DE102018000183B4 - Transmission device for a motor vehicle, in particular for a motor vehicle - Google Patents

Abstract

Transmission device (10) for a motor vehicle, with a housing (12), and with a planetary gear (14), which has: - a first planetary gear set (16) accommodated in the housing (12), which has a first sun gear (18), a first planet carrier (20) and a first ring gear (22); - a second planetary gear set (26) accommodated in the housing (12), which has a second sun gear (28), a second planet carrier (30) and a second ring gear (32) which is non-rotatably connected to the first planet carrier (20) via an internal shaft (36) of the planetary gear (14); - a drive shaft (40), via which torques can be introduced into the planetary gear (14); - a first shift element ( 46), by means of which the drive shaft (40) can be connected to the first ring gear (22) in a rotationally fixed manner; - a second switching element (48) by means of which the drive shaft (40) can be connected to the first sun gear (18) in a rotationally fixed manner, and rotatably with the second planet carrier he (30) connected first output shaft (50), via which torques can be provided by the planetary gear (14); - an electrical machine (54), by means of which torques can be provided, which via the second sun gear (28) into the planetary gear (14 ) can be initiated; and characterized bya third shift element (60), by means of which the first sun gear (18) can be connected to the second sun gear (28) in a rotationally fixed manner, a second output shaft (64) of the planetary gear (14) and a transmission stage (66) being provided which the first output shaft (50) is coupled or can be coupled to the second output shaft (64).

Description

The invention relates to a transmission device for a motor vehicle, in particular for a motor vehicle, according to the preamble of patent claim 1.

Transmission devices in particular for hybrid motor vehicles are for example from the DE 10 2012 220 517 A1 , the US 2007/0 142 158 A1 and the DE 10 2013 006 028 A1 known.

Such a transmission device for a motor vehicle, in particular for a motor vehicle, is also already from the EP 1 416 193 B1 known. The transmission device comprises a housing and a planetary gear, which has a first planetary gear set accommodated in the housing and having a first sun gear, a first planet carrier and a first ring gear. Furthermore, the planetary gear set comprises a second planetary gear set received in the housing, which has a second sun gear, a second planet carrier and a second ring gear. The planetary gear also includes an internal shaft of the planetary gear, via which the second ring gear is connected to the first planet carrier in a rotationally fixed manner. The planetary gear also has a drive shaft via which torques can be introduced into the planetary gear. The drive shaft is also referred to as the input shaft. The planetary gear includes a first shift element, by means of which the drive shaft can be connected to the first ring gear in a rotationally fixed manner. In addition, the planetary gear has a second shift element by means of which the drive shaft can be connected to the first sun gear in a rotationally fixed manner. The drive shaft can thus be connected to the first ring gear and to the first sun gear alternately by means of the first switching element and by means of the second switching element. The planetary gear also includes an output shaft connected to the second planetary carrier in a rotationally fixed manner, via which torque can be provided by the planetary gear or can be diverted from the planetary gear.

From the generic JP 2008 - 143 242 A a transmission device is known which also has an electrical machine by means of which torques can be provided which can be introduced into the planetary gear via the second sun gear.

The object of the present invention is to further develop a transmission device of the type mentioned at the beginning in such a way that particularly advantageous drivability can be achieved.

This object is achieved by a transmission device with the features of claim 1. Advantageous refinements with expedient developments of the invention are specified in the remaining claims.

In order to present a transmission device of the type specified in the preamble of claim 1 in such a way that particularly advantageous drivability of the transmission device or of the motor vehicle can be achieved, an electrical machine is provided in a manner known in principle, by means of which torques can be provided which are transferred to the second sun gear via the Planetary gear can be initiated. This means that the sun gear can be driven by means of the electric machine, in particular by means of a rotor of the electric machine, so that, for example, the electric machine, in particular the rotor, can be coupled or preferably coupled to the second sun gear at least indirectly, in particular directly. The first sun gear, the first planet carrier, the first ring gear, the second sun gear, the second planet carrier and the second ring gear are, for example, respective components of the planetary gear or are also referred to as components of the planetary gear. In relation to a torque flow from the electrical machine to and in particular in the planetary gear, the second sun gear is preferably the first component in relation to the components to which the electrical machine provided by the electrical machine, in particular via its rotor, and along the torque flow from the electrical machine to and in particular into the planetary gear running or directed torques are transmitted, so that especially when the planetary gear is driven by means of the electrical machine, in particular by means of the rotor of the electrical machine, the torques provided by the electrical machine based on the components of the planetary gear are transmitted or act first on the second sun gear and possibly only then on the other components that are different from the second sun gear or on at least one of the other components.

The planetary gear is driven by the electric machine, for example, in such a way that the torques provided by the electric machine are introduced into the planetary gear. For example, at least one wheel of the motor vehicle can be driven by means of the electrical machine. In particular, for example, several wheels of the motor vehicle can be driven by means of the electric machine. Thus, for example, the motor vehicle can be driven electrically by means of the electrical machine.

According to the invention, it is provided that the gear device, in particular the planetary gear, has a third shift element, by means of which the first sun gear can be connected to the second sun gear in a rotationally fixed manner. The components, the housing, the drive shaft, also referred to as the input shaft, and the first output shaft, also referred to as the output shaft, are, for example, respective components of the transmission device or are also referred to as components. The components, the first output shaft and the drive shaft are, for example, respective components of the transmission device or are also referred to as components. The respective component is for example rotatable relative to the housing about an axis of rotation, also referred to as the main axis of rotation, for example, when the respective component is not connected to the housing in a rotationally fixed manner, that is, not fixed to the housing in a rotationally fixed manner. Furthermore, it is conceivable that, for example, at least two of the components can be rotated relative to one another, in particular about the main axis of rotation, if the respective two components are not connected to one another in a rotationally fixed manner.

The feature that the second ring gear is non-rotatably connected to the first planet carrier via the internal shaft of the planetary gear can in particular be understood to mean that the second ring gear is permanently non-rotatably connected to the first planet carrier via the internal shaft. For this purpose, for example, the internal shaft, in particular permanently, is non-rotatably connected to the second ring gear and, in particular permanently, is non-rotatably connected to the first planet carrier. The feature that the first output shaft is non-rotatably connected to the second planetary carrier can in particular be understood to mean that the first output shaft is permanently non-rotatably connected to the second planetary carrier. The or such a permanently rotationally fixed connection between at least two of the components and in the present case, for example, between the second ring gear and the first planetary carrier or between the second planetary carrier and the first output shaft can in particular be understood as meaning that the permanently rotationally fixedly connected components always or permanently, the means that they are permanently non-rotatably connected to one another, so that a switching element is not provided by means of which the permanent non-rotatable connection between the components could alternately be canceled and established, but the permanent non-rotatable connection is always provided. In contrast to this, the respective switching element enables the respective non-rotatable connection or coupling to be selectively and reversibly, i.e. non-destructively, alternately established and released several times in succession, so that the non-rotatable connection or the non-rotatable coupling can be established or released as required.

The first switching element can be switched, for example, between a first connection state and a first release state. The first connection state corresponds, for example, to at least one first connection position, the first release state, for example, corresponding to at least one first release position. The first switching element can be moved between the first connection position and the first release position, in particular relative to the housing and / or translationally. In the first connection state, the drive shaft is non-rotatably connected to the first ring gear by means of the first shift element, so that the drive shaft cannot rotate relative to the first ring gear, in particular about the main axis of rotation, when the planetary gear is driven, i.e. when torques are introduced into the planetary gear. In the first release state, however, the first switching element releases the drive shaft for rotation relative to the first ring gear, in particular about the main axis of rotation, so that the first switching element rotates or can rotate relative to the drive shaft in particular, in particular about the main axis of rotation, when the planetary gear is driven.

Accordingly, for example, the second switching element can be switched between a second connection state and a second release state. The second connection state corresponds, for example, to at least one second connection position, the second release state, for example, corresponding to at least one second release position. The second switching element can be moved, for example, in particular relative to the housing and / or translationally, between the second connection position and the second release position. In the second connection state, for example, the drive shaft is non-rotatably connected to the first sun gear by means of the second shift element, so that the drive shaft does not or can not rotate relative to the first sun gear, in particular about the main axis of rotation, when the planetary gear is driven. In the second release state, however, the second switching element releases the drive shaft for rotation relative to the sun gear, in particular around the main axis of rotation, so that the drive shaft in particular then rotates or can rotate relative to the first sun gear, in particular around the main axis of rotation, if that Planetary gear is driven.

Corresponding to this, the third switching element is, for example, between a third Connection status and a third release status switchable. The third connection state corresponds, for example, to at least one third connection position, the third release state, for example, corresponding to at least one third release position. Here, for example, the third switching element can be moved, in particular translationally and / or relative to the housing, between the third connection position and the third release position. In the third connection state, for example, the first sun gear is non-rotatably connected to the second sun gear by means of the third switching element, so that the first sun gear cannot rotate or rotate relative to the second sun gear, in particular about the main axis of rotation, when the planetary gear is driven . In the third release state, however, the third switching element releases the first sun gear for rotation relative to the second sun gear, in particular about the main axis of rotation, so that, for example, the first sun gear then in particular rotates or rotates relative to the second sun gear, in particular about the main axis of rotation can when the planetary gear is driven.

The respective torques which can be introduced into the planetary gear via the drive shaft or via the second sun gear are also referred to as drive torques or drive torques. The torques that can be provided by the planetary gear via the first output shaft are also referred to as output torques or output torques. For example, the planetary gear, in particular in at least one state, in particular the switching state, has a gear ratio which, for example, differs in amount from one. In this way, for example, the respective drive torque is converted into a respective output torque that is different from the respective drive torque. In other words, for example, the respective drive torque has a first value, with the fact that the respective drive torque is converted by means of the translation or by means of the planetary gear, the respective output torque that results from the respective drive torque, for example a second value different from the first value having. The planetary gear can provide the respective output torque via the first output shaft.

In particular, it is provided that the electrical machine has the rotor and a stator, the rotor being drivable by the stator and thus rotatable relative to the stator about a machine axis of rotation of the electrical machine. The machine axis of rotation runs, for example, parallel to the main axis of rotation, it being possible for the machine axis of rotation to coincide with the main axis of rotation. It is provided, for example, that the rotor is at least indirectly, in particular directly, permanently non-rotatably connected to the second sun gear.

Furthermore, it is provided according to the invention that the planetary gear has a second output shaft via which, for example, the planetary gear can provide torques, in particular output torques. Furthermore, the transmission device comprises a transmission stage via which the first output shaft is coupled or can be coupled to the second output shaft.

With the transmission device according to the invention, it is possible to implement several, in particular shiftable, gears in a particularly compact and efficient manner, so that particularly advantageous drivability can be implemented. In particular, six gears, in particular forward gears, can be implemented, for example, the six gears being internal combustion engine gears, in particular forward gears. This means, for example, that the motor vehicle can be driven via the six internal combustion engine gears, in particular forward gears, by means of a drive machine, in particular designed as an internal combustion engine, and can thereby be driven forward. It is also possible, for example, to display at least or exactly three electrical gears and various stepless driving ranges. In addition, a particularly large spread can be achieved. For this purpose, for example, the use of two or three single planetary gear sets and, for example, five shift elements is sufficient.

In particular, six gears, in particular forward gears, can be implemented as hybrid gears, with a spread of, for example, 5.8 being possible. As an alternative or in addition, the three electric gears mentioned can be created as virtual gears. In addition, it is possible to operate the transmission device, in particular the planetary gear, as a continuously variable transmission with an electrically variable transmission, that is, as an EVT transmission, in order, for example, to implement the EVT transmission as a starting EVT transmission, via which the motor vehicle , in particular by means of the electric machine, can be approached particularly advantageously. Furthermore, it is possible for the planetary gear sets to be designed as single planetary gear sets, as a result of which the complexity and the costs of the transmission device can be kept within a particularly low framework.

For example, in order to be able to realize particularly advantageous shiftability and consequently particularly advantageous drivability, in an advantageous embodiment of the invention a fourth switching element is provided, by means of which the first ring gear can be connected to the housing in a rotationally fixed manner. The fourth switching element can be switched, for example, between a fourth connection state and a fourth release state. The fourth connection state corresponds, for example, to at least one fourth connection position, the fourth release state, for example, corresponding to at least one fourth release position. For example, the fourth switching element can be moved between the fourth connection position and the fourth release position, in particular relative to the housing and / or in a translatory manner. In the fourth connection state, the first ring gear is non-rotatably connected to the housing by means of the fourth switching element and is thus fixed in a non-rotatable manner on the housing, so that the first ring gear in particular does not rotate or can rotate relative to the housing, in particular about the main axis of rotation, when the planetary gear is driven. In the fourth release state, however, the fourth switching element releases the first ring gear for rotation relative to the housing, in particular about the main axis of rotation, so that, for example, the first ring gear then in particular, in particular about the main axis of rotation, rotates or can rotate relative to the housing, when the planetary gear is driven.

In a further embodiment of the invention, it is provided that a connection, caused by the internal shaft of the planetary gear, of gear set elements or shifting elements of the gear mechanism different from the first planet carrier and the second ring gear is omitted. In other words, it is provided that the internal shaft does not connect any further gear set elements or shifting elements to one another, so that only or exclusively the second ring gear is non-rotatably connected to the first planetary carrier via the internal shaft. As a result, the complexity can be kept particularly low, so that advantageous drivability can be achieved in an efficient and space-saving manner.

In a further particularly advantageous embodiment of the invention, the transmission stage is designed as a third planetary gear set which has a third sun gear, a third planet carrier and a third ring gear. The third planet carrier is connected or can be connected to the second planet carrier in a rotationally fixed manner. By using the third planetary gear set, at least one or more advantageous gear ratios can be created in a way that is economical in terms of space and weight, so that particularly advantageous drivability can be achieved. In the context of the invention it is preferably provided that the third planetary gear set is not part of the planetary gear, so that the third planetary gear set is, for example, a unit different from the planetary gear and external to the planetary gear, wherein the third planetary gear set can be accommodated in the housing. It can be provided that the third planetary gear set can be driven by the planetary gear via the second planetary carrier, so that, for example, the planetary gear can provide torques via the second planetary carrier that relate to and in particular to the third planetary gear set and in particular to the or third Planet carrier can be transmitted. The respective planet carrier is also referred to as a web.

In order to be able to realize particularly advantageous drivability, it is provided in a further embodiment of the invention that the third ring gear is connected or can be connected to the second sun gear in a rotationally fixed manner.

Another embodiment is characterized in that the third sun gear is connected or can be connected to the housing in a rotationally fixed manner, as a result of which a particularly advantageous gear ratio or several advantageous gear ratios can be realized in a particularly space-saving manner.

It has also been shown to be particularly advantageous if an output gear, in particular designed as a gear, is provided, via which, for example, the transmission device can provide torques for driving at least one wheel or several wheels of the motor vehicle. For this purpose, the output gear is, for example, non-rotatably connected to at least one of the output shafts. In order to be able to keep the installation space requirement particularly low, especially in the axial direction of the transmission device, the invention also provides that the third planetary gear set on the output gear, the first planetary gear set on the third planetary gear set and the second planetary gear set on the first planetary gear set follows. In other words, it is preferably provided that the output gear and the planetary gear sets are arranged one after the other or one after the other in the axial direction of the transmission device: output gear, third planetary gear set, first planetary gear set, second planetary gear set. The axial direction of the transmission device coincides with the main axis of rotation, for example. In particular, it is provided that the three planetary gear sets are arranged coaxially to one another and in this way one after the other. Furthermore, it is provided that the electric machine surrounds the first planetary gear set and / or the second planetary gear set in each case at least partially, in particular at least predominantly or completely. In other words it is For example, it is provided that the first planetary gear set and / or the second planetary gear set, in particular in the axial direction of the transmission device, are at least partially, in particular at least predominantly or completely, received in the electrical machine. Thus, for example, the first planetary gear set and / or the second planetary gear set are each covered at least partially, in particular at least predominantly or completely, in the radial direction of the transmission device towards the outside by the electric machine. The radial direction runs perpendicular to the axial direction.

In a further embodiment of the invention, it is provided that in the axial direction of the transmission device the first planetary gear set follows the output gear, the second planetary gear set follows the first planetary gear set and the third planetary gear set follows the second planetary gear set, the electric machine at least partially surrounding the third planetary gear set . In other words, it is provided that the planetary gear sets and the driven gear are arranged one behind the other or one after the other in the following sequence in the axial direction of the transmission device: driven gear, first planetary gear set, second planetary gear set, third planetary gear set. The third planetary gear set is at least partially, in particular at least predominantly or completely, arranged in the electrical machine in the axial direction, so that, for example, the third planetary gear set is at least partially, in particular at least predominantly or completely, covered outwardly by the electrical machine in the radial direction of the transmission device is. As a result, the space requirement of the transmission device, in particular in the axial direction, can be kept particularly low.

In a particularly advantageous embodiment of the invention, the transmission stage is linked to a transmission stage switching element which is provided for switching the transmission stage. The gear stage switching element enables at least two different gear ratios to be set via the gear stage.

The transmission stage is advantageously linked to exactly one shift element, namely the transmission stage shift element.

The third planetary gear set, which represents an embodiment of the transmission stage, is advantageously connected to the transmission stage shifting element. The gear ratio shift element is designed to decouple the third planetary gear set from a torque flow running from a drive machine to an axle drive. The expression of the decoupling from the torque flow means that in a first shift position of the gear step shift element there is a torque flow between different elements of the third planetary gear set and in a second shift position of the gear step shift element there is no torque flow between different elements of the third planetary gear set. In the second shift position, the third planetary gear set is decoupled from the torque flow between the drive machine and the axle drive.

The drive machine is, for example, the electrical machine or a drive machine provided in addition to the electrical machine, which can be designed, for example, as a further electrical machine or as an internal combustion engine. The respective drive machine can provide torques which can be transmitted, for example, via the planetary gear and / or the third planetary gear set to the axle gear, which can be part of the gear unit. The torques made available by the drive machine are transmitted along the aforementioned torque flow from the respective drive machine to the axle drive. The gear ratio shift element can be switched, for example, between a fifth connection state and a fifth release state. The fifth connection state corresponds, for example, to at least one fifth connection position, the fifth release state corresponding to at least one fifth release position. In this case, for example, the ratio step switching element can be moved between the fifth connection position and the fifth release position, in particular relative to the housing and / or in a translatory manner. In the fifth connection state, the third planetary gear set is coupled to the torque flow from the prime mover to the axle transmission by means of the gear ratio shift element, so that, for example, the third planetary gear set is tied in or integrated into the torque flow from the prime mover to the axle gear via the gear ratio change element. In the fifth release state, however, the third planetary gear set is decoupled from the torque flow from the prime mover to the axle gear by means of the gear ratio shifting element, so that the torques provided by the prime mover, which are transmitted along the torque flow from the prime mover to the axle gear, are not via the third planetary gear set be directed.

In a particularly advantageous embodiment of the invention, the first output shaft is permanently connected to or with the axle drive via at least one tooth engagement Coupled transmission device, whereby a particularly advantageous drivability can be shown in a space-saving and weight-saving manner.

The first output shaft is particularly advantageously permanently coupled to the axle drive via precisely one tooth engagement.

The axle drive can thus be part of the transmission device and is assigned, for example, to an axle of the motor vehicle, the axle having at least two wheels spaced apart from one another in the transverse direction of the vehicle. The wheels can be driven via the axle drive and via the planetary gear from the electric machine or from at least one of the drive machines or from the drive machines. The axle drive is a differential gear, which is also referred to as a differential. The axle drive is designed as a bevel gear differential, for example. The axle drive, in particular its function, is already sufficiently known from the general prior art. In particular, the axle drive has at least the function of allowing speed compensation between the wheels of the axle when the motor vehicle is cornering, so that, for example, the outside wheel can rotate at a higher speed than the inside wheel.

Finally, it has been shown to be particularly advantageous if the transmission device has a spur gear part transmission, which has a first gear configured as a fixed gear and a second gear configured as a fixed or loose gear, the first gear being coupled to a shaft of the second planet carrier, and wherein the second gear is coupled or can be coupled to a shaft of the second sun gear. The respective gear is thus arranged, for example, on a respective transmission shaft. If the respective gear is designed, for example, as a fixed gear, the respective gear is permanently connected to the respective gear shaft in a rotationally fixed manner. However, if the respective gearwheel is designed, for example, as a loose wheel, then the respective gearwheel or loose wheel can be coupled non-rotatably to the respective gear shaft. For this purpose, the idler gear is assigned, for example, a coupling element which can be switched between a coupling state and a release state. In the coupling state, the idler gear is non-rotatably connected to the transmission shaft via the coupling element, so that torques can be transmitted between the idler gear and the transmission shaft. In the released state, however, the coupling element releases the idler gear for rotation relative to the gear shaft so that the idler gear can rotate relative to the gear shaft and so that no torques can be transmitted between the idler gear and the gear shaft.

The transmission device according to the invention can in particular be designed as a multi-stage transmission based on the coupled planetary gear sets, with the power loss being able to be kept particularly low. In particular, six forward gears can be implemented, which can be internal combustion engine forward gears, since, for example, the motor vehicle can be driven by means of the internal combustion engine via the six internal combustion engine forward gears and can be driven forward.

The feature that the first output shaft is coupled to the second output shaft via the transmission stage can in particular be understood to mean that the first output shaft is permanently coupled to the second output shaft via the transmission stage, in particular in a torque-transmitting manner, so that torques are permanently transmitted between the output shafts can. If, for example, one of the output shafts is rotated, the other output shaft is always driven by the one output shaft via the transmission stage, so that the other output shaft is rotated with the one output shaft.

The feature that the first output shaft can be coupled to the second output shaft via the transmission stage can in particular be understood to mean that the transmission stage switching element is provided for this coupling capability. In this case, for example, the gear ratio switching element can be moved between the fifth connection position and the fifth release position, in particular relative to the housing and / or in a translatory manner. In the fifth connection state, the first output shaft is coupled to the second output shaft in a torque-transmitting manner by means of the transmission stage switching element via the transmission stage, so that when one of the output shafts is driven and, for example, rotated about the main axis of rotation relative to the housing, torques from the one output shaft are transmitted the shifting element and the transmission stage are transmitted to the other output shaft and, for example, the respective other output shaft is driven by the one output shaft through the transmission step and the transmission step switching element. In the fifth release state, however, for example, the first output shaft is decoupled from the second output shaft or vice versa, so that, for example, when the gear stage shifting element is in the fifth release state and one of the output shafts is being driven, a gear step and the gear stage shifting element take place and the other output shaft is not driven by the one output shaft. This means that the output shafts can be Switching element are coupled with one another and decoupled from one another as required.

The feature that the third planet carrier is non-rotatably connected to the second planet carrier can in particular be understood to mean that the third planet carrier is permanently non-rotatably connected to the second planet carrier. The feature that the third planetary carrier can be connected to the second planetary carrier in a rotationally fixed manner can in particular be understood to mean that, for example, a seventh switching element is provided, which can be switched, for example, between a seventh connection state and a seventh release state. The seventh connection state corresponds, for example, to at least one seventh connection position, the seventh release state, for example, corresponding to at least one seventh release position. For example, the seventh switching element can be moved between the seventh connection position and the seventh release position, in particular relative to the housing and / or in a translatory manner. In the seventh connection state, the third planet carrier is non-rotatably connected to the second planet carrier by means of the seventh shift element, so that the third planet carrier cannot rotate or rotate relative to the second planet carrier, in particular about the main axis of rotation, when the planetary gear is driven. In the seventh release state, however, the seventh switching element releases the third planet carrier for rotation relative to the second planet carrier, in particular about the main axis of rotation, so that, for example, the third planet carrier then in particular rotates or rotates relative to the second planet carrier, in particular about the main axis of rotation can when the planetary gear is driven.

The feature that the third ring gear is non-rotatably connected to the second sun gear can in particular be understood to mean that the third ring gear is permanently non-rotatably connected to the second sun gear. The feature that the third ring gear can be connected to the second sun gear in a rotationally fixed manner can in particular be understood to mean that, for example, an eighth switching element is provided, which, for example, can be switched between an eighth connection state and an eighth release state. The eighth connection state corresponds, for example, to at least one eighth connection position, the eighth release state, for example, corresponding to at least one eighth release position. For example, the eighth switching element can be moved between the eighth connection state and the eighth release state, in particular relative to the housing and / or in a translatory manner. In the eighth connection state, the third ring gear is non-rotatably connected to the second sun gear by means of the eighth shift element, so that the third ring gear in particular does not rotate or can rotate relative to the second sun gear, in particular about the main axis of rotation, when the planetary gear is driven. In the eighth release state, however, the eighth switching element releases the third ring gear for rotation relative to the second sun gear, in particular about the main axis of rotation, so that the third ring gear then in particular rotates or can rotate relative to the second sun gear, in particular about the main axis of rotation when the planetary gear is driven.

The feature that the third sun gear is non-rotatably connected to the housing can be understood in particular that the third sun gear is permanently non-rotatably connected to the housing, so that the third sun gear is permanently attached to the housing in a non-rotatable manner. The feature that the third sun gear can be connected non-rotatably to the housing can in particular be understood to mean that, for example, a ninth switching element is provided, which can be switched between a ninth connection state and a ninth release state, for example. The ninth connection state corresponds, for example, to at least one ninth connection position, the ninth release state, for example, corresponding to at least one ninth release position. For example, the ninth switching element can be moved between the ninth connection position and the ninth release position, in particular translationally and / or relative to the housing. In the ninth connection state, the third sun gear is non-rotatably connected to the housing by means of the ninth switching element, so that the third sun gear cannot rotate or rotate relative to the housing, in particular about the main axis of rotation, when the planetary gear is driven. In the ninth release state, however, the ninth switching element releases the third sun gear for rotation relative to the housing, in particular about the main axis of rotation, so that in particular the third sun gear can then rotate or rotate relative to the housing, in particular about the main axis of rotation, if the planetary gear is driven.

The feature that the second gear is coupled to the shaft of the second sun gear can in particular be understood to mean that the second gear is permanently connected or coupled to the shaft of the second sun gear in a rotationally fixed manner. The feature that the second gear can be coupled to the shaft of the second sun gear can in particular be understood that, for example, a tenth switching element is provided, which can be switched between a tenth connection state and a tenth release state, for example. The tenth connection state corresponds, for example, to at least a tenth connection position, the tenth release state, for example, corresponding to at least a tenth release position. For example, the tenth switching element can be moved between the tenth connection position and the tenth release position, in particular relative to the housing and / or in a translatory manner. In the tenth connection state, the second gear is non-rotatably coupled or connected by means of the tenth switching element to the shaft of the second sun gear and thus, for example, to the second sun gear, so that, for example, the second gear wheel does not move relative to the shaft of the second sun gear or relative to the second sun gear, in particular about the main axis of rotation, rotates or can rotate when the planetary gear is driven. In the tenth release state, however, the tenth switching element releases, for example, the second gear for rotation relative to the shaft or relative to the second sun gear, in particular about the main axis of rotation, so that in particular then the second gear is relative to the shaft or relative to the second The sun gear, in particular about the main axis of rotation, rotates or can rotate when the planetary gear is driven.

• - hohe Verzahnungswirkungsgrade
• - koaxiale Anordnung
• - elektrische Maschine mit integriertem Radsatz
• - eine Schaltlogik, aufgrund derer mindestens zwei der Schaltelemente als formschlüssige Schaltelemente ausgebildet werden können
• - weitere Klauenschaltelemente beziehungsweise formschlüssige Schaltelemente durch Einsatz der elektrischen Maschine möglich
• - das Achsgetriebe kann vorne angeordnet werden
• - die inneren Schaltelemente sind sehr gut zugänglich
• - Drehmomentbelastungen der Schaltelemente sind sehr gering
• - Planetendifferenzdrehzahlen sind sehr gering

In particular, it is conceivable that at least one of the switching elements or at least two of the switching elements or all switching elements is or are designed as a form-fitting switching element or form-fitting switching element and in particular as a claw or claw coupling in order to achieve a particularly efficient, non-rotatable connection. The respective form-fitting switching element can be equipped with or without a synchronization unit in order to achieve a further reduction in loss. Furthermore, it is conceivable that the respective shift element is designed, for example, as a non-positive or frictional shift element and in this case, for example, as a friction or multi-plate clutch. In particular, the respective switching element can be designed as a brake and, for example, as a frictional or non-positive switching element. In addition, the following advantages, for example, can be realized by means of the transmission device according to the invention:

• - high gear efficiency
• - coaxial arrangement
• - electric machine with integrated wheel set
• - A switching logic, based on which at least two of the switching elements can be designed as positive switching elements
• - Further claw switching elements or positive switching elements are possible by using the electrical machine
• - the axle drive can be arranged at the front
• - the inner switching elements are very accessible
• - The torque loads on the switching elements are very low
• - Planetary differential speeds are very low

In particular, the transmission device can be designed as a hybrid transmission since, for example, the motor vehicle can be driven via the electrical machine and alternatively or additionally via the internal combustion engine. In other words, the transmission device according to the invention can be used particularly advantageously for a hybrid drive train which has the electric machine and the internal combustion engine, so that the motor vehicle can be driven via the transmission device by means of the electric machine and by means of the internal combustion engine.

Further advantages, features and details of the invention emerge from the following description of preferred exemplary embodiments and with reference to the drawing. The features and combinations of features mentioned above in the description as well as the features and combinations of features mentioned below in the description of the figures and / or shown alone in the figures can be used not only in the respectively specified combination, but also in other combinations or on their own, without the scope of Invention to leave.

• 1 eine schematische Darstellung einer erfindungsgemäßen Getriebeeinrichtung gemäß einer ersten Ausführungsform;
• 2 eine schematische Darstellung der Getriebeeinrichtung gemäß einer zweiten Ausführungsform;
• 3 eine schematische Darstellung der Getriebeeinrichtung gemäß einer dritten Ausführungsform; und
• 4 eine schematische Darstellung der Getriebeeinrichtung gemäß einer vierten Ausführungsform.

The drawing shows in:

• 1 a schematic representation of a transmission device according to the invention according to a first embodiment;
• 2 a schematic representation of the transmission device according to a second embodiment;
• 3 a schematic representation of the transmission device according to a third embodiment; and
• 4th a schematic representation of the transmission device according to a fourth embodiment.

Identical or functionally identical elements are provided with the same reference symbols in the figures.

1 shows a schematic representation of a first embodiment of a transmission device 10 for a motor vehicle, in particular for a motor vehicle such as a passenger car. The transmission device 10 includes an in 1 housing shown particularly schematically 12 and a planetary gear 14th . The planetary gear 14th includes one in the housing 12 arranged or recorded first planetary gear set 16 , which is a first sun gear 18th , a first planet carrier 20th and a first ring gear 22nd having. The first planetary gear set also includes 16 at least one first planetary gear 24 , which is rotatable on the planet carrier 20th is mounted and on the one hand with the sun gear 18th and on the other hand with the ring gear 22nd combs. The planetary gear 14th further includes one in the housing 12 recorded or arranged second planetary gear set 26th , which is a second sun gear 28 , a second planet carrier 30th and a second ring gear 23. The second planetary gear set also has 26th at least a second planet gear 34 on, which is rotatable on the second planet carrier 30th is mounted and on the one hand with the sun gear 28 and on the other hand with the ring gear 32 combs.

The planetary gear 14th also has an at least partially, in particular at least predominantly or completely, in the housing 12 recorded internal wave 36 on which the second ring gear 32 , in particular permanent, non-rotatably with the first planet carrier 20th connected is. For example, the internal shaft 36 , in particular permanent, non-rotatably with the ring gear 32 and, in particular permanently, non-rotatably with the planet carrier 20th connected. Through this non-rotatable connection of the ring gear 32 and the planet carrier 20th run for example the planet carrier 20th and the ring gear 32 in particular then together and thus as a block, in particular about an axis of rotation, also referred to as the main axis of rotation 38 to when the planetary gear 14th is driven, that is, when torques in the planetary gear 14th be initiated. This means that especially when the planetary gear 14th is driven, the planet carrier 20th and the ring gear 32 together and thus simultaneously around the axis of rotation 38 relative to the housing 12 rotate, especially when the planet carrier 20th and the ring gear 32 not rotatably on the housing 12 are set.

The planetary gear 14th also has a drive shaft also referred to as an input shaft 40 on, via which torques also referred to as drive torques or drive torques in the planetary gear 14th can be initiated. One of the driving forces is in 1 by an arrow 42 illustrated. The respective drive torque is obtained, for example, from a first drive machine 44 provided, which is designed for example as an internal combustion engine or as an internal combustion engine. In other words, the prime mover 44 the respective drive torque, in particular via an output shaft of the drive machine 44 , providing that from the prime mover 44 provided drive torque on the drive shaft 40 can be transferred.

The planetary gear includes 14th a first switching element 46 , by means of which the drive shaft 40 rotatably with the first ring gear 22nd is connectable. Furthermore includes the planetary gear 14th a second switching element 48 , by means of which the drive shaft 40 rotatably with the first sun gear 18th is connectable. This means the drive shaft 40 for example, optionally by means of the switching elements 46 and 48 with the sun gear 18th and the ring gear 22nd can be connected, so that, for example, from the drive shaft 40 provided drive torques via the sun gear 18th or via the ring gear 22nd in the planetary gear 14th can optionally be initiated.

The planetary gear 14th also has a first output shaft 50 on which the planetary gear 14th can also provide torques referred to as output torques or output torques. The first output shaft 50 is, in particular permanently, non-rotatably with the second planet carrier 30th connected so that the planetary gear 14th the respective output torque via the planet carrier 30th and on the first output shaft 50 transmits.

In order to realize particularly advantageous drivability, the transmission device comprises 10 an electrical machine designed, for example, as a second drive machine 52 , by means of which torques can be provided in the form of second drive torques. To this end, the electrical machine includes 54 for example a stator 56 and a rotor 58 , which is about a machine axis of rotation relative to the stator 56 is rotatable. In particular, the rotor 58 from the stator 56 driven and thereby about the machine axis of rotation relative to the stator 56 be rotated. The machine axis of rotation runs parallel to the axis of rotation, for example 38 or coincides with the axis of rotation 38 together. It is provided that the electrical machine 54 , especially about the rotor 58 , provided second drive torque via the second sun gear 28 in the planetary gear 14th can be initiated. The electrical machine is for this purpose 54 , especially the rotor 58 , at least indirectly or directly to the second sun gear 28 tied up.

It can be provided that the rotor 58 rotatably with the sun gear 28 is connected or connectable, so that the electrical machine 54 about the rotor 58 provided second drive torque via the sun gear 28 in the planetary gear 14th can be initiated. At the in 1 First embodiment shown, it is provided that the rotor 58 , at least indirectly, permanently non-rotatably with the sun gear 28 connected is.

The transmission device also includes 10 , especially the planetary gear 14th , a third switching element 60 , by means of which the sun gear 18th rotatably with the sun gear 28 is connectable. In the first embodiment, there is also a fourth switching element 62 provided by means of which the first ring gear 22nd non-rotatably on the housing 12 fixable, that is, non-rotatably with the housing 12 is connectable. Especially good 1 can be seen that one through the internal shaft 36 effected connection of the first planet carrier 20th and the second ring gear 32 different wire set elements or switching elements is omitted, so that by means of the internal shaft 36 exclusively or solely the planet carrier 20th and the ring gear 32 , in particular permanently, are non-rotatably connected to one another.

It also includes the transmission device 10 , especially the planetary gear 14th , a second output shaft 64 , via which, for example, the planetary gear 14th , in particular other, can provide output torques. There is a translation level 66 provided over which the first output shaft 50 with the second output shaft 64 is coupled or can be coupled in the present case. The translation level 66 is in the first embodiment as a third planetary gear set 68 formed, which a third sun gear 70 , a third planet carrier 72 and a third ring gear 74 having. Also includes the third planetary gear set 68 at least a third planetary gear 76 , which is rotatable on the planet carrier 72 is mounted and on the one hand with the sun gear 70 and on the other hand with the ring gear 74 combs. Here is the third planet carrier 72 , especially about the first output shaft 50 , permanently rotatably with the planet carrier 30th connected. In other words, for example, is the first output shaft 50 permanently rotatably with the planet carrier 72 and permanently rotatably with the planet carrier 30th connected, so that for example that of the planetary gear 14th via the output shaft 50 provided torques via the planet carrier 72 in the third planetary gear set 68 can be initiated.

In all of the embodiments, gear shifting element is provided, by means of which the gear step 66 can be switched.

In the embodiment of 1 can be used as a fifth switching element 78 trained translation stage switching element the ring gear 74 of the third planetary gear set 68 rotatably with the sun gear 28 get connected. Furthermore is the sun gear 70 permanently rotatably with the housing 12 connected. In addition, for example, the ring gear 22nd via the switching element 62 rotatably with the sun gear 70 get connected. In particular, it is provided, for example, that the third planetary gear set 68 to exactly one shift element, namely to the gear shift element in the form of the fifth shift element 78 , is connected. This is the fifth switching element 78 trained gear ratio shift element designed to the third planetary gear set 68 from one of at least one of the prime movers to an in 1 Not shown axle drive to decouple running torque flow and to connect to the torque flow.

The transmission device 10 also includes an output gear designed in particular as a gear, in particular as a spur gear 80 , via which the transmission device 10 Can provide torques for driving at least one wheel of the motor vehicle, wherein in 1 one of these torques by an arrow 82 is illustrated. Here are the output gear 80 and the planetary gear sets 16 , 26th and 68 in the axial direction of the transmission device 10 arranged one after the other in the following order: driven gear 80 , third planetary gear set 68 , first planetary gear set 16 , second planetary gear set 26th .

The output gear 80 meshes advantageously with a gear, not shown, of an axle drive, particularly advantageously with a drive wheel of the axle drive for introducing torques into the axle drive.

2 shows a second embodiment of the transmission device 10 . The transmission device according to the second embodiment differs from the first embodiment in particular in that the sun gear 70 not permanently rotatable with the housing 12 is connected, but in the second embodiment comprises the transmission device 10 a sixth switching element 84 , by means of which the sun gear 70 rotatably with the housing 12 is connectable. In addition, in the second embodiment, in comparison to the first embodiment, the fifth switching element is omitted 78 so that the ring gear 74 permanently rotatably with the sun gear 28 is connected, in particular via the second output shaft 64 . For example, the rotor 58 permanently non-rotatably with the output shaft 64 and about this with the sun gear 28 and permanently rotatably with the ring gear 74 connected.

In the case of the 2 The second embodiment shown represents the sixth switching element 84 represents the gear stage switching element by means of which the gear stage 66 can be switched.

3 shows a third embodiment of the transmission device. In the third embodiment, the third is sun gear 70 permanently rotatably with the housing 12 connected. There is also a seventh switching element 86 provided by means of which the third planet carrier 72 non-rotatably with the output gear 80 can be connected, in particular via the output shaft 50 so that for example the planet carrier 72 by means of the seventh switching element 86 non-rotatably with the output shaft 50 is connectable. Furthermore, there is the electrical machine 54 , especially the rotor 58 , permanently rotatably with the third ring gear 74 connected. Also is the rotor 58 permanently rotatably with the second sun gear 28 connected so that by the electrical machine 54 about the rotor 58 provided torques on the ring gear 74 transmitted and via the ring gear 74 in the planetary gear set 68 are initiated, and those of the electrical machine 54 about the rotor 58 The torques provided are applied to the sun gear 28 transferred and via this in the planetary gear 14th initiated. While, for example, in the second embodiment, the output shaft 50 about the translation level 66 permanent torque transmission with the output shaft 64 is connected, since based on a torque flow from the output shaft 50 about the translation level 66 to the output shaft 64 or vice versa between the output shaft 50 and the output shaft 64 no switching element is arranged, is the output shaft in the first embodiment 50 about the translation level 66 by means of the switching element 78 with the output shaft 64 connectable. Here is in the torque flow from the output shaft 50 about the translation level 66 to the output shaft 64 or vice versa the switching element 78 between the output shafts 50 and 64 arranged. The output shaft is correspondingly in the third embodiment 50 about the translation level 66 with the output shaft 64 can be connected or coupled, as it relates to the torque flow from the output shaft 50 about the translation level 66 to the output shaft 64 or vice versa in this torque flow between the output shafts 50 and 64 the seventh switching element 86 is arranged. Thus, in the third embodiment, the output shaft 64 by means of the seventh switching element 86 with the output shaft 50 be coupled to transmit torque.

In the case of the 3 The third embodiment shown represents the seventh switching element 86 represents the gear stage switching element by means of which the gear stage 66 can be switched.

In the 3 The third embodiment shown has the special feature that by means of the seventh switching element 86 the output gear 80 and thus also a dme output gear 80 coupled axle drive completely from the first planetary gear set 16 and from the second planetary gear set 26th and the translation level 66 can be decoupled.

Finally shows 4th a fourth embodiment of the transmission device 10 . The fourth embodiment differs from the first, second and third embodiment in particular in that the gear ratio 66 as a spur gear unit 88 is formed which has at least one or, in the present case, several spur gear stages 90 and 92 having. The spur gear stage 90 includes a first gear 94 and a second gear meshing therewith 96 , which is designed as a fixed gear and permanently rotatably fixed with a gear shaft 98 of the spur gear unit 88 connected is. The spur gear stage 92 includes a third gear 100 and a fourth gear 102 , which is designed as a fixed gear and permanently rotatably fixed to the gear shaft 98 connected is. Here is the gear 94 permanently non-rotatably with the output shaft 50 and through this permanently rotatably with the planet carrier 30th connected. There is also an eighth switching element 104 provided, which acts as a coupling. By means of the eighth switching element 104 is the gear 100 and thus, for example, a shaft with which the gear 100 , in particular permanently, non-rotatably connected, non-rotatably with the output shaft 64 connectable, especially via the rotor 58 .

The spur gear unit 88 also includes a fifth gear designed as a pinion 106 , which for example with a particular as a ring gear 108 trained gear of an axle drive 110 the gear mechanism 10 combs. The gear 106 is for example the driven gear 80 or takes over the function of the output gear 80 . In the fourth embodiment of the planetary gear 14th provided torques via the gear stage 66 on the crown wheel 108 and thus on the axle drive 110 transferred from which then - as in 4th by arrows 112 is illustrated - two wheels spaced apart in the vehicle transverse direction of an axle of the motor vehicle can be driven.

In an embodiment not illustrated in the figures, it is conceivable that the eighth switching element 104 formed clutch alternatively on or on the gear shaft 98 is arranged. Then, for example, is the gear 102 not designed as a fixed gear, but as a loose gear. The eighth switching element 104 or the coupling is then, for example, a coupling element which can be switched between a coupling state and a release state. The gear wheel is in the released state of the coupling element 102 in the axial direction of the transmission shaft 98 or about the axial direction of the transmission shaft 98 relative to the gear shaft 98 rotatable so that no torque between the gear 102 and the gear shaft 98 can be transferred. In the coupled state, however, the gear is 102 by means of the coupling or by means of the coupling element in a rotationally fixed manner with the gear shaft 98 connected so that torques between the transmission shaft 98 and the gear 102 can be transferred. In this embodiment, not shown in the figures, and in the fourth embodiment, the eighth switching element comes 104 the same function as over the eighth switching element 104 the output shaft 64 with the gear shaft 98 can be coupled. In the fourth embodiment, the eighth shift element is related to a torque flow from the output shaft 64 to or on the gear shaft 98 between the gear 100 and the output shaft 64 and thus between the gear 102 and the output shaft 64 arranged. In the embodiment not shown in the figures, the eighth switching element is related to a torque flow from the output shaft 64 to and in particular to the gear shaft 98 between the gear shaft 98 and the gear 102 arranged. As a result, an arrangement that is advantageous in terms of installation space can be represented.

In the case of the 4th The fourth embodiment shown represents the eighth switching element 104 represents the gear stage switching element by means of which the gear stage 66 can be switched.

List of reference symbols

10

Transmission device

12

casing

14th

Planetary gear

16

first planetary gear set

18th

first sun gear

20th

first planet carrier

22nd

first ring gear

24

first planet gear

26th

second planetary gear set

28

second sun gear

30th

second planet carrier

32

second ring gear

34

second planet gear

36

internal shaft

38

Axis of rotation

40

drive shaft

42

arrow

44

Prime mover

46

first switching element

48

second switching element

50

first output shaft

52

electric machine

54

electric machine

56

stator

58

rotor

60

third switching element

62

fourth switching element

64

second output shaft

66

Translation stage

68

third planetary gear set

70

third sun gear

72

third planet carrier

74

third ring gear

76

third planetary gear

78

fifth switching element

80

Output gear

82

arrow

84

sixth switching element

86

seventh switching element

88

Spur gear unit

90

Spur gear stage

92

Spur gear stage

94

gear

96

gear

98

Gear shaft

100

gear

102

gear

104

eighth switching element

106

gear

108

Crown wheel

110

Axle drive

112

arrow

Claims (11)

Transmission device (10) for a motor vehicle, with a housing (12), and with a planetary gear (14), which has: - a first planetary gear set (16) accommodated in the housing (12), which has a first sun gear (18), a first planet carrier (20) and a first ring gear (22); - A second planetary gear set (26) accommodated in the housing (12), which has a second sun gear (28), a second planet carrier (30) and a second ring gear (32), which via an internal shaft (36) of the planetary gear (14 ) is rotatably connected to the first planet carrier (20); - A drive shaft (40), via which torques can be introduced into the planetary gear (14); - A first switching element (46) by means of which the drive shaft (40) can be connected to the first ring gear (22) in a rotationally fixed manner; - A second switching element (48), by means of which the drive shaft (40) can be connected to the first sun gear (18) in a rotationally fixed manner, and - a first output shaft (50) connected to the second planet carrier (30) in a rotationally fixed manner, via which torques from the planetary gear (14) can be provided; - An electrical machine (54), by means of which torques can be made available, which can be introduced into the planetary gear (14) via the second sun gear (28); and characterized by a third switching element (60), by means of which the first sun gear (18) can be connected to the second sun gear (28) in a rotationally fixed manner, a second output shaft (64) of the planetary gear (14) and a transmission stage (66) being provided, via which the first output shaft (50) is coupled or can be coupled to the second output shaft (64). Transmission device (10) after Claim 1 , characterized in that a fourth switching element (62) is provided, by means of which the first ring gear (22) can be connected non-rotatably to the housing (12). Transmission device (10) after Claim 1 or 2 , characterized in that a connection brought about by the internal shaft (36) of the first planet carrier (20) and the second ring gear (32) different gear set elements or switching elements is omitted. Transmission device (10) according to one of the preceding claims, characterized in that a third planetary gear set (68) is provided which has a third sun gear (70), a third planet carrier (72) and a third ring gear (74), the third planet carrier (72) is non-rotatably connected or connectable to the second planet carrier (30). Transmission device (10) after Claim 4 , characterized in that the third ring gear (74) is non-rotatably connected or can be connected to the second sun gear (28). Transmission device (10) after Claim 4 or 5 , characterized in that the third sun gear (70) is non-rotatably connected or connectable to the housing (12). Transmission device (10) according to one of the Claims 4 to 6th , characterized in that an output gear (80) is provided, the third planetary gear set (68) on the output gear (80), the first planetary gear set (16) on the third planetary gear set (68) and the second planetary gear set (26) follows the first planetary gear set (16), and wherein the electric machine (54) at least partially surrounds the first planetary gear set (16) and / or the second planetary gear set (26). Transmission device (10) according to one of the Claims 4 to 6th , characterized in that an output gear (80) is provided, wherein in the axial direction of the transmission device (10) the first planetary gear set (16) on the output gear (80), the second planetary gear set (26) on the first planetary gear set (16) and the third planetary gear set (68) follows the second planetary gear set (26), and wherein the electric machine (54) at least partially surrounds the third planetary gear set (68). Transmission device (10) according to one of the Claims 4 to 8th , characterized in that the transmission stage (66) is connected to exactly one transmission stage switching element (78, 84, 86, 104) which is designed to switch the transmission stage (66). Transmission device (10) according to one of the preceding claims, characterized in that the first output shaft (50) is permanently coupled to an axle drive of the transmission device (10) via precisely one tooth engagement. Transmission device (10) according to one of the Claims 1 to 3 , characterized in that a spur gear sub-gear (88) is provided which has a first gear (96) designed as a fixed wheel and one designed as a fixed or loose wheel second gear (102), wherein the first gear (96) is coupled to a shaft of the second planet carrier (30), and wherein the second gear (102) is coupled or can be coupled to a shaft of the second sun gear (28).

Images