DE102016211392A1 - Transmission for a motor vehicle - Google Patents

Abstract

The invention relates to a transmission (G) for a motor vehicle, wherein the transmission (G) comprises a drive shaft (GW1), an output shaft (GW2), three planetary gear sets (P1, P2, P3) and five shift elements (K1, B1, B2, B3 , K2), wherein by selectively operating the five switching elements (K1, B1, B2, B3, K2) six forward gears and one reverse gear between the drive shaft (GW1) and the output shaft (GW2) are switchable, and drive train for a motor vehicle with a such transmission (G).

Description

The invention relates to a transmission for a motor vehicle, as well as a motor vehicle drive train with such a transmission. In the present case, a transmission refers to a multi-speed transmission, i. H. There are several different ratios as gears between a arrival and an output side of the transmission switchable by actuation of corresponding switching elements, and 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 2009264237 A1 is a gearbox for a motor vehicle, in which between a drive shaft and an output shaft, three planetary gear sets are provided, which each consist of a sun gear, a ring gear and a respective planet web. Further, a plurality of switching elements are provided by the selective actuation of the planetary gear sets are coupled to each other to define different gears between the input and the output shaft. A total of six forward gears, and a reverse gear between the drive shaft and the output shaft can be switched.

It is the object of the present invention to provide an alternative embodiment to the prior art transmission with six forward gears and one reverse gear between a drive shaft and an output shaft.

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 16.

According to the invention, a transmission comprises a drive shaft and an output shaft, and at least functionally a first, a second and a third planetary gear set. The planetary gear sets each comprise a plurality of elements, the planetary gear sets serving to guide a flow of power from the drive shaft to the output shaft. For this purpose, a first, a second, a third, a fourth and a fifth switching element are provided, through whose selective actuation the planetary gear sets can be coupled with each other by connecting different gears between the input and output shafts.

In this case, the drive shaft can be connected via the first switching element with the first element of the first planetary gear set, which is also fixable by means of the second switching element to a non-rotatable component. Furthermore, the second element of the first planetary gear set can be fixed on the non-rotatable component via the third switching element. Finally, the third element of the first planetary gear set and the second element of the second planetary gear set are rotatably connected to each other and together are rotationally fixed to the output shaft in connection.

In other words, therefore, the third element of the first planetary gear set and the second element of the second planetary gear set are permanently in communication with each other and are also connected together with the output shaft of the transmission.

By closing the first formwork element, the drive shaft of the transmission is rotatably connected to the first element of the first planetary gear set, whereas an actuation of the second switching element entails a setting of the first element of the first planetary gear set on the non-rotatable component. The non-rotatable component is preferably a transmission housing of the transmission or a part of such a transmission housing. Furthermore, a closing of the third switching element leads to a rotationally fixed coupling of the second element of the first planetary gear set with the rotationally fixed component.

Consequently, the first switching element is designed as a clutch, which rotates when operating rotatable components of the transmission equal to each other, while the second and the third switching element are present as brakes that slow down when driven the respective rotatable component of the transmission to a standstill and fix on the non-rotatable component ,

An inventively ausgestaltetes transmission is characterized by a compact design, low component loads and a good gear efficiency.

Preferably, the first and the second switching element are arranged axially on one of a connection point of the drive shaft zugwandten side of the first planetary gear set and are thus on a drive side of the transmission. In this respect, the first and the second switching element are easily accessible. In addition, the first and the second switching element could possibly be supplied via a common supply line. The third switching element is located preferably radially surrounding and substantially axially at the height of the first planetary gear set.

The fact that a first, a second and a third planetary gear set are "at least functionally" means, in the sense of the invention, that the gearbox according to the invention has at least three planetary gear sets in terms of its function. Specifically, the three planetary gear sets can be present as separate planetary gear sets, which are interconnected or interconnectable in the manner according to the invention, or more of the planetary gear sets are combined into sets of wheels, such as a Ravigneaux wheelset. In the former case, each of the planetary gear sets would have elements in the form of one sun gear, one ring gear, and one planet land each, whereas combined planetary gear sets share one or more common elements in the latter case.

According to one embodiment of the invention, the drive shaft is also rotatably connected to the second element of the third planetary gear set, whose third element rotatably coupled to the second element of the first planetary gear set and whose first element by means of the fourth switching element on the rotationally fixed component can be fixed. The fourth switching element is thus designed as a brake in this case, which sets the first element of the third switching element on the rotationally fixed component when actuated. In addition, the fourth switching element is preferably arranged axially on one side of the third planetary gear set facing away from a connection point of the drive shaft.

According to an alternative embodiment of the invention, the drive shaft is also rotatably connected to the second element of the third planetary gear, the third element by means of the fourth switching element rotatably coupled to the second element of the first planetary gear set and whose first element is fixed to the rotationally fixed component. In this case, the fourth switching element is thus designed as a coupling which, when actuated, connects the third element of the third switching element and the second element of the first planetary gear set rotatably with one another. In this case, the fourth switching element is provided in particular radially surrounding and axially substantially at the height of the third planetary gear set.

Further alternatively to the two aforementioned variants, the drive shaft can also be rotatably coupled by means of the fourth switching element with the second element of the third planetary gear set, whose third element rotatably coupled to the second element of the first planetary gear set and whose first element is fixed to the non-rotatable component. Again, the fourth switching element is designed as a coupling which rotatably coupled to each other when actuated, the drive shaft and the second element of the third planetary gear set. In this case, the fourth switching element is arranged in particular axially between the second planetary gear set and the third planetary gear set.

According to a further embodiment of the invention, which can be combined with one of the aforementioned variants, the first element of the second planetary gear set can be rotatably coupled via the fifth switching element to the drive shaft, whereas the third element of the second planetary gear rotatably connected to the second element of the first planetary gear set is. The fifth switching element is thus realized as a coupling which, when actuated, connects the first element of the second planetary gear set and the drive shaft in a torque-proof manner with each other. In this case, the fifth shifting element is preferably arranged axially on one side of the first planetary gear set facing a connection point of the drive shaft and thus lies together with the first shifting element on a drive side of the transmission. Thus, the first switching element and the fifth switching element could be supplied via a common supply line.

According to an alternative embodiment of the invention, which is also alternative to the embodiment mentioned immediately above, which can also be combined with one of the variants mentioned above in the aforementioned embodiment, the first element of the second planetary gear set is non-rotatably connected to the drive shaft, whereas the third element of the second planetary gear set is connected via the fifth Switching element rotatably coupled to the second element of the first planetary gear set. Again, the fifth switching element is designed as a coupling, which in the closed state, the third element of the second planetary gear set and the second element of the first planetary gear rotatably connected to each other. In particular, the fifth switching element is arranged radially surrounding and axially substantially at the height of the second planetary gear set.

In each of the aforementioned variants of a transmission according to the invention, six forward gears, and one reverse gear can be realized. In this case, a first forward gear is switched by operating the third and the fifth shift element, while a second forward gear is formed by closing the second and the fifth shift element. Further, a third forward speed results by operating the first and fifth shift elements, whereas a fourth forward speed is switchable by operating the fourth and fifth shift elements. Furthermore, a fifth forward gear by closing the first and the fourth switching element are shown, wherein the second and the fourth switching element are to be actuated for the circuit of a sixth forward gear. On the other hand, the reverse gear results by actuating the first and the third switching element.

With a suitable choice of stationary gear ratios of the planetary gear sets this is a suitable for the application in the field of a motor vehicle translation series realized. For a sequential shift of the forward gears according to their order is 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.

Advantageously, in the transmission according to the invention, a reverse gear for a drive via the drive motor upstream of the transmission can be realized. This can be realized as an alternative or in addition to an arrangement of an electric machine in the transmission, in order to be able to realize a reverse drive of the motor vehicle in case of failure of the electric machine.

In a further development of the invention, the first planetary gear set and the second planetary gear set form a Ravigneaux wheel set in that the first planetary gear set and the second planetary gear set have at least one common element. In this case, this is particularly preferably a common planetary web, in which case it is possible for there to be two individual parts which are rigidly connected to one another, or the common planetary web is formed in one piece. Possibly. In addition, the planetary gear sets can share a common ring gear, whereby here also two rigidly interconnected items or a one-piece ring gear can be realized.

It is a further embodiment of the invention that the respective planetary gear set is present as a minus planetary gear set, wherein each of the respective first element of the respective planetary gear is a respective sun gear, in the respective second element of the respective planetary gear set to a respective planet web and the respective third element of the respective planetary gear set is a respective ring gear. A minus planetary set is composed in a manner known in principle to the person skilled in the art from the elements sun gear, planet carrier and ring gear, the planet carrier guiding at least one but preferably several planetary gears, which in each case mesh both with the sun gear and with the surrounding ring gear. Of the three planetary gear sets then one or more planetary gear sets are designed as such Minusplanetensätze. However, the second and third planetary gear set or the first and third planetary gear sets are particularly preferably in the form of minus planetary gear sets, whereby a particularly compact construction can be realized.

Alternatively or in addition thereto, the respective planetary gear set is in the form of a positive planetary gear set, the respective first element of the respective planetary gear set then being a respective sun gear, the respective second element of the respective planetary gear set being a respective ring gear and the respective third element of the respective one Planetenradsatzes is about a respective planetary ridge. In a Plusplanetensatz the elements sun gear, ring gear and planetary ridge are also present, the latter at least one pair of planetary leads, in which one planetary gear with the inner sun gear and the other planet gear meshing with the surrounding ring gear, and the planet gears mesh with each other. In the transmission according to the invention, one or more planetary gear sets may be designed as such Plusplanetensätze, which is in particular in the first or the second planetary gear set is a Plusplanetensatz.

Where there is a connection of the individual elements, a minus planetary set can be replaced by a Plusplanetensatz, in which case compared to the execution as Minusplanetensatz the Hohlrad- and the Planetensteganbindung to exchange each other, and a respective Getriebestandübersetzung is to increase by one. Conversely, a plus planetary set could be replaced by a minus planetary set, if the connection of the elements of the transmission makes this possible. In this case, the ring gear and the planet web connection would then also have to be exchanged with each other, as well as a respective gearbox ratio reduced by one. As already mentioned, however, the second and the third planetary gear sets are preferably designed as minus planetary gear sets, while the first planetary gearset is present in particular as a plus planetary gearset. In contrast, according to an alternative variant, the first and the third planetary gear set are implemented as minus planetary gear sets and the second planetary gearset as a plus planetary gear set.

In a further development of the invention, one or more switching elements are each realized as non-positive switching elements. Frictional switching elements have the advantage that they can be switched under load, so that a change between the courses without interruption of traction is executable. But particularly preferably, the third switching element and / or the fifth switching element is designed in each case as a form-locking switching element, such as a dog clutch or lock synchronization. Because the third switching element is involved in the first forward gear and the reverse gear, so that in a successive upshift of the gears here only an opening of the third switching element is to be completed. The fifth switching element is involved in the circuit of the four forward gears, so that only takes place here 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, connection points of the input and output shafts are coaxial with one another. Here, the connection point of the drive shaft is preferably provided at one axial end of the transmission, while the connection point of the output shaft is configured in particular at the same axial end. Particularly preferably, the connection point of the output shaft is axially between the second and the third switching element. Further preferably, the outer interface of the output shaft then has a toothing which meshes with a toothing of a shaft arranged parallel to the axis of the drive shaft axis of the transmission. The axle differential of a drive axle can then be arranged on this shaft. 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 rotatably coupled to one of the rotatable components of the transmission. Preferably, a stator of the electric machine is then non-rotatably connected to the non-rotatable component of the transmission, wherein the electric machine in this case can be operated by electric motor and / or generator 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 the axial direction to this, in the latter case then a coupling via an intermediate spur gear or a traction mechanism can be realized.

Preferably, the rotor of the electric machine is rotatably coupled to the drive shaft, thereby a purely electric driving the motor vehicle is shown in a suitable manner. In the variant of the transmission according to the invention, in which the third element of the third planetary gear set via the fourth switching element with the second element of the first planetary gear set is coupled, but the rotor could also be rotatably connected to the third element of the third planetary gear set. Because in this case, the rotor of the electric machine via the third planetary gear set is permanently coupled to the drive shaft and rotates due to the translation of the third planetary gear set constantly faster than the drive shaft. Therefore, this site is suitable for the connection of a high-speed, compact electric machine.

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 also be 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 as a Such start-up element may be formed 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.

In a further development of the invention, a planetary stage is also provided as a constant stage, of which elements sun gear, ring gear and planetary gear a first element is coupled to the output shaft, while a second element of the planetary stage permanently fixed and rotatably connected to a third element of the planetary stage with an output of the transmission is. The subsequent switching of a constant stage allows a modification of the translation to a suitable overall translation. A constant stage embodied as a planetary stage can be arranged in a compact manner, and in principle a design as a spur gear stage would also be conceivable within the meaning of the invention. In this case, the constant stage is preferably integrated into the transmission, that is to say lying inside a transmission housing. Alternatively, the constant level could also be connected downstream of the transmission as a separate unit within a drive train.

More preferably, the output shaft is coupled via an intermediate shaft to the first element of the constant stage, wherein the intermediate shaft carries two spur gears, of which a spur gear meshes with a spur gear on the output shaft and a spur gear with a non-rotatably connected to the first element of the constant gear spur gear. In particular, the first element of the constant stage is the sun gear of the planetary stage, while the second element is a ring gear and the third element is a planetary land. The third element of the constant stage can then be directly connected in a rotationally fixed manner to a drive side of a subsequent differential. Thus, the third element of the constant stage may be connected to a differential cage of the differential designed as a transverse or longitudinal differential.

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

If, on the other hand, a switching element is provided between two components of the transmission, these components are not permanently coupled to one another in a rotationally fixed manner, but a rotationally fixed coupling is only performed via 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 connected thereto 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 over this 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.

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

1 a schematic view of a motor vehicle drive train, in which a transmission according to the invention is used;

2 a schematic view of a transmission according to a first embodiment of the invention;

3 a schematic representation of a transmission according to a second embodiment of the invention;

4 a schematic view of a transmission according to a third embodiment of the invention;

5 a schematic representation of a transmission according to a fourth embodiment of the invention;

6 a schematic view of a transmission according to a fifth embodiment of the invention;

7 a schematic representation of a transmission according to a sixth embodiment of the invention;

8th a schematic view of a transmission according to a seventh embodiment of the invention;

9 a schematic representation of a transmission according to an eighth embodiment of the invention;

10 a schematic view of a transmission according to a ninth embodiment of the invention;

11 a schematic representation of a transmission according to a tenth embodiment of the invention;

12 a schematic view of a transmission according to an eleventh embodiment of the invention;

13 a schematic representation of a transmission according to a twelfth embodiment of the invention;

14 a schematic view of a transmission according to a thirteenth embodiment of the invention; and

15 an exemplary circuit diagram of the transmission of the 2 to 14 ,

1 shows a schematic view of a motor vehicle drive train in which an internal combustion engine VKM is connected via an intermediate torsional vibration damper TS with a transmission G. On the output side, the transmission G is followed by an axle drive AG, via which a drive power is distributed to drive wheels DW of a drive axle of the motor vehicle. The transmission G and the axle drive AG are combined in a common transmission housing. In this case, the torsional vibration damper TS can be integrated with this transmission housing.

Out 2 is a schematic representation of the transmission G according to a first embodiment of the invention. As can be seen, the transmission G comprises a first planetary gearset P1, a second planetary gearset P2 and a third planetary gearset P3. Each of the planetary gear P1, P2 and P3 each have a first element E11 or E12 or E13, depending on a second element E21 or E22 or E23 and a third element E31 or E32 or E33. The respective first element E11 or E12 or E13 is always formed by a sun gear of the respective planetary gear set P1 or P2 or P3, while the second planetary gear P2 and the third planetary gear P3, the respective second element E22 or E23 than ever Planet web present. The respective remaining third element E32 or E33 is then formed in the second planetary gear P2 and the third planetary gear P3 by a respective ring gear. On the other hand, in the case of the first planetary gearset P1, the second element E21 is a ring gear and the third element E31 is a planetary gear.

The planetary gear sets P2 and P3 are thus in each case designed as a minus planetary sets, in which the respective planetary web, but preferably several planet gears rotatably mounted, which are in detail with the radially inner sun gear and with the surrounding ring gear in meshing engagement. The first planetary gear set P1, however, exists as a positive planetary set, in which the planetary gear carries at least one pair of planetary gears of the planetary gears a planetary gear with the radially inner sun gear and a planet gear with the radially surrounding ring gear meshing, and the planet gears of the pair of wheels mesh with each other.

Wherever it allows the connection, but also single or both planetary gear sets P2, P3 could be executed as plus planetary gear sets. Conversely, the first planetary gear set could also be used P1, if the connection allows it, to be implemented as a minus planetary set. Compared to a respective embodiment as a minus planetary set would then in a Plusplanetensatz the respective second element E22 or E23 formed by the respective ring gear and the respective third element E32 or E33 through the respective planetary web and also a respective Getriebestandübersetzung be increased by one. By contrast, in an embodiment of the Plusplanetensatzes as Minusplanetensatz the second element E21 should be designed as a planetary land and the third element E31 as a ring gear and reduce the Getriebestandübersetzung by one.

As in 2 can be seen, the transmission G comprises a total of five switching elements in the form of a first switching element K1, a second switching element B1, a third switching element B2, a fourth switching element B3 and a fifth switching element K2. In this case, the switching elements K1, B1, B2, B3 and K2 are each designed as non-positive switching elements and are preferably before as lamella switching elements. In addition, the first switching element K1 and the fifth switching element K2 are designed here as clutches, while the second switching element B1, the third switching element B2 and the fourth switching element B3 are present as brakes.

A drive shaft GW1 of the transmission G is non-rotatably connected to the second element E23 of the third planetary gear set P3 and can on the one hand via the fifth switching element K2 with the first element E12 of the second planetary gear P2 and on the other hand by means of the first switching element K1 with the first element E11 of first planetary gearset P1 rotatably connected. Apart from the rotationally fixed coupling with the drive shaft GW1, the first element E11 of the first planetary gear set P1 can still be fixed via the second switching element B1 on a non-rotatable component GG, which may be the transmission housing of the transmission G or a part of the transmission housing.

As further in 2 can be seen, the third element E31 of the first planetary gear P1 and the second element E22 of the second planetary gear set P2 are rigidly connected to each other and are also non-rotatably in common with an output shaft GW2 of the transmission G in combination. In addition, the second element E21 of the first planetary gear set P1, the third element E32 of the second planetary gear set P2 and the third element E33 of the third planetary gear set P3 permanently rotatably coupled to each other and can be fixed together by means of the third switching element B2 on the rotationally fixed component GG. With the latter, the first element E13 of the third planetary gear set P3 can be coupled non-rotatably by actuation of the fourth switching element B3.

The planetary gear sets P1, P2 and P3 are arranged axially in the order of the first planetary gear set P1, second planetary gear set P2 and third planetary gear set P3, wherein the first switching element K1, the second switching element B1 and the fifth switching element K2 axially on a side facing away from the second planetary gear set P2 of the first planetary gear set P1 are placed, on which also a connection point GW1-A of the drive shaft GW1 is located. In this case, a supply of the first switching element K1, the second switching element B2 and the fifth switching element K2 could possibly take place via a common line. In addition, the first switching element K1 and the fifth switching element K2 are preferably arranged directly next to one another.

On the other hand, the fourth switching element B3 is disposed at an axially opposite end of the transmission G and thus lies on a side facing away from the first planetary gear P1 and the second planetary gear P2 side of the third planetary gear set P3. Finally, the third switching element B2 is provided axially at the height and radially surrounding the first planetary gear set P1.

Coaxially to the connection point GW1-A of the drive shaft GW1, there is also formed a connection point GW2-A of the output shaft GW2, which lies at the same axial end of the transmission as the connection point GW1-A and axially between the second switching element B1 and the third switching element B2. The connection point GW1-A of the drive shaft GW1 is used in the motor vehicle drive train 1 a connection to the internal combustion engine VKM, while the transmission G is connected at the junction GW2-A of the output shaft GW2 with the following axle drive AG. Preferably, the connection point GW2-A here has a toothing, which meshes in the installed state of the transmission G with an associated toothing of a shaft, not shown. This shaft is then arranged axially parallel to the input and output shafts GW1 and GW2, it being possible for an axle drive to be arranged on this shaft. In that sense, that is in 2 shown gear G suitable for use in a motor vehicle drive train, which is aligned transversely to the direction of travel of the motor vehicle

Out 3 is a schematic representation of a transmission G according to a second embodiment of the invention, it largely according to the previous variant 2 equivalent. The only difference is that the first planetary gearset P1 is designed as a minus planetary gear set, while the second planetary gearset P2 is now present as a positive planetary gearset. Accordingly, the second element E21 of the first planetary gear set P1 is now through formed a planetary land, while the third element E31 of the first planetary gear P1 is present as a ring gear. In the case of the second planetary gearset P2, the second element E22 is now a ring gear, whereas the third element E32 of the second planetary gearset P2 is designed as a planetary web. As a further difference, the third shift element B2 is now provided axially substantially at the level of and radially surrounding the third planetary gear set P3. Otherwise, the embodiment corresponds to 3 the previous variant 2 , Insofar, this is going on 2 Described reference.

In 4 a transmission G is shown according to a third embodiment of the invention, which also essentially of the variant 2 equivalent. It is different, however, that in addition an electric machine EM is provided, the stator S is fixed to the non-rotatable component GG, while a rotor R of the electric machine EM rotatably connected to the drive shaft GW1. Furthermore, the drive shaft GW1 at its junction GW1-A via an intermediate separating clutch K0, which is designed here as a lamellar switching element, are rotatably connected to a connecting shaft AN, which in turn is connected to a crankshaft of the internal combustion engine VKM means of the intermediate torsional vibration damper TS.

A purely electric driving can be realized via the electric machine EM, in which case the separating clutch K0 is opened in order to decouple the drive shaft GW1 from the connecting shaft AN and not to drag the internal combustion engine VKM along. Otherwise, the embodiment corresponds to 4 according to the variant 2 so that reference is made to what has been described.

5 shows a schematic view of a transmission G according to a fourth embodiment of the invention, which again substantially in 2 corresponds to the variant shown. Unlike the variant after 2 However, the third element E33 of the third planetary gear set P3 is not permanently rotationally fixed to the second element E21 of the first planetary gear set P1 and the third element E32 of the second planetary gear set P2 is connected, but only by actuation of a fourth switching element K3 rotatably coupled to the second element E21 of the first planetary gear P1 and the third element E32 of the second planetary gear set P2. The fourth switching element K3 is designed for this purpose as a clutch and placed axially substantially at the height of the third planetary gear P3 and radially surrounding this. Otherwise, the embodiment corresponds to 5 according to the variant 2 so that reference is made to what has been described. In addition, could also in the embodiment according to 5 , analogous to the variant according to 3 , the first planetary gear set P1 as a minus planetary gear set and the second planetary gear set P2 as a positive planetary gear set are realized.

Out 6 is a schematic representation of a transmission G according to a fifth embodiment of the invention. This embodiment corresponds essentially to the variant 5 , in contrast, in addition to an electric machine EM is provided. A stator S of this electric machine EM is fixed to the non-rotatable component GG, while a rotor R is rotatably connected to the third element E33 of the third planetary gear P3. Due to the permanent rotationally fixed connection of the second element E23 of the third planetary gear set P3 to the drive shaft GW1 and the rigid connection of the first element E13 of the third planetary gear set P3 to the non-rotatable component GG, the rotor R rotates faster than the drive shaft GW1. In this respect, the electric machine EM can be designed as a high-speed, compact electric machine.

In addition, the drive shaft GW1 at its junction GW1-A again via an intermediate and designed as a lamellae switching element separating coupling K0 with a connecting shaft AN are rotatably connected, which is connected to a crankshaft of the internal combustion engine VKM means of the intermediate torsional vibration damper TS. The electric machine EM can realize a purely electric driving, in which case the separating clutch K0 is opened in order to decouple the drive shaft GW1 from the connecting shaft AN and not to drag along the internal combustion engine VKM. Otherwise, the embodiment corresponds to 6 according to the variant 5 so that reference is made to what has been described. As an alternative to the previously described arrangement of the electric machine EM, an electric machine could also be connected to the drive shaft GW1, as in the variant according to FIG 4 the case is. In addition, the first planetary gear set P1 could be configured as a minus planetary gearset and the second planetary gearset P2 as a positive planetary gearset.

7 shows a schematic view of a transmission G according to a sixth embodiment of the invention, which largely of the variant 2 equivalent. It is different that the first element E13 of the third planetary gear set P3 is permanently fixed to the rotationally fixed component GG. Furthermore, the drive shaft GW1 is not rigid with the second Element E23 of the third planetary gear set P3, but is only by closing a fourth switching element K3 rotatably coupled to the second element E23 of the third planetary gear set P3. The fourth switching element K3 is designed as a clutch and placed axially between the second planetary gear set P2 and the third planetary gear set P3. Incidentally, the possibility of design according to 7 according to the variant 2 so that reference is made to what has been described. Again in this embodiment, as in the variant according to 3 , the first planetary gear set P1 as a minus planetary gear set and the second planetary gear set P2 as a positive planetary gear set are realized. Furthermore, in the embodiment according to 7 Also, an electric machine connected to the drive shaft GW1 and a disconnect clutch are provided, as in the variant according to 4 was realized.

Further, go out 8th a schematic representation of a transmission G according to a seventh embodiment of the invention. This corresponds essentially to the possibility of design according to 2 , with the difference that the first element E12 of the second planetary gear set P2 is permanently connected in a rotationally fixed manner to the drive shaft GW1. Furthermore, the third element E32 of the second planetary gearset P2 is not rigidly connected to the second element E21 of the first planetary gear set P1 and the third element E33 of the third planetary gear set P3, but is only rotatably coupled thereto by actuation of a fifth switching element K2. The fifth switching element K2 is arranged axially substantially at the level of and radially surrounding the second planetary gear P2. Otherwise, the embodiment corresponds to 8th according to the variant 2 so on that too 2 Described reference is made. Also in the embodiment according to 8th For example, the first planetary gearset P1 could be configured as a minus planetary gearset and the second planetary gearset P2 as a positive planetary gearset, as in the variant according to FIG 3 has been realized.

In 9 a transmission G is shown according to an eighth embodiment of the invention, which essentially according to the previous variant 8th equivalent. As with the possibility of design 4 , However, here is additionally provided an electric machine EM, whose stator S is fixed to the non-rotatable component GG, while a rotor R of the electric machine EM rotatably connected to the drive shaft GW1. Furthermore, the drive shaft GW1 at its junction GW1-A via an intermediate separating clutch K0, which is again designed as a lamellae switching element, are rotatably connected to a connecting shaft AN, which is connected within the motor vehicle drive train with a crankshaft of the internal combustion engine VKM means of the intermediate torsional vibration damper TS ,

A purely electric driving can be realized via the electric machine EM, in which case the separating clutch K0 is opened in order to decouple the drive shaft GW1 from the connecting shaft AN and not to drag the internal combustion engine VKM along. Otherwise, the embodiment corresponds to 9 according to the variant 8th so that reference is made to what has been described. In this respect, the first planetary gearset P1 as a minus planetary gear set and the second planetary gearset P2 as a plus planetary gearset could also be configured here.

Out 10 Furthermore, a ninth embodiment possibility of a gear G is apparent, which in this case essentially according to the variant 5 equivalent. In contrast, the first element E12 of the second planetary gear set P2, as in the embodiment according to 8th , permanently rotatably connected to the drive shaft GW1, while the third element E32 of the second planetary gear set P2 is not permanently non-rotatably connected to the second element E21 of the first planetary gear set P1, but only by operation of a fifth switching element K2 rotatably coupled thereto. The latter is placed axially substantially at the level of and radially surrounding the second planetary gear set P2. The variants after 5 and 8th So were in the design option to 10 combined together. Otherwise, the embodiment corresponds to 10 according to the variant 5 so that reference is made to what has been described. Again, in addition, analogous to the variant according to 3 , the first planetary gear set P1 as a minus planetary gear set and the second planetary gear set P2 as a positive planetary gear set are realized.

11 shows a schematic representation of a transmission G according to a tenth embodiment of the invention. This embodiment largely corresponds to the variant 10 , In contrast, an electric machine EM is provided, whose stator S is fixed to the non-rotatable component GG, while a rotor R rotatably connected to the third element E33 of the third planetary gear P3. Due to the permanent rotationally fixed connection of the second element E23 of the third planetary gear set P3 to the drive shaft GW1 and the rigid connection of the first element E13 of the third planetary gear set P3 with the non-rotatable component GG, the rotor R also rotates faster than the drive shaft GW1 here. As a result, the electric machine EM can be designed as a high-speed, compact electric machine.

Furthermore, the drive shaft GW1 is again connected at its connection point GW1-A with a separating clutch K0 designed as a lamellae switching element, via which the drive shaft GW1 can be non-rotatably connected to a connection shaft AN. The connection shaft AN is then connected within the motor vehicle drive train via the intermediate torsional vibration damper TS to a crankshaft of the internal combustion engine VKM. Via the electric machine EM, a purely electric driving can be realized, wherein the separating clutch K0 is opened in order to decouple the drive shaft GW1 from the connecting shaft AN and not to tow the internal combustion engine VKM. Otherwise, the embodiment corresponds to 11 according to the variant 10 so that reference is made to what has been described. As an alternative to the previously described arrangement of the electric machine EM, an electric machine could also be connected to the drive shaft GW1, as in the variant according to FIG 4 the case is. In addition, the first planetary gear set P1 could be configured as a minus planetary gearset and the second planetary gearset P2 as a positive planetary gearset.

In 12 In addition, an eleventh embodiment possibility of a transmission G is shown, which in this case essentially according to the variant 7 equivalent. In contrast and analogous to the variant according to 8th however, the first element E12 of the second planetary gearset P2 is rigidly connected to the drive shaft GW1, while the third element E32 of the second planetary gearset P2 is not permanently non-rotatably connected to the second element E21 of the first planetary gear set P1 and the third element E33 of the third planetary gear set P3, but only by pressing a fifth switching element K2 rotatably coupled with these. The fifth switching element K2 is hereby placed axially substantially at the level of and radially surrounding the second planetary gear set P2. The variants after 7 and 8th So were in the design option to 12 combined together. Otherwise, the embodiment corresponds to 12 according to the variant 7 so that reference is made to what has been described. Again, in addition, analogous to the variant according to 3 , the first planetary gear set P1 as a minus planetary gear set and the second planetary gear set P2 as a positive planetary gear set are realized. Furthermore, in the embodiment according to 12 Also, an electric machine connected to the drive shaft GW1 and a disconnect clutch are provided, as in the variant according to 4 was realized.

Further shows 13 a schematic representation of a transmission G according to a twelfth embodiment of the invention, which thereby largely the variant 2 equivalent. The only difference is that out 2 Known wheelset is now followed by a constant level KS downstream in the form of a planetary stage PS. This planetary stage PS includes elements E1, E2 and E3, wherein the first element E1 is formed by a sun gear, the second element E2 by a ring gear and the third element E3 by a planetary web. The planetary web leads thereby several planet gears, which mesh both with the radially inner sun gear, as well as the radially surrounding ring gear. In this respect, the planetary stage PS is designed as a minus planetary set.

Specifically, the second element E2 of the planetary stage PS is permanently fixed, while the third element E3 of the planetary stage is rotatably connected to an output AB in the form of a differential cage DK of the following axle drive AG. The first element E1 of the planetary stage PS is coupled to the output shaft GW2, this being realized via two intermediate spur gear stages SS1 and SS2. Thus, the output shaft GW2 is provided at its junction GW2-A with a spur gear SR1, which is provided with a non-rotatably provided on an intermediate shaft ZW spur gear SR2 in meshing engagement. The two spur gears SR1 and SR2 together form the first spur gear SS1. Also placed on the intermediate shaft ZW is a spur gear SR3 which meshes with a spur gear SR4. The spur gear SR4 is then rotatably connected to the first element E1 of the planetary stage PS. The spur gears SR3 and SR4 together form the second spur gear SS2.

The planetary stage PS has presently in particular a translation in short, in order to realize a suitable post-translation in the transmission G, which preferably has a very long gear ratio in the first forward gear. In the present case, the planetary stage PS is integrated with the transmission G, the second element E2 of the planetary stage PS being fixed to the non-rotatable component GG. In principle, the constant stage KS in the form of the planetary stage PS but could also be present separately to the transmission G. Otherwise, the embodiment corresponds to 13 according to the variant 2 so that reference is made to what has been described.

Finally, in 14 a schematic view of a transmission G according to a thirteenth embodiment of the invention shown. This corresponds again essentially to the variant 2 In contrast, the first planetary gear set P1 and the second planetary gear set P2 form a Ravigneaux wheel set. For this purpose, the third element E31 of the first planetary gear P1 and the second element E22 of the second planetary gear P2 to a common element ER1 of Ravigneaux wheelset in the form of a combined planetary PS. Likewise, the second element E21 of the first planetary gear set P1 and the third element E32 of the second planetary gear set P2 are formed by a common element ER2 of the Ravigneaux wheel set in the form of a common ring gear HO. Finally, the third switching element B2 is provided radially surrounding and axially substantially at the level of the ring gear HO. Otherwise, the embodiment corresponds to 14 according to the variant 2 so that reference is made to what has been described. Again, in addition, analogous to the variant according to 3 , the first planetary gear set P1 as a minus planetary gear set and the second planetary gear set P2 as a positive planetary gear set are realized. Furthermore, could also in the embodiment according to 14 an electric machine connected to the drive shaft GW1 and a disconnect clutch are provided, as in the variant according to 4 was realized.

In 15 is an exemplary circuit diagram for the respective transmission G from the 2 to 14 tabulated. As can be seen, in each case a total of six forward gears 1 to 6, and a reverse gear R1 can be realized, wherein in the columns of the circuit diagram is marked with an X respectively, which of the switching elements K1, B1, B2, B3 or K3 and K2 in which the forward gears 1 to 6 and the reverse gear R1 are respectively closed. In each of the forward gears 1 to 6 and the reverse gear R1 are each two of the switching elements K1, B1, B2, B3 or K3 and K2 closed, to open at a successive circuit of the forward gears 1 to 6 each one of the switching elements involved and a another switching element is to close in the following.

As in 15 can be seen, a first forward gear 1 is switched by operating the third switching element B2 and the fifth switching element K2, starting from this, a second forward gear 2 is formed by the third switching element B2 is opened and subsequently the second switching element B1 is closed. Furthermore, it is then possible to switch to a third forward gear 3 by opening the second shift element B1 again and closing the first shift element K1. Proceeding from this, a fourth forward gear 4 results by opening the first shift element K1 and closing the fourth shift element B3 or K3. Subsequently, a fifth forward gear 5 results by opening the fifth shift element K2 and actuating the first shift element K1, starting from this in a sixth forward gear 6 is switched by the first switching element K1 is opened again and the second switching element B1 is closed.

The reverse gear R1, in which a reverse drive of the motor vehicle can be realized even when driven by the internal combustion engine VKM, however, is switched by closing the first switching element K1 and the third switching element B2.

As in the 2 to 14 is shown, the switching elements B2 and K2 are designed as non-positive switching elements. However, the two switching elements B2 and K2 could also be realized in each case as a form-locking switching element, such as, for example, as a blocking synchronization or as a claw switching element.

In the 13 shown arrangement of a constant level KS can also according to the variants of 3 to 12 or 14 are used by the output shaft GW2 is coupled in accordance with the following constant level KS.

Finally, that can be done in 14 summarized summarizing the first planetary gear set P1 and the second planetary gear set P2 to a Ravigneaux wheelset analogous to the variants of 3 to 13 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.

reference numeral

• G

  transmission

  GG

  Non-rotating component

  P1

  First planetary gear set

  E11

  First element of the first planetary gear set

  E21

  Second element of the first planetary gear set

  E31

  Third element of the first planetary gear set

  P2

  Second planetary gear set

  E12

  First element of the second planetary gear set

  E22

  Second element of the second planetary gear set

  E32

  Third element of the second planetary gear set

  P3

  Third planetary gear set

  E13

  First element of the third planetary gear set

  E23

  Second element of the third planetary gear set

  E33

  Third element of the third planetary gear set

  ER1

  element

  ER2

  element

  K1

  First switching element

  B1

  Second switching element

  B2

  Third switching element

  B3

  Fourth switching element

  K2

  Fifth switching element

  K3

  Fourth switching element

  1

  First forward

  2

  Second forward speed

  3

  Third forward

  4

  Fourth forward

  5

  Fifth forward speed

  6

  Sixth forward

  R1

  reverse gear

  LV1

  drive shaft

  Level 1-A

  External interface of the drive shaft

  GW2

  output shaft

  GW2-A

  External interface of the output shaft

  EM

  electric machine

  S

  stator

  R

  rotor

  AT

  connecting shaft

  K0

  separating clutch

  VKM

  Internal combustion engine

  TS

  torsional vibration damper

  AG

  transaxles

  DW

  drive wheels

  KS

  constant level

  PS

  planetary stage

  E1

  first element planetary stage

  E2

  second element planetary stage

  E3

  third element planetary stage

  FROM

  output

  DK

  differential carrier

  SS1

  first spur gear

  SS2

  second spur gear

  SR1

  spur gear

  SR2

  spur gear

  SR3

  spur gear

  SR4

  spur gear

  ZW

  intermediate shaft

  PS

  planet spider

  HO

  ring gear

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 2009264237 A1 [0002]

Claims (16)

 Transmission (G) for a motor vehicle, comprising a drive shaft (GW1) and an output shaft (GW2), and at least functionally a first (P1), a second (P2) and a third planetary gear set (P3), wherein the planetary gear sets (P1, P2 , P3) each comprise a plurality of elements (E11, E12, E13, E21, E22, E23, E31, E32, E33) and serve to guide a power flow from the drive shaft (GW1) to the output shaft (GW2), wherein a first (K1 ), a second (B1), a third (B2), a fourth (B3; K3) and a fifth switching element (K2) are provided, through the selective actuation of the planetary gear sets (P1, P2, P3) under different gears (1 to 6, R1) between An- (GW1) and output shaft (GW2) are mutually coupled, wherein - The drive shaft (GW1) via the first switching element (K1) rotationally fixed to the first element (E11) of the first planetary gear set (P1) is connectable, which also by means of the second switching element (B1) on a non-rotatable component (GG) can be fixed, - Wherein the second element (E21) of the first planetary gear set (P1) via the third switching element (B2) on the rotationally fixed component (GG) can be fixed, - And wherein the third element (E31) of the first planetary gear set (P1) and the second element (E22) of the second planetary gear set (P2) are rotatably connected to each other and together in rotation with the output shaft (GW2) are in communication. Transmission (G) according to claim 1, characterized in that the drive shaft (GW1) also rotatably connected to the second element (E23) of the third planetary gear set (P3), the third element (E33) rotatably connected to the second element (E21) of the coupled to the first planetary gear set (P1) and the first element (E13) by means of the fourth switching element (B3) on the non-rotatable component (GG) can be fixed. Transmission (G) according to claim 1, characterized in that the drive shaft (GW1) also rotatably connected to the second element (E23) of the third planetary gear set (P3), the third element (E33) by means of the fourth switching element (K3) rotatably with the second element (E21) of the first planetary gear set (P1) coupled and whose first element (E13) on the non-rotatable component (GG) is fixed. Transmission (G) according to claim 1, characterized in that the drive shaft (GW1) also by means of the fourth switching element (K3) rotatably coupled to the second element (E23) of the third planetary gear set (P3), the third element (E33) rotatably with coupled to the second element (E21) of the first planetary gear set (P1) and whose first element (E13) is fixed to the non-rotatable component (GG). Transmission (G) according to one of the preceding claims, characterized in that the first element (E12) of the second planetary gear set (P2) via the fifth switching element (K2) rotatably coupled to the drive shaft (GW1), whereas the third element (E32) of the second planetary gear set (P2) rotationally fixed to the second element (E21) of the first planetary gear set (P1) is connected. Transmission (G) according to one of claims 1 to 4, characterized in that the first element (E12) of the second planetary gear set (P2) rotatably connected to the drive shaft (GW1), whereas the third element (E32) of the second planetary gear set (P2 ) via the fifth switching element (K2) rotatably coupled to the second element (E21) of the first planetary gear set (P1) can be coupled. Transmission (G) according to one of the preceding claims, characterized in that a first forward gear (1) by operating the third (B2) and the fifth switching element (K2), a second forward gear (2) by operating the second (B1) and a fifth forward gear (K2), a third forward gear (3) by operating the first (K1) and the fifth shift element (K2), a fourth forward gear (4) by operating the fourth (B3; K3) and the fifth shift element (K2), a fifth forward speed (5) by operating the first (K1) and fourth shifting elements (B3; K3), a sixth forward speed (6) by operating the second (B1) and fourth shifting elements (B3; K3), and a reverse gear ( R1) is switchable by operating the first (K1) and the third switching element (B2). Transmission (G) according to one of the preceding claims, characterized in that the first planetary gear set (P1) and the second planetary gear set (P2) form a Ravigneaux wheelset by the first planetary gear set (P1) and the second planetary gear set (P2) via at least one common element (ER1, ER2). Transmission (G) according to one of the preceding claims, characterized in that the respective planetary gear set (P2, P3; P1, P3) is in the form of a minus planetary gearset, wherein the respective first element (E12, E13; E11, E13) of the respective planetary gear set (P2, P3, P1, P3) about a respective sun gear, at the respective second element (E22, E23; E21, E23) of the respective planetary gear set (P2, P3, P1, P3) about a respective planet land and at the respective one third element (E32, E33, E31, E33) of the respective planetary gear set (P2, P3, P1, P3) is a respective ring gear. Transmission (G) according to one of the preceding claims, characterized in that the respective planetary gear set (P1; P2) is present as a positive planetary gear set, wherein the respective first element (E11; E12) of the respective planetary gear set (P1; a respective sun gear, wherein the respective second element (E21; E22) of the respective planetary gear set (P1; P2) is a respective ring gear and the respective third element (E31; E32) of the respective planetary gear set (P1; P2) is a respective planet gear , Transmission (G) according to one of the preceding claims, characterized in that one or more switching elements (K1, B1, B2, B3, K2, K1, B1, B2, K3, K2) are each realized as non-positive switching element. Transmission according to one of the preceding claims, characterized in that the third switching element and / or the fifth switching element is realized as a form-locking switching element. Transmission (G) according to one of the preceding claims, characterized in that an electric machine (EM) is provided, whose rotor (R) is coupled to a component. Transmission (G) according to one of the preceding claims, characterized in that in addition a separating clutch (K0) is provided, via which the drive shaft (GW1) with a connecting shaft (AN) is rotatably connected. Transmission (G) according to one of the preceding claims, characterized in that in addition a planetary stage (PS) is provided as a constant stage (KS), of the elements sun gear, ring gear and planetary gear a first element (E1) with the output shaft (GW2) is coupled while a second element (E2) of the planetary stage (PS) permanently fixed and a third element (E3) of the planetary stage (PS) with a power take-off (AB) is rotatably connected.  Motor vehicle drive train comprising a transmission (G) according to one or more of claims 1 to 15.

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