DE102017207189A1 - 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 gearset system (PS) with five shafts (W1, W2, W3, W4, W5) and an 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 eight 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 planetary gearset system with five shafts and an additional planetary gear, wherein a first, a second, a third, a fourth and a fifth switching element are provided by their selective actuation different power flow guides on the planetary gearset and the additional planetary gear set with different gears between drive shaft and output shaft are represented.

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 AT 15018 U2 goes out a gearbox, which is composed of a planetary gear set and an additional planetary gear set. The Planetenradsatzsystem are assigned five waves, via which elements of the Planetenradsatzsystems are connected within the transmission. Furthermore, the transmission comprises in a variant of AT 15018 U2 five switching elements, the selective actuation of different power flow guides on the Planetenradsatzsystem and the 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 14.

According to the invention, a transmission comprises a drive shaft and an output shaft, and a five-shaft planetary gear set system and an additional planetary gear set. 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 Planetenradsatzsystem and the additional planetary gear set are preferably, starting from a junction of the drive shaft, axially arranged in the order additional planetary gear and planetary gear set. 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 via the first switching element can be rotatably connected to the first shaft of the Planetenradsatzsystems whose second shaft can be fixed by means of the second switching element to a non-rotatable component. Further, the third shaft of the Planetenradsatzsystems can be rotatably connected via the third switching element with the output shaft in connection, which can also be rotatably connected by means of the fourth switching element with the fourth shaft of the Planetenradsatzsystems. Furthermore, in the additional planetary gear set, there is a first coupling of a first element of the additional planetary gear set with the rotationally fixed component, a second coupling of a second element of the additional planetary gear set with the fifth shaft of the Planetenradsatzsystems, and a third coupling of a third element of the additional planetary gear set with the drive shaft , Of these couplings are two couplings as permanent non-rotatable compounds before, while the remaining coupling a rotationally fixed connection can be made via the fifth switching element.

In other words, in the transmission according to the invention thus when driving the first switching element, the drive shaft rotatably connected to the first shaft of the Planetenradsatzsystems, while the second switching element fixed in the closed state, the second shaft of the Planetenradsatzsystems to the rotationally fixed component. Upon actuation of the third switching element, the third shaft of the Planetenradsatzsystems and the output shaft of the transmission are rotatably connected to each other, whereas in the closed state of the fourth switching element, a rotationally fixed connection of the output shaft to the fourth shaft of the Planetenradsatzsystems is made.

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

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

In the transmission according to the invention, the second switching element is designed as a brake which brakes when stopped, the second shaft of the planetary gearset system to a standstill and fixed to the rotationally fixed 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. The fifth switching element is designed either as a brake or as a clutch, depending on the rotatable connection to be made.

Preferably, the first switching element is arranged axially at the height of the planetary gear set system and radially surrounding this. By contrast, the second switching element, the third switching element and the fourth switching element are axially provided in particular on one of the junction of the drive shaft side facing away from the Planetenradsatzsystems, in which case the third switching element adjacent to the Planetenradsatzsystem and then axially follow the fourth switching element and then the second switching element , More preferably, the third switching element and the fourth switching element are placed axially directly adjacent to each other, wherein the third switching element is offset radially inwardly relative to the fourth switching element. Due to this spatial arrangement, a common supply of the third switching element and the fourth switching element could therefore 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 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 first shaft. In addition, the Planetenradsatzsystem has at least a second planetary gear, which meshes both with a second sun gear, which is rotatably connected to the third shaft, as well as with a second ring gear, which rotatably with the fourth wave in Connection stands. In this case, the at least one first planetary gear and the at least one second planetary gear mesh with each other and are guided together via a planetary web of the Planetenradsatzsystems, which is rotatably connected to the fifth shaft.

The Planetenradsatzsystem is thus composed in this case of two sun gears, two ring gears and a planetary land, wherein a first sun gear and a first ring gear are preferably provided in a first axial gear plane and mesh with at least one first planetary gear while a second ring gear and a second sun gear are placed in particular in a second axial gear plane and are 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 in pairs meshed with each other. Particularly preferred are several first planetary gears and accordingly also a plurality of second planetary gears provided.

In the present case, therefore, the Planetenradsatzsystem is functionally formed by two planetary gear sets, which are each designed as a minus planetary gear sets. The two planetary gear sets are preferably axially adjacent to each other, wherein the at least one planetary gear of a planetary gear and the at least one planetary gear of the other planetary gear mesh in pairs 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 the present case, this is in particular the at least one first planetary gear of the planetary gear set system.

According to one embodiment of the invention, the fifth shaft of the planetary gearset system is non-rotatably connected to the second element of the additional planetary gear set, whose third element is non-rotatably in communication with the drive shaft. In addition, the first element of the additional planetary gear set can be fixed via the fifth switching element on the rotationally fixed component.

In this case, therefore, the second element of the additional planetary gear set is permanently non-rotatably connected to the fifth shaft of the Planetenradsatzsystems, while the drive shaft is constantly rotatably in communication with the third element of the additional planetary gear set. The fifth switching element sets when actuated, the first element of the additional planetary gear set on the non-rotatable component and prevents this as a result of a rotational movement. In this case, the fifth shifting element designed as a brake is preferably provided axially on one side of the planetary gearset system facing away from the drive shaft and is furthermore preferably axially immediately adjacent to the second shifting element at the axial end of the transmission. In this respect, a common supply of the second switching element and the fifth switching element could be realized here.

According to an alternative embodiment of this invention, the fifth shaft of the planetary gearset is rotatably connected to the second element of the additional planetary gear set, whose first element is fixed to the non-rotatable component. Furthermore, the third element of the additional planetary gear set can be connected in a rotationally fixed manner to the drive shaft by means of the fifth shifting element.

In this variant, therefore, the first element of the additional planetary gear set is permanently fixed to the rotationally fixed component and is thus constantly prevented from rotating. The second element of the additional planetary gear set and the fifth shaft are permanently connected to each other in a rotationally fixed manner, while the third element of the additional planetary gear set is not brought into rotation with the drive shaft until the fifth switching element is closed. The designed in this case as a fifth clutch element is in this case preferably provided axially on one of the connection point of the drive shaft facing side of the additional planetary gear set.

Further alternatively, the drive shaft is non-rotatably connected to the third element of the additional planetary gear set, whose first element is fixed to the rotationally fixed component. Further, the second element of the additional planetary gear set can be rotatably connected via the fifth switching element to the fifth shaft of the planetary gear set.

In this case, therefore, the first element of the additional planetary gear set is permanently fixed to the non-rotatable component and thus stands still permanently. Furthermore, the third element of the additional planetary gear set is constantly rotatably connected to the drive shaft, whereas the second element of the additional planetary gear set rotatably with the fifth wave of the first by turning the fifth switching element Planetary gear set system is associated. The fifth switching element, which is designed as a clutch, is placed in particular axially between the additional planetary gear set and the planetary gear set system.

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

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, a sixth switching element is also provided, via which the additional planetary gear set can be blocked. Specifically, while the blocking of the additional planetary gear set can be achieved by the sixth switching element when actuated, the first element and the third element of the additional planetary gear rotatably connected to each other. Alternatively, the blocking is realized by non-rotatably connecting the second element and the third element of the additional planetary gearset via the sixth shifting element or, alternatively, by non-rotatably connecting the first element and the second element of the additional planetary gearset by means of the sixth shifting element.

In a further development of the abovementioned refinement option, a fourth forward gear in a second variant can then also be actuated by actuating the first, the third and the sixth shifting element, in a third variant by closing the first, the fourth and the sixth shifting element, and in a fourth variant of the third, fourth and sixth switching elements. In addition, a ninth forward speed can be switched by closing the second, third and sixth shift elements, and an additional gear by operating the second, third and sixth shift elements. The latter does not fit perfectly into the rest of the translation series.

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 gear set but also, if it allows the connection of the individual elements of the additional planetary, as a plus-planetary gear, wherein it is the first element of the additional planetary gear then a sun gear at the second element of the additional planetary gear a ring gear and the third element of the additional planetary gear set is a 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.

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. there Then in comparison to the plus-planetary gear set also the ring gear and the planetary web connection would have to be exchanged with each other, as well as reduce a gearbox ratio by one.

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 fourth switching element can also be designed as a positive switching element, such as a dog clutch or lock synchronization. Because the fourth switching element is involved in the representation of the first to fifth forward gear, so that ultimately takes place only an opening in the course of a successive upshift. A form-fitting switching element has the advantage over a non-positive switching element that only slight drag torques occur in the opened state, so that a higher efficiency can be realized.

According to a further embodiment of the invention, the output shaft has a toothing, via which the output shaft is in operative connection with an axially parallel to the output shaft arranged differential gear. Here, the toothing is preferably provided at a connection point of the output shaft, wherein said connection point of the output shaft is preferably axially between the fourth switching element and the second switching element in the region of an axial end of the transmission. This type of arrangement is particularly suitable for use in a motor vehicle with a transversely oriented to the direction of travel of the motor vehicle drive train.

In a further development of the invention, an electric machine is provided whose rotor is connected to the drive shaft, one of the five 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 may be formed as such a starting element by it or it is 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 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 eine schematische Darstellung eines Getriebes gemäß einer sechsten Ausgestaltungsmöglichkeit der Erfindung;
• 8 eine schematische Ansicht eines Getriebes entsprechend einer siebten Ausführungsform der Erfindung;
• 9 ein beispielhaftes Schaltschema der Getriebe aus den 2 bis 8;
• 10 eine schematische Ansicht eines Getriebes entsprechend einer achten Ausführungsform der Erfindung;
• 11 eine schematische Darstellung eines Getriebes gemäß einer neunten Ausgestaltungsmöglichkeit der Erfindung;
• 12 eine schematische Ansicht eines Getriebes entsprechend einer zehnten Ausführungsform der Erfindung; und
• 13 ein beispielhaftes Schaltschema der Getriebe aus den 10 bis 12.

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

• 1 a schematic view of a motor vehicle drive train, in which a transmission according to the invention is used;
• 2 a schematic view of a transmission according to a first embodiment of the invention;
• 3 a schematic representation of a transmission according to a second embodiment of the invention;
• 4 a schematic view of a transmission according to a third embodiment of the invention;
• 5 a schematic representation of a transmission according to a fourth embodiment of the invention;
• 6 a schematic view of a transmission according to a fifth embodiment of the invention;
• 7 a schematic representation of a transmission according to a sixth embodiment of the invention;
• 8th a schematic view of a transmission according to a seventh embodiment of the invention;
• 9 an exemplary circuit diagram of the transmission of the 2 to 8th ;
• 10 a schematic view of a transmission according to an eighth embodiment of the invention;
• 11 a schematic representation of a transmission according to a ninth embodiment of the invention;
• 12 a schematic view of a transmission according to a tenth embodiment of the invention; and
• 13 an exemplary circuit diagram of the transmission of the 10 to 12 ,

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 a second sun gear SO2 , 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. Likewise, the at least one second planetary gear also meshes PR2 in a second axial gear plane II both with the radially inner second sun gear SO2 , as well as with the radially surrounding second ring gear HO2 , 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 lower stationary gear ratio, as a second gear stage, which by the second ring gear HO2 that has at least one second planetary gear PR2 and the second sun wheel SO2 is formed.

Furthermore, the planet gears PR1 and PR2 also in pairs with each other in meshing by the at least one first planetary gear PR1 axially in the region of the at least one second planetary gear PR2 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.

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 web and also a gearbox ratio can 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 five waves W1 . W2 . W3 . W4 and W5 assigned, of which the first wave W1 within the planetary gear set system PS rotatably with the first ring gear HO1 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 second sun gear SO2 connected is. On the other hand, there is the fourth wave W4 rotatably with the second ring gear HO2 while in the case of the fifth wave W5 the planetary bridge PG is.

Outside the planetary gear set system PS can the first wave W1 over the first switching element K1 rotationally fixed with a drive shaft LV1 of the transmission G are connected, which also permanently rotatably with the third element E31 of the additional planetary gear set P1 communicates. The second wave W2 of the planetary gear set system PS can also by closing the second switching element B1 on a non-rotatable component GG be set, which is preferably the transmission housing of the transmission G or part of the transmission housing. Furthermore, the third wave W3 of the planetary gear set system by means of the third switching element K2 rotatably with an output shaft GW2 of the transmission G be associated with the output shaft GW2 also by closing the fourth switching element K3 rotatably with the fourth wave W4 of the planetary gear set system PS can be connected.

As well as in 2 It can be seen that this is the fifth wave W5 of the planetary gear set system PS and the second element E21 of the additional planetary gear set P1 permanently rotatably connected to each other, whereas the first element E11 of the additional planetary gear set P1 by closing the fifth switching element B2 on the non-rotatable component GG fixed and thus can be prevented in the sequence of a rotational movement.

Both the drive shaft LV1 , as well as the output shaft GW2 each form one 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 via a - not shown here - toothing with the following differential gear AG connected is. While the junction Level 1-A the drive shaft LV1 while at an axial end of the transmission G is configured, is the junction GW2-A the output shaft GW2 at an axially opposite end and is here transverse to the junction Level 1-A the drive shaft LV1 aligned.

The additional planetary gear set P1 and the planetary gear set system PS are on the connection point Level 1-A the drive shaft LV1 axially following in order additional planetary gear set P1 and planetary gear set system PS arranged.

As well as in 2 can be seen, is the first switching element K1 in the wheel plane I of the planetary gear set system PS arranged and thus lies axially in the region of the first sun gear SO1 and the first ring gear HO1 and radially surrounding these. On the other hand, the second switching element B1 , the third switching element K2 , the fourth switching element K3 and the fifth switching element B2 axially on one of the connection points Level 1-A the drive shaft LV1 remote side of the planetary gear set system PS arranged, wherein the third switching element K2 in this case axially adjacent to the planetary gear set system PS is and then then first the fourth switching element K3 , then the connection point GW2-A the output shaft GW2 , then the second switching element B1 and finally the fifth switching element B2 consequences. Specifically, is the third switching element K2 axially adjacent to the fourth switching element K3 , as well as the second switching element B1 axially adjacent to the fifth switching element B2 provided, so that in each case a common supply is possible.

3 shows a schematic view of a transmission G according to a second embodiment of the invention, this embodiment substantially according to the variant 2 equivalent. In contrast to the possibility of design according to 2 In this case, however, it is the first element E11 of the additional planetary gear set P1 permanently on the non-rotatable component GG fixed and thus stands still, whereas the third element E31 of the additional planetary gear set P1 no longer permanently rotatable with the drive shaft LV1 is connected, but a non-rotatable connection only when closing a fifth switching element K4 will be produced. The fifth switching element K4 is designed as a clutch and axially on one of the connection point Level 1-A the drive shaft LV1 facing side of the additional planetary gear set P1 intended. Otherwise, the embodiment corresponds to 3 according to the variant 2 so that reference is made to what has been described.

Out 4 is a schematic representation of a transmission G according to a third embodiment of the invention. This embodiment also largely corresponds to the variant 2 , but in contrast to the variant of 2 and as in the embodiment according to 3 the first element E11 of the additional planetary gear set P1 permanently on the non-rotatable component GG is fixed. In addition, there is the second element E21 of the additional planetary gear set P1 not permanently rotatable with the fifth shaft W5 of the planetary gear set system PS but a non-rotatable connection is only by closing a fifth switching element K4 produced. The fifth switching element K4 , which is designed as a clutch, is axially between the additional planetary gear set P1 and the planetary gear set system PS intended. Otherwise, the embodiment corresponds to 4 according to the variant 2 so that reference is made to what has been described.

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

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

Further shows 6 a schematic view of a transmission G according to a fifth embodiment of the invention, which thereby largely the previous variant 5 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 directly 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 6 according to the variant 5 so that reference is made to what has been described.

Moreover, in 7 a schematic representation of a transmission G according to a sixth embodiment of the invention, which also again essentially according to the variant 5 equivalent. As in the embodiment according to 6 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 7 the embodiment according to 5 so that reference is made to what has been described.

Further shows 8th a schematic view of a transmission G according to a seventh embodiment of the invention, wherein this embodiment possibility essentially of the variant 2 equivalent. It is different, however, that the connection point GW2-A the output shaft GW2 now at the same axial end of the transmission G is relocated, as the connection point Level 1-A the drive shaft LV1 , In addition, now is the fourth switching element K3 axially between the planetary gear set system PS and the third switching element K2 arranged. Incidentally, the possibility of design according to 8th according to the variant 2 so that reference is made to what has been described.

In 9 is an exemplary circuit diagram for the respective transmission G from the 2 to 7 tabulated. As can be seen, in each case a total of eight forward gears 1 to 8th 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 and B2 respectively. K4 in which of the forward gears 1 to 8th each is closed. In each of the forward gears 1 to 8th are each three of the switching elements K1 . B1 . K2 . K3 and B2 respectively. K4 closed, with a successive circuit of the forward gears 1 to 8th each one of the involved switching elements to open and another switching element is to close in the following.

As in 9 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 K3 switched, starting from this, a second forward gear 2 is formed by the first switching element K1 opened and in the following the fifth switching element B2 respectively. K4 is closed. In addition, then in a third forward gear 3 be switched by the second switching element B1 opened and the first switching element K1 is closed. Based on this results then a fourth forward gear 4 by opening the first switching element K1 and closing the third switching element K2 , This is followed by a fifth forward gear 5 by opening the fifth switching element B2 respectively. K4 and closing the first switching element K1 shown, of which starting in a sixth forward gear 6 is switched by the fourth switching element K3 opened and the fifth switching element B2 respectively. K4 is closed. To shift to a seventh forward gear 7 is then the fifth switching element B2 respectively. K4 to open and the second switching element B1 close. Finally, there is an eighth forward speed 8th starting from the seventh forward gear 7 by the first switching element K1 opened and the fifth switching element B2 respectively. K4 is closed.

Further, go out 10 a schematic representation of a transmission G according to an eighth embodiment of the invention, which also again essentially according to the variant 2 equivalent. Unlike the variant after 2 is now additionally a sixth switching element K5 provided, which when actuated the first element E11 and the third element E31 of the additional planetary gear set P1 rotatably connects to each other and thereby blocking the additional planetary gear set P1 causes. The designed as a clutch, the sixth switching element K5 is in this case axially on one of the connection point Level 1-A the drive shaft LV1 facing side of the additional planetary gear set P1 intended. Otherwise, the design option corresponds to 10 according to the variant 2 so that reference is made to what has been described.

Further shows 11 a schematic view of a transmission G according to a ninth embodiment of the invention, which in turn largely the possibility of design according to 2 equivalent. It is different, however, that in addition a sixth switching element K5 is provided, which in the closed state, the second element E21 and the third element E31 of the additional planetary gear set P1 rotatably connects to each other and thereby blocking the additional planetary gear set P1 causes. In this case, the sixth switching element K5 designed as a coupling and axially on one of the connection point Level 1-A the drive shaft LV1 facing side of the additional planetary gear set P1 intended. Otherwise, the embodiment corresponds to 11 otherwise the variant 2 so that reference is made to what has been described.

Finally, go out 12 still a schematic representation of a transmission G according to a tenth embodiment of the invention. This design option again essentially corresponds to the variant 2 , in difference now in addition a sixth switching element K5 is provided, upon actuation of the first element E11 and the second element E21 of the additional planetary gear set P1 rotatably connected to each other. This then has a blocking of the additional planetary gear set P1 result. The designed as a clutch, the sixth switching element K5 is in this case axially on one of the connection point Level 1-A the drive shaft LV1 facing side of the additional planetary gear set P1 intended. Otherwise, the design option corresponds to 12 according to the variant 2 so that reference is made to what has been described.

In 13 is now an exemplary circuit diagram of the transmission G from the 10 to 12 in this case, this circuit diagram substantially corresponds to the circuit diagram 9 equivalent. The only difference is that by providing the additional sixth switching element K5 in addition to the forward gears 1 to 8th even more variants of a fourth forward gear 4.2 . 4.3 and 4.4 , a ninth forward gear 9 and an additional gear ZG are switchable. A fourth forward gear 4.1 corresponds to the first forward gear 4 according to the wiring diagram 9 , Likewise, the other forward gears 1 to 3 such as 5 to 8th on the to 9 described manner shown.

In the present case results in a fourth forward gear 4.2 by actuating the first switching element K1 , the third switching element K2 and the sixth switching element K5 , Alternatively, a fourth forward gear 4.3 by closing the first switching element K1 , the fourth switching element K3 and the sixth switching element K5 and a fourth forward gear 4.4 by actuating the third switching element K2 , the fourth switching element K3 and the sixth switching element K5 shown. In addition, there is the ninth forward gear 9 by closing the second switching element B1 , the third switching element K2 and the sixth switching element K5 , Finally, the additional gear can ZG by actuating the second switching element B1 , the third switching element K2 and the sixth switching element K5 will be realized.

As in the 2 to 8th and 10 to 12 is shown, is the fourth switching element K3 designed as non-positive switching element. However, the fourth switching element could K3 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 3 . 4 and 8th as well as 10 to 12 can correspond to one of the variants of the 5 to 7 with an electric machine EM be provided. In addition, the variants of the 10 to 12 with a sixth switching element K5 also according to the transmissions from the 3 . 4 and 8th will be realized.

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

Fifth switching element

K5

Sixth switching element

1

First forward

2

Second forward speed

3

Third forward

4

Fourth forward

4.1

Fourth forward

4.2

Fourth forward

4.3

Fourth forward

4.4

Fourth forward

5

Fifth forward speed

6

Sixth forward

7

Seventh forward

8th

Eighth forward

9

Ninth forward

ZG

additional transition

LV1

drive shaft

Level 1-A

junction

GW2

output shaft

GW2-A

junction

EM

electric machine

S

stator

R

rotor

AT

connecting shaft

K0

separating clutch

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

• AT 15018 U2 [0003]

Claims (18)

A transmission (G) for a motor vehicle, comprising a drive shaft (GW1) and an output shaft (GW2), and a five-shaft planetary gear set (PS) (W1, W2, W3, W4, W5) and an additional planetary gear set (P1) a first (K1), a second (B1), a third (K2), a fourth (K3) and a fifth switching element (B2; K4) are provided by their selective actuation different power flow guides on the planetary gear set (PS) and the additional Planetary gear (P1) under circuit of different gears between drive shaft (GW1) and output shaft (GW2) can be displayed, characterized in that the drive shaft (GW1) via the first switching element (K1) rotatably connected to the first shaft (W1) of the Planetenradsatzsystems (PS ) is connectable, the second shaft (W2) by means of the second switching element (B1) on a non-rotatable component (GG) can be fixed, - that the third shaft (W3) of the Planetenradsatzsystems (PS) via the third Schaltelem ent (K2) rotatably connected to the output shaft (GW2) is brought into connection, which also by means of the fourth switching element (K3) rotatably connected to the fourth shaft (W4) of the Planetenradsatzsystems (PS) is connectable, - and that in the additional planetary gear set (P1 ) a first coupling of a first element (E11) of the additional planetary gear set (P1) with the non-rotatable component (GG), a second coupling of a second element (E21) of the additional planetary gear set (P1) with the fifth shaft (W5) of the Planetenradsatzsystems (PS ), as well as a third coupling of a third element (E31) of the additional planetary gear set (P1) with the drive shaft (GW1), of these couplings two couplings as permanent non-rotatable connections, while the remaining coupling a rotationally fixed connection on the fifth Switching element (B2; K4) can be produced. 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 first shaft (W1), wherein the Planetenradsatzsystem (PS) also has at least one second planetary gear (PR2), both with a second sun gear (SO2), the rotation with the third shaft (W3) is connected, as well as with a second ring gear (HO2) meshes, which in rotation with the fourth shaft (W4) is in communication, and wherein the at least one first planetary gear (PR1) and the at least one second planetary gear (PR2) with each other meshing with each other and are guided together via a planetary web (PG) of the Planetenradsatzsystems (PS), which is non-rotatably connected to the fifth shaft (W5). Transmission (G) to Claim 2 , characterized in that in each case one of the meshing with each other planet gears (PR1, PR2) is extended axially in the region of the other planetary gear (PR2). Transmission (G) according to one of the preceding claims, characterized in that the fifth shaft (W5) of the Planetenradsatzsystems (PS) rotatably connected to the second element (E21) of the additional planetary gear set (P1) whose third element (E31) rotatably with the drive shaft (GW1) is in communication, wherein the first element (E11) of the additional planetary gear set (P1) via the fifth switching element (B2) on the rotationally fixed component (GG) can be fixed. Transmission (G) according to one of Claims 1 to 3 , characterized in that the fifth shaft (W5) of the Planetenradsatzsystems (PS) rotatably connected to the second element (E21) of the additional planetary gear set (P1) whose first element (E11) is fixed to the non-rotatable component (GG), said Third element (E31) of the additional planetary gear set (P1) by means of the fifth switching element (K4) rotatably connected to the drive shaft (GW1) is connectable. Transmission (G) according to one of Claims 1 to 3 , characterized in that the drive shaft (GW1) is non-rotatably connected to the third element (E31) of the additional planetary gear set (P1) whose first element (E11) is fixed to the non-rotatable component (GG), the second element (E21) of additional planetary gear set (P1) via the fifth switching element (K4) rotatably connected to the fifth shaft (W5) of the Planetenradsatzsystems (PS) 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 (K3), - a second forward gear (2) Actuating the second (B1), the fourth (K3) and the fifth shift element (B2; K4), - a third forward gear (3) by actuating the first (K1), the fourth (K3) and the fifth shift element (B2; K4 a fourth forward gear (4; 4.1) by actuating the third (K2), the fourth (K3) and the fifth shifting element (B2; K4), - a fifth forward gear (5) by actuating the first (K1), third (K2) and the fourth switching element (K3), - a sixth forward speed (6) by operating the first (K1), the third (K2) and the fifth shifting element (B2; K4), - a seventh forward speed (7) by operating the first (K1), the second (B1) and of the third shift element (K2), and an eighth forward gear can be shifted by actuating the second (B1), the third (K2) and the fifth shift element (B2; K4). Transmission (G) according to one of the preceding claims, characterized in that in addition a sixth switching element (K5) is provided, via which the additional planetary gear set (P1) is lockable. Transmission (G) to Claim 8 , characterized in that the sixth switching element (K5) when actuated the first element (E11) and the third element (E31) of the additional planetary gear set (P1) or the second element (E21) and the third element (E31) of the additional planetary gear set ( P1) or the first element (E11) and the second element (E21) of the additional planetary gear set (P1) rotatably connected to each other. Transmission (G) to Claim 8 or 9 , characterized in that a ninth forward gear (9) by switching the second (B1), the third (K2) and the sixth switching element (K5) is switchable. 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 10 , 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, K4, K1, B1, K2, K3, B2, K5 ) are each realized as non-positive switching element. Transmission according to one of the preceding claims, characterized in that the fourth switching element (K3) is realized as a form-locking 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, the rotor (R) with the drive shaft (GW1), one of the five shafts (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 17 ,

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