DE102017216296B4 - Hybrid unit for a motor vehicle - Google Patents

Abstract

Hybrid unit (HE) for a motor vehicle, comprising an electric machine (EM) and a transmission (G) with a drive shaft (GW1), an output shaft (GW2), and a first planetary gear set (P1) and a second planetary gear set (P2), wherein the Planetary gear sets (P1, P2) each comprise several elements (E11, E21, E31, E12, E22, E32), the gearbox (G) having a first (B1), a second (K1), a third (K2), a fourth (B2) and a fifth switching element (K3), wherein a rotor (R) of the electric machine (EM) on the drive shaft (GW1), on the output shaft (GW2) or at least one of the elements (E11, E21, E31, E12, E22, E32) of the planetary gear sets (P1, P2) is connected, characterized in that - the first element (E11) of the first planetary gear set (P1) can be fixed in a rotationally fixed manner via the first switching element (B1), - that the second element (E21 ) of the first planetary gear set (P1) and the output shaft (GW2) are connected to one another in a rotationally fixed manner, - that the output shaft (GW2) can be connected to the drive shaft (GW1) in a rotationally fixed manner by means of the second switching element (K1), as well as via the third switching element (K2 ) can be connected in a rotationally fixed manner to the third element (E32) of the second planetary gear set (P2), - that the third element (E32) of the second planetary gear set (P2) can be fixed in a rotationally fixed manner by means of the fourth switching element (B2), - that the drive shaft (GW1) is non-rotatably connected to the first element (E12) of the second planetary gear set (P2), the second element (E22) and the third element (E31) of the first planetary gear set (P1) are non-rotatably connected to one another, - and that by closing the fifth switching element (K3) two of the elements (E12, E22, E32) of the second planetary gear set (P2) can be connected.

Description

The invention relates to a hybrid unit for a motor vehicle, comprising an electric machine and a transmission with a drive shaft, an output shaft and a first planetary gear set and a second planetary gear set, the planetary gear sets each comprising a plurality of elements, the transmission having a first, a second, a third, has a fourth and a fifth switching element, wherein a rotor of the electric machine is connected to the drive shaft, to the output shaft or at least one of the elements of the planetary gear sets. The invention further relates to a motor vehicle drive train for a hybrid vehicle and methods for operating a hybrid unit.

In hybrid vehicles, hybrid units are known, which are composed of one or more electric machines and a transmission. The transmission is usually designed as a multi-speed transmission, i.e. H. Several different transmission ratios can be switched as gears between a drive shaft and an output shaft of the transmission by actuating corresponding switching elements, this preferably being carried out automatically. Depending on the arrangement of the switching elements, these are clutches or brakes. The transmission is used to appropriately implement the tractive power offered by a drive machine of the motor vehicle with regard to various criteria, with the gears of the transmission usually also being used in interaction with the at least one electric machine to represent purely electric driving. The at least one electric machine can often also be integrated in different ways via the transmission to display different operating modes.

From the DE 10 2013 013 947 A1 creates a hybrid unit for a motor vehicle that consists of a transmission and an electric machine. The transmission has a planetary design and is composed of two planetary gear sets, each of which is formed by the elements sun gear, planetary web and ring gear. The transmission is also assigned a total of five switching elements, which can be used to display different power flow routings.

A total of four gears can be achieved between a drive shaft and an output shaft of the transmission when driven by a drive machine upstream of the hybrid unit, as well as two electric gears when driven by the electric machine.

It is the object of the present invention to create an alternative embodiment to the hybrid unit for a motor vehicle known from the prior art, with which different operating modes can be represented in a suitable manner with a compact structure.

This task is solved based on the preamble of claim 1 in conjunction with its characterizing features. The following dependent claims each reflect advantageous developments of the invention. A motor vehicle drive train for a hybrid vehicle is also the subject of claim 15. Furthermore, claims 16 to 18 each relate to methods for operating a hybrid unit.

According to the invention, a hybrid unit comprises an electric machine and a transmission, the transmission having a drive shaft, an output shaft and a first planetary gear set and a second planetary gear set. The planetary gear sets also include several elements, with the transmission being assigned a first, a second, a third, a fourth and a fifth switching element, through the selective actuation of which different power flows can be represented by switching different gears of the transmission. Furthermore, a rotor of the electric machine is connected to the drive shaft, to the output shaft or at least one of the elements of the planetary gear sets.

For the purposes of the invention, a “shaft” is to be understood as meaning a rotatable component of the transmission, via which associated components of the hybrid unit are connected to one another in a rotationally fixed manner or via which such a connection is established when a corresponding switching element is actuated. The shaft can connect the components to one another axially or radially or both axially and radially. The respective shaft can also be present as an intermediate piece via which a respective component is connected radially, for example.

For the purposes of the invention, “axial” means an orientation in the direction of an axis along which the planetary gear sets are arranged coaxially with one another. “Radial” then means an orientation in the diameter direction of a shaft that lies on this axis.

The output shaft of the transmission preferably has teeth, via which the output shaft is then in operative connection in the motor vehicle drive train with a differential gear arranged axially parallel to the output shaft. Here the toothing is preferably on one Connection point of the output shaft is provided, this connection point of the output shaft preferably being located axially at one end of the transmission, at which a connection point of the drive shaft is also provided. This type of arrangement is particularly suitable for use in a motor vehicle with a drive train aligned transversely to the direction of travel of the motor vehicle.

The invention now includes the technical teaching that the first element of the first planetary gear set can be fixed in a rotationally fixed manner via the first switching element. In addition, the second element of the first planetary gear set and the output shaft are connected to one another in a rotationally fixed manner and can be connected together, on the one hand, in a rotationally fixed manner to the drive shaft by means of the second switching element and, on the other hand, in a rotationally fixed manner to the third element of the second planetary gear set via the third switching element. The third element of the second planetary gear set can also be fixed in a rotationally fixed manner by means of the fourth switching element. Furthermore, the drive shaft is connected in a rotationally fixed manner to the first element of the second planetary gear set, the second element and the third element of the first planetary gear set being connected to one another in a rotationally fixed manner. Finally, the second planetary gear set can be locked via the fifth switching element in that the fifth switching element connects two of the elements of the second planetary gear set to one another in a rotationally fixed manner.

In other words, the drive shaft is permanently connected in a rotationally fixed manner to the first element of the second planetary gear set, while the output shaft is constantly connected in a rotationally fixed manner to the second element of the first planetary gear set. In addition, the third element of the first planetary gear set and the second element of the second planetary gear set are permanently connected to one another in a rotationally fixed manner.

When the first switching element is actuated, the first element of the first planetary gear set is fixed in a rotationally fixed manner and is therefore prevented from rotating. In contrast, in the closed state, the second switching element connects the second element of the first planetary gear set and the output shaft to the drive shaft in a rotationally fixed manner, so that a rigid through drive from the drive shaft to the output shaft is possible. The second element of the first planetary gear set and the output shaft are also connected in a rotationally fixed manner to the third element of the second planetary gear set when the third switching element is actuated, the latter also being fixed in a rotationally fixed manner in the closed state of the fourth switching element and thus being prevented from rotating. Finally, the fifth switching element blocks the second planetary gear set when actuated.

According to the invention, a respective rotation-proof connection of the rotatable components of the hybrid unit is preferably implemented via one or more intermediate shafts, which can also be present as short intermediate pieces if the components are in a spatially close position. Specifically, the components that are permanently connected to one another in a rotationally fixed manner can each be present either as individual components that are connected to one another in a rotationally fixed manner or in one piece. In the second-mentioned case, the respective components and the possibly existing shaft are then formed by a common component, this being realized in particular when the respective components in the hybrid unit are spatially close to one another.

For components of the hybrid unit and here in particular components of the transmission, which are only connected to one another in a rotationally fixed manner by actuating a respective switching element, a connection is also preferably implemented via one or more intermediate shafts.

A rotationally fixed fixing is carried out in particular by a rotationally fixed connection to a rotationally fixed component of the transmission, which is preferably a permanently stationary component, preferably a housing of the hybrid unit, a part of such a housing or a component of the transmission connected to it in a rotationally fixed manner.

In the transmission of the hybrid unit according to the invention, the first switching element and the fourth switching element are designed as brakes, which, when activated, brake the respective component of the transmission to a standstill and fix it on the non-rotatable component. In contrast, the second, the third and the fifth switching element are present as clutches, which, when actuated, align the rotational movements of the associated rotatable components of the transmission and subsequently connect them to one another in a rotationally fixed manner.

In the actuated state, the fifth switching element ensures that the second planetary gear set is locked, this being achieved by the fifth switching element connecting two elements of the second planetary gear set to one another in a rotationally fixed manner in the closed state. In the case of the two planetary gear sets being designed as negative planetary gear sets, this can be achieved by a rotationally fixed connection of the first element and the second element of the second planetary gear set or of the second element and the third element of the second plane tenwheel set must be realized. However, when the first planetary gear set is designed as a minus planetary gear set and the second planetary gear set as a plus planetary gear set, there are two variants in which the fifth switching element in the actuated state is the first element and the third element of the second planetary gear set or the second element and the third element of the second planetary gear set connects together in a rotationally fixed manner.

In the case of the transmission, a separating clutch can be provided on the drive side, which in the actuated state connects the drive shaft in a rotationally fixed manner to a connecting shaft, which in turn is coupled to the drive machine connected upstream of the hybrid unit. This separating clutch can in principle be designed as a non-positive or positive switching element, but is particularly preferably in the form of a friction clutch.

Overall, a hybrid unit according to the invention is characterized by a compact design, low component loads, good gearing efficiency and low transmission losses.

In the transmission according to the invention, four mechanical gears can be achieved by selectively closing two switching elements each. This results in a first mechanical gear by operating the first and fourth switching elements, while a second mechanical gear can be achieved by operating the first and third switching elements. Furthermore, a third mechanical gear can be shifted by closing the first and fifth switching elements, whereas a fourth mechanical gear results in a first variant by actuating the first and second switching elements. In addition, fourth gear can be achieved in a second variant by closing the second and third switching elements, in a third variant by actuating the second and fourth shifting elements, in a fourth variant by closing the second and fifth shifting elements and in a fifth variant by actuating the third and fifth switching elements can be switched.

With a suitable choice of stationary gear ratios for the planetary gear sets, a series of ratios suitable for use in a motor vehicle is achieved. For a successive switching of the gears according to their order, the state of two switching elements must always be varied by opening one of the switching elements involved in the previous gear and closing another switching element to represent the subsequent gear. This also means that switching between gears can happen very quickly.

According to an advantageous embodiment of the invention, the rotor of the electric machine is constantly connected to the third element of the first planetary gear set and the second element of the second planetary gear set. Arranging the electric machine in this area is advantageous because this allows different operating modes of the hybrid unit to be implemented in a simple manner.

As an operating mode, purely electric driving in a first electric gear can be represented by closing the first switching element, whereby the associated fixing of the first element of the first planetary gear set on the non-rotatable component results in a connection of the electric machine to the output shaft with a constant gear ratio. Since two switching elements each need to be closed for the mechanical gears, the drive motor connected upstream of the hybrid unit is not coupled. Starting from purely electrical operation, the upstream drive machine can also be started in the first mechanical gear, the second mechanical gear, the third mechanical gear and the first variant of the fourth mechanical gear, since the first switching element is involved in each of these mechanical gears. In this respect, starting can take place in a simple manner. In the electric gear, the vehicle can move forwards and backwards, depending on which direction of rotation is initiated via the electric machine.

For the purposes of the invention, a “mechanical gear” means one of the representable gears of the transmission of the hybrid unit, in which a power flow is guided from the drive shaft to the output shaft and which is therefore suitable for travel when driven by the drive machine upstream of the hybrid unit. The term “electric gear”, on the other hand, means a gear in which a flow of power takes place from the electric machine to the output shaft and thus travel is achieved when driven by the electric machine.

As a further operating mode, with the arrangement of the electric machine described above, a start-up mode for reversing when driven via the drive shaft and thus the drive machine upstream of the hybrid unit can also be implemented. For this purpose, the third switching element is closed, so that a superimposed state is created on the second planetary gear set, in which the rotational movement of the via the third switching element The third element of the second planetary gear set, which is non-rotatably connected to the output shaft, is determined by the superimposition of the rotational movements of the first element and the second element of the second planetary gear set. By supporting the torque via the electric machine on the second element of the second planetary gear set, starting for reverse travel can be achieved.

As a further operating mode, a charging operation of an electrical energy storage device can also be implemented by simply closing the fifth switching element and thereby establishing a connection between the drive shaft and the electric machine and thus also between the upstream drive machine and the electric machine due to the blocking of the second planetary gear set. At the same time, there is no frictional connection to the output shaft, so that the transmission is in a neutral position. Apart from charging operation, the upstream drive machine can also be started via the electric machine. Alternatively, the charging operation and the starting operation can also be implemented by closing the fourth switching element, whereby the electric machine and the drive shaft are indirectly connected to one another in a rotationally fixed manner.

Since the electric machine is coupled to the output shaft when the first switching element is closed, power shifts can also be implemented between the first and second mechanical gears, between the second and third mechanical gears and between the third mechanical gear and the first variant of the fourth mechanical gear as the electric machine can provide support during the circuits. The synchronization of the switching element to be closed during a shift can be carried out by speed control of the upstream drive machine or by synchronized switching elements or by another, separate synchronization device, such as a transmission brake or another electric machine. If a separating clutch is also provided on the drive side of the drive shaft, the inertial mass of the upstream drive machine can be decoupled during synchronization. Within the scope of the invention, it is also conceivable to optionally use a further electric machine to support the synchronization, which is directly or indirectly operatively connected to the drive shaft.

The transmission according to the invention can also be operated in such a way that a reduction in the speed of the electric machine is achieved during mechanical or hybrid driving in fourth gear. In the first variant of the fourth mechanical gear, hybrid driving is initially carried out in that the first switching element initially remains closed either after a torque-assisted shift from third to fourth gear via the electric machine or after the drive machine has been started in fourth gear. In order to reduce the speed of the electric machine in fourth gear at higher driving speeds, you can switch from the first variant of fourth gear to the second variant, since here the rotor of the electric machine has a lower speed than in the first variant of fourth gear. This switchover takes place while maintaining the tractive force by the drive machine upstream of the hybrid unit. First, the load-free, first switching element is laid out and then the load-free, third switching element is inserted, with the speed adjustment being carried out by speed control of the electric machine. If a separating clutch is also provided, via which the drive shaft can be connected to a connecting shaft on the drive side, the upstream drive machine can also be decoupled in the second variant of fourth gear. The latter makes sense if recuperation is to take place via the electric machine even at higher driving speeds and the drive machine has to be decoupled and switched off.

For the purposes of the invention, a “permanent connection” of the rotor of the electric machine with the second element of the second planetary gear set and the third element of the first planetary gear set is to be understood as meaning a constant coupling between these components, so that between the rotor of the electric machine and the second element of the The same speed dependency permanently prevails between the second planetary gear set and the third element of the first planetary gear set. The electric machine can be arranged either coaxially with the planetary gear sets or axially offset from them. In the former case, the rotor of the electric machine can either be directly connected to the transmission in a rotationally fixed manner or coupled to it via one or more intermediate transmission stages, the latter enabling a more favorable design of the electric machine with higher speeds and lower torque. The at least one transmission stage can be designed as a spur gear stage and/or as a planetary gear stage.

If, on the other hand, the electric machine is provided with an axial offset to the planetary gear sets, a coupling takes place via one or more intermediate transmission stages and/or a traction drive. The one or more translation stages can also be defined in detail neither be realized as a spur gear stage nor as a planetary stage. A traction drive can be either a belt drive or a chain drive.

According to a further possible embodiment of the invention, exactly one electric machine is provided, which is set up to drive the output shaft. In this case, the hybrid unit according to the invention only has an electric machine, which can also act as a drive for the output shaft, which is then preferably connected to the third element of the first planetary gear set and the second element of the second planetary gear set. This has the advantage that a compact structure and low manufacturing costs for the hybrid unit can be achieved.

Alternatively, a second electric machine can be provided, the rotor of which is constantly connected to the drive shaft. The functionality of the hybrid unit can be further increased by such a design.

It is a further embodiment of the invention that the transmission has a further switching element, via which two of the elements of the first planetary gear set can be connected. In other words, a further switching element is additionally provided, which blocks the first planetary gear set in the actuated state. For this purpose, the further switching element connects two of the elements of the first planetary gear set to one another in a rotationally fixed manner, with particularly preferably the first element and the second element of the first planetary gear set being connected to one another in a rotationally fixed manner in the actuated state of the further switching element.

By providing the further switching element, the fourth mechanical gear can be represented in further variants. In a further variant, the fourth gear results from actuating the second and the further switching element, in a further variant by actuating the fifth and the further switching element and in a further variant by actuating the third and the further switching element. In addition, an additional gear can be formed by actuating the fourth and further switching elements, although this additional gear does not fit optimally into the remaining gear range.

In addition, a second electrical gear is created by closing the further switching element, so that two electrical gears can be formed in this embodiment of the hybrid unit. Starting from this second electrical gear, the upstream drive machine can be started in fourth mechanical gear.

Furthermore, in the aforementioned embodiment, in order to reduce the speed of the electric machine, it is possible to shift from the first variant of the fourth gear to the variant of the fourth gear, in which the second switching element and the further switching element are closed. This is done while maintaining the tractive force via the upstream drive machine, with the load-free, first switching element first being laid out and then the load-free, further switching element being inserted. The speed is adjusted by controlling the speed of the electric machine. The advantage of using the further variant of fourth gear is that, on the one hand, the drive machine can be disconnected at any time by opening the second switching element, even without a separating clutch, while the electric machine is driving the vehicle or braking in the course of recuperation. In addition, when the vehicle slows down, a downshift to the third mechanical gear can be prepared by changing back to the first variant of the fourth gear while the upstream drive machine receives the traction. In the first variant of the fourth mechanical gear, the first switching element is then closed, which is required to support the tractive force via the electric machine when shifting down to the third mechanical gear.

According to a further possible embodiment of the invention, which can be used as an alternative or in addition to the aforementioned embodiment of the invention, the transmission also has an additional switching element, via which the first element of the first planetary gear set can be connected to the drive shaft in a rotationally fixed manner. An additional switching element is therefore provided, which in the closed state connects the first element of the first planetary gear set and the drive shaft to one another in a rotationally fixed manner.

In the course of the aforementioned design option, further variants of the fourth mechanical gear can also be presented. In a further variant, the fourth gear is achieved by actuating the second and the additional switching element, in a further variant by actuating the fifth and the additional shifting element and in a further variant by actuating the third and the additional shifting element. In addition, an additional gear can be realized by closing the fourth and additional switching elements. However, the latter does not fit perfectly into the rest of the translation series.

In a hybrid unit designed according to the design option described above, a starting mode for forward travel when driven via the drive shaft can also be implemented. For this purpose, the additional switching element is closed so that the rotational movements of the drive shaft and the electric machine are superimposed on the first planetary gear set. This is because the first element of the first planetary gear set is connected to the drive shaft in a rotationally fixed manner, while the electric machine is permanently coupled in a rotationally fixed manner to the third element of the first planetary gear set. As a result, a rotational movement of the second element of the first planetary gear set and thus of the output shaft is defined by a superposition of the rotational movements initiated via the electric machine and the upstream drive machine. This allows electrodynamic starting for forward travel to be realized.

In a further development of the invention, one or more switching elements are each implemented as a positive switching element. The respective switching element is preferably designed either as a claw switching element or as a locking synchronization. Positive switching elements have the advantage over non-positive switching elements that lower drag losses occur in the open state, so that better transmission efficiency can be achieved. In particular, in the hybrid unit according to the invention, all switching elements are implemented as positive switching elements, so that the lowest possible drag losses can be achieved.

Within the scope of the invention, the two planetary gear sets can each be present as negative planetary gear sets, with a first element of the respective planetary gear set then being a sun gear, a second element of the respective planetary gear set being a planetary web and a third element of the respective planetary gear set being a Ring gear is. A minus planetary set is composed, in a manner known in principle to those skilled in the art, of the elements sun gear, planetary web and ring gear, with the planetary web having at least one, but preferably several, planetary gears rotatably mounted, each of which is connected to both the sun gear and the comb the surrounding ring gear.

Alternatively, one or both planetary gear sets could, if the connection of the respective elements allows it, be present as a plus planetary gear set, with the first element of the respective planetary gear set then being a sun gear and the second element of the respective planetary gear set being a ring gear and the third element of the respective planetary gear set is a planetary web. In a plus planetary set, the elements sun gear, ring gear and planetary web are also present, with the latter leading at least one pair of planetary gears, in which one planetary gear meshes with the internal sun gear and the other planetary gear meshes with the surrounding ring gear, and the planetary gears mesh with each other.

Where it is possible to connect the individual elements, a minus planetary set can be converted into a plus planetary set, whereby the ring gear and the planetary web connection must then be swapped with each other compared to the version as a minus planetary set, and a gear ratio must be increased by one. Conversely, a plus planetary set could also be replaced by a minus planetary set, provided the connection of the transmission elements allows this. In comparison to the plus planetary set, the ring gear and the planetary web connection would also have to be exchanged with each other, and a gear ratio would have to be reduced by one. According to a first variant of the invention, both planetary gear sets are designed as minus planetary gear sets, whereas in a second embodiment of the invention the first planetary gear set is in the form of a minus planetary gear set and the second planetary gear set is in the form of a plus planetary gear set.

In a further development of the invention, at least two switching elements are combined to form a switching element pair, each of which is assigned an actuating element, whereby either one switching element or the other switching element of the respective switching element pair can be actuated from a respective neutral position. This is implemented in switching elements of the transmission that have a common shaft and are not operated in one gear at the same time, and has the advantage that the number of actuating elements can be reduced and thus the manufacturing effort can be reduced. If necessary, even three switching elements can be actuated via a common actuating element, provided that all three switching elements create a connection to one and the same shaft and cannot be actuated at the same time.

Depending on the specific design of the hybrid unit, the second switching element and the fifth switching element and/or the third switching element and the fourth switching element and/or the fourth switching element and the fifth switching element and/or the second switching element and the third switching element and/or the fourth Switching element and the fifth switching element and / or the first switching element and the further switching element and / or the first switching element and the additional Switching element can be combined in pairs and each have a common actuating element. In addition, combining the first switching element, the further switching element and the additional switching element is also possible, so that three switching elements can each be actuated via a common actuating element. The first switching element is then preferably in the middle position.

Within the scope of the invention, the transmission of the hybrid unit can 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 is used to design a starting process by allowing a slip speed between the internal combustion engine and the drive shaft of the transmission. One of the switching elements of the transmission or the possibly existing separating clutch can also be designed as such a starting element in that it is present as a friction switching element. In addition, in principle, a freewheel to the gearbox housing or to another shaft can be arranged on each shaft of the transmission.

The hybrid unit according to the invention is in particular part of a motor vehicle drive train for a hybrid vehicle and is then arranged between a drive engine of the motor vehicle, which is designed in particular as an internal combustion engine, and further components of the drive train following in the direction of power flow to the drive wheels of the motor vehicle. Here, the drive shaft of the transmission of the hybrid unit is either permanently coupled in a rotationally fixed manner to a crankshaft of the internal combustion engine or can be connected to it via an intermediate separating clutch or a starting element, whereby a torsional vibration damper can also be provided between the internal combustion engine and the transmission. On the output side, the transmission within the motor vehicle drive train is then preferably coupled to a differential gear of a drive axle of the motor vehicle, although here there can also be a connection to a longitudinal differential, via which distribution to several driven axles of the motor vehicle takes place. The differential gear or the longitudinal differential can be arranged with the gear in a common housing.

A torsional vibration damper can also be integrated into this housing.

The fact that two components of the hybrid unit are “connected” or “coupled” in a rotationally fixed manner or are “connected to one another” means, in the sense of the invention, a permanent coupling of these components so that they cannot rotate independently of one another. In this respect, no switching element is provided between these components, which can be elements of the planetary gear sets and/or shafts and/or a non-rotatable component of the transmission, but rather the corresponding components are rigidly coupled to one another.

If, on the other hand, a switching element is provided between two components, these components are not permanently coupled to one another in a rotationally fixed manner, but a rotationally fixed coupling is only carried out by actuating the intermediate switching element. Actuation of the switching element in the sense of the invention means that the switching element in question is transferred to a closed state and as a result the components directly coupled thereto align their rotational movements with one another. If the switching element in question is designed as a positive switching element, the components that are directly connected to one another in a rotationally fixed manner will run at the same speed, while in the case of a non-positive switching element, speed differences can exist between the components even after the same has been actuated. In the context of the invention, this desired or unwanted state is nevertheless referred to 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. There are also possibilities to combine individual features with one another, including those that emerge from the claims, the following description of preferred embodiments of the invention or directly from the drawings. Reference in 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 eine erfindungsgemäße Hybrideinheit zur Anwendung kommt;
• 2 - 14 je eine schematische Ansicht einer Hybrideinheit entsprechend einer ersten bis dreizehnten Ausführungsform der Erfindung;
• 15 ein beispielhaftes Schaltschema von Getrieben der Hybrideinheiten aus den 2 bis 14;
• 16 - 26 je eine schematische Darstellung einer Hybrideinheit gemäß einer vierzehnten bis vierundzwanzigsten Ausgestaltungsmöglichkeit der Erfindung;
• 27 ein beispielhaftes Schaltschema von Getrieben der Hybrideinheiten aus den 16 bis 26;
• 28 bis 34 je eine schematische Darstellung einer Hybrideinheit gemäß einer fünfundzwanzigsten bis einunddreißigsten Ausgestaltungsmöglichkeit der Erfindung;
• 35 ein beispielhaftes Schaltschema von Getrieben der Hybrideinheiten aus den 28 bis 34;
• 36 - 40 je eine schematische Ansicht einer Hybrideinheit entsprechend einer einunddreißigsten bis vierzigsten Ausführungsform der Erfindung; und
• 41 ein beispielhaftes Schaltschema von Getrieben der Hybrideinheiten aus den 36 bis 40.

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 hybrid unit according to the invention is used;
• 2 - 14 each a schematic view of a hybrid unit according to a first to thirteenth embodiment of the invention;
• 15 an exemplary switching diagram of the transmissions of the hybrid units from the 2 until 14 ;
• 16 - 26 a schematic representation of a hybrid unit according to a fourteenth to twenty-fourth possible embodiment of the invention;
• 27 an exemplary switching diagram of the transmissions of the hybrid units from the 16 until 26 ;
• 28 until 34 each a schematic representation of a hybrid unit according to a twenty-fifth to thirty-first embodiment option of the invention;
• 35 an exemplary switching diagram of the transmissions of the hybrid units from the 28 until 34 ;
• 36 - 40 each a schematic view of a hybrid unit according to a thirty-first to fortieth embodiment of the invention; and
• 41 an exemplary switching diagram of the transmissions of the hybrid units from the 36 until 40 .

1 shows a schematic view of a motor vehicle drive train of a hybrid vehicle, wherein in the motor vehicle drive train an internal combustion engine VKM is connected to a transmission G of a hybrid unit HE via an intermediate torsional vibration damper TS. The transmission G is followed by a differential gear AG on the output side, via which drive power is distributed to drive wheels DW of a drive axle of the motor vehicle. The transmission G and the torsional vibration damper TS are combined with an electric machine EM in a common housing of the hybrid unit HE, into which the differential gear AG can then also be integrated. As also in 1 can be seen, the internal combustion engine VKM, the torsional vibration damper TS, the transmission G of the hybrid unit HE and also the differential gear AG are aligned transversely to a direction of travel of the motor vehicle.

Out of 2 shows a schematic representation of the hybrid unit HE according to a first embodiment of the invention. As can be seen, the hybrid unit HE is composed of the transmission G and the electric machine EM, which are combined together in the housing of the hybrid unit HE. The transmission G comprises two planetary gear sets P1 and P2, each of the planetary gear sets P1 and P2 having a first element E11 or E12, a second element E21 or E22 and a third element E31 or E32. The respective first element E11 or E12 is each formed by a sun gear of the respective planetary gear set P1 or P2, while the respective second element E21 or E22 in the planetary gear sets P1 and P2 is each present as a planetary web. The remaining third element E31 or E32 is then formed by a respective ring gear of the respective planetary gear set P1 or P2.

In the present case, the planetary gear sets P1 and P2 are each designed as minus planetary sets, in which the respective planetary web has one, but preferably several, planet gears rotatably mounted, which are in mesh with the radially inner sun gear and also with the surrounding ring gear.

Where the connection allows it, one or both planetary gear sets P1 and P2 could be designed as plus planetary gear sets. In the case of a plus planetary set, the planetary web then carries at least one pair of planetary gears, of which a planetary gear meshes with the radially inner sun gear and a planetary gear meshes with the radially surrounding ring gear, and the planetary gears of the gear pair mesh with one another. In comparison to a respective version as a minus planetary set, the respective second element E21 or E22 would then have to be formed by the respective ring gear and the respective third element E31 or E32 by the respective planetary web and also a respective one Gear ratio can be increased by one.

As in 2 As can be seen, the transmission G comprises a total of five switching elements in the form of a first switching element B1, a second switching element K1, a third switching element K2, a fourth switching element B2 and a fifth switching element K3. The switching elements B1, K1, K2, B2 and K3 are each designed as positive switching elements and are preferably in the form of claw switching elements. In addition, the second switching element K1, the third switching element K2 and the fifth switching element K3 are designed as clutches, while the first switching element B1 and the fourth switching element B2 are designed as brakes.

The first element E11 of the first planetary gear set P1 can be fixed via the first switching element B1 to a rotationally fixed component GG, which is in particular the housing of the hybrid unit HE or a part of the housing. The second element E21 of the first planetary gear set P1 is connected in a rotationally fixed manner to an output shaft GW2 of the transmission G, wherein the second element E21 of the first planetary gear set P1 and the output shaft GW2 are jointly connected in a rotationally fixed manner to a drive shaft GW1 of the transmission G via the second switching element K1 and, on the other hand, are connected in a rotationally fixed manner to the third element E32 of the second planetary gear set P2 by means of the third switching element K2 can be brought.

As also in 2 As can be seen, the third element E32 of the second planetary gear set P2 can also be fixed to the non-rotatable component GG by actuating the fourth switching element B2. The first element E12 of the second planetary gear set P2 is also permanently connected to the drive shaft GW1 in a rotationally fixed manner, whereas the second element E22 of the second planetary gear set P2 and the third element E31 of the first planetary gear set P1 are constantly connected to one another in a rotationally fixed manner and are directly connected in a rotationally fixed manner to a rotor R the electric machine EM are connected. The electric machine EM is placed coaxially with the two planetary gear sets P1 and P2, with a stator S of the electric machine EM being attached to the rotationally fixed component GG. Finally, by actuating the fifth switching element K3, a blocking of the second planetary gear set P2 is caused by the fifth switching element K3, in the actuated state, connecting the first element E12 and the second element E22 of the second planetary gear set P2 to one another in a rotationally fixed manner.

Both the drive shaft GW1 and the output shaft GW2 each form a connection point GW1-A or GW2-A, with the connection point GW1-A in the motor vehicle drive train 1 serves to connect to the internal combustion engine VKM, while the transmission G is connected to the subsequent differential gear AG at the connection point GW2-A. The connection points GW1-A and GW2-A of the drive shaft GW1 and the output shaft GW2 are designed at an axial end of the transmission G, with the output shaft GW2 with its connection point GW2-A being aligned transversely to the connection point GW1-A of the drive shaft GW1. The two planetary gear sets P1 and P2 are arranged axially following the connection point GW1-A of the drive shaft GW1 in the order of the first planetary gear set P1 and the second planetary gear set P2.

How also from 2 As can be seen, the first switching element B1 is provided axially on a side of the first planetary gear set P1 facing the connection point GW1-A, whereas the second switching element K1 and the fifth switching element K3 are placed together axially between the first planetary gear set P1 and the second planetary gear set P2. The two switching elements K1 and K3 lie axially directly next to one another and can be actuated individually from a neutral position via a common actuating element - not shown here - so that the second switching element K1 and the fifth switching element K3 are designed as a double switching element.

The third switching element K2 and the fourth switching element B2 are provided axially in the area of the second planetary gear set P2 and radially surrounding it and are also axially directly next to one another. Furthermore, the two switching elements K2 and B2 also share a common actuating element - not shown - via which, in addition to a neutral position, either the third switching element K2 or the fourth switching element B2 can be actuated.

The electric machine EM is arranged at an end of the transmission G that is axially opposite to the connection point GW1.

Also goes out 3 a schematic representation of a hybrid unit HE according to a second embodiment of the invention, which essentially follows the previous variant 2 corresponds. What is different, however, is that a fifth switching element K3 now causes the second planetary gear set P2 to lock, in that the fifth switching element K3, in the actuated state, connects the second element E22 and the third element E32 of the second planetary gear set P2 to one another in a rotationally fixed manner. Furthermore, the third switching element K2 is now provided axially on a side of the first planetary gear set P1 facing the connection point GW1 -A of the drive shaft GW1, while the fifth switching element K3 is now arranged axially adjacent to the fourth switching element B2.

The fourth switching element B2 and the fifth switching element K3 share a common actuating element, via which either the fourth switching element B2 or the fifth switching element K3 can be actuated from a neutral position. The second switching element K1, on the other hand, is placed alone axially between the first planetary gear set P1 and the second planetary gear set P2 and is provided radially in the area of the second element E21 of the first planetary gear set P1. Otherwise, the embodiment corresponds 3 according to the previous variant 2 , so that reference is made to what has been described.

Out of 4 shows a schematic representation of a hybrid unit HE according to a third embodiment of the invention. This embodiment essentially corresponds according to the variant 2 , in contrast to this, the second element E22 of the second planetary gear set P2 is formed by a ring gear and the third element E32 of the second planetary gear set P2 is formed by a planetary web. In this respect, the second planetary gear set P2 is designed as a plus planetary gear set. As a further difference, in the closed state, a fifth switching element K3 connects the first element E12 and the third element E32 of the second planetary gear set P2 to one another in a rotationally fixed manner and thereby causes the second planetary gear set P2 to lock.

The second switching element K1 and the third switching element K2 are also arranged axially between the first planetary gear set P1 and the second planetary gear set P2 and are designed as a double switching element, in that the second switching element K1 and the third switching element K2 are assigned a common actuating element, via which from a neutral position either the second switching element K1 or the third switching element K2 can be actuated. The fourth switching element B2 and the fifth switching element K3, on the other hand, are placed axially on a side of the second planetary gear set P2 that is remote from the connection point GW1-A and are also designed as a double switching element with a common actuating element. In addition, the electric machine EM is provided axially between the first planetary gear set P1 and the second planetary gear set P2. Otherwise, the embodiment corresponds to 4 according to the variant 2 , so that reference is made to what has been described.

Furthermore shows 5 a schematic view of a hybrid unit HE according to a fourth possible embodiment of the invention, which largely follows the variant 2 corresponds. What is different is that the electric machine EM is now not placed coaxially, but offset from the axis of the planetary gear sets P1 and P2. As a result, a rotor of the electric machine EM - not shown in detail here - and the third element E31 of the first planetary gear set P1 and the second element E22 of the second planetary gear set P2 are not directly connected to one another in a rotationally fixed manner, but rather are coupled to one another via an intermediate spur gear stage SRS. A spur gear SR1 of the spur gear stage SRS is connected in a rotationally fixed manner to the third element E31 of the first planetary gear set P1 and the second element E22 of the second planetary gear set P2 and meshes with a spur gear SR2, which is arranged in a rotationally fixed manner on an input shaft EW of the electric machine EM. This input shaft EW then establishes the connection to the rotor within the electric machine EM. Otherwise, the embodiment corresponds to 5 according to the variant 2 , so that reference is made to what has been described.

In addition, it is in 6 a schematic representation of a hybrid unit HE according to a fifth embodiment of the invention is shown, which again essentially follows the variant 2 corresponds. As with the design 5 However, the electric machine EM is not placed coaxially, but offset from the axis of the planetary gear sets P1 and P2. A rotationally fixed coupling between the third element E31 of the first planetary gear set P1 and the second element E22 of the second planetary gear set P2 and a rotor - not shown - of the electric machine EM is implemented via a traction drive ZT, which is preferably in the form of a chain drive. This traction drive ZT couples the third element E31 of the first planetary gear set P1 and the second element E22 of the second planetary gear set P2 with an input shaft EW of the electric machine EM. Otherwise the variant corresponds to 6 according to the embodiment 2 , so that reference is made to what has been described.

7 shows a schematic view of a hybrid unit HE according to a sixth embodiment of the invention. This design option also largely corresponds to the embodiment 2 , whereby here again the electric machine EM is not placed coaxially, but offset from the axis of the planetary gear sets P1 and P2. Unlike the previous variants 5 and 6 the electric machine EM is connected to the third element E31 of the first planetary gear set P1 and the second element E22 of the second planetary gear set P2 via several transmission stages in the form of a planetary stage P and a spur gear stage SRS. The planetary stage P is composed of a sun gear SO, a planetary web PS and a ring gear HO, with the planetary web PS rotatably supporting at least one planetary gear PR, which meshes with both the radially inner sun gear SO and the surrounding ring gear HO . In this respect, the planetary stage P is designed as a minus planetary set.

The planetary web PS of the planetary stage P is permanently connected in a rotationally fixed manner to the second element E22 of the second planetary gear set P2 and thus also to the third element E31 of the first planetary gear set P1, while the ring gear HO is constantly fixed to the rotationally fixed component GG and is therefore permanently prevented from rotating . On the other hand, the sun gear SO is connected in a rotationally fixed manner to a spur gear SR1 of the spur gear stage SRS, which meshes with a spur gear SR2. The spur gear SR2 in turn is then rotationally fixed on an input shaft EW of the Elektroma Machine EM provided. Otherwise, the design options correspond to 7 according to the variant 2 , so that reference is made to what has been described.

Out of 8th shows a schematic representation of a hybrid unit HE according to a seventh embodiment of the invention, which again essentially follows the variant 2 corresponds. However, in this case too, the electric machine EM is not placed coaxially, but offset from the axis of the two planetary gear sets P1 and P2. In addition, as with the previous variant 7 , a connection of the electric machine EM to the transmission G via two transmission stages in the form of a planetary stage P and a spur gear stage SRS. A sun gear SO of the planetary stage P following the second planetary gear set P2 is permanently fixed to the rotationally fixed component GG, while a planetary web PS leading at least one planetary gear PR is permanently connected in a rotationally fixed manner to the second element E22 of the second planetary gear set P2. The at least one planet gear PR is in mesh with the sun gear SO and with a ring gear HO, which is connected in a rotationally fixed manner to a spur gear SR1 of the subsequent spur gear stage SRS.

The ring gear HO and the spur gear SR1 can be formed in one piece by providing the ring gear HO on an outer circumference with teeth defining the spur gear SR1. Within the spur gear stage SRS, the spur gear SR1 then meshes with a spur gear SR2, which is placed in a rotationally fixed manner on an input shaft EW of the electric machine EM. In the present case, the planetary stage P and the spur gear stage SRS are arranged essentially in an axial plane, the embodiment according to 8th otherwise according to the variant 2 corresponds, so that reference is made to what has been described.

9 shows a schematic representation of a hybrid unit HE according to an eighth embodiment of the invention, which in turn largely follows the variant 2 is modeled. In this case too, however, the electric machine EM is arranged axially offset from the planetary gear sets P1 and P2, with the electric machine EM being connected via two transmission stages in the form of a spur gear stage SRS and a planetary stage P. A spur gear SR1 of the spur gear stage SRS is connected in a rotationally fixed manner to the second element E22 of the second planetary gear set P2 and meshes with a spur gear SR2 of the spur gear stage SRS, which is connected in a rotationally fixed manner with a planetary web PS of the subsequent planetary stage P. The planetary web PS guides several planet gears PR1 and PR2, each of which meshes with a radially inner sun gear SO and a surrounding ring gear HO. The ring gear HO is permanently fixed to the non-rotatable component GG, whereas the sun gear SO is non-rotatably connected to an input shaft EW of the electric machine EM. The planetary stage P is arranged coaxially with the electric machine EM. Otherwise the design options correspond 9 according to the variant 2 , so that reference is made to what has been described.

Out of 10 shows a schematic view of a hybrid unit HE according to a ninth embodiment of the invention, which largely follows the immediately preceding variant 9 corresponds. The only difference is that the sun gear SO is now permanently fixed to the non-rotatable component GG, while the ring gear HO is non-rotatably connected to the input shaft EW of the electric machine EM. Otherwise, the embodiment corresponds to 10 according to the variant 9 , so that reference is made to what has been described.

Furthermore shows 11 a schematic representation of a hybrid unit HE according to a tenth embodiment of the invention. This design option largely corresponds to the variant 2 , in contrast to this, the electric machine EM, which is arranged coaxially to the planetary gear sets P1 and P2, is not directly connected in a rotationally fixed manner, but rather a connection is implemented via an intermediate planetary stage P. This planetary stage P is composed of a sun gear SO, a ring gear HO and a planetary web PS, the latter rotatably guiding at least one planet gear PR, which meshes with both the sun gear SO and the ring gear HO. The sun gear SO is permanently fixed to the non-rotatable component GG, while the planetary web PS is constantly connected to the second element E22 of the second planetary gear set P2 in a non-rotatable manner. Finally, the ring gear HO is permanently connected to the rotor R of the electric machine EM in a rotationally fixed manner.

As a further difference, the third switching element K2 and the fourth switching element B2 are now provided axially on a side of the first planetary gear set P1 facing the connection point GW1-A. Specifically, the two switching elements K2 and B2 lie axially between the connection point GW2-A of the output shaft GW2 and the first planetary gear set P1. Otherwise the design options correspond 11 according to the variant 2 , so that reference is made to what has been described.

Also goes out 12 a schematic view of a hybrid unit HE according to an eleventh embodiment of the invention, which essentially follows the immediately preceding variant 11 corresponds. The only difference is that the ring gear HO of the planetary stage P is now permanently fixed to the non-rotatable component GG, while the sun gear SO is non-rotatably connected to the rotor R of the electric machine EM. Otherwise the embodiment corresponds to 12 according to the variant 11 , so that reference is made to what has been described.

Furthermore shows 13 a schematic representation of a hybrid unit HE according to a twelfth possible embodiment of the invention. This design option largely corresponds to the variant 2 , in contrast to this, the first switching element B1 is now designed as a non-positive switching element in the form of a multi-disc brake. Otherwise the design options correspond 13 according to the variant 2 , so that reference is made to what has been described.

Out of 14 shows a schematic view of a hybrid unit HE according to a thirteenth embodiment of the invention, which largely follows the immediately preceding variant 13 corresponds. The only difference is that the drive shaft GW1 can now be connected in a rotationally fixed manner to a connecting shaft AN, which is located within the drive train, via a separating clutch K0 1 which establishes the connection to the upstream internal combustion engine VKM. The separating clutch K0 is designed as a multi-plate clutch. Otherwise, the embodiment corresponds to 14 according to the variant 13 , so that reference is made to what has been described.

In 15 is an exemplary switching diagram for the respective transmission G from the 2 until 14 presented in tabular form. As can be seen, a total of four mechanical gears 1 to 4.5 can be implemented, with an 4.5 is closed in each case. In each of the mechanical gears 1 to 4.5, two of the switching elements B1, K1, K2, B2 and K3 are closed, whereby when the mechanical gears 1 to 4.5 are shifted successively, one of the switching elements involved opens and another switching element subsequently closes is close.

As in 15 As can be seen, a first mechanical gear 1 is shifted by actuating the first switching element B1 and the fourth switching element B2, from which a second mechanical gear 2 is formed by opening the fourth switching element B2 and subsequently closing the third switching element K2. It is then possible to shift into a third mechanical gear 3 by opening the third switching element K2 and closing the fifth switching element K3. Based on this, a fourth mechanical gear then results in a first variant 4.1 by opening the fifth switching element K3 and closing the second switching element K1. The fourth mechanical gear can also be activated in a second variant 4.2 by actuating the second switching element K1 and the third switching element K2, in a third variant 4.3 by closing the second switching element K1 and the fourth switching element B2, in a fourth variant 4.4 by actuating the second switching element K1 and the fifth switching element K3, as well as in a fifth variant 4.5 by closing the third switching element K2 and the fifth switching element K3.

Although the switching elements B1, K1, K2, B2 and K3 are each designed as positive switching elements, switching between the mechanical gears 1 to 4.1 can be achieved under load. The reason for this is that the first switching element B1 is involved in all gears 1 to 4.1, so that during the shifts the output can be supported via the electric machine, which in the closed state of the first switching element B1 via the first planetary gear set P1 with the output shaft GW2 is coupled. Synchronization of the circuits can be achieved by appropriate control of the upstream internal combustion engine VKM, so that the switching element to be designed can be opened without load and the switching element to be closed subsequently can be closed without load.

The HE hybrid units 2 until 14 can also be operated in other operating modes with the help of the electric machine EM: purely electric driving can take place in a first electric gear E1, for which the first switching element B1 must be converted into a closed state, as shown 15 emerges. Because in the closed state of the first switching element B1, the electric machine EM is connected to the output shaft GW2 with a constant gear ratio, the gear ratio of the first electrical gear E1 corresponding to the gear ratio of the third mechanical gear 3.

Advantageously, starting from the first electrical gear E1, the internal combustion engine VKM can shift into one of the mechanical gears 1 to 4.1 must be started, since the first switching element B1 is closed in each of the mechanical gears 1 to 4.1. In this respect, you can quickly switch from purely electric driving to driving using the internal combustion engine or hybrid driving.

A starting function for reversing can also be implemented as a further operating mode. For this purpose, the third switching element K2 must be closed, which creates a superposition state on the second planetary gear set P2. The first element E12 of the second planetary gear set P2 is driven via the internal combustion engine VKM by means of the drive shaft GW 1, while a torque is supported on the second element E22 via the electric machine EM and the third element E32 is connected to the output shaft due to the closed state of the third switching element K2 GW2 is connected. In the course of supporting the electric machine EM, a starting process can be designed.

Furthermore, a charging or starting function can be implemented by closing the fifth switching element K3. Because in the closed state of the fifth switching element K3, the electric machine EM is coupled to the drive shaft GW1 and thus also to the internal combustion engine VKM. At the same time, however, there is no adhesion to the output shaft GW2, with the drive shaft GW1 and the rotor R running at the same speed. In generator operation of the electric machine EM, an electrical energy storage device can be charged via the internal combustion engine VKM, while in electromotive operation of the electric machine EM, starting the internal combustion engine VKM via the electric machine EM is possible. This can also be achieved in an analogous manner by closing the fourth switching element B2, in which case the rotor runs slower than the drive shaft GW 1.

In addition, the first switching element B1 is designed as a non-positive switching element, as in the variants 13 and 14 shown, a start-up in charging mode can be realized in generator operation of the electric machine EM if the switching element B1 is operated in a slipping manner. In addition, if the fourth switching element B2 is actuated at the same time, a delay-free start from stationary charging mode in the first forward gear 1 can also be achieved.

Will further, as in 14 shown, a separating clutch K0 is provided, a drag start of the internal combustion engine VKM from the first electrical gear E1 can be achieved via the separating clutch K0 if the first switching element B1 is also closed in a slipping manner.

Finally, a speed reduction of the electric machine can be designed in mechanical or hybrid operation: after a torque-assisted shift from the third mechanical gear to the fourth mechanical gear via the electric machine EM or after the internal combustion engine VKM is started into the fourth mechanical gear, hybrid driving results in fourth mechanical gear 4.1. In order to reduce the speed of the electric machine EM in fourth gear at higher driving speeds, it is possible to switch from the first variant 4.1 of the fourth mechanical gear to the second variant 4.2 of the fourth mechanical gear, in which the rotor has a lower speed. This switchover takes place while maintaining the tractive force via the internal combustion engine VKM. For this purpose, the then load-free, first switching element B1 is designed and the likewise load-free, third switching element K2 is inserted, with the speed adjustment being carried out by speed control of the electric machine EM.

Furthermore shows 16 a schematic representation of a hybrid unit HE according to a fourteenth embodiment of the invention. This embodiment also largely corresponds to the variant 2 , but in contrast to this, a further switching element K4 is now provided, which in the actuated state connects the first element E11 of the first planetary gear set P1 in a rotationally fixed manner with the second element E21 of the first planetary gear set P1 and thereby causes the first planetary gear set P1 to lock. Axially, the further switching element K4 is provided on a side of the first planetary gear set P1 facing the connection point GW1 -A and is located directly adjacent to the first switching element B1. The two switching elements B1 and K4 are combined to form a double switching element in that the first switching element B1 and the further switching element K4 are assigned a common actuating element, via which either the first switching element B1 or the further switching element K4 can be actuated from a neutral position. Otherwise, the embodiment corresponds to 16 according to the variant 2 , so that reference is made to what has been described.

Furthermore goes out 17 a schematic view of a hybrid unit HE according to a fifteenth embodiment of the invention, which essentially follows the previous variant 16 corresponds. What is different, however, is that a fifth switch ment K3 in this case causes the second planetary gear set P2 to lock, in that the second element E22 and the third element E32 of the second planetary gear set P2 are connected to one another in a rotationally fixed manner by the fifth switching element K3 in the actuated state. Furthermore, the third switching element K2 is now provided axially on a side of the first planetary gear set P1 facing the connection point GW1-A of the drive shaft GW1, while the fifth switching element K3 is now arranged axially adjacent to the fourth switching element B2.

The fourth switching element B2 and the fifth switching element K3 are combined to form a double switching element and share a common actuating element, via which either the fourth switching element B2 or the fifth switching element K3 can be actuated from a neutral position. The second switching element K1, on the other hand, is placed axially alone between the first planetary gear set P1 and the second planetary gear set P2 and is provided radially in the area of the second element E21 of the first planetary gear set P1. Otherwise, the embodiment corresponds 17 according to the previous variant 16 , so that reference is made to what has been described.

18 shows a schematic view of a hybrid unit HE according to a sixteenth embodiment of the invention, which is also essentially the variant 16 corresponds. What is different, however, is that the second element E22 of the second planetary gear set P2 is formed by a ring gear and the third element E32 of the second planetary gear set P2 is formed by a planetary web. In this respect, the second planetary gear set P2 is designed as a plus planetary gear set. In addition, in the closed state, a fifth switching element K3 connects the first element E12 and the third element E32 of the second planetary gear set P2 to one another in a rotationally fixed manner and thereby causes the second planetary gear set P2 to lock.

The second switching element K1 and the third switching element K2 are also arranged axially between the first planetary gear set P1 and the second planetary gear set P2 and are designed as a double switching element, in that the second switching element K1 and the third switching element K2 are assigned a common actuating element, via which from a neutral position either the second switching element K1 or the third switching element K2 can be actuated. The fourth switching element B2 and the fifth switching element K3, on the other hand, are placed axially on a side of the second planetary gear set P2 that is remote from the connection point GW1-A and are also designed as a double switching element with a common actuating element. In addition, the electric machine EM is provided axially between the first planetary gear set P1 and the second planetary gear set P2. Otherwise, the embodiment corresponds to 18 according to the variant 16 , so that reference is made to what has been described.

Further goes out 19 a schematic representation of a hybrid unit HE according to a seventeenth embodiment of the invention, which largely follows the variant 16 corresponds. What is different is that the electric machine EM is now not placed coaxially, but offset from the axis of the planetary gear sets P1 and P2. Here, a rotor of the electric machine EM - not shown in detail here - and the third element E31 of the first planetary gear set P1 and the second element E22 of the second planetary gear set P2 are not directly connected to one another in a rotationally fixed manner, but rather are coupled to one another in a rotationally fixed manner via an intermediate spur gear stage SRS. A spur gear SR1 of the spur gear stage SRS is connected in a rotationally fixed manner to the third element E31 of the first planetary gear set P1 and the second element E22 of the second planetary gear set P2 and meshes with a spur gear SR2, which is arranged in a rotationally fixed manner on an input shaft EW of the electric machine EM. This input shaft EW then establishes the connection to the rotor within the electric machine EM. Otherwise, the embodiment corresponds to 19 according to the variant 16 , so that reference is made to what has been described.

In addition, it is in 20 a schematic representation of a hybrid unit HE according to an eighteenth embodiment of the invention is shown, which again essentially follows the variant 16 corresponds. As with the design 19 However, the electric machine EM is not placed coaxially, but offset from the axis of the planetary gear sets P1 and P2. A rotationally fixed coupling between the third element E31 of the first planetary gear set P1 and the second element E22 of the second planetary gear set P2 and a rotor - not shown - of the electric machine EM is implemented via a traction drive ZT, which is preferably in the form of a chain drive. This traction drive ZT couples the third element E31 of the first planetary gear set P1 and the second element E22 of the second planetary gear set P2 with an input shaft EW of the electric machine EM. Otherwise the variant corresponds to 20 according to the embodiment 16 , so that reference is made to what has been described.

Furthermore shows 21 a schematic representation of a hybrid unit HE corresponds according to a nineteenth possible embodiment of the invention. This design option largely corresponds to the variant 16 , in contrast to this, the electric machine EM, which is arranged coaxially to the planetary gear sets P1 and P2, is not directly connected in a rotationally fixed manner, but rather a connection is implemented via an intermediate planetary stage P. This planetary stage P is composed of a sun gear SO, a ring gear HO and a planetary web PS, the latter rotatably guiding at least one planet gear PR, which meshes with both the sun gear SO and the ring gear HO. The sun gear SO is permanently fixed to the non-rotatable component GG, while the planetary web PS is constantly connected to the second element E22 of the second planetary gear set P2 in a non-rotatable manner. Finally, the ring gear HO is permanently connected to the rotor R of the electric machine EM in a rotationally fixed manner.

As a further difference, the third switching element K2 and the fourth switching element B2 are provided axially on a side of the first planetary gear set P1 facing the connection point GW1-A. Specifically, the two switching elements K2 and B2 lie axially between the connection point GW2-A of the output shaft GW2 and the first planetary gear set P1. Otherwise the design options correspond 21 according to the variant 16 , so that reference is made to what has been described.

Also goes out 22 a schematic view of a hybrid unit HE according to a twentieth embodiment of the invention, which essentially follows the immediately preceding variant 21 corresponds. The only difference is that the ring gear HO of the planetary stage P is now permanently fixed to the non-rotatable component GG, while the sun gear SO is non-rotatably connected to the rotor R of the electric machine EM. Otherwise the embodiment corresponds to 22 according to the variant 21 , so that reference is made to what has been described.

23 shows a schematic view of a hybrid unit HE according to a twenty-first embodiment of the invention, which is also essentially the variant 16 corresponds. What is different, however, is that the further switching element K4 is now designed as a non-positive switching element, with the further switching element K4 specifically being in the form of a multi-plate clutch. Otherwise, the embodiment corresponds to 23 according to the variant 16 , so that reference is made to what has been described.

In addition, it is in 24 a schematic representation of a hybrid unit HE according to a twenty-second embodiment of the invention is shown, which again essentially follows the variant 16 corresponds. As with the design 23 the further switching element K4 is implemented as a non-positive switching element, with the first switching element B1 now also being present as a non-positive switching element. Both switching elements B1 and K4 are specifically designed as multi-plate switching elements. Otherwise the variant corresponds to 24 according to the embodiment 16 , so that reference is made to what has been described.

Furthermore shows 25 a schematic representation of a hybrid unit HE according to a twenty-third possible embodiment of the invention. This design option largely corresponds to the variant 23 , in contrast to which a separating clutch K0 is now additionally provided, via which the drive shaft GW1 can be connected in a rotationally fixed manner to a connecting shaft AN at its connection point GW1-A. The connecting shaft AN then turns off within the drive train 1 a connection to the internal combustion engine VKM. Otherwise the design options correspond 25 according to the variant 23 , so that reference is made to what has been described.

Further goes out 26 a schematic representation of a hybrid unit HE according to a twenty-fourth embodiment of the invention, which largely follows the variant 24 corresponds. What is different is that, as with the immediately preceding variant 25 , a separating clutch K0 is provided, via which the drive shaft GW1 can be non-rotatably connected to a connecting shaft AN at its connection points GW1-A. The connecting shaft ON is then off within the drive train 1 connected to the internal combustion engine VKM. Otherwise, the embodiment corresponds to 26 according to the variant 24 , so that reference is made to what has been described.

In 27 is now an exemplary switching diagram of the transmission G of the hybrid units HE from the 16 until 26 shown, which essentially corresponds to the circuit diagram 15 corresponds. What is different is that by providing the further switching element K4, in addition to the mechanical gears 1 to 4.5, further variants 4.6 to 4.8 of the fourth gear and an additional gear ZG1 can be switched. This results in another variant 4.6 of the fourth mechanism gear by actuating the second switching element K1 and the further switching element K4, a further variant 4.7 of the fourth mechanical gear by closing the fifth switching element K3 and the further switching element K4 and a further variant 4.8 of the fourth gear by actuating the third switching element K2 and the other Switching element K4. The additional gear ZG 1, on the other hand, can be switched by closing the fourth switching element B2 and the further switching element K4, whereby the additional gear ZG 1 does not fit optimally into the remaining gear range.

Also with the hybrid units HE from the 16 until 26 can the different, in 15 operating modes described can be implemented. Due to the arrangement of the further switching element K4, a second electrical gear E2 can also be represented by closing the further switching element K4, from which the internal combustion engine VKM can be started in one of the variants 4.6 to 4.8 of the fourth gear from this electrical gear E2. Is the further switching element K4 then, as in the variants according to 23 until 26 shown, designed as a non-positive switching element, pull-up and pull-down shifts between the electrical gears E1 and E2 can be carried out under load. If the first switching element B1 is also present as a non-positive switching element, a change between gears E1 and E2 can always take place under load.

In addition, HE can be made from the hybrid units 16 until 26 A reduction in the speed of the electric machine EM can also be achieved by switching to the further variant 4.6 of fourth gear. For this purpose, starting from the first variant 4.1, while maintaining the tractive force via the internal combustion engine VKM, the load-free first switching element B1 is first laid out and the additional switching element K4, which is also load-free, is inserted, with a speed adjustment to represent the load freedoms taking place by speed control of the electric machine EM. Apart from the fact that a reduction in the speed of the rotor R of the electric machine EM can be achieved by switching to the further variant 4.6 of the fourth gear, it is also possible to decouple the internal combustion engine VKM at any time by opening the second switching element K1, if via the electric machine EM should be driven or braked (recuperation).

In addition, starting from the further variant 4.6 of the fourth gear, a downshift to the third mechanical gear 3 can be prepared by first changing from the further variant 4.6 to the first variant 4.1, in which case the tractive force is in turn supported by the internal combustion engine VKM. Starting from the first variant 4.1, a downshift can then be implemented without any problems, since in this case the first switching element B1 is closed again.

Will further, as in 25 also 26 shown, a separating clutch K0 is provided, a drag start of the internal combustion engine VKM can also be achieved from the first electrical gear E2 via the separating clutch K0 if the further switching element K4 is also closed in a slipping manner.

Furthermore shows 28 a schematic representation of a hybrid unit HE according to a twenty-fifth embodiment of the invention. This embodiment also largely corresponds to the variant 2 , but in contrast to this, an additional switching element K5 is now provided, which in the actuated state connects the first element E11 of the first planetary gear set P1 to the drive shaft GW1 in a rotationally fixed manner. Axially, the additional switching element K5 is provided on a side of the first planetary gear set P1 facing the connection point GW1 -A and is located axially directly adjacent to the first switching element B1. The two switching elements B1 and K5 are combined to form a double switching element in that the first switching element B1 and the additional switching element K5 are assigned a common actuating element, via which either the first switching element B1 or the additional switching element K5 can be actuated from a neutral position. Otherwise, the embodiment corresponds to 28 according to the variant 2 , so that reference is made to what has been described.

Furthermore goes out 29 a schematic view of a hybrid unit HE according to a twenty-sixth embodiment of the invention, which essentially follows the previous variant 28 corresponds. What is different, however, is that in this case a fifth switching element K3 causes the second planetary gear set P2 to lock, in that the second element E22 and the third element E32 of the second planetary gear set P2 are connected to one another in a rotationally fixed manner by the fifth switching element K3 in the actuated state.

Furthermore, the third switching element K2 is now provided axially on a side of the first planetary gear set P1 facing the connection point GW1-A of the drive shaft GW1, while the fifth switching element K3 is arranged axially adjacent to the fourth switching element B2. The The fourth switching element B2 and the fifth switching element K3 are combined to form a double switching element and share a common actuating element, via which either the fourth switching element B2 or the fifth switching element K3 can be actuated from a neutral position. The second switching element K1, on the other hand, is placed alone axially between the first planetary gear set P1 and the second planetary gear set P2 and is provided radially in the area of the second element E21 of the first planetary gear set P1. Otherwise, the embodiment corresponds 29 according to the previous variant 28 , so that reference is made to what has been described.

30 shows a schematic view of a hybrid unit HE according to a twenty-seventh embodiment of the invention, which is also essentially the variant 28 corresponds. What is different, however, is that the second element E22 of the second planetary gear set P2 is formed by a ring gear and the third element E32 of the second planetary gear set P2 is formed by a planetary web. In this respect, the second planetary gear set P2 is designed as a plus planetary gear set. In addition, in the closed state, a fifth switching element K3 connects the first element E12 and the third element E32 of the second planetary gear set P2 to one another in a rotationally fixed manner and thereby causes the second planetary gear set P2 to lock.

The second switching element K1 and the third switching element K2 are also arranged axially between the first planetary gear set P1 and the second planetary gear set P2 and are designed as a double switching element, in that the second switching element K1 and the third switching element K2 are assigned a common actuating element, via which from a neutral position either the second switching element K1 or the third switching element K2 can be actuated. The fourth switching element B2 and the fifth switching element K3, on the other hand, are placed axially on a side of the second planetary gear set P2 that is remote from the connection point GW1-A and are also designed as a double switching element with a common actuating element. In addition, the electric machine EM is provided axially between the first planetary gear set P1 and the second planetary gear set P2. Otherwise, the embodiment corresponds to 30 according to the variant 28 , so that reference is made to what has been described.

Further goes out 31 a schematic representation of a hybrid unit HE according to a twenty-eighth possible embodiment of the invention, which largely follows the variant 28 corresponds. What is different is that the electric machine EM is now not placed coaxially, but offset from the axis of the planetary gear sets P1 and P2. Here, a rotor of the electric machine EM - not shown in detail here - and the third element E31 of the first planetary gear set P1 and the second element E22 of the second planetary gear set P2 are not directly connected to one another in a rotationally fixed manner, but rather are coupled to one another in a rotationally fixed manner via an intermediate spur gear stage SRS. A spur gear SR1 of the spur gear stage SRS is connected in a rotationally fixed manner to the third element E31 of the first planetary gear set P1 and the second element E22 of the second planetary gear set P2 and meshes with a spur gear SR2, which is arranged in a rotationally fixed manner on an input shaft EW of the electric machine EM. This input shaft EW then establishes the connection to the rotor within the electric machine EM. Otherwise, the embodiment corresponds to 31 according to the variant 28 , so that reference is made to what has been described.

In addition, it is in 32 a schematic representation of a hybrid unit HE according to a twenty-ninth embodiment of the invention is shown, which again essentially follows the variant 28 corresponds. As with the design 31 However, the electric machine EM is not placed coaxially, but offset from the axis of the planetary gear sets P1 and P2. A rotationally fixed coupling between the third element E31 of the first planetary gear set P1 and the second element E22 of the second planetary gear set P2 on the one hand and a rotor - not shown - of the electric machine EM on the other hand is implemented via a traction drive ZT, which is preferably in the form of a chain drive. This traction drive ZT couples the third element E31 of the first planetary gear set P1 and the second element E22 of the second planetary gear set P2 with an input shaft EW of the electric machine EM. Otherwise the variant corresponds to 32 according to the embodiment 28 , so that reference is made to what has been described.

Furthermore shows 33 a schematic representation of a hybrid unit HE according to a thirtieth possible embodiment of the invention. This design option largely corresponds to the variant 28 , in contrast to this, the electric machine EM, which is arranged coaxially to the planetary gear sets P1 and P2, is not directly connected in a rotationally fixed manner, but rather a connection is realized via an intermediate planetary stage P. This planetary stage P is composed of a sun gear SO, a ring gear HO and a planetary web PS, the latter of which has at least one planetary gear PR rotatably mounted, which includes both the sun gear SO and the ring gear HO are in tooth mesh. The sun gear SO is permanently fixed to the non-rotatable component GG, while the planetary web PS is constantly connected to the second element E22 of the second planetary gear set P2 in a non-rotatable manner. Finally, the ring gear HO is permanently connected to the rotor R of the electric machine EM in a rotationally fixed manner.

As a further difference, the third switching element K2 and the fourth switching element B2 are now provided axially on a side of the first planetary gear set P1 facing the connection point GW1 -A. Specifically, the two switching elements K2 and B2 lie axially between the connection point GW2-A of the output shaft GW2 and the first planetary gear set P1. Otherwise the design options correspond 33 according to the variant 28 , so that reference is made to what has been described.

Also goes out 34 a schematic view of a hybrid unit HE according to a thirty-first embodiment of the invention, which essentially follows the immediately preceding variant 33 corresponds. The only difference is that the ring gear HO of the planetary stage P is now permanently fixed to the non-rotatable component GG, while the sun gear SO is non-rotatably connected to the rotor R of the electric machine EM. Otherwise the embodiment corresponds to 34 according to the variant 33 , so that reference is made to what has been described.

In 35 is an exemplary switching diagram of the transmission G of the hybrid units HE from the 28 until 34 shown, which again essentially corresponds to the circuit diagram 15 corresponds. The only difference is that by providing the additional switching element K5, in addition to the mechanical gears 1 to 4.5, further variants 4.9 to 4.11 of the fourth gear and an additional gear ZG2 can be switched. This results in a further variant 4.9 of the fourth mechanical gear by actuating the second switching element K1 and the additional switching element K5, a further variant 4.10 of the fourth mechanical gear by closing the fifth switching element K3 and the additional switching element K5 and a further variant 4.11 of the fourth gear by actuating the third switching element K2 and the additional switching element K5. The additional gear ZG2, on the other hand, can be switched by closing the fourth switching element B2 and the additional switching element K5, whereby the additional gear ZG2 does not fit optimally into the remaining gear range.

Also with the hybrid unit HE from the 28 until 34 the different ones can 15 operating modes described can be implemented. In addition, a starting function for forward travel can be implemented due to the additional switching element K5 that is now provided. For this purpose, the additional switching element K5 is closed, whereby the first element E11 of the first planetary gear set P1 is connected in a rotationally fixed manner to the drive shaft GW1 and thus also to the internal combustion engine VKM. Since the electric machine is also coupled in a rotationally fixed manner to the third element E31 of the first planetary gear set P1, the rotational movements of the drive shaft GW1 and the rotor of the electric machine EM are superimposed on the first planetary gear set P1. This means that a starting process for forward travel can be designed by supporting a torque via the electric machine EM. If the first switching element B1 is also designed as a non-positive switching element, then the too 15 additional functions described can be implemented. The same applies if a separating clutch K0 is also provided.

Also shows 36 a schematic representation of a hybrid unit HE according to a thirty-second embodiment of the invention. This embodiment also largely corresponds to the variant 2 , but in contrast to this, a further switching element K4 and an additional switching element K5 are now provided. In the actuated state, the further switching element K4 connects the first element E11 of the first planetary gear set P1 in a rotationally fixed manner with the second element E21 of the first planetary gear set P1 and thereby causes the first planetary gear set P1 to lock. In contrast, when actuated, the additional switching element K5 connects the first element E11 of the first planetary gear set P1 to the drive shaft GW1 in a rotationally fixed manner.

Axially, the further switching element K4 is provided on a side of the first planetary gear set P1 facing the connection point GW1-A and is located directly adjacent to the first switching element B1. The two switching elements B1 and K4 are combined to form a double switching element in that the first switching element B1 and the further switching element K4 are assigned a common actuating element, via which either the first switching element B1 or the further switching element K4 can be actuated from a neutral position. The additional switching element K5, on the other hand, is provided axially between the first planetary gear set P1 and the second planetary gear set P2 and lies specifically axially between the first planetary gear set P1 and the second switching element K1. Due to this arrangement, the second switching element K1, the fifth switching element K3 and the additional switching element K5 can be combined and have a common actuating element. Otherwise, the embodiment corresponds to 36 according to the variant 2 , so that reference is made to what has been described.

Furthermore goes out 37 a schematic view of a hybrid unit HE according to a thirty-third embodiment of the invention, which essentially follows the previous variant 36 corresponds. What is different, however, is that in this case a fifth switching element K3 causes the second planetary gear set P2 to lock, in that the second element E22 and the third element E32 of the second planetary gear set P2 are connected to one another in a rotationally fixed manner by the fifth switching element K3 in the actuated state.

Furthermore, the third switching element K2 is now provided axially on a side of the first planetary gear set P1 facing the connection point GW1-A of the drive shaft GW1, while the fifth switching element K3 is now arranged axially adjacent to the fourth switching element B2. The fourth switching element B2 and the fifth switching element K3 are combined to form a double switching element and share a common actuating element, via which either the fourth switching element B2 or the fifth switching element K3 can be actuated from a neutral position. The second switching element K1, on the other hand, is placed alone axially between the first planetary gear set P1 and the second planetary gear set P2 and is provided radially in the area of the second element E21 of the first planetary gear set P1. Otherwise, the embodiment corresponds 37 according to the previous variant 36 , so that reference is made to what has been described.

38 shows a schematic view of a hybrid unit HE according to a thirty-fourth embodiment of the invention, which is also essentially the variant 36 corresponds. What is different, however, is that the second element E22 of the second planetary gear set P2 is formed by a ring gear and the third element E32 of the second planetary gear set P2 is formed by a planetary web. In this respect, the second planetary gear set P2 is designed as a plus planetary gear set. In addition, in the closed state, a fifth switching element K3 connects the first element E12 and the third element E32 of the second planetary gear set P2 to one another in a rotationally fixed manner and thereby causes the second planetary gear set P2 to lock.

The second switching element K1 and the third switching element K2 are also arranged axially between the first planetary gear set P1 and the second planetary gear set P2 and are designed as a double switching element, in that the second switching element K1 and the third switching element K2 are assigned a common actuating element, via which from a neutral position either the second switching element K1 or the third switching element K2 can be actuated. However, a combination of the second switching element K1, the third switching element K2 and the additional switching element K5 could also be implemented. The fourth switching element B2 and the fifth switching element K3, on the other hand, are placed axially on a side of the second planetary gear set P2 that is remote from the connection point GW1-A and are also designed as a double switching element with a common actuating element. In addition, the electric machine EM is provided axially between the first planetary gear set P1 and the second planetary gear set P2. Otherwise, the embodiment corresponds to 38 according to the variant 36 , so that reference is made to what has been described.

Further goes out 39 a schematic representation of a hybrid unit HE according to a thirty-fifth possible embodiment of the invention, which largely follows the variant 36 corresponds. What is different is that the electric machine EM is now not placed coaxially, but offset from the axis of the planetary gear sets P1 and P2. Here, a rotor of the electric machine EM - not shown in detail here - and the third element E31 of the first planetary gear set P1 and the second element E22 of the second planetary gear set P2 are not directly connected to one another in a rotationally fixed manner, but rather are coupled to one another in a rotationally fixed manner via an intermediate spur gear stage SRS. A spur gear SR1 of the spur gear stage SRS is connected in a rotationally fixed manner to the third element E31 of the first planetary gear set P1 and the second element E22 of the second planetary gear set P2 and meshes with a spur gear SR2, which is arranged in a rotationally fixed manner on an input shaft EW of the electric machine EM. This input shaft EW then establishes the connection to the rotor within the electric machine EM. Otherwise, the embodiment corresponds to 39 according to the variant 36 , so that reference is made to what has been described.

Finally it's in 40 a schematic representation of a hybrid unit HE according to a thirty-sixth embodiment of the invention is shown, which again essentially follows the variant 36 corresponds. As with the design 39 but the electric machine EM is not coaxial, but placed axially offset from the planetary gear sets P1 and P2. A rotationally fixed coupling between the third element E31 of the first planetary gear set P1 and the second element E22 of the second planetary gear set P2 and a rotor - not shown - of the electric machine EM is implemented via a traction drive ZT, which is preferably in the form of a chain drive. This traction drive ZT couples the third element E31 of the first planetary gear set P1 and the second element E22 of the second planetary gear set P2 with an input shaft EW of the electric machine EM. Otherwise the variant corresponds to 40 according to the embodiment 36 , so that reference is made to what has been described.

In 41 is now an exemplary switching diagram of the transmission G of the hybrid units HE from the 36 until 40 shown, this circuit diagram being a combination of the circuit diagrams from 15 , 27 and 35 represents. In this respect, reference is made to the descriptions with regard to the gears that can be represented and the operating modes that can be implemented 15 , 27 and 35 Referenced. If the first switching element B1 or the further switching element K4 or both switching elements B1 and K4 are designed as non-positive switching elements, the further switching elements can also be used 15 or. 27 the functions described can be implemented. The same applies if a separating clutch K0 is also provided.

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

Reference symbols

HEY

Hybrid unit

G

transmission

GG

Torsion-proof 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

B1

First switching element

K1

Second switching element

K2

Third switching element

B2

Fourth switching element

K3

Fifth switching element

K4

another switching element

K5

additional switching element

K0

Separating clutch

1

First mechanical gear

2

Second mechanical gear

3

Third mechanical gear

4.1

Fourth mechanical gear

4.2

Fourth mechanical gear

4.3

Fourth mechanical gear

4.4

Fourth mechanical gear

4.5

Fourth mechanical gear

4.6

Fourth mechanical gear

4.7

Fourth mechanical gear

4.8

Fourth mechanical gear

4.9

Fourth mechanical gear

4.10

Fourth mechanical gear

4.11

Fourth mechanical gear

ZG1

Additional gear

ZG2

Additional gear

E1

first electric gear

E2

second electric gear

GW1

drive shaft

GW1-A

Connection point

GW2

output shaft

GW2-A

Connection point

AT

connecting shaft

E.M

Electric machine

S

stator

R

rotor

SRS

Spur gear stage

SR1

spur gear

SR2

spur gear

P

Planetary stage

SO

sun gear

P.S

planetary bridge

PR

Planetary gear

PR1

Planetary gear

PR2

Planetary gear

HO

ring gear

EW

input shaft

ZT

Traction drive

VKM

Internal combustion engine

T.S

Torsional vibration damper

AG

Differential gear

DW

drive wheels

Claims (18)

Hybrid unit (HE) for a motor vehicle, comprising an electric machine (EM) and a transmission (G) with a drive shaft (GW1), an output shaft (GW2), and a first planetary gear set (P1) and a second planetary gear set (P2), wherein the Planetary gear sets (P1, P2) each comprise several elements (E11, E21, E31, E12, E22, E32), the gearbox (G) having a first (B1), a second (K1), a third (K2), a fourth (B2) and a fifth switching element (K3), wherein a rotor (R) of the electric machine (EM) on the drive shaft (GW1), on the output shaft (GW2) or at least one of the elements (E11, E21, E31, E12, E22, E32) of the planetary gear sets (P1, P2) is connected, characterized in that - the first element (E11) of the first planetary gear set (P1) can be fixed in a rotationally fixed manner via the first switching element (B1), - that the second element (E21 ) of the first planetary gear set (P1) and the output shaft (GW2) are connected to one another in a rotationally fixed manner, - that the output shaft (GW2) can be connected to the drive shaft (GW1) in a rotationally fixed manner by means of the second switching element (K1), as well as via the third switching element (K2 ) can be connected in a rotationally fixed manner to the third element (E32) of the second planetary gear set (P2), - that the third element (E32) of the second planetary gear set (P2) can be fixed in a rotationally fixed manner by means of the fourth switching element (B2), - that the drive shaft (GW1) is non-rotatably connected to the first element (E12) of the second planetary gear set (P2), the second element (E22) and the third element (E31) of the first planetary gear set (P1) are non-rotatably connected to one another, - and that by closing the fifth switching element (K3) two of the elements (E12, E22, E32) of the second planetary gear set (P2) can be connected. Hybrid unit (HE). Claim 1 , characterized in that by selectively closing the five switching elements (B1, K1, K2, B2, K3) in pairs - a first mechanical gear (1) by actuating the first (B1) and the fourth switching element (B2), - a second mechanical gear (2) by operating the first (B1) and the third switching element (K2), - a third mechanical gear (3) by operating the first (B1) and the fifth switching element (K3), and a fourth mechanical gear - in a first variant (4.1) by actuating the first (B1) and the second switching element (K1), - in a second variant (4.2) by actuating the second (K1) and the third switching element (K2), - in a third variant ( 4.3) by actuating the second (K1) and the fourth switching element (B2), - in a fourth variant (4.4) by actuating the second (K1) and the fifth switching element (K3) and - in a fifth variant (4.5) by actuating of the third (K2) and the fifth switching element (K3). Hybrid unit (HE). Claim 1 or 2 , characterized in that the rotor (R) of the electric machine (EM) is constantly connected to the third element (E31) of the first planetary gear set (P1) and the second element (E22) of the second planetary gear set (P2). Hybrid unit (HE). Claim 3 , characterized in that a first electrical gear (E1) results from closing the first switching element (B1). Hybrid unit (HE) according to one of the preceding claims, characterized in that exactly one electric machine (EM) is provided, which is set up to drive the output shaft (GW2). Hybrid unit (HE) according to one of the Claims 1 until 4 , characterized in that a second electric machine is provided, the rotor of which is constantly connected to the drive shaft (GW1). Hybrid unit (HE) according to one of the preceding claims, characterized in that the transmission (G) has a further switching element (K4), via which two of the elements (E11, E21, E31) of the first planetary gear set (P1) can be connected. Hybrid unit (HE). Claim 7 , characterized in that the fourth gear is also activated in a further variant (4.6) by actuating the second (K1) and the further switching element (K4), in a further variant (4.7) by actuating the fifth (K3) and the further switching element (K4) and in a further variant (4.8) by actuating the third (K2) and the further switching element (K4), as well as an additional gear (ZG1) by operating the fourth (B2) and the further switching element (K4). Hybrid unit (HE). Claim 7 or 8th , characterized in that a second electrical gear (E2) results from closing the further switching element (K4). Hybrid unit (HE) according to one of the preceding claims, characterized in that the transmission (G) also has an additional switching element (K5), via which the first element (E11) of the first planetary gear set (P1) can be connected to the drive shaft (GW1) in a rotationally fixed manner is. Hybrid unit (HE). Claim 10 , characterized in that the fourth gear is also activated in a further variant (4.9) by actuating the second (K1) and the additional switching element (K5), in a further variant (4.10) by actuating the fifth (K3) and the additional shifting element (K5) and in a further variant (4.11) by operating the third (K2) and the additional switching element (K5), as well as an additional gear (ZG2) by operating the fourth (B2) and the additional switching element (K5). Hybrid unit (HE) according to one of the preceding claims, characterized in that one or more of the switching elements (B1, K1, K2, B2, K3; B1, K1, K2, B2, K3, K4; B1, K1, K2, B2, K3, K5; B1, K1, K2, B2, K3, K4, K5) are each implemented as a positive switching element. Hybrid unit (HE) according to one of the preceding claims, characterized in that - at least one of the planetary gear sets (P1, P2) is present as a minus planetary gear set, the respective first element (E11, E12) of the respective planetary gear set (P1, P2 ) around a respective sun gear, in the respective second element (E21, E22) of the respective planetary gear set (P1, P2) around a respective planetary web and in the respective third element (E31, E32) of the respective planetary gear set (P1, P2) around a respective one Ring gear is, and / or that at least one of the planetary gear sets (P2) is present as a plus planetary gear set, the respective first element (E12) of the respective planetary gear set (P2) being a respective sun gear, the respective second element (E22 ) of the respective planetary gear set (P2) is a respective ring gear and the respective third element (E32) of the respective planetary gear set (P2) is a respective planetary web. Hybrid unit (HE) according to one of the preceding claims, characterized in that at least two switching elements (K1, K3; K2, B2; B2, K3; K1, K2; K3, B2; B1, K4; B1, K5) each form a pair of switching elements are summarized, each of which is assigned an actuating element, with either one switching element (K1; K2; B2; K3; B1) or the other switching element (K3; B2; K3; K2; K4) being activated from a respective neutral position via the respective one actuating element ; K5) of the respective switching element pair can be actuated. Motor vehicle drive train for a hybrid vehicle, comprising a hybrid unit (HE) according to one or more of the Claims 1 until 14 . Method for operating a hybrid unit (HE). Claim 3 , characterized in that the third switching element (K2) is closed to represent a starting mode for reversing when driven via the drive shaft (GW1). Method for operating a hybrid unit (HE). Claim 3 , characterized in that to represent a charging operation or a starting operation, only the fifth switching element (K3) or the fourth switching element (B2) is closed. Method for operating a hybrid unit (HE). Claim 3 and 10 , characterized in that the additional switching element (K5) is closed to represent a starting mode for forward travel when driven via the drive shaft (GW1).

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