DE102017207196A1 - Transmission for a motor vehicle - Google Patents

Abstract

The invention relates to a transmission (G) for a motor vehicle, wherein the transmission (G) has a drive shaft (GW1), an output shaft (GW2), a planetary gear set system (PS) with at least four shafts (W1, W2, W3, W4) and a additional planetary gear set (P1) and at least five switching elements (K1, B1, K2, K3, B2), wherein by selectively operating the at least five switching elements (K1, B1, K2, K3, B2) at least seven forward gears between the drive shaft (GW1) and the output shaft (GW2) are switchable, and drive train for a motor vehicle with such a transmission (G).

Description

The invention relates to a transmission for a motor vehicle, comprising a drive shaft and an output shaft, and a Planetenradsatzsystem with at least four shafts and an additional planetary gear, wherein a first, a second, a third, a fourth and a fifth switching element are provided by the selective Actuation different power flow guides on the Planetenradsatzsystem and the additional planetary gear set under different gears between drive shaft and output shaft can be displayed.

In the present case, a transmission is thus a multi-speed transmission, d. H. There are several different ratios as gears between the drive shaft and the output shaft of the transmission by operating corresponding switching elements switchable, this is preferably done automatically. Depending on the arrangement of the switching elements, these are clutches or brakes. Such transmissions are mainly used in motor vehicles to implement a traction power supply of a prime mover of the respective motor vehicle in terms of various criteria suitable.

From the US 7,442,145 B2 goes out a gearbox, which is composed of a planetary gear set and an additional planetary gear set. In this case, the planetary gearset four shafts are assigned, via which elements of the Planetenradsatzsystems are connected within the transmission. Further, the transmission comprises five switching elements, through the selective actuation of different power flow guides on the Planetenradsatzsystem and the at least one additional planetary gear set can be realized by switching different gears between the drive shaft and output shaft.

It is the object of the present invention to provide an alternative embodiment to the known from the prior art gearbox with a compact design as possible.

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 Planetenradsatzsystem with at least four shafts and an additional planetary gear. Furthermore, at least five switching elements are provided, through the selective actuation of which different power flow guides can be represented via the planetary gearset system and the additional planetary gear set with shifting of different gears between drive shaft and output shaft.

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, an orientation in the direction of an axis is meant, along which the Planetenradsatzsystem and the additional planetary gear are arranged coaxially to each other. The term "radial" is understood to mean an orientation in the diameter direction of a shaft lying on this axis.

The planetary gear set system and the additional planetary gear set are preferably arranged axially starting from a connection point of the drive shaft in the order of planetary gear set system and additional planetary gear set. Alternatively, following the connection point of the drive shaft, first the additional planetary gear set and then the planetary gear set system.

The invention now includes the technical teaching that the drive shaft is rotatably connected to the first shaft of the Planetenradsatzsystems, the second shaft via the first switching element rotatably connected to a third element of the additional planetary gear set, which further by means of the second switching element on a non-rotatable component can be fixed. Furthermore, the third shaft of the planetary gearset system can be non-rotatably connected via the third switching element to a first element of the additional planetary gear set, which can also be connected in rotation with the fourth shaft by means of the fourth switching element. Finally, the fourth wave of the Planetenradsatzsystems can still be set on the fifth switching element on the rotationally fixed component, whereas a second element of the additional planetary gear set is rotatably connected to the output shaft.

In other words, in the transmission according to the invention thus the drive shaft permanently rotatably connected to the first shaft of the Planetenradsatzsystems, while the output shaft constantly rotatably in communication with the second element of the additional planetary gear set.

Upon actuation of the first switching element, the second shaft of the Planetenradsatzsystems is rotatably connected to the third element of the additional planetary gear set, wherein the third element of the additional planetary gear set also fixed in the closed state of the second switching element on the rotationally fixed component and thus prevented from rotating. The third switching element connects in the actuated state, the third shaft of the Planetenradsatzsystems and the first element of the additional planetary gear rotatably together, while the fourth switching element in the closed state establishes a rotationally fixed connection of the fourth shaft of the Planetenradsatzsystems with the first element of the additional planetary gear set. Finally, even the fifth switching element in the actuated state, the fifth shaft of the Planetenradsatzsystems fixed to the rotationally fixed component and prevents the fifth wave so that a rotational movement.

The non-rotatable component of the transmission according to the invention is a permanently stationary component of the transmission, preferably a transmission housing or a part of such a transmission housing.

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

Depending on the axial arrangement of the planetary gear set system and the additional planetary gearset, the first shifting element is either provided axially on one side of the additional planetary gearset facing away from the drive shaft or lies axially in the area of the connection point of the drive shaft. By contrast, the second switching element is placed in particular in a gear plane of the additional planetary gear set and thus lies axially substantially at the height of and radially surrounding the additional planetary gear set.

In contrast, the third switching element and the fourth switching element are axially arranged in particular between the Planetenradsatzsystem and the additional planetary gear, wherein the fourth switching element is further preferably axially between the Planetenradsatzsystem and the third switching element. Furthermore, the third switching element and the fourth switching element in this case are provided axially directly adjacent to each other and radially substantially at the same height, so that a common supply would be conceivable here. The fifth shift element is placed in particular in the region of the planetary gearset system and thus at the same axial height as well as radially surrounding it.

A respective rotationally fixed connection of the rotatable elements of the planetary gear sets according to the invention preferably realized via one or more intermediate waves, which may be present in a spatially dense position of the elements as 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 each other in a rotationally fixed manner only by actuation of a respective switching element, a connection is likewise preferably realized via one or more intermediate waves.

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

According to one embodiment of the invention, the Planetenradsatzsystem has at least a first planetary gear, which is in mesh with both a first sun gear, which is rotatably connected to the second shaft, as well as with a first ring gear, which is non-rotatably in communication with the fourth shaft. In addition, the Planetenradsatzsystem has at least a second planetary gear meshing with a second ring gear, which is non-rotatably in communication with the first shaft. In this case, the at least one first planetary gear and the at least one second planetary gear are in meshing engagement with one another and are jointly guided over a planetary land of the Planetenradsatzsystems, which is rotatably connected to the third shaft.

The Planetenradsatzsystem is thus composed in this case of a sun gear, two ring gears and a planetary web, with a first sun gear and a first ring gear here preferably provided in a first axial gear plane and mesh with at least one first planet gear, while a second ring gear is placed in particular in a second axial gear plane and is in meshing engagement with at least one second planet gear. The planetary gears are guided together over the planetary gear of the planetary gear set system and are also meshed with each other.

In the present case, therefore, the Planetenradsatzsystem is functionally formed by two planetary gear sets, each designed as a minus planetary gear sets, the one planetary gear while no sun gear. The two planetary gear sets are preferably axially adjacent to each other, wherein the at least one planetary gear of the one planetary gear and the at least one planetary gear of the other planetary mesh with each other. In addition, the planet gears are guided rotatably supported via a common planetary web.

In a further development of the aforementioned embodiment, each one of the planet gears meshing with each other is extended axially into the region of the respective other planetary gear. Preferably, the respective planetary gear is executed extended axially, which is associated with the translation stage of the Planetenradsatzsystems with the smaller stand translation.

In such a transmission seven forward gears can be realized by selectively closing three switching elements. In this case, a first forward gear is switched by operating the second, the third and the fifth shift element, while a second forward gear is formed by closing the second, the third and the fourth shift element. Further, a third forward speed results by operating the first, second and third shift elements, whereas a fourth forward speed is switchable by operating the first, second and fourth shift elements. Further, a fifth forward speed can be represented by closing the first, the third and the fourth shift element, wherein the first, the fourth and the fifth shift element are to be actuated for the circuit of a sixth forward gear. In addition, there is a seventh forward gear by actuating the first, the third and the fifth switching element.

With a suitable choice of stationary gear ratios of the Planetenradsatzsystems and the additional planetary gear set a suitable for the application in the field of a motor vehicle translation series is realized. For a sequential shift of the forward gears according to their order is always the state of two switching elements to vary by one of the switching elements involved in the previous forward gear to open and another switching element to represent the subsequent forward gear is close. This then has the consequence that a shift between the courses can proceed very quickly.

According to one embodiment of the invention, the planetary gear set system is also associated with a fifth shaft, which can be rotatably connected by means of a sixth switching element with the third element of the additional planetary gear set. In other words, in this case, the planetary gear set system has a total of five shafts, wherein the fifth shaft can be connected in rotation with the third element of the additional planetary gear set by closing a sixth switching element. The designed as a coupling, the sixth switching element is in this case preferably provided axially on one of the connection point of the drive shaft facing away side of the additional planetary gear, wherein it is further preferably immediately adjacent to the first switching element. The first switching element and the sixth switching element are also preferably arranged radially at the same height, wherein the first switching element is located axially between the additional planetary gear and the sixth switching element. Due to this spatial arrangement, a common supply of the first switching element and the sixth switching element could be realized.

In a further development of the aforementioned refinement possibility, the fifth shaft is then non-rotatably connected to a second sun gear of the planetary gear set system, wherein the second sun gear is in meshing engagement with the at least one second planet gear. In this variant, the planetary gear set system is then composed of two sun gears, two ring gears and a planet carrier, which rotatably supports the at least one first planet gear and the at least one second planet gear. The at least one second planetary gear is then in meshing engagement both with the radially surrounding, second ring gear, as well as the radially inner second sun gear.

In a designed according to the aforementioned embodiment possibility gearbox eight forward gears, two reverse gears and an additional gear can be realized by selectively closing each of three switching elements. Thus, a first forward gear results by actuating the second, the fourth and the sixth shift element, while a second forward gear can be shifted by closing the second, the third and the fifth shift element. In addition, a third forward gear by closing the second, the third and the fourth switching element formed, whereas for the representation of a fourth forward gear, the first, the second and the third switching element are to be actuated. Furthermore, a fifth forward gear results by actuating the first, the second and the fourth shift element, while a sixth forward gear is shown in a first variant by closing the first, the third and the fourth shift element. Alternatively, in a second variant, a sixth forward gear can also be activated by actuating the third, fourth and sixth shifting element, in a third variant by closing the first, the third and the sixth shifting element, and in a fourth variant by actuating the first, the fourth and the sixth switching element.

A seventh forward speed is obtained by operating the first, fourth and fifth shift elements, while for the representation of an eighth forward speed, the first, third and fifth shift elements are to be closed. A first reverse gear may be formed by closing the third, fifth and sixth shift elements, whereas a second reverse gear is engaged when the fourth, fifth and sixth shift elements are closed. In addition, an additional gear can be formed by the second, the third and the sixth switching element are actuated, this additional gear does not fit optimally in the rest of the translation series.

Advantageously, in addition to the eight forward gears and two reverse gears can be realized, in which a reversing of the motor vehicle takes place when driven via a drive upstream of the transmission engine.

It is a further embodiment of the invention that the additional planetary gear is present as a minus planetary gear, wherein it is a sun gear in the first element of the additional planetary gear, in the second element of the additional planetary gear around a planet and the third element of the additional planetary gear is a ring gear. A minus planetary set is composed in a manner known in principle to the person skilled in the art from the elements sun gear, planet carrier and ring gear, wherein the planet carrier at least one, but preferably several planetary gears leads, in each case both with the sun gear, as well as the surrounding ring gear comb.

Alternatively, the additional planetary gearset but could also be present as a plus-planetary gear set, wherein it is a sun gear at the first element of the additional planetary gear, a ring gear at the second element of the additional planetary gear and a planetary gear at the third element of the additional planetary gearset is. 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.

Where there is a connection of the individual elements, a minus planetary gear set can be converted into a plus-planetary gear set, in which case compared to the design as a minus planetary gear set the Hohlrad- and the Planetensteganbindung to swap with each other, and a 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 transmission gear ratio reduced by one. Preferably, however, the additional planetary gear set is designed as a minus planetary gear set.

In a further development of the invention, one or more switching elements are each realized as non-positive switching elements. Non-positive switching elements have the advantage that they can be switched under load, so that a change between the courses without interruption of traction is enforceable. The second switching element can also be designed as a positive switching element, such as a dog clutch or lock synchronization. Because the second switching element is involved in the representation of the first to fourth or the first to fifth forward gear, so that ultimately only one opening takes place 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 output shaft has a toothing, via which the output shaft is in operative connection with a differential gear disposed axially parallel to the output shaft. Here, the toothing is preferably provided at a connection point of the output shaft, said connection point of the output shaft is preferably axially located at the same axial end of the transmission, as the junction of the drive shaft. Alternatively, a connection point of the output shaft but also axially be provided at an opposite end of the transmission.

In a development of the invention, an electric machine is provided whose rotor is connected to the drive shaft, one of the shafts, one of the elements of the additional planetary gear set or to the output shaft. Preferably, then a stator of the electric machine is rotatably connected to the non-rotatable component of the transmission. In addition, the electric machine can in this case in particular be operated by an electric motor and / or as a generator in order to realize different functions. In particular, a purely electric driving, a boosting via the electric machine, a deceleration and recuperation and / or a synchronization in the transmission via the electric machine can be performed. The rotor of the electric machine can be coaxial with the respective component or be arranged offset in relation to this, 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 or belt 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. Alternatively, however, a separate starting clutch may 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 a differential gear 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 differential gear 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 context of the invention a permanent connection of the latter Components, so that they can not rotate independently. In this respect, no switching element is provided between these components, in which it may be elements of the planetary gear sets and / or shafts and / or a non-rotatable component of the transmission, but the corresponding components are rigidly coupled together.

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

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

• 1 eine schematische Ansicht eines Kraftfahrzeugantriebsstranges, in welchem ein erfindungsgemäßes Getriebe zur Anwendung kommt;
• 2 eine schematische Ansicht eines Getriebes entsprechend einer ersten Ausführungsform der Erfindung;
• 3 eine schematische Darstellung eines Getriebes gemäß einer zweiten Ausgestaltungsmöglichkeit der Erfindung;
• 4 eine schematische Ansicht eines Getriebes entsprechend einer dritten Ausführungsform der Erfindung;
• 5 eine schematische Darstellung eines Getriebes gemäß einer vierten Ausgestaltungsmöglichkeit der Erfindung;
• 6 eine schematische Ansicht eines Getriebes entsprechend einer fünften Ausführungsform der Erfindung;
• 7 ein beispielhaftes Schaltschema der Getriebe aus den 2 bis 6;
• 8 eine schematische Ansicht eines Getriebes entsprechend einer sechsten Ausführungsform der Erfindung; und
• 9 ein beispielhaftes Schaltschema des Getriebes aus 8.

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

• 1 a schematic view of a motor vehicle drive train, in which a transmission according to the invention is used;
• 2 a schematic view of a transmission according to a first embodiment of the invention;
• 3 a schematic representation of a transmission according to a second embodiment of the invention;
• 4 a schematic view of a transmission according to a third embodiment of the invention;
• 5 a schematic representation of a transmission according to a fourth embodiment of the invention;
• 6 a schematic view of a transmission according to a fifth embodiment of the invention;
• 7 an exemplary circuit diagram of the transmission of the 2 to 6 ;
• 8th a schematic view of a transmission according to a sixth embodiment of the invention; and
• 9 an exemplary circuit diagram of the transmission 8th ,

1 shows a schematic view of a motor vehicle drive train, in which an internal combustion engine VKM via an intermediate torsional vibration damper TS with a gear G connected is. The transmission G on the output side is a differential gear 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 gear housing, in which then the differential gear 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 differential gear AG aligned transversely to a 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 planetary gear set system PS and an additional planetary gear set P1 , wherein the Planetenradsatzsystem PS from a first sun wheel SO1 , at least one first planetary gear PR1 a first ring gear HO1 , at least one second planetary gear PR2 , a second ring gear HO2 and a planetary bridge PG composed.

As in 2 It can be seen, are the planetary gears PR1 and PR2 together over the planetary bridge PG rotatably mounted, wherein the at least one first planetary gear PR1 in a first axial wheel plane I both with the radially inner, first sun gear SO1 , as well as with the radially surrounding, the first ring gear HO1 is in meshing. In contrast, the at least one second planetary gear mesh PR2 in a second axial gear plane II only with the radially surrounding second ring gear HO2 , a sun gear is not provided here. In this case, form the first ring gear HO1 that has at least one first planetary gear PR1 and the first sun wheel SO1 a first gear stage, which has a higher stationary gear ratio, as a second gear stage, which by the second ring gear HO2 and the at least one second planetary gear PR2 is formed.

Furthermore, the planet gears PR1 and PR2 also with each other in tooth engagement by the at least one second planetary gear PR2 axially in the region of the at least one first planetary gear PR1 is extended. The planetary gear set system becomes purely functional PS So formed by two planetary gear sets, which are designed as minus planetary gear sets and of which a planetary gear set is executed without sun gear.

The additional planetary gear set P1 is made up of a first element E11 , a second element E21 and a third element E31 together, the first element E11 by a sun wheel SO3 , the second element E21 through a planetary bridge PG3 and the third element E31 through a ring gear HO3 is formed. In this respect, the additional planetary gear set P1 in the present case designed as a minus planetary gear set, in which the planet web PG3 a, but preferably more planet gears PR3 rotatably mounted, which in detail with the radially inner sun gear SO3 and also with the surrounding ring gear HO3 in mesh.

Where it allows the connection, the additional planetary gear set could P1 but also be executed as a plus-planetary gear set. Compared to a version as a minus planetary gear set would then have the second element in a plus-planetary gear set E21 through the ring gear and the third element E31 formed by the planetary ridge and also a respective Getriebestandübersetzung be increased by one.

As in 2 can be seen, includes the gearbox G a total of five switching elements in the form of a first switching element K1 , a second switching element B1 , a third switching element K2 , a fourth switching element K3 and a fifth switching element B2 , Here are the switching elements K1 . B1 . K2 . K3 and B2 each designed as non-positive switching elements and are preferably before as lamella switching elements. In addition, the first switching element K1 , the third switching element K2 and the fourth switching element K3 designed here as couplings, while the second switching element B1 and the fifth switching element B2 as brakes.

The planetary gear set system PS are four waves W1 . W2 . W3 and W4 assigned, of which the first wave W1 within the planetary gear set system PS rotatably with the second ring gear HO2 connected is. Also within the planetary gear set system PS is the second wave W2 rotatable with the first sun gear SO1 in contact while the third wave W3 rotatably with the planetary bridge PG connected is. On the other hand, there is the fourth wave W4 rotatably with the first ring gear HO1 in connection.

Outside the planetary gear set system PS is the first wave W1 rotatably with a drive shaft GW1 of the transmission G connected, wherein the drive shaft GW1 and the first shaft W1 of the planetary gear set system PS can also be configured in one piece. Due to the rotationally fixed connection with the drive shaft GW1 is also the second ring gear HO2 permanently non-rotatably connected to drive shaft GW1. Furthermore, the second wave W2 of the planetary gear set system PS over the first switching element K1 non-rotatable with the third element E31 of the additional planetary gear set P1 be connected, the third element E31 of the additional planetary gear set P1 also still by closing the second switching element B1 on a non-rotatable component GG can be fixed, which is preferably the transmission housing of the transmission G or part of the transmission housing.

As well as in 2 It can be seen, the third wave W3 of the planetary gear set system PS over the third switching element K2 non-rotatable with the first element E11 of the additional planetary gear set P1 be associated with which also the fourth wave W4 of the planetary gear set system PS by closing the fourth switching element K3 rotatably connected. In addition, the fourth wave W4 of the planetary gear set system by closing the fifth switching element B2 on the non-rotatable component GG be fixed. Finally, there is the second element E21 of the additional planetary gear set P1 permanently rotationally fixed with an output shaft GW2 of the transmission G connected.

Both the drive shaft GW1, and the output shaft GW2 each form a connection point Level 1-A respectively. GW2-A out, with the connection point Level 1-A in the motor vehicle drive train 1 a connection to the internal combustion engine VKM serves while the gearbox G at the junction GW2-A with the following differential gear AG connected is. While the junction Level 1-A the drive shaft GW 1 while at an axial end of the transmission G is configured, is the junction GW2-A axially between the planetary gear set system PS and the additional planetary gear set P1 , where the output shaft GW2 with her connection point GW2-A here across the junction Level 1-A the drive shaft GW1 is aligned.

The additional planetary gear set P1 and the planetary gear set system PS are on the connection point Level 1-A axially following the drive shaft GW1 in the order of planetary gearset system PS and additional planetary gear set P1 arranged.

As in 2 can be seen, is the first switching element K1 axially on one of the connection points Level 1-A the drive shaft GW1 facing away from the additional planetary gear set P1 provided while the second switching element B1 in a wheel plane of the additional planetary gear set P1 lies and thus axially substantially at the height of and radially surrounding the additional planetary gear P1 is arranged.

The third switching element K2 and the fourth switching element K3 are axial between the planetary gear set system PS and the additional planetary gear set P1 provided, wherein the fourth switching element K3 in this case axially between the Planetenradsatzsystem PS and the third switching element K2 lies. Radial are the third switching element K2 and the fourth switching element K3 essentially at the same height and radially surrounding the first ring gear HO1 , wherein due to the juxtaposition of the third switching element K2 and the fourth switching element K3 a common supply of the two switching element K2 and K3 it is possible. By contrast, the fifth switching element B2 in the first wheel plane I provided and thus lies axially substantially in the region of the first sun gear SO1 and the first ring gear HO1 and radially surrounding these.

The connection point GW2-A the output shaft GW2 is also axially between the third switching element K2 and the additional planetary gear set P1 intended.

Out 3 is a schematic representation of a transmission G according to a second 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 connected to the drive shaft GW1. Furthermore, the drive shaft GW1 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 GW1 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 3 according to the variant 2 so that reference is made to what has been described.

Further shows 4 a schematic view of a transmission G according to a third embodiment of the invention, which thereby largely the previous variant 3 equivalent. The difference is that the electric machine EM not coaxial, but off-axis to the drive shaft LV1 is arranged. As a result, a - not shown in detail here - rotor of the electric machine EM and the drive shaft LV1 not rotatably connected to each other, but via an intermediate spur gear SRS coupled together. This is a spur gear SR1 the spur gear stage SRS rotatably on the drive shaft LV1 placed and combs with a spur gear SR2 , which rotatably on an input shaft EW the electric machine EM is arranged. This input shaft EW then puts inside the electric machine EM the connection to the rotor. Otherwise, the embodiment corresponds to 4 according to the variant 3 so that reference is made to what has been described.

Moreover, in 5 a schematic representation of a transmission G according to a fourth embodiment of the invention, which also again essentially according to the variant 3 equivalent. As in the embodiment according to 4 but is the electric machine EM not coaxial, but off-axis to the drive shaft LV1 placed. A non-rotatable coupling between the drive shaft LV1 and a - not shown - rotor of the electric machine EM is via a traction drive ZT realized, which is preferably present as a chain drive. This traction drive ZT coupled thereby the drive shaft LV1 with an input shaft EW the electric machine EM , Otherwise, the variant corresponds to 5 the embodiment according to 3 so that reference is made to what has been described.

Further shows 6 a schematic view of a transmission G according to a fifth embodiment of the invention. This embodiment also largely corresponds to the variant 2 , in contrast to the planetary gear set system PS and the additional planetary gear set P1 are arranged axially in a modified manner. So follows axially to the junction Level 1-A the drive shaft LV1 first the additional planetary gear set P1 and first then the planetary gear set system PS , in which case the wheel plane II of the planetary gear set system PS the connection point Level 1-A the drive shaft LV1 facing. This also has the consequence that the connection point GW2-A the output shaft GW2 is provided at the same axial end as the connection point Level 1-A the drive shaft LV1 , Likewise, now is the first switching element K1 at the same axial end of the transmission G provided as the connection point LV1 -A. With regard to the connection of the individual components of the transmission G and also otherwise the possibility of design corresponds to 6 otherwise the variant 2 so that reference is made to what has been described.

In 7 is an exemplary circuit diagram for the respective transmission G from the 2 to 5 tabulated. As can be seen, in each case a total of seven forward gears 1 to 7 can be realized, wherein in the columns of the circuit diagram is marked with an X respectively, which of the switching elements K1 . B1 . K2 . K3 and B2 in which of the forward gears 1 to 7 each is closed. In each of the forward gears 1 to 7 are each three of the switching elements K1 . B1 . K2 . K3 and B2 closed, in each case one of the involved switching elements to open at a successive circuit of the forward gears 1 to 7 and another switching element is to close below.

As in 7 can be seen, a first forward gear 1 by pressing the second switching element B1 , the third switching element K2 and the fifth switching element B2 switched, starting from this, a second forward gear 2 is formed by the fifth switching element B2 opened and in the following the fourth switching element K3 is closed. In addition, then in a third forward gear 3 be switched by the fourth switching element K3 opened and the first switching element K1 is closed. Based on this results in a fourth forward gear 4 by opening the third switching element K2 and closing the fourth switching element K3 , Subsequently, a fifth forward gear 5 by opening the second switching element B1 and closing the third switching element K2 be switched from this, starting in a sixth forward gear 6, by the third switching element K2 opened again and the fifth switching element B2 is closed. To shift to a seventh forward gear 7 is then the fourth switching element K3 to open and the third switching element K2 close.

Finally shows 8th a schematic view of a transmission G according to a sixth embodiment of the invention, which in turn largely the variant according to 2 equivalent. It is different, however, that the planetary gear set PS now a second sun wheel SO2 which is in the second wheel plane II is provided and with the at least one second planetary gear PR2 combs. In addition, the planetary gear set is PS now a fifth wave W5 associated with which the second sun gear SO2 is rotatably connected and the means of a sixth switching element K4 non-rotatable with the third element E31 of the additional planetary gear set P1 can be associated. The designed as a clutch, the sixth switching element K4 is axially adjacent to the first switching element K1 provided and is radially substantially at the same height as the first switching element K1 , Specifically, the first switching element K1 while axially between the additional planetary gear P1 and the sixth switching element K4 arranged. Due to the adjacent placement of the two switching elements K1 and K4 they could be supplied via a common supply line. Otherwise, the embodiment corresponds to 8th according to the variant 2 so that reference is made to what has been described.

In 9 is still an exemplary circuit diagram for the transmission G out 8th tabulated. There are a total of eight forward gears 1 to 8, two reverse gears R1 and R2 and an additional gear ZG be realized, which is marked in the columns of the circuit diagram with an X respectively, which of the switching elements K1 . B1 . K2 . K3 . B2 and K4 in which of the forward gears 21 to 28, the reverse gears R1 and R2 and the additional gear ZG each is closed. In each of the gears are each three of the switching elements K1 . B1 . K2 . K3 . B2 and K4 closed, wherein at a successive circuit of the forward gears 21 to 28, except for a circuit of a first forward gear 21 in a second forward gear 22 and circuits in a sixth forward gear 26.2 and in a sixth forward gear 26.3, each one of the involved switching elements to open and another switching element is to be concluded in the following.

As in 9 can be seen, the first forward gear 21 by operating the second switching element B1 , the fourth switching element K3 and the sixth switching element K4 connected, starting from this, the second forward gear 22 is formed by the fourth switching element K3 and the sixth switching element K4 opened and in the following the third switching element K2 and the fifth switching element B2 getting closed. In addition, then can be switched to a third forward gear 23 by the fifth switching element B2 opened and the fourth switching element K3 is closed. Proceeding from this, a fourth forward gear 24 then results by opening the fourth shift element K3 and closing the first switching element K1 , Subsequently, a fifth forward gear 25 by opening the third switching element K2 and closing the fourth switching element K3 be switched from this, starting in a sixth forward gear 26.1, by the second switching element B1 opened and the third switching element K2 is closed. Alternatively, a sixth forward gear 26.2 may also be actuated by actuating the third shift element K2 , the fourth switching element K3 and the sixth switching element K4 being represented. Further alternatively, a sixth forward gear 26.3 results by closing the first switching element K1 , the third switching element K2 and the sixth switching element K4 or a sixth forward gear 26.4 by operating the first switching element K1 , the fourth switching element K3 and the sixth switching element K4 ,

To shift a seventh forward gear 27 are the first switching element K1 , the fourth switching element K3 and the fifth switching element B2 to conclude, starting from this, in an eighth forward gear 28 is transitioned by the fourth switching element K3 in an unactuated and the third switching element K2 is transferred to an actuated state.

As in 9 can be seen, is a first reverse gear R1 by closing the third switching element K2 , the fifth switching element B2 and the sixth switching element K4 switched while a second reverse gear R2 by actuating the fourth switching element K3 , the fifth switching element B2 and the sixth switching element K4 results. The additional gear ZG can by closing the second switching element B1 , the third switching element K2 and the sixth switching element K4 However, this does not fit optimally in the rest of the translation series.

As in the 2 to 6 and 8th 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.

Also the variants of the transmission G according to the 6 and 8th can according to one of the variants of 3 to 5 with an electric machine EM be provided. In addition, the variants after 6 and after 8th be combined with each other.

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

Additional planetary gear set

E11

First element of the additional planetary gear set

E21

Second element of the additional planetary gear set

E31

Third element of the additional planetary gear set

SO3

sun

PG3

planet spider

PR3

planet

HO3

ring gear

PS

Planetenradsatzsystem

SO1

first sun gear

SO2

second sun wheel

PG

planet spider

PR1

first planetary gear

PR2

second planetary gear

HO1

first ring gear

HO2

second ring gear

W1

first wave

W2

second wave

W3

third wave

W4

fourth wave

W5

fifth wave

I

first wheel plane

II

second wheel plane

K1

First switching element

B1

Second switching element

K2

Third switching element

K3

Fourth switching element

B2

Fifth switching element

K4

Sixth switching element

1, 21

First forward

2, 22

Second forward speed

3, 23

Third forward

4, 24

Fourth forward

5, 24

Fifth forward speed

6

Sixth forward

26.1

Sixth forward

26.2

Sixth forward

26.3

Sixth forward

26.4

Sixth forward

7, 27

Seventh forward

28

Eighth forward

R1

First reverse

R2

Second reverse

ZG

additional transition

GW 1

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

SRS

spur gear

SR1

spur gear

SR2

spur gear

EW

input shaft

ZT

traction drive

VKM

Internal combustion engine

TS

torsional vibration damper

AG

differential gear

DW

drive wheels

QUOTES INCLUDE IN THE DESCRIPTION

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

Cited patent literature

• US 7442145 B2 [0003]

Claims (15)

Transmission (G) for a motor vehicle, comprising a drive shaft (GW1) and an output shaft (GW2), and a planetary gear set (PS) with at least four shafts (W1, W2, W3, W4) and an additional planetary gear set (P1), wherein a a first (K1), a second (B1), a third (K2), a fourth (K3) and a fifth switching element (B2) are provided by their selective actuation different power flow guides on the planetary gear set (PS) and the additional planetary gear set (P1 ) can be represented by switching different gears between drive shaft (GW1) and output shaft (GW2), characterized in that - the drive shaft (GW1) is connected in a rotationally fixed manner to the first shaft (W1) of the planetary gearset system (PS) whose second shaft (W2) via the first switching element (K1) rotatably connected to a third element (E31) of the additional planetary gear set (P1) is connected, which further by means of the second switching element (B1) on a non-rotatable Baueleme nt (GG) can be fixed, - that the third shaft (W3) of the Planetenradsatzsystems (PS) via the third switching element (K2) rotatably connected to a first element (E11) of the additional planetary gear set (P1) is connected, which also means of the fourth switching element (K3) rotatably connected to the fourth shaft (W4) is brought into connection, - that the fourth shaft (W4) of the planetary gearset system (PS) further via the fifth switching element (B2) on the non-rotatable component (GG) can be fixed, - and that second element (E21) of the additional planetary gear set (P1) rotatably connected to the output shaft (GW2) is connected. Transmission (G) to Claim 1 , characterized in that the Planetenradsatzsystem (PS) at least one first planetary gear (PR1), which is connected both with a first sun gear (SO1), which is non-rotatably connected to the second shaft (W2), as well as with a first ring gear (HO1) is in meshing engagement, which is non-rotatably in communication with the fourth shaft (W4), wherein the Planetenradsatzsystem (PS) also has at least one second planetary gear (PR2) which meshes with a second ring gear (HO2), which rotatably with the first shaft (W1) is in communication, and wherein the at least one first planetary gear (PR1) and the at least one second planetary gear (PR2) mesh with each other and together over a planetary web (PG) of the Planetenradsatzsystems (PS) are guided, which rotatably with the third wave (W3) is connected. Transmission (G) to Claim 2 , characterized in that in each case one of the meshing with each other planetary gears (PR1, PR2) is extended axially into the region of the respective other planetary gear (PR1). Transmission (G) according to one of the preceding claims, characterized in that - a first forward gear (1) by operating the second (B1), the third (K2) and the fifth switching element (B2), - a second forward gear (2) Actuating the second (B1), the third (K2) and the fourth switching element (K3), - a third forward gear (3) by operating the first (K1), the second (B1) and the third switching element (K2), - a fourth forward speed (4) by operating the first (K1), the second (B1) and the fourth shift element (K3), - a fifth forward speed (5) by operating the first (K1), the third (K2) and the fourth shift element (K3), - a sixth forward gear (6) by operating the first (K1), the fourth (K3) and the fifth shifting element (B2), - and a seventh forward gear (7) by operating the first (K1), the third (K2) and the fifth switching element (B2) is switchable. Transmission (G) according to one of Claims 1 to 3 , in that the Planetenradsatzsystem (PS) also a fifth shaft (W5) is assigned, which by means of a sixth switching element (K4) rotatably connected to the third element (E31) of the additional planetary gear set (P1) is connectable. Transmission (G) to Claim 5 and one of the Claims 2 or 3 , characterized in that the fifth shaft (W5) is non-rotatably connected to a second sun gear (SO2) of the Planetenradsatzsystems (PS), wherein the second sun gear (SO2) with the at least one second planet gear (PR2) is in meshing engagement. Transmission (G) to Claim 5 or 6 characterized in that - a first forward gear (21) by operating the second (B1), the fourth (K3) and the sixth shifting element (K4), - a second forward gear (22) by operating the second (B1), the third (K2) and the fifth shift element (B2), - a third forward gear (23) by operating the second (B1), the third (K2) and the fourth shift element (K3), - a fourth forward gear (24) by operating the first (K1), the second (B1) and the third shift element (K2), - a fifth forward gear (25) by operating the first (K1), the second (B1) and the fourth shift element (K3), - a sixth forward gear ( 26.1) by actuating the first (K1), the third (K2) and the fourth switching element (K3) or (26.2) by actuating the third (K2), the fourth (K3) and the sixth Switching element (K4) or (26.3) by actuating the first (K1), the third (K2) and the sixth switching element (K4) or (26.4) by actuating the first (K1), the fourth (K3) and the sixth switching element ( K4), - a seventh forward gear (27) by operating the first (K1), the fourth (K3) and the fifth switching element (B2), - an eighth forward gear (28) by operating the first (K1), the third (K2 ) and the fifth shift element (B2), - a first reverse gear (R1) by actuating the third (K2), the fifth (B2) and the sixth shift element (K4), - and a second reverse gear (R2) by operating the fourth ( K3), the fifth (B2) and the sixth switching element (K4). Transmission (G) according to one of the preceding claims, characterized in that the additional planetary gear set (P1) is in the form of a minus planetary gear set, wherein the first element (E11) of the additional planetary gear set (P1) is a sun gear (SO3) the second element (E21) of the additional planetary gearset (P1) is a planetary gear (PG3) and the third element (E31) of the additional planetary gearset (P1) is a ring gear (HO3). Transmission to one of the Claims 1 to 7 , characterized in that the additional planetary gear set is present as a plus-planetary gear set, wherein it is a sun gear in the first element of the additional planetary gear, a ring gear in the second element of the additional planetary gear set and a planet gear in the third element of the additional planetary gear set , Transmission (G) according to one of the preceding claims, characterized in that one or more switching elements (K1, B1, K2, K3, B2, K1, B1, K2, K3, B2, 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 output shaft (GW2) has a toothing, via which the output shaft (GW2) with an axially parallel to the output shaft (GW2) arranged differential gear (AG) is in operative connection. Transmission (G) according to one of the preceding claims, characterized in that an electric machine (EM) is provided, whose rotor (R) is connected to the drive shaft (GW1), one of the shafts (W1 to W4; W1 to W5), one of the elements (E11, E21, E31) of the additional planetary gear set (P1) or with the output shaft (GW2) is connected. 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 ,

Images