetary gear set and the second element of the second planetary gear set are also set on actuation of the fifth switching element on the rotationally fixed component. This also the third element of the fourth Planetenradsatz in the closed state of the sixth switching element is stopped.

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, wherein a plurality of elements of the planetary gear sets can be connected to the same rotationally fixed component.

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

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

In the transmission according to the invention, the first, the second, the fifth and the sixth switching element are designed as brakes that slow down when actuated, the respective rotatable component or rotatably connected to each other, rotatable components of the transmission to a standstill and set on a non-rotatable component. In contrast, the third, the fourth and the seventh switching element are in the form of clutches which, when actuated, in each case match the respective associated rotatable components of the transmission in their rotational movements and subsequently connect them to one another in a torque-proof manner.

Preferably, the first switching element, the second switching element, the third switching element and the fifth switching element are axially provided on a side facing the junction of the drive shaft side of the first planetary gear, more preferably, the first switching element is axially immediately adjacent to the first planetary gear and then the fifth switching element, then follow the second and finally the third switching element. While the first switching element, the second switching element and the fifth switching element are provided radially surrounding the first planetary gear, the third switching element is radially in the region of the first planetary gear and thus internal to the first Switching element, the second switching element and the fifth switching element placed. Due to the arrangement of the switching elements in the same area, a common supply could be realized via one or more common supply lines.

By contrast, the fourth shift element is arranged axially in particular between the second planetary gear set and the third planetary gear set and is preferably located radially in the region of the second element of the second planetary gear set. The sixth switching element is preferably provided in the gear plane of the fourth planetary gear set and thus lies axially substantially at the height of the fourth planetary gear set and radially surrounding this.

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

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

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

According to one embodiment of the invention, the first element of the fourth planetary gear set is non-rotatably connected to the first element of the fifth planetary gear set, whose third element is non-rotatably in communication with the output shaft. In addition, the second element of the fifth planetary gear set can be rotatably connected to the drive shaft via the seventh switching element.

In this case, therefore, the first element of the fifth planetary gear set is permanently non-rotatably connected to the first element of the fourth planetary gear set and is thus constantly non-rotatably in connection with the third element of the third planetary gear set and the second element of the first planetary gear set. The third element of the fifth planetary gear set is also permanently non-rotatably connected to the output shaft and thus also the second element of the fourth planetary gear set, whereas in the second element of the fifth planetary gear set a rotationally fixed connection to the drive shaft is made only by operating the seventh switching element. The seventh switching element is preferably axially provided on one of the connection point of the drive shaft facing away side of the fifth planetary gear set and is radially in particular in the region of the second element of the fifth planetary gear set.

According to an alternative embodiment of the invention, the first element of the fourth planetary gear set is non-rotatably connected to the first element of the fifth planetary gear set in connection, the second element is rotatably connected to the drive shaft. Furthermore, the third element of the fifth planetary gear set can be connected in rotation with the output shaft via the seventh switching element.

In this variant, therefore, the first element of the fifth planetary gear set is permanently connected in a rotationally fixed manner to the first element of the fourth planetary gear set, so that there is also a permanently rotationally fixed connection to the third element of the third planetary gear set and to the second element of the first planetary gear set. Likewise, the second element of the fifth planetary gear is constantly rotatably connected to the drive shaft, while in the case of the third element of the fifth planetary gear set a rotationally fixed connection to the output shaft is made only in the closed state of the seventh switching element. Here, the seventh switching element is preferably provided in the gear plane of the fifth planetary gear set and thus lies axially substantially at the level of the fifth planetary gear set and radially surrounding this.

Further alternatively, the second element of the fifth planetary gear set is rotatably connected to the drive shaft, the third element is non-rotatably connected to the output shaft in connection. In addition, the first element of the fifth planetary gear set can be rotatably connected via the seventh switching element with the first element of the fourth planetary gear set.

In this case, therefore, the second element of the fifth planetary gear set is permanently non-rotatably connected to the drive shaft, while the output shaft is constantly rotatably connected to the third element of the fifth planetary gear set. On the other hand, the first element of the fifth planetary gear set will not rotate with the first element of the first by turning the seventh switching element fourth planetary gear set and also the third element of the third planetary gear set and the second element of the first planetary gear set in combination. The seventh switching element is in this case preferably provided axially between the third planetary gear set and the fourth planetary gear set and lies radially in particular in the region of the third elements of the third planetary gear set and the fourth planetary gear set.

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

Further, a seventh forward speed is obtained by operating the second, fourth and seventh shift elements, while an eighth forward speed is switchable by operating the third, fourth and seventh shift elements. In contrast, a ninth forward gear can be switched by operating the first, the fourth and the seventh switching element, whereas for the circuit of a tenth forward gear to close the first, the third and the seventh switching element. An eleventh forward speed is obtained by operating the first, second and seventh shift elements while closing the first, fifth and seventh shift elements forms a twelfth forward speed. Further, in a thirteenth forward gear can be switched by the second, the fifth and the seventh switching element are actuated, whereas a fourteenth forward gear results in closing the third, the fifth and the seventh switching element.

In a further development of the invention, a first reverse gear results by actuating the second, the fifth and the sixth shifting element, while a second reverse gear is engaged when the third, the fifth and the sixth 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 first, the second and the fifth variant of the sixth forward gear always to vary the state of each two shift elements by opening one of the preceding forward gear involved switching elements and another To close switching element for displaying the subsequent forward gear is. This then has the consequence that a shift between the courses can proceed very quickly.

Advantageously, in the transmission according to the invention 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 set is present as a minus planetary gear, wherein it is at the respective first element of the respective planetary gear set to a respective sun gear, at the respective second element of the respective planetary gear set is a respective planetary gear and at the respective third element of the respective planetary gear set to a respective ring gear. A minus planetary set is composed in a manner known in principle to the person skilled in the art from the elements sun gear, planet carrier and ring gear, wherein the planet carrier carries at least one but preferably a plurality of planetary gears which in each case mesh with both the sun gear and the surrounding ring gear , Of the five 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. Preferably, however, all planetary gear sets are available as minus planetary gear sets, whereby a compact design can be realized.

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

According to a further embodiment of the invention, the 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 the 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, then in the latter case, a coupling via one or more intermediate gear ratios, for example in the form of spur gears, or a traction drive, such as a chain drive, be realized can.

Preferably, however, the rotor of the electric machine is rotatably coupled to the drive shaft, whereby a purely electric driving of the motor vehicle is represented in a suitable manner. More preferably, one or more of the switching elements are used as internal starting elements for electric driving. For this purpose, in particular, the second switching element or the sixth switching element, since these are closed both in 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 for both the forward electrical as well be used for the electric reverse. The rotor of the electric machine could be apart from the drive shaft also connected to one of the other, rotatable components of the transmission.

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

In general, the transmission can in principle be preceded by a starting element, for example a hydrodynamic torque converter or a friction clutch. This starting element can then also be part of the transmission and serves to design a start-up process by allowing a slip speed between the internal combustion engine and the drive shaft of the transmission. In this case, one of the switching elements of the transmission or the possibly existing separating clutch can be designed as such a starting element by being present as a friction switching element. In addition, a freewheel to the transmission housing or to another shaft can in principle be arranged on each shaft of the transmission.

The transmission according to the invention is in particular part of a motor vehicle drive train and is then arranged between a drive motor of the motor vehicle designed in particular as an internal combustion engine and further components of the drive train following in the direction of power flow to drive wheels of the motor vehicle. Here, the drive shaft of the transmission is either permanently non-rotatably coupled to a crankshaft of the internal combustion engine or connected via an intermediate disconnect clutch or a starting element with this, between the engine and transmission also a torsional vibration damper can be provided. On the output side, the transmission within the motor vehicle drive train is then preferably coupled to an axle drive of a drive axle of the motor vehicle, although here also a connection to a longitudinal differential may be present, via which a distribution takes place on a plurality of driven axles of the motor vehicle. The axle or the longitudinal differential can be arranged with the transmission in a common housing. Likewise, a torsional vibration damper can also be integrated into this housing.

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

However, if a switching element is provided between two components of the transmission, then these components are not permanently rotatably coupled to each other, but a rotationally fixed coupling is made only by pressing the intermediate switching element. In this case, an actuation of the switching element in the sense of the invention means that the relevant switching element is transferred into a closed state and, as a result, the components directly coupled to it in their rotational movements equal to one another. In the case of an embodiment of the relevant switching element as a form-locking switching element on this directly rotatably interconnected components are running at the same speed, while in the case of a non-positive switching element can also exist after pressing desselbigen speed differences between the components. This intentional or unwanted state is still referred to in the context of the invention as a rotationally fixed connection of the respective components via the switching element.

The invention is not limited to the specified combination of the features of the main claim or the claims dependent thereon. It also results in ways to combine individual features, even if they emerge from the claims, the following description of preferred embodiments of the invention or directly from the drawings. The reference of the claims to the drawings by use of reference numerals is not intended to limit the scope of the claims.

• 1 eine schematische Ansicht eines Kraftfahrzeugantriebsstranges, in welchem ein erfindungsgemäßes Getriebe zur Anwendung kommt;
• 2 eine schematische Ansicht eines Getriebes entsprechend einer ersten Ausführungsform der Erfindung;
• 3 eine schematische Darstellung eines Getriebes gemäß einer zweiten Ausgestaltungsmöglichkeit der Erfindung;
• 4 eine schematische Ansicht eines Getriebes entsprechend einer dritten Ausführungsform der Erfindung;
• 5 eine schematische Darstellung eines Getriebes gemäß einer vierten Ausgestaltungsmöglichkeit der Erfindung; und
• 6 ein beispielhaftes Schaltschema der Getriebe aus den 2 bis 5.

Advantageous embodiments of the invention, which are explained below, are shown in the drawings. It shows:

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

1 shows a schematic view of a motor vehicle drive train, in which an internal combustion engine VKM via an intermediate torsional vibration damper TS with a gear G connected is. The transmission G on the output side is an axle drive AG downstream, via which a drive power on drive wheels DW a drive axle of the motor vehicle is distributed. The gear G and the torsional vibration damper TS are summarized in a common gearbox housing, in which then the axle drive AG can be integrated. As well as in 1 it can be seen, are the internal combustion engine VKM , the torsional vibration damper TS , The gear G and also the axle drive AG aligned in the direction of travel of the motor vehicle.

Out 2 is a schematic representation of the transmission G according to a first embodiment of the invention. As can be seen, the transmission includes G a first planetary gear set P1 , a second planetary gear set P2 , a third planetary gear set P3 , a fourth planetary gear set P4 and a fifth planetary gear set P5 , Each of the planetary gear sets P1 . P2 . P3 . P4 and P5 each has a first element E11 respectively. E12 respectively. E13 respectively. E14 respectively. E15 , a second element each E21 respectively. E22 respectively. E23 respectively. E24 respectively. E25 and a third element each E31 respectively. E32 respectively. E33 respectively. E34 respectively. E35 on. The respective first element E11 respectively. E12 respectively. E13 respectively. E14 respectively. E15 is always by a sun gear of the respective planetary gear set P1 respectively. P2 respectively. P3 respectively. P4 respectively. P5 formed while the respective second element E21 respectively. E22 respectively. E23 respectively. E24 respectively. E25 at the planetary gear sets P1 . P2 . P3 . P4 and P5 each as a planetary bridge is present. The remaining third element E31 respectively. E32 respectively. E33 respectively. E34 respectively. E35 is then by a respective ring gear of the respective planetary gear set P1 respectively. P2 respectively. P3 respectively. P4 respectively. P5 educated.

The planetary gear sets P1 . P2 . P3 . P4 and P5 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 . P4 and P5 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 respectively. E25 through the respective ring gear and the respective third element E31 respectively. E32 respectively. E33 respectively. E34 respectively. E35 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 , the fourth planetary gear set P4 and the fifth planetary gear set P5 axially in the order of the first planetary gear set P1 , second planetary gear set P2 , third planetary gear set P3 , fourth planetary gear set P4 and fifth planetary gear set P5 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 seven switching elements in the form of a first switching element B1 , a second switching element B2 , a third switching element K1 , a fourth switching element K2 , a fifth switching element B3 , a sixth switching element B4 and a seventh switching element K3 , Here are the switching elements B1 . B2 . K1 . K2 . B3 . B4 and K3 each designed as non-positive switching elements and are preferably before as lamella switching elements. In addition, the first switching element B1 , the second switching element B2 , the fifth switching element B3 and the sixth switching element B4 designed here as brakes, while the third switching element K1 , the fourth switching element K2 and the seventh switching element K3 present as couplings.

In the present case, the first element E11 of the first planetary gear set P1 over the first switching element B1 on a non-rotatable component GG be set, which is preferably a transmission housing of the transmission G or part of a transmission housing. At the or a non-rotatable component GG can also be the first element E12 of the second planetary gear set P2 by closing the second switching element B2 be stopped, the first element E12 of the second planetary gear set P2 also by means of the third switching element K1 rotatably with the drive shaft LV1 can be associated.

The drive shaft LV1 is permanently rotatable with the first element E13 of the third planetary gear set P3 in conjunction and can also still on the seventh switching element K3 rotatably with the second element E25 of the fifth planetary gear set P5 connected, as well as by closing the fourth switching element K2 rotatably with the second element E22 of the second planetary gear set P2 and the third element E31 of the first planetary gear set P1 be associated. The second element E22 of the second planetary gear set P2 and the third element E31 of the first planetary gear set P1 are permanently connected to each other in a rotationally fixed manner and can, apart from the connectivity with the drive shaft LV1 , nor by closing the fifth switching element B3 on the or a non-rotatable component GG be fixed.

As well as in 2 It can be seen that these are the second element E21 of the first planetary gear set P1 , the third element E33 of the third planetary gear set P3 , the first element E14 of the fourth planetary gear set P4 and the first element E15 of the fifth planetary gear set P5 rotatably connected. Likewise, the third element is also available E32 of the second planetary gear set P2 and the second element E23 of the third planetary gear set P3 permanently rotatably connected with each other. On the other hand, the third element E34 of the fourth planetary gear set P4 by closing the sixth switching element P4 on the or a non-rotatable component GG be set while the second element E24 of the fourth planetary gear set P4 together with the third element E35 of the fifth planetary gear set P5 Constantly rotatable with the output shaft GW2 communicates.

As well as in 2 can be seen, are the first switching element B1 , the second switching element B2 , the third switching element K1 and the fifth switching element B3 axially on one of the connection points Level 1-A the drive shaft LV1 facing side of the first planetary gear set P1 placed. Specifically, the first switching element lies B1 while axially adjacent to the first planetary gear P1 , then axially then the fifth switching element B3 , then the second switching element B2 and finally, the third switching element K1 consequences. Radial are the first switching element B1 , the second switching element B2 and the fifth switching element B3 surrounding the first planetary gear set P1 provided while the third switching element K1 radially in the region between the second element E21 and the third element E31 of the first planetary gear set P1 lies.

The fourth switching element K2 is axially between the second planetary gear set P2 and the third planetary gear set P3 arranged and located radially in the region of the second element E22 of the second planetary gear set P2 , In contrast, the sixth switching element B4 axially in the gear plane of the fourth planetary gear set P4 placed and thus lies axially substantially at the height of the fourth planetary gear set P4 , and radially surrounding this. Finally, there is the seventh switching element K3 axially on one of the connection points Level 1-A facing away and thus the connection point GW2-A facing side of the fifth planetary gear set P5 provided, wherein the seventh switching element K3 while radially in the region of the second element E25 of the fifth planetary gear set P5 lies.

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 difference is that the second element E25 of the fifth planetary gear set P5 now permanently rotatably with the drive shaft LV1 while the third element E35 of the fifth planetary gear set P5 no longer permanently rotatable with the output shaft GW2 connected is. A non-rotatable connection between the third element E35 of the fifth planetary gear set P5 and the output shaft GW2 is only by closing a seventh switching element K3 made in the wheel plane of the fifth planetary gear set P5 is arranged horizontally. This is the seventh switching element K3 axially substantially at the height of the fifth planetary gear set P5 and radially surrounding this. 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 Possibility of embodiment of the invention. Again, this design option corresponds again largely to the variant 2 , in contrast to the second element E25 of the fifth planetary gear set P5 now constantly rotatably with the drive shaft LV1 connected while the first element E15 of the fifth planetary gear set P5 only by pressing a seventh switching element K3 rotatably with the second element E21 of the first planetary gear set P1 , the third element E33 of the third planetary gear set P3 and the first element E14 of the fourth planetary gear set P4 is associated. The seventh switching element K3 is axially between the third planetary gear P3 and the fourth planetary gear set P4 provided and is located radially in the region of the third elements E33 and E34 of the third planetary gear set P3 and the fourth planetary gear set P4 , Otherwise, the design option corresponds to 4 according to the variant 2 so that reference is made to what has been described.

Finally shows 5 a schematic representation of a transmission G according to a fourth embodiment of the invention. This embodiment corresponds essentially to the variant 2 , in contrast, in addition to an electric machine EM is provided, whose stator S on the non-rotatable component GG is fixed while a rotor R the electric machine EM rotatably with the drive shaft LV1 connected is. Furthermore, the drive shaft LV1 at the junction Level 1-A via an intermediate separating clutch K0 , which is designed here as a lamellae switching element, with a connecting shaft AT rotatably connected, which in turn connected to a crankshaft of the internal combustion engine VKM by means of the intermediate torsional vibration damper TS connected is. Due to the rotationally fixed connection of the rotor R with the drive shaft LV1 is the electric machine EM coaxial with the drive shaft LV1 placed.

About the electric machine EM In this case, a purely electric driving can be realized, in which case the separating clutch K0 is opened to the drive shaft LV1 from the connection shaft AT to decouple and the internal combustion engine VKM not to lug. Otherwise, the embodiment corresponds to 5 according to the variant 2 so that reference is made to what has been described.

In 6 is an exemplary circuit diagram for the transmission G from the 2 to 5 tabulated. As can be seen, in each case a total of fourteen forward gears 1 to 14 , 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 . B2 . K1 . K2 . B3 . B4 and K3 in which of the forward gears 1 to 14 and the reverse gears R1 and R2 each is closed. In each of the forward gears 1 to 14 and the reverse gears R1 and R2 are each three of the switching elements B1 . B2 . K1 . K2 . B3 . B4 and K3 closed, with a successive circuit of the forward gears 1 to 14 , except for a sixth forward gear 6.1 , a sixth forward gear 6.2 and a sixth forward gear 6.5 to open one of the involved switching elements and to close another switching element in the following.

As in 6 can be seen, is a first forward gear 1 by actuating the first switching element B1 , the second switching element B2 and the sixth switching element B4 switched, starting from this, a second forward gear 2 is formed by the second switching element B2 opened and in the following the third switching element K1 is closed. Furthermore, a third forward gear 3 switched by starting from the second forward gear 2 the third switching element K1 opened and the fourth switching element K2 is closed. Based on this results then a fourth forward gear 4 by opening the first switching element B1 and closing the third switching element K1 , This results in a fifth forward gear 5 by opening the third switching element K1 and actuating the second switching element B2 , starting from this in a sixth forward gear 6.1 is switched by both the second switching element B2 as well as the fourth switching element K2 opened and the first switching element B1 and the seventh switching element K3 getting closed.

Alternatively, but also a sixth forward gear 6.2 be represented by the fifth switching element B3 , the sixth switching element B4 and the seventh switching element K3 be operated. Further, a sixth forward speed 6.3 by closing the second switching element B2 , the sixth switching element B4 and the seventh switching element K3 switchable, as well as a sixth forward gear 6.4 by actuating the fourth switching element K2 , the sixth switching element B4 and the seventh switching element K3 represented. In addition, there is still a sixth forward speed 6.5 by closing the third switching element K1 , the sixth switching element B4 and the seventh switching element K3 , Preference is given to the sixth forward gear 6.3 or 6.4 , to switch, since in both cases, only the switching state of two switching elements is to change for switching.

To shift to a seventh forward gear 7 are then the second switching element B2 , the fourth switching element K2 and the seventh switching element K3 close. Furthermore, starting from from the seventh forward gear 7 an eighth forward gear 8th by the second switching element B2 opened and the third switching element K1 is pressed. To further upshift into a ninth forward gear 9 is the third switching element below K1 to reopen and the first switching element B1 close. Furthermore, the ninth forward gear 9 in a tenth forward gear 10 switched by the fourth switching element K2 in an unactuated state and then the third switching element K1 is transferred to an actuated state. To further upshift into an eleventh forward gear 11 is then starting from the tenth forward gear 10 the third switching element K1 to open and in the following the second switching element B2 close.

Furthermore, there is a twelfth forward speed 12 starting from the eleventh forward gear 11 by the second switching element B2 in an unactuated state and the fifth switching element B3 is transferred to an actuated state. This results in a thirteenth forward gear 13 by opening the first switching element B1 and actuating the second switching element B2 Starting from this, in a fourteenth forward gear 14 is switched by the second switching element B2 opened and the third switching element K1 is closed.

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 second switching element B2 , the fifth switching element B3 and the sixth switching element B4 connected. In contrast, there is the second reverse gear R2 by actuating the third switching element K1 , the fifth switching element B3 and the sixth switching element B4 ,

As in the 2 to 5 is shown, is the sixth switching element B4 designed as non-positive switching element. However, the sixth switching element could B4 Also be realized as a form-locking switching element, such as locking synchronization or as a claw switching element. Furthermore, the gears can also G according to the embodiments of 3 and 4 analogous to the variant according to 5 be hybridized.

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

LIST OF REFERENCE NUMBERS

G

transmission

GG

Non-rotating component

P1

First planetary gear set

E11

First element of the first planetary gear set

E21

Second element of the first planetary gear set

E31

Third element of the first planetary gear set

P2

Second planetary gear set

E12

First element of the second planetary gear set

E22

Second element of the second planetary gear set

E32

Third element of the second planetary gear set

P3

Third planetary gear set

E13

First element of the third planetary gear set

E23

Second element of the third planetary gear set

E33

Third element of the third planetary gear set

P4

Fourth planetary gear set

E14

First element of the fourth planetary gear set

E24

Second element of the fourth planetary gear set

E34

Third element of the fourth planetary gear set

P5

Fifth planetary gear set

E15

First element of the fifth planetary gear set

E25

Second element of the fifth planetary gear set

E35

Third element of the fifth planetary gear set

B1

First switching element

B2

Second switching element

K1

Third switching element

K2

Fourth switching element

B3

Fifth switching element

B4

Sixth switching element

K3

Seventh switching element

1

First forward

2

Second forward speed

3

Third forward

4

Fourth forward

5

Fifth forward speed

6.1

Sixth forward

6.2

Sixth forward

6.3

Sixth forward

6.4

Sixth forward

6.5

Sixth forward

7

Seventh forward

8th

Eighth forward

9

Ninth forward

10

Tenth forward

11

Eleventh forward

12

Twelfth forward

13

Thirteenth forward

14

Fourteenth forward

R1

First reverse

R2

Second reverse

LV1

drive shaft

Level 1-A

junction

GW2

output shaft

GW2-A

junction

EM

electric machine

S

stator

R

rotor

AT

connecting shaft

K0

separating clutch

VKM

Internal combustion engine

TS

torsional vibration damper

AG

transaxles

DW

drive wheels

QUOTES INCLUDE IN THE DESCRIPTION

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

Cited patent literature

• DE 10115995 A1 [0003]

Claims (14)

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), a fourth (P4) and a fifth planetary gear set ( P5), wherein the planetary gear sets (P1, P2, P3, P4, P5) each have a plurality of elements (E11, E12, E13, E14, E15, E21, E22, E23, E24, E25, E31, E32, E33, E34, E35 ), wherein a first (B1), a second (B2), a third (K1), a fourth (K2), a fifth (B3), a sixth (B4) and a seventh switching element (K3) are provided whose selective actuation different power flow guides on the planetary gear sets (P1, P2, P3, P4, P5) with different gears (1 to 14, R1 and R2) between the drive shaft (GW1) and output shaft (GW2) are represented, characterized in that - the first element (E11) of the first planetary gear set (P1) via the first switching element (B1) on a non-rotatable component (GG) can be fixed, - that the ers te element (E12) of the second planetary gear set (P2) by means of the second switching element (B2) on a non-rotatable component (GG) can be fixed, - that the first element (E12) of the second planetary gear set (P2) also via the third switching element (K1) rotatably connected to the drive shaft (GW1) which is non-rotatably connected to the first element (E13) of the third planetary gear set (P3) and by means of the fourth switching element (K2) rotationally fixed to the second element (E22) of the second planetary gear set (P2) and the third element (E31) of the first planetary gear set (P1) is connectable, - that the second element (E22) of the second planetary gear set (P2) and the third element (E31) of the first planetary gear set (P1) rotatably connected to each other and together over the Fifth switching element (B3) on a non-rotatable component (GG) can be fixed, - that the second element (E21) of the first planetary gear set (P1) rotatably connected to the third element (E33) of the third Planetenradsa tts (P3) and the first element (E14) of the fourth planetary gear set (P4) is in communication, whereas the third element (E32) of the second planetary gear set (P2) rotatably connected to the second element (E23) of the third planetary gear set (P3) is connected in that the output shaft (GW2) is non-rotatably connected to the second element (E24) of the fourth planetary gear set (P4) whose third element (E34) can be fixed to a non-rotatable component (GG) by means of the sixth switching element (B4), and that in the fifth planetary gear set (P5) a first coupling of the first element (E15) of the fifth planetary gear set (P5) with the first element (E14) of the fourth planetary gear set (P4), a second coupling of the second element (E25) of the fifth planetary gear set (P5) with the drive shaft (GW1), and a third coupling of the third element (E35) of the fifth planetary gear set (P5) with the output shaft (GW2), of these couplings two couplings as permane Non-rotatable connections are present, while in the remaining coupling a rotationally fixed connection by means of the seventh switching element (K3) can be produced. Transmission (G) to Claim 1 , characterized in that the first element (E14) of the fourth planetary gear set (P4) rotatably connected to the first element (E15) of the fifth planetary gear set (P5), the third element (E35) rotatably connected to the output shaft (GW2) is in communication , wherein the second element (E25) of the fifth planetary gear set (P5) via the seventh switching element (K3) rotatably connected to the drive shaft (GW1) is connectable. Transmission (G) to Claim 1 , characterized in that the first element (E14) of the fourth planetary gear set (P4) rotatably with the first element (E15) of the fifth planetary gear set (P5) is in communication, the second element (E25) rotatably connected to the drive shaft (GW1) is connected wherein the third element (E35) of the fifth planetary gear set (P5) via the seventh switching element (K3) rotatably connected to the output shaft (GW2) is brought into connection. Transmission (G) to Claim 1 , characterized in that the second element (E25) of the fifth planetary gear set (P5) is non-rotatably connected to the drive shaft (GW1) whose third element (E35) rotatably connected to the output shaft (GW2) is in communication, wherein the first element (E15 ) of the fifth planetary gear set (P5) via the seventh switching element (K3) rotatably connected to the first element (E14) of the fourth planetary gear set (P4) is connectable. Transmission (G) according to one of the preceding claims, characterized in that a first forward gear (1) by operating the first (B1), the second (B2) and the sixth switching element (B4), a second forward gear (2) by operating the a third forward gear (3) by operating the first (B1), the fourth (K2) and the sixth shifting element (B4), a fourth forward gear (4) ) by operating the third (K1), the fourth (K2) and the sixth shifting element (B4), a fifth forward speed (5) by operating the second (B2), the fourth (K2) and the sixth shifting element (B4) sixth forward gear (6.1) by actuating the first (B1), the sixth (B4) and the seventh switching element (K3) or (6.2) by operating the fifth (B3), the sixth (B4) and the seventh switching element (K3) or (6.3) by operating the second (B2), the sixth ( B4) and the seventh switching element (K3) or (6.4) by actuating the fourth (K2), the sixth (B4) and the seventh switching element (K3) or (6.5) by actuating the third (K1), the sixth (B4) and the seventh shift element (K3), a seventh forward speed (7) by operating the second (B2), the fourth (K2) and the seventh shift element (K3), an eighth forward speed (8) by operating the third (K1), fourth (K2) and seventh switching element (K3), a ninth forward gear (9) by operating the first (B1), fourth (K2) and seventh switching elements (K3), a tenth forward gear (10) by operating the first (K3) B1), the third (K1) and the seventh switching element (K3), an eleventh forward speed (11) by operating the first (B1), the second n (B2) and the seventh switching element (K3), a twelfth forward gear (12) by actuating the first (B1), the fifth (B3) and the seventh switching element (K3), a thirteenth forward gear (13) by actuating the second B2), the fifth (B3) and the seventh switching element (K3), and a fourteenth forward gear (14) by operating the third (K1), the fifth (B3) and the seventh switching element (K3) is switchable. Transmission (G) according to one of the preceding claims, characterized in that a first reverse gear (R1) by operating the second (B2), the fifth (B3) and the sixth switching element (B4), and a second reverse gear (R2) by pressing of the third (K1), the fifth (B3) and the sixth switching element (B4) is switchable. Transmission (G) according to one of the preceding claims, characterized in that the respective planetary gear set (P1, P2, P3, P4, P5) is present as a minus planetary gear set, wherein it is at the respective first element (E11, E12, E13, E14 , E15) of the respective planetary gear set (P1, P2, P3, P4, P5) about a respective sun gear, at the respective second element (E21, E22, E23, E24, E25) of the respective planetary gear set (P1, P2, P3, P4, P5) around a respective planetary land and at the respective third element (E31, E32, E33, E34, E35) of the respective planetary gear set (P1, P2, P3, P4, P5) is a respective ring gear. Transmission according to one of the preceding claims, characterized in that the respective planetary gear set is present as a plus-planetary gear set, wherein it is at the respective first element of the respective planetary gear set to a respective sun gear, at the respective second element of the respective planetary gear set to a respective ring gear and at the respective third element of the respective planetary gear set is a respective planet web. Transmission (G) according to one of the preceding claims, characterized in that one or more switching elements (B1, B2, K1, K2, B3, B4, K3) are each realized as a force-locking switching element. Transmission according to one of the preceding claims, characterized in that the sixth switching element is realized as a form-locking switching element. Transmission (G) according to one of the preceding claims, characterized in that the drive shaft (GW1) and the output shaft (GW2) are coaxial with each other and each form a connection point (GW1-A, GW2-A), wherein the connection point (GW1- A) of the drive shaft (GW1) and the connection point (GW2-A) of the output shaft (GW2) lie at opposite axial ends. Transmission (G) according to one of the preceding claims, characterized in that 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 13 ,

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