DE102017206797A1 - 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 six shift elements (K1, B1 , B2, K2, K3, B3), wherein ten forward gears and three reverse gears between the drive shaft (GW1) and the output shaft (GW2) are switchable by selectively operating the six shift elements (K1, B1, B2, K2, K3, B3) , 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 and sixth shifting 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 10 2015 214 217 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, 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 three reverse gears 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.

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, 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. Further, six switching elements are provided, through the selective actuation of different power flow guides on the planetary gear sets under different gears between drive shaft and output shaft can be displayed.

In the context of the invention, a "shaft" is understood to mean a rotatable component of the transmission via which each associated components of the transmission are connected to one another in an axially and / or rotationally fixed manner or via which such a connection can be produced upon actuation of a corresponding switching element. Thus, the respective shaft can also be present as an intermediate piece, via which a respective component is connected radially, for example.

By "axial" in the context of the invention is meant an orientation in the direction of an axis along which the planetary gear sets are arranged coaxially to one another. The term "radial" is understood to mean an orientation in the diameter direction of a shaft lying on the axis.

The planetary gear sets are preferably arranged in the axial direction in the order of the first planetary gearset, the second planetary gearset, the third planetary gearset, 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 drive shaft is non-rotatably connected to the second element of the second planetary gear set, whose first element is fixed to a non-rotatable component and the third element is non-rotatably connected to the first element of the fourth planetary gear set. Furthermore, the second element of the fourth planetary gear set and the third element of the fifth planetary gear set are non-rotatably connected to each other and can be rotatably connected together via the first switching element with the first element of the third planetary gear set. Furthermore, the second element of the third planetary gear set and the third element of the fourth planetary gear set are rotatably connected to each other and can be fixed by means of the second switching element to a rotationally fixed component.

The first element of the fifth planetary gear set can be fixed on the one hand via the third switching element to a non-rotatable component and on the other by means of the fourth switching element rotatably connected to the third element of the third planetary gear set. moreover For example, the third element of the third planetary gear set can be connected in a rotationally fixed manner to the second element of the fifth planetary gear set via the fifth switching element, which is connected in a rotationally fixed manner to the output shaft. Finally, in the first planetary gear set, there is a first coupling of the first element of the first planetary gear set with a rotationally fixed component, a second coupling of the second element of the first planetary gear set with the second element of the second planetary gear set, and a third coupling of the third element of the first planetary gear set with the first Element of the third planetary gear set. Of these couplings are two couplings as permanent non-rotatable compounds before, while the remaining coupling a rotationally fixed connection by means of the sixth switching element can be produced.

In other words, therefore, in the transmission according to the invention, the drive shaft permanently rotatably connected to the second element of the second planetary gear set, while the output shaft is constantly rotatably connected to the second element of the fifth planetary gear in conjunction. Furthermore, the first element of the second planetary gear set is constantly fixed to a rotationally fixed component and is thus permanently prevented from rotating. In addition, the third element of the second planetary gear set and the first element of the fourth planetary gear set are constantly rotatably connected to each other, whereas the third element of the fourth planetary gear set is permanently connected rotationally fixed to the second element of the third planetary gear set. Likewise, the second element of the fourth planetary gear set and the third element of the fifth planetary gear set are permanently connected to each other in a rotationally fixed manner.

Upon actuation of the first shift member, the first member of the third planetary gear set is non-rotatably connected to the second element of the fourth planetary gear set and the third element of the fifth planetary gear set, while closing of the second shift element is a common setting of the second element of the third planetary gear set and the third element of the fourth Planet gearset pulls on a non-rotatable component after. At the latter, the first element of the fifth planetary gear set can be fixed by pressing the third switching element and thus prevented from rotating, wherein the first element of the fifth planetary gear set can also be rotatably connected via the fourth switching element with the third element of the third planetary gear in combination , Apart from that, the third element of the third planetary gear is still in the closed state of the fifth switching element rotatably connected to the second element of the fifth planetary gear and thus connected to the output shaft.

The rotationally fixed components of the transmission according to the invention are permanently stationary components of the transmission, preferably a transmission housing or a part of such a transmission housing or a component attached to the transmission housing. The first element of the second 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 third planetary gear set and the third element of the fourth planetary gear are rotatably connected only in the closed state of the second switching element with a rotationally fixed component and thus stopped. Likewise, the first element of the fifth planetary gear is prevented from rotating only by actuation of the third switching element by setting on a rotationally fixed component.

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

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

In the transmission according to the invention, the first, the fourth and the fifth switching element are designed as clutches, which in each case match the respective rotatable components of the transmission in their rotational movements each other and connect in the following rotation with each other. In contrast, the second and the third switching element as brakes, which slow down when actuated, the respective rotatable component or the rotatably interconnected, rotatable components of the transmission to a standstill and fix it on a non-rotatable component. The sixth switching element is depending on manufactured Connection designed either as a brake or as a clutch.

Preferably, the first switching element is provided axially between the third planetary gear set and the fourth planetary gear set and is further preferably radially in the region of the second element of the fourth planetary gear set. In contrast, the second switching element is in particular placed axially between the second planetary gear set and the third planetary gear set. Radially, the second switching element can be provided surrounding the third planetary gear set.

In contrast, the third switching element, the fourth switching element and the fifth switching element are preferably axially provided on a side facing away from a connection point of the drive shaft side of the fifth planetary gear and are further preferably axially adjacent to each other. In this case, the fifth shift element is then provided in particular adjacent to the fifth planetary gear set, which then axially first follow the fourth shift element and finally the third shift element. Radially, the third switching element, the fourth switching element and the fifth switching element are provided in particular surrounding the fifth planetary gear set. Due to this spatial arrangement, a common supply of two or even all three switching elements could be realized.

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

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

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

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

In this case, therefore, the second element of the first planetary gear set is constantly rotatably connected to the second element of the second planetary gear set, while also the third element of the first planetary gear and the first element of the third planetary gear set permanently non-rotatably in communication. In contrast, the first element of the first planetary gear set is fixed only by closing the sixth switching element to a rotationally fixed component and thus prevented from rotating. In this respect, the sixth switching element is present as a brake, which is preferably provided axially on one of the connection point of the drive shaft facing side of the first planetary gear set and more preferably placed radially surrounding the first planetary gear.

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

In this variant, accordingly, the first element of the first planetary gear set is constantly fixed to a rotationally fixed component and is also prevented in the sequence and permanently to a rotational movement. In addition, the third element of the first planetary gear set and the first element of the third planetary gear are constantly rotatably connected to each other, whereas in the case of the second switching element of the first planetary gear rotatable connection to the second element of the second planetary gear set is made only with actuation of the sixth switching element, which accordingly as Clutch is designed. Preferably, the sixth switching element is provided axially between the first planetary gear set and the second planetary gear set and lies radially in particular in the region of the third elements of the first planetary gear set and the second planetary gear set.

Further alternatively, the second element of the second planetary gear set is rotatably connected to the second element of the first planetary gear set, whose first element is fixed to a non-rotatable component. In contrast, the third element of the first planetary gear set by means of the sixth switching element rotatably connected to the first element of the third planetary gear set.

Also in this variant, therefore, the first element of the first planetary gear set is constantly fixed to a rotationally fixed component and is thus permanently prevented from rotating. Furthermore, the second element of the first planetary gear set and the second element of the second planetary gear set are permanently connected to each other in a rotationally fixed manner, so that the second element of the first planetary gear set is permanently connected in a rotationally fixed manner to the drive shaft. On the other hand, the third element of the first planetary gear set is non-rotatably connected to the first element of the third planetary gear set only in the closed state of the sixth switching element, wherein the sixth switching element is designed accordingly as a clutch. In particular, the sixth switching element is provided in the gear plane of the first planetary gear set and is accordingly axially substantially at the height of the first planetary gear set and radially surrounding this.

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

Further, a third forward speed results by operating the first, third and fourth shift elements, whereas a fourth forward speed is switchable by operating the third, fourth and sixth shift elements. Further, a fifth forward speed can be represented by closing the third, fifth and sixth shifting elements, and for the sixth forward speed shifting, the first, third and sixth shifting elements are to be operated. In addition, a seventh forward speed is obtained by operating the first, fifth and sixth shifting elements, while an eighth forward speed is switchable by operating the first, fourth and sixth shifting elements. In contrast, a ninth forward gear can be switched by operating the fourth, the fifth and the sixth shifting element, whereas for the circuit of a tenth forward gear, the first, the fourth and the fifth shifting element are to be closed.

In a further development of the invention results in a first reverse by operating the second, the fourth and the sixth switching element, while a second reverse gear is switched upon closing of the first, the second and the fifth switching element. In addition, a third reverse gear is represented by operating the second, the fifth and the sixth switching element.

With a suitable choice of stationary gear ratios of the planetary gear sets this is a suitable for the application in the field of a motor vehicle translation series realized. For a sequential shift of the forward gears according to their order is, except for the second and the third variant of the second 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 switching element for display to close 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, three reverse gears can be realized for a drive via the drive machine preceding 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.

In a further development of the invention, a first additional gear can be switched by operating the second, the fourth and the fifth switching element, while a second additional gear results in closing the first, the third and the fifth switching element. These two additional gears can be represented in the individual aforementioned variants of a transmission according to the invention, but the additional gears do not fit well in the translation series.

It is a further embodiment of the invention that the respective planetary gear set is present as a minus planetary gear set, wherein the respective first element of the respective planetary gear set is 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 second switching element is designed as a form-locking switching element, such as a dog clutch or lock synchronization. For the second switching element is involved in the circuit of the first two forward gears and the reverse gears, so that a closing of the second switching element is to take place in a stoppage 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 is rotatably connected to a power take-off. In this case, the transmission according to the invention is thus equipped with a power take-off, via which a drive of ancillary units or the like can take place. More preferably, the power take-off attaches to the second element of the first planetary gear set. Alternatively, the power take-off can also be arranged in front of the gear set.

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

In a further development of the invention, an electric machine is provided whose rotor is rotatably coupled to one of the rotatable components of the transmission. Preferably, then a stator of the electric machine is rotatably connected to a non-rotatable component of the transmission. In addition, the electric machine can 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 off-axis to this be arranged, in the latter case, then a coupling via one or more intermediate gear ratios, for example in the form 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 first switching element, the second switching element or the fourth switching element, since these are closed in each case in at least one 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 converted into a closed state and in the sequence, the directly coupled thereto components in their rotational movements equal to each other. In the case of an embodiment of the relevant switching element as a form-locking switching element on this directly rotatably interconnected components are running at the same speed, while in the case of a non-positive switching element can also exist after pressing desselbigen speed differences between the components. This intentional or unwanted state is still referred to in the context of the invention as a rotationally fixed connection of the respective components via the switching element.

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

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

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

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

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

Out 2 is a schematic representation of the transmission G according to a first embodiment of the invention. As can be seen, the transmission includes G a first planetary gear set P1 , a second planetary gear set P2 , a third planetary gear set P3 , 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. Compared to a respective version as a minus planetary gear set would then for the transfer to a plus Planet 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 six switching elements in the form of a first switching element K1 , a second switching element B1 , a third switching element B2 , a fourth switching element K2 , a fifth switching element K3 and a sixth switching element B3 , Here are the switching elements K1 . B1 . B2 . K2 . K3 and B3 each designed as non-positive switching elements and are preferably before as lamella switching elements. In addition, the second switching element B1 , the third switching element B2 and the sixth switching element B3 in the present case designed as brakes, while the first switching element K1 , the fourth switching element K2 and the fifth switching element K3 present as couplings.

In the present case is the drive shaft LV1 rotatably with the second element E22 of the second planetary gear set P2 and the second element E21 of the first planetary gear set P1 connected, wherein the first element E12 of the second planetary gear set P2 permanently on a non-rotatable component GG is fixed, which in particular is a transmission housing of the transmission G or a part of such a transmission housing is. Further, the third element E31 of the first planetary gear set P1 and the first element E13 of the third planetary gear set P3 rotatably connected to each other and can together via the first switching element K1 rotatably with the second element E24 of the fourth planetary gear set P4 and the third element E35 of the fifth planetary gear set P5 be associated. The second element E24 of the fourth planetary gear set P4 and the third element E35 of the fifth planetary gear set P5 are constantly connected to each other in a rotationally fixed manner.

As well as in 2 it can be seen, the third element stand E32 of the second planetary gear set P2 and the first element E14 of the fourth planetary gear set P4 rotatably connected with each other. Furthermore, the third element E34 of the fourth planetary gear set P4 rotatably with the second element E23 of the third planetary gear set P3 connected and can together with this by means of the second switching element B1 on the non-rotatable component GG be fixed. The first element E15 of the fifth planetary gear set P5 can on the one hand via the third switching element B2 on the non-rotatable component GG fixed, and on the other hand by closing the fourth switching element K2 non-rotatable with the third element E33 of the third planetary gear set P3 be associated.

Apart from the connectivity with the first element E15 of the fifth planetary gear set P5 can the third element E33 of the third planetary gear set P3 via the fifth switching element K3 rotatably with the second element E25 of the fifth planetary gear set P5 be connected, which permanently rotatably connected to the output shaft GW2 communicates. In this respect, the third element E33 of the third planetary gear set P3 by closing the fifth switching element K3 also rotatably with the output shaft GW2 connected. Finally, there may be the first element E11 of the first planetary gear set P1 via the sixth switching element B3 on the non-rotatable component GG be fixed.

The first switching element K1 is axially between the third planetary gear set P3 and the fourth planetary gear set P4 arranged and lies radially in the region of the second element E24 of the fourth planetary gear set P4 , In contrast, the second switching element B1 axially between the second planetary gear set P2 and the third planetary gear set P3 provided and placed radially surrounding these.

As well as in 2 can be seen, are the third switching element B2 , the fourth switching element K2 and the fifth switching element K3 axially immediately adjacent to each other on one of the connection points Level 1-A the drive shaft LV1 facing away side of the fifth planetary gear set P5 intended. Accordingly, the third switching element lie B2 , the fourth switching element K2 and the fifth switching element K3 axially between the fifth planetary gear set P5 and the connection point GW2-A the output shaft GW2 , Concretely follows axially on the fifth planetary gear P5 first the fifth switching element K3 , then the fourth switching element K2 and finally, the third switching element B2 , Radial are the fifth switching element K3 and the fourth switching element K2 towards the third switching element B2 placed inwardly offset, which is radially surrounding the fifth planetary gear set P5 is arranged. Finally, there is the sixth switching element B3 axially on one of the connection points Level 1-A facing side of the first planetary gear set B1 provided, as well as arranged radially surrounding this.

In addition, goes out 3 a schematic representation of a transmission G according to a second embodiment of the invention, which in this case essentially according to the previous variant 2 equivalent. The only difference is that now additionally a power take-off PTO is provided, via which a drive of ancillaries is possible. The power take-off PTO is rotatably with the second element E21 of the first planetary gear set P1 and thus also with the drive shaft LV1 connected. Axial is the power take-off PTO between the first planetary gear set P1 and the sixth switching element B3 , Otherwise, the embodiment corresponds to 3 the previous variant 2 so that reference is made to what has been described.

4 shows a schematic view of a transmission G according to a third embodiment of the invention. Again, this design option corresponds again largely to the variant 2 , in contrast to the first element E11 of the first planetary gear set P1 now together with the first element E12 of the second planetary gear set P2 on the non-rotatable component GG is fixed. Accordingly, the first element becomes E11 of the first planetary gear set P1 permanently prevented from rotating. In contrast, the second element E21 of the first planetary gear set P1 no longer permanently rotatable with the second element E22 of the second planetary gear set P2 connected, but a non-rotatable connection is only by closing a sixth switching element K4 produced. The sixth switching element K4 is designed as a clutch and is located axially between the first planetary gear P1 and the second planetary gear set P2 and radially in the region of the third elements E31 and E32 of the first planetary gear set P1 and the second planetary gear set P2 , Otherwise, the design option corresponds to 4 according to the variant 2 so that reference is made to what has been described.

Furthermore goes out 5 a schematic representation of a transmission G according to a fourth embodiment of the invention, which also again largely the variant 2 equivalent. It is different, however, that the first element E11 of the first planetary gear set P1 together with the first element E12 of the second planetary gear set P2 constantly on the non-rotatable component GG is fixed. By contrast, the third element E31 of the first planetary gear set P1 no longer permanently rotatable with the first element E13 of the third planetary gear set P3 connected, but a non-rotatable connection is only by closing a sixth switching element K4 made, which is designed as a clutch. The sixth switching element K4 lies in the wheel plane of the first planetary gear set P1 and, accordingly, is axially substantially at the same height as the first planetary gear set P1 and arranged radially surrounding this. Otherwise, the embodiment corresponds to 5 according to the variant 2 so that reference is made to what has been described.

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

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

In 7 is an exemplary circuit diagram for the transmission G from the 2 to 6 tabulated. As can be seen, in each case a total of ten forward gears 1 to 10 , as well as three reverse gears R1 . R2 and R3 be realized, which is marked in the columns of the circuit diagram with an X respectively, which of the switching elements K1 . B1 . B2 . K2 . K3 and B3 respectively. K4 in which of the forward gears 1 to 10 and the reverse gears R1 . R2 and R3 each closed is. In each of the forward gears 1 to 10 and the reverse gears R1 . R2 and R3 are each three of the switching elements K1 . B1 . B2 . K2 . K3 and B3 respectively. K4 closed, with a successive circuit of the forward gears 1 to 10 , except for a second forward gear 2.2 and 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 7 can be seen, is a first forward gear 1 by actuating the first switching element K1 , the second switching element B1 and the fourth switching element K2 switched, starting from this, a second forward gear 2.1 is formed by the fourth switching element K2 opened and in the following the third switching element B2 is closed. Alternatively, but also a second forward gear 2.2 be represented by the second switching element B1 , the third switching element B2 and the sixth switching element B3 respectively. K4 be operated. There is also a second forward gear 2.3 by closing the second switching element B1 , the third switching element B2 and the fifth switching element K3 switchable, as well as a second forward gear 2.4 by actuating the second switching element B1 , the third switching element B2 and the fourth switching element K2 represented. Preference is given to the second forward gear 2.1 or 2.4 , to switch, since in both cases, only the switching state of two switching elements is to change for switching.

Furthermore, a third forward gear 3 switched by the first switching element K1 , the third switching element B2 and the fourth switching element K2 getting closed. Based on this results then a fourth forward gear 4 by opening the first switching element K1 and closing the sixth switching element B3 respectively. K4 , This results in a fifth forward gear 5 by opening the fourth switching element K2 and actuating the fifth switching element K3 , starting from this in a sixth forward gear 6 is switched by the fifth switching element K3 opened again and the first switching element K1 is closed.

To shift to a seventh forward gear 7 is then the third switching element in the following B2 to open and the fifth switching element K3 close. Furthermore, starting from the seventh forward gear 7 an eighth forward gear 8th by the fifth switching element K3 opened and the fourth switching element K2 is pressed. To further upshift into a ninth forward gear 9 is the first switching element below K1 to open and the fifth switching element K3 close. Furthermore, the ninth forward gear 9 in a tenth forward gear 10 switched by the sixth switching element B3 respectively. K4 in an unactuated state and then the first switching element K1 is transferred to an actuated state.

The first reverse R1 , in which a reverse drive of the motor vehicle even when driven by the internal combustion engine VKM can be realized, however, by closing the second switching element B1 , the fourth switching element K2 and the sixth switching element B3 respectively. K4 connected. In contrast, there is the second reverse gear R2 by actuating the first switching element K1 , the second switching element B1 and the fifth switching element K3 , Finally, the third reverse gear R3 by closing the second switching element B1 , the fifth switching element K3 and the sixth switching element B3 respectively. K4 being represented.

In the transmissions go out of the 2 to 6 can also have a first additional gear Z1 and a second additional gear Z2 are shown, which, however, not good in the translation series of the respective transmission G fit. This results in the first additional gear Z1 by closing the second switching element B1 , the fourth switching element K2 and the fifth switching element K3 while the second additional gear Z2 by actuating the first switching element K1 , the third switching element B2 and the fifth switching element K3 is representable.

As in the 2 to 6 is shown, the second switching element B1 designed as non-positive switching element. However, the second switching element could B1 Also be realized as a form-locking switching element, such as locking synchronization or as a claw switching element. Furthermore, the gears can also G according to the embodiments of 3 to 5 analogous to the variant according to 6 be hybridized.

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

K1

First switching element

B1

Second switching element

B2

Third switching element

K2

Fourth switching element

K3

Fifth switching element

B3

Sixth switching element

K4

Sixth switching element

1

First forward

2.1

Second forward speed

2.2

Second forward speed

2.3

Second forward speed

2.4

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

R3

Third reverse

Z1

First additional gear

Z2

Second additional gear

LV1

drive shaft

Level 1-A

junction

GW2

output shaft

GW2-A

junction

PTO

PTO

EM

electric machine

S

stator

R

rotor

AT

connecting shaft

K0

separating clutch

VKM

Internal combustion engine

TS

torsional vibration damper

AG

transaxles

DW

drive wheels

QUOTES INCLUDE IN THE DESCRIPTION

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

Cited patent literature

• DE 102015214217 A1 [0003]

Claims (15)

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 (K1), a second (B1), a third (B2), a fourth (K2), a fifth (K3) and a sixth switching element (B3; K4) are provided by their selective actuation different Force flow guides on the planetary gear sets (P1, P2, P3, P4, P5) under circuit of different gears (1 to 10, R1, R2, R3) between the drive shaft (GW1) and the output shaft (GW2) can be represented, characterized in that the drive shaft (GW1) rotatably connected to the second element (E22) of the second planetary gear set (P2) is in communication, the first element (E12) on a non-rotatable Bauele fixed (GG) and whose third element (E32) rotationally fixed to the first element (E14) of the fourth planetary gear set (P4) is connected, - that the second element (E24) of the fourth planetary gear set (P4) and the third element (E35) the fifth planetary gear set (P5) rotatably connected to each other and together via the first switching element (K1) rotatably connected to the first element (E13) of the third planetary gear set (P3), - that the second element (E23) of the third planetary gear set (P3 ) and the third element (E34) of the fourth planetary gear set (P4) rotatably connected to each other and by means of the second switching element (B1) on a non-rotatable component (GG) can be fixed, - that the first element (E15) of the fifth planetary gear set (P5) one on the third switching element (B2) on a non-rotatable component (GG) can be fixed and on the other by means of the fourth switching element (K2) rotationally fixed to the third element (E33) of the third Planetenradsat zes (P3) is connectable, - that the third element (E33) of the third planetary gear set (P3) also rotatably on the fifth switching element (K3) with the second element (E25) of the fifth planetary gear set (P5) is brought into connection rotatably is connected to the output shaft (GW2), - and that in the first planetary gear set (P1) a first coupling of the first element (E11) of the first planetary gear set (P1) with the non-rotatable component (GG), a second coupling of the second element (E21 ) of the first planetary gear set (P1) with the second element (E22) of the second planetary gear set (P2), as well as a third coupling of the third element (E31) of the first planetary gear set (P1) with the first element (E13) of the third planetary gear set (P3) consists of these couplings two couplings as permanent non-rotatable connections, while the remaining coupling a rotationally fixed connection by means of the sixth switching element (B3; K4) can be produced. Transmission (G) to Claim 1 , characterized in that the second element (E22) of the second planetary gear set (P2) is non-rotatably connected to the second element (E21) of the first planetary gear set (P1), the third element (E31) rotatably connected to the first element (E13) of the third Planetary gear set (P3) is in communication, wherein the first element (E11) of the first planetary gear set (P1) by means of the sixth switching element (B3) to a rotationally fixed component (GG) can be fixed. Transmission (G) to Claim 1 , characterized in that the first element (E13) of the third planetary gear set (P3) rotatably connected to the third element (E31) of the first planetary gear set (P1) is in communication, the first element (E11) is fixed to a non-rotatable component (GG) wherein the second element (E21) of the first planetary gear set (P1) via the sixth switching element (K4) rotatably connected to the second element (E22) of the second planetary gear set (P2) is connectable. Transmission (G) to Claim 1 characterized in that the second element (E22) of the second planetary gear set (P2) is non-rotatably connected to the second element (E21) of the first planetary gear set (P1) whose first element (E11) is fixed to a non-rotatable component (GG), wherein the third element (E31) of the first planetary gear set (P1) by means of the sixth switching element (K4) rotatably connected to the first element (E13) of the third planetary gear set (P3) is connectable. Transmission (G) according to one of the preceding claims, characterized in that a first forward gear (1) by operating the first (K1), the second (B1) and the fourth switching element (K2), a second forward gear (2.1) by operating the first (K1), the second (B1) and the third switching element (B2) or (2.2) by operating the second (B1), the third (B2) and the sixth switching element (B3; K4) or (2.3) by operating the second (B1), third (B2) and fifth shifting elements (K3) or (2.4) by operating the second (B1), third (B2) and fourth shifting elements (K2), a third forward speed (3) Actuating the first (K1), third (B2) and fourth switching elements (K2), a fourth forward speed (4) by operating the third (B2), fourth (K2) and sixth (B3; K4) switching elements fifth forward speed (5) by operating the third (B2), the fifth (K3) and the sixth shifting element (B3; K4), a sixth forward speed (6) by operating the first (K1), the third (B2) and the sixth A seventh forward gear (7) by operating the first (K1), the fifth (K3) and the sixth shifting element (B3; K4), an eighth forward speed (8) by actuating the first (K1), a ninth forward gear (9) by operating the fourth (K2), the fifth (K3) and the sixth shifting element (B3; K4), a tenth forward gear (10) of the fourth (K2) and the sixth shifting element (B3; K4) by actuating the first (K1), the fourth (K2) and the fifth shifting element (K3), a first reverse gear (R1) by actuating the second (B1), fourth (K2) and sixth switching elements (B3; K4), a second reverse gear (R2) by operating the first (K1), the second (B1) and the fifth shifting element (K3), and a third reverse gear (R3) by operating the second (B1), the fifth (K3) and the sixth switching element (B3; K4) is switchable. Transmission (G) according to one of the preceding claims, characterized in that a first additional gear (Z1) by pressing the second (B1), the fourth (K2) and the fifth switching element (K3), and a second additional gear (Z2) by pressing the first (K1), the third (B2) and the fifth switching element (K3) 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 (K1, B1, B2, K2, K3, B3, K1, B1, B2, K2, K3, K4) are each realized as non-positive switching element. Transmission according to one of the preceding claims, characterized in that the second switching element is realized as a positive switching element. Transmission (G) according to one of the preceding claims, characterized in that the drive shaft (GW1) is non-rotatably connected to a power take-off (PTO). 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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