Drive unit for a motor vehicle, in particular for a motor car

Abstract

Drive unit (10) for a motor vehicle, comprising a first driven axle (14) which has a hybrid drive system (20) with an internal combustion engine (22), a first electric machine (30), a planetary gear set (38) with exactly three shafts (40, 42, 44), namely a sum shaft, a first differential shaft and a second differential shaft, and a first axle drive (60), and with a second driven axle which has a second electric machine, wherein the first electric machine (30) is coupled or can be coupled to the first differential shaft of the planetary gear set (38) in a torque-transmitting manner, wherein: - the internal combustion engine (22) is or can be coupled to the sum shaft of the planetary gear (38) in a rotationally fixed manner, and - the second differential shaft of the planetary gear (38) is coupled to the axle gear (60) in such a way that torques can be routed out of the planetary gear (38) and into the axle gear (60) via the second differential shaft, - a final reduction spur gear stage (74) is provided, which includes a gear (76) which is permanently and rotationally fixed to a differential housing of the first axle drive (60), characterized by an input spur gear stage (77) by means of which the first electric machine (30) is coupled to the first differential shaft in a torque-transmitting manner, wherein the input spur gear stage (77) is arranged along a rotational axis (46) of the sum shaft such that the input spur gear stage (77) is at least partially at the same height as the final reduction spur gear stage (74).

Description

[0001] The invention relates to a drive device for a motor vehicle, in particular for a motor vehicle, according to the preamble of patent claim 1.

[0002] DE 10 2017 009 704 A1 discloses a hybrid drive system with an internal combustion engine having a crankshaft.

[0003] Furthermore, hybrid drive systems are known from DE 10 2015 120 669 A1, DE 11 2016 004 784 T5, DE 101 41 923 A1 and in particular from the generic CN 1 09 866 599 B.

[0004] The object of the present invention is to improve a drive device of the type mentioned at the beginning.

[0005] This object is achieved by a drive device having the features of patent claim 1. Advantageous embodiments with expedient further developments of the invention are specified in the remaining claims.

[0006] The invention relates to a drive device for a motor vehicle, preferably designed as a motor vehicle, in particular as a passenger car. This means that the motor vehicle, in its fully manufactured state, has the drive device, also referred to as a drive system or vehicle drive system, and can be driven by means of the drive device. The drive device has a first driven axle and a second driven axle. The feature that the respective axle is driven, i.e. drivable, is to be understood in particular that the respective axle has at least or exactly two vehicle wheels, also simply referred to as wheels, which, in the fully manufactured state of the motor vehicle having the drive device and thus the axles, are spaced from one another, for example in the transverse direction of the vehicle, and are arranged in particular on opposite sides of the motor vehicle in the transverse direction of the vehicle.The respective vehicle wheels of the respective axle are drivable, thereby enabling the motor vehicle to be driven. The vehicle wheels are ground contact elements by which the motor vehicle can be or is supported downwards on the ground in the vertical direction of the vehicle. For example, if the axles, i.e., the vehicle wheels of the axles, and thus the motor vehicle, are driven by the drive device while the motor vehicle is supported downwards on the ground in the vertical direction of the vehicle via its ground contact elements (vehicle wheels), the motor vehicle is driven along the ground, and the vehicle wheels roll, in particular directly, on the ground.

[0007] The first driven axle has a hybrid drive system which has an internal combustion engine, also referred to as an internal combustion engine and preferably designed as a reciprocating piston engine, and a first electric machine. For example, the vehicle wheels of the first axle can be driven by means of the internal combustion engine and by means of the first electric machine. Preferably, the hybrid drive system is assigned exclusively to the vehicle wheels of the first axle with respect to the vehicle wheels of the axles, so that exclusively the vehicle wheels of the first axle can be driven by means of the hybrid drive system, i.e. by means of the internal combustion engine and by means of the first electric machine with respect to the vehicle wheels of the axles, in particular with respect to a state in which the, in particular all, vehicle wheels of the first axle and the second axle have no contact with the ground, and are therefore floating in the air.In other words, for example, a drive torque provided by the hybrid drive system relative to the vehicle wheels of the first axle and the second axle can be transmitted exclusively to the vehicle wheels of the first axle. The first driven axle also comprises a planetary gear set with exactly three shafts: a master shaft, a first differential shaft, and a second differential shaft. This means that the first shaft of the planetary gear set is the master shaft, the second shaft of the planetary gear set is the first differential shaft, and the third shaft of the planetary gear set is the second differential shaft.

[0008] The second driven axle has a second electric machine. Preferably, the second electric machine is assigned exclusively to the vehicle wheels of the second axle with respect to the or all of the vehicle wheels of the first axle and the second axle. As already explained with regard to the hybrid drive system and the first axle, this is to be understood in particular as meaning that, with respect to the vehicle wheels of the first axle and the vehicle wheels of the second axle, only the vehicle wheels of the second axle can be driven by means of the second electric machine, in particular with respect to the aforementioned state. Furthermore, it is provided that the first electric machine is or can be coupled to the first differential shaft of the planetary gear system in a torque-transmitting manner, in particular in a rotationally fixed manner.The respective electric machine comprises, for example, a respective stator and a respective rotor, which is drivable by means of the respective stator and thus rotatable about a respective machine rotational axis relative to the respective stator. In this case, the feature that the first electric machine is or can be coupled in a rotationally fixed manner to the first differential shaft of the planetary gear system is understood to mean, for example, that the rotor of the first electric machine is or can be coupled in a rotationally fixed manner to the first differential shaft of the planetary gear system, i.e., is connected or connectable.

[0009] In the context of the present disclosure, the feature that two components are connected to one another in a rotationally fixed manner is to be understood as meaning that the components connected to one another in a rotationally fixed manner are arranged coaxially to one another and, in particular when the components are driven, rotate together or simultaneously about a component rotation axis common to the components at the same angular velocity, in particular relative to a housing of the drive device. The feature that two components are connected or coupled to one another in a torque-transmitting manner is to be understood as meaning that the components are coupled or connected to one another in such a way that torques can be transmitted between the components, wherein, when the components are connected or coupled to one another in a rotationally fixed manner, the components are also connected or coupled to one another in a torque-transmitting manner.

[0010] The feature that two components are permanently connected or coupled to one another in a torque-transmitting manner does not mean that a switching element is provided that can be switched between a coupling state that connects or couples the components to one another in a torque-transmitting manner and a decoupling state in which no torque can be transmitted between the components. Rather, the components are always and therefore permanently torque-transmitting, i.e., connected or coupled to one another in such a way that torque can be transmitted between the components. Thus, for example, one of the components can be driven by the other component, or vice versa.In particular, the feature that the components are permanently connected or coupled to one another in a rotationally fixed manner is to be understood as meaning that a switching element is not provided which can be switched between a coupling state that connects or couples the components to one another in a rotationally fixed manner and a decoupling state in which the components are decoupled from one another and rotatable relative to one another, so that no torque can be transmitted between the components. Instead, the components are always, and therefore permanently, connected or coupled to one another in a rotationally fixed manner. Furthermore, the feature that two components can be connected or coupled to one another in a rotationally fixed manner is to be understood as meaning that the components are assigned a switching element which can be switched between at least one coupling state and at least one decoupling state.In the coupled state, the components are connected or coupled to each other in a rotationally fixed manner by means of the switching element. In the uncoupled state, the components are decoupled from each other, so that in the uncoupled state, the components can rotate relative to each other about the component rotation axis.

[0011] The same applies to the feature that two components can be connected or coupled to one another in a torque-transmitting manner. Thus, for example, the feature that two components can be connected or coupled to one another in a torque-transmitting manner means that the components are assigned a switching element that can be switched between at least one connected state and at least one released state. In the connected state, the components are coupled or connected to one another in a torque-transmitting manner by means of the switching element, so that torques can be transmitted between the components. In the released state, the components are decoupled from one another, so that in the released state, no torques can be transmitted between the components.With respect to the first electrical machine, in particular the rotor of the first electrical machine, and the first differential shaft, the drive device is provided with a coupling between the first electrical machine, in particular the rotor, and the first differential shaft, in particular permanently and non-rotatably, or the first electrical machine, in particular the rotor of the first electrical machine, can be non-rotatably coupled to the first differential shaft. In this regard, the first electrical machine, in particular the rotor of the first electrical machine, is a first of the aforementioned components, and the first differential shaft is the second component.

[0012] In order to be able to realize particularly advantageous operation of the drive device and thus of the motor vehicle, it is provided in a known manner that the internal combustion engine is or can be coupled, i.e. connected or connectable, in a rotationally fixed manner to the summing shaft of the planetary gear. This is to be understood in particular as the following: The internal combustion engine has an output shaft, for example designed as a crankshaft, which can be driven in particular by combustion processes taking place in the internal combustion engine. The output shaft, in particular the crankshaft, of the internal combustion engine is or can be coupled in a rotationally fixed manner to the summing shaft of the planetary gear. Via the output shaft, the internal combustion engine can provide at least a first torque, which is also referred to as the first drive torque. The vehicle wheels of the first axle can be driven by means of the internal combustion engine using the first torque.Because the combustion engine or the output shaft is or can be coupled in a rotationally fixed manner to the summing shaft of the planetary gear set, the first torque can be transmitted from the output shaft to the summing shaft. In particular, it is provided that, with respect to a torque flow via which the first torque can be transmitted from the output shaft to the summing shaft, the other shafts of the planetary gear set are arranged outside the torque flow or at least not between the output shaft and the summing shaft. Furthermore, it is provided in a known manner that the second differential shaft of the planetary gear set is coupled to the axle drive in such a way that torques can be diverted from the planetary gear set via the second differential shaft and introduced into the axle drive.For example, with respect to a second torque flow, via which the torques can be diverted from the planetary gear via the second differential shaft and introduced into the axle drive, i.e., transmitted to the axle drive, the other, remaining shafts of the planetary gear are arranged outside the second torque flow or at least not between the second differential shaft and the axle drive. The axle drive is preferably a differential gear, via which the vehicle wheels of the first axle can be driven by the hybrid drive system, i.e., by the internal combustion engine and the first electric motor.As is already well known from the general state of the art, the axle drive is designed to allow different wheel speeds of the vehicle wheels of the first axle, for example, when cornering the motor vehicle, in particular such that the outer wheel of the first axle rotates faster, i.e., at a higher wheel speed, than the inner wheel of the first axle. This arrangement enables electrodynamic starting of the motor vehicle, especially when initially stationary, thus enabling particularly advantageous operation.

[0013] Furthermore, a final transmission spur gear stage is provided in a known manner, which comprises a gear which is permanently connected in a rotationally fixed manner to a differential housing of the first axle transmission.

[0014] According to the invention, an input spur gear stage is provided, by means of which the first electric machine is coupled to the first differential shaft in a torque-transmitting manner. According to the invention, the input spur gear stage is arranged along a rotational axis of the sum shaft such that the input spur gear stage is arranged at least partially at the same height as the final gear ratio spur gear stage.

[0015] In order to be able to realize particularly advantageous operation, one embodiment of the invention provides that the drive device has a blocking clutch, also referred to as a coupling element or interlocking coupling element, which is designed to connect the two differential shafts to one another in a rotationally fixed manner. This means that the blocking clutch can be switched between at least one first coupling state and at least one first decoupling state. For example, the blocking clutch has at least one blocking element which is movable, in particular relative to the housing and / or translationally and / or rotationally, between at least one first coupling position bringing about the first coupling state and at least one first decoupling position bringing about the first decoupling state.In the first coupling state, the differential shafts of the planetary gear are connected to each other in a rotationally fixed manner by means of the interlocking clutch. In the first decoupling state, however, the interlocking clutch allows relative rotation between the differential shafts, particularly around a shaft rotation axis.

[0016] A further embodiment is characterized in that the drive device has a countershaft, which is provided in particular in addition to the shafts of the planetary gear set, and which is arranged parallel and axially offset to a rotational axis of the summing shaft of the planetary gear set and thus parallel and axially offset to the summing shaft of the planetary gear set. The rotational axis of the summing shaft of the planetary gear set is also referred to as the summing shaft rotational axis and can, for example, coincide with the aforementioned shaft rotational axis. In particular, in a state in which the shafts of the planetary gear set are not connected to one another in a rotationally fixed manner, the shafts can rotate relative to one another about the shaft rotational axis or summing shaft rotational axis common to the shafts, particularly when the planetary gear set is driven, i.e. when torques are introduced into the planetary gear set.

[0017] Furthermore, it is provided that the countershaft is arranged parallel to and offset from a rotational axis of the axle drive, also referred to as the axle drive rotational axis. This can be understood in particular as the following: By introducing the aforementioned torques into the axle drive, the axle drive can be driven and is thereby rotated about the axle drive rotational axis, in particular relative to the aforementioned housing. The axle drive can distribute the torques that were or are introduced into the axle drive, in particular to the vehicle wheels of the first axle, whereby the vehicle wheels of the first axle can be driven and are driven via the axle drive.

[0018] Furthermore, it is provided that the second differential shaft and the countershaft are coupled, i.e., connected, to each other in a torque-transmitting manner by means of at least one spur gear stage. This allows for particularly advantageous drivability and thus particularly advantageous operation of the motor vehicle.

[0019] A further embodiment is characterized in that, viewed along the rotational axis of the sum shaft, i.e., viewed in the axial direction of the sum shaft, the planetary gear set is arranged downstream of the internal combustion engine, the interlocking clutch downstream of the planetary gear set, and the spur gear stage downstream of the interlocking clutch. In other words, it is preferably provided that, viewed along the rotational axis of the sum shaft, the planetary gear set, the interlocking clutch, and the spur gear stage follow one another in the following order, i.e., are arranged one after the other: the internal combustion engine - the planetary gear set - the interlocking clutch - the spur gear stage. This allows for particularly advantageous operation in a particularly space-efficient manner.

[0020] In a further, particularly advantageous embodiment of the invention, a final-ratio spur gear stage, also referred to as a final-drive spur gear stage, is provided in addition to the spur gear stage. The final-ratio spur gear stage is arranged between the planetary gear and the locking clutch, viewed along the master shaft rotation axis, thereby enabling particularly advantageous operation in a particularly space-efficient manner.

[0021] Finally, it has proven particularly advantageous if an input spur gear stage is provided, in particular in addition to the spur gear stage, by means of which the first electric machine, i.e. the rotor of the first electric machine, is coupled to the first differential shaft in a torque-transmitting manner. This makes it possible to achieve particularly advantageous drivability in a space- and weight-efficient manner. In order to keep the installation space requirement particularly low and thus to be able to create particularly advantageous drivability in a space-efficient manner, it is further preferably provided that, viewed along the total shaft rotation axis, the input spur gear stage is arranged after the combustion engine, the interlocking clutch after the input spur gear stage, the planetary gear set after the interlocking clutch, and the spur gear set after the planetary gear set.In other words, it has proven particularly advantageous if, viewed along the sum shaft rotation axis and thus in the axial direction of the sum shaft, the internal combustion engine, the input spur gear stage, the interlocking clutch, the planetary gear and the spur gear stage follow one another in the following order, i.e. are arranged one after the other: The internal combustion engine - the input spur gear stage - the interlocking clutch - the planetary gear - the spur gear stage.

[0022] Since the planetary gear set has exactly three shafts in the form of the first differential shaft, the second differential shaft, and the summation shaft, the planetary gear set is a three-shaft planetary gear set, which can have different construction variants or embodiments. In a first construction variant of the planetary gear set, the planetary gear set is designed as a simple planetary gear set. In other words, the planetary gear set has a planetary set, also referred to as a planetary gear set, which is designed as a simple planetary set. The planetary set has at least one or more planet gears. Furthermore, the planetary gear set has, in particular, a sun gear, in particular, a planet carrier, also referred to as a web, and, in particular, a ring gear. The at least one planet gear or the planet gears of the planetary set is or are rotatably mounted on the planet carrier.Because the planetary gear set is designed as a simple planetary gear set, the respective planetary gear meshes, in particular simultaneously, with the sun gear (also referred to as the sun) and the ring gear, but not with any other planetary gear. In particular, it is provided that the sun gear is connected or coupled, in particular permanently and non-rotatably, to a first of the shafts, the planet carrier is connected or coupled, in particular permanently and non-rotatably, to a second of the shafts, and the ring gear is connected or coupled, in particular permanently and non-rotatably, to the third shaft of the planetary gear set. For example, it is conceivable that the internal combustion engine, in particular the output shaft of the internal combustion engine, is directly or indirectly connected to the planet carrier, i.e. to the shaft that is connected, in particular permanently and non-rotatably, to the planet carrier, so that in this case, for example, the shaft that is also referred to as the carrier shaft and is connected, in particular permanently and non-rotatably, to the planet carrier is the master shaft.It is conceivable that the first electric machine, in particular the rotor of the first electric machine, is connected, in particular rotationally fixed, to the ring gear, and an output of the planetary gear set is connected to the sun gear. Thus, for example, the ring gear or the shaft rotationally fixed to the ring gear is one of the differential shafts, and the output or the sun gear or the shaft rotationally fixed to the sun gear is the other differential shaft. The output means that the aforementioned torques are output from the planetary gear set via the output and transferred, in particular via the spur gear stage, to the axle drive, thus being introduced into the axle drive.

[0023] Furthermore, it is conceivable that the second electric machine, in particular the rotor of the second electric machine, is connected to the sun gear or to the shaft connected to the sun gear, and the output is connected to the ring gear. In other words, it is conceivable that the ring gear or the shaft connected to the ring gear is the output via which the torque is transferred from the planetary gear, thus provided by the planetary gear and transmitted to the axle drive.

[0024] In a second design variant of the planetary gear, it is conceivable for the planetary set of the planetary gear to be designed as a double planetary set or as a double planet. This means in particular that at least one planet gear or the or all planet gears of the planetary gear set are designed as double planets, i.e. as double planet gears. In this regard, there is, for example, an even number of planet gears, where the even number is denoted, for example, by n and is greater than 1. A first half of all planet gears and thus of the entirety of the planet gears meshes with the sun gear and with a planet gear of the second half of the entirety of the planet gears, where the second half of the entirety of the planet gears meshes with the ring gear and with a planet gear of the first half of the entirety of the planet gears.In particular, it is provided that meshing of the first half with the ring gear does not occur, and meshing of the second half with the sun gear does not occur. In this case, it is particularly conceivable for the internal combustion engine, in particular the output shaft, to be directly or indirectly connected to the ring gear or to the shaft connected to the ring gear, so that the ring gear or the shaft connected to the ring gear is the master shaft. For example, the first electrical machine, in particular the rotor of the first electrical machine, is connected to the carrier shaft, which here is one of the differential shafts, and for example, the output is connected to the sun gear or to the shaft connected to the sun gear, or the output is the shaft connected to the sun gear, so that the output, the sun gear or the shaft connected to the sun gear is the other differential shaft.Furthermore, it is conceivable that the second electric machine, in particular the rotor of the second electric machine, is connected to the sun gear or to the shaft connected to the sun gear and the output is connected to the carrier shaft or to the planet carrier, so that, for example, the carrier shaft can be the output.

[0025] Further advantages, features, and details of the invention will become apparent from the following description of preferred embodiments and from the drawings. 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 respective specified combinations, but also in other combinations or on their own, without departing from the scope of the invention.

[0026] The drawing shows: Fig. 1 shows a partial schematic representation of a first embodiment of a drive device for a motor vehicle; Fig. 2 shows a partial schematic representation of a second embodiment of the drive device; Fig. 3 shows a partial schematic representation of a third embodiment of the drive device not falling under claim 1; Fig. 4 shows a partial schematic representation of a fourth embodiment of the drive device not falling under claim 1; and Fig. 5 a switching table to illustrate operating modes in which the drive device can be operated.

[0027] In the figures, identical or functionally identical elements are provided with the same reference numerals.

[0028] Fig. Fig. 1 shows a schematic representation of a first embodiment of a drive device 10 for a motor vehicle, in particular a passenger car. The drive device 10, also referred to as a drive system, in particular the motor vehicle as a whole, has at least or exactly two axles, also referred to as vehicle axles, which are arranged in the vehicle's longitudinal direction, which in Fig. 1 by a double arrow 12, are arranged consecutively and thus one behind the other. A first of the axes is in Fig. 1 and designated 14. The second axle is not shown in the figures. The respective axle is a driven axle, which will be explained in more detail below. The respective axle has at least or exactly two vehicle wheels, also referred to as wheels, with the exactly two vehicle wheels of the first vehicle axle 14 in Fig. 1 is designated 16. The previous and following statements regarding the vehicle wheels 16 of the first driven vehicle axle 14 can easily be applied to the vehicle wheels of the second driven axle, and vice versa. As can be seen from the example of the vehicle wheels 16, the vehicle wheels 16 are spaced apart from one another in the transverse direction of the vehicle and are arranged on opposite sides of the motor vehicle in the transverse direction of the vehicle, wherein the transverse direction of the vehicle is illustrated by a double arrow 18 and runs perpendicular to the longitudinal direction of the vehicle. The first driven vehicle axle 14 has a hybrid drive system 20, which has an internal combustion engine 22, also referred to as an internal combustion engine. The internal combustion engine 22, also simply referred to as an engine, has an engine housing 24 with cylinders 26, in which combustion processes take place during fired operation of the internal combustion engine 22.A respective piston is accommodated in each cylinder 26 for translational movement. Each piston is pivotally coupled to an output shaft 28, in this case embodied as a crankshaft, of the internal combustion engine 22 via a respective connecting rod. The combustion processes occurring in the cylinders 26 drive the pistons, which drives the output shaft 28 via the connecting rods, causing it to rotate relative to the engine housing 24 about an output shaft rotation axis. The internal combustion engine 22 can provide first torques, also referred to as first drive torques, via the output shaft 28.

[0029] The hybrid drive system 20 also includes a first electric machine 30 having a first stator 32 and a first rotor 34. The first rotor 34 is drivable by the first stator 32 and is thus rotatable about a machine rotation axis 36 relative to the stator 32. Via its rotor 34, the electric machine 30 can provide second torques, also referred to as second drive torques. The vehicle wheels 16 of the driven vehicle axle 14 can be driven by the internal combustion engine 22 and by the electric machine 30, i.e., by the respective first drive torque and by the respective second drive torque.

[0030] The hybrid drive system 20 also includes a planetary gear 38 with exactly three shafts 40, 42 and 44. A first of the shafts 40, 42 and 44 is a sum shaft of the planetary gear 38, a second of the shafts 40, 42 and 44 is a first differential shaft of the planetary gear 38, and the third of the shafts 40, 42 and 44 is a second differential shaft of the planetary gear 38. The shafts 40, 42 and 44 are arranged around a rotational axis 46 common to the shafts 40, 42 and 44. Fig. 1, the housing 48 of the drive device 10 is shown particularly schematically, wherein, for example, at least the planetary gear 38 is at least partially arranged in the housing 48. It can be seen that the shafts 40, 42, and 44 are arranged coaxially with one another.

[0031] The planetary gear 38 has, in particular, a sun gear 50, also referred to as a sun. Furthermore, the planetary gear 38 has, in particular, a ring gear 52. Furthermore, the planetary gear 38 has, in particular, a planet carrier 54, also referred to as a web. Fig. In the first embodiment shown in Figure 1, the sun gear 50 is coupled or connected, in particular permanently, in a rotationally fixed manner to the shaft 40. Furthermore, the ring gear 52 is connected or coupled, in particular permanently, in a rotationally fixed manner to the shaft 42, and the planet carrier 54 is connected, in particular permanently, in a rotationally fixed manner to the shaft 44. The sun gear 50, the ring gear 52, and the planet carrier 54 (web) are gear elements of the planetary gear 38, wherein the gear elements are arranged coaxially to one another and are rotatable about the rotation axis 46 relative to the housing 48 and, if necessary, relative to one another. The planetary gear 38 also has a planetary gear set 56 with a plurality of planet gears 58, which are rotatably mounted on the web.In the first embodiment, the planetary gear set 56 is designed as a simple planetary gear set, so that the respective planetary gear 58 meshes directly and simultaneously with both the sun gear 50 and the ring gear 52, without meshing with another planetary gear.

[0032] The first driven vehicle axle 14 also includes an axle drive 60, which is also referred to as a differential or differential gear or is designed as a differential or differential gear. The vehicle wheels 16 can be driven by the axle drive 60, in particular such that the vehicle wheels 16 can be driven by the hybrid drive system 20 via the axle drive 60. This is to be understood in particular that the axle drive 60 can be driven by means of the respective aforementioned drive torque or by means of a respective torque resulting from the respective drive torque and can thus be rotated relative to the housing 48 about an axis of rotation, also referred to as the axle drive rotation axis 61. The vehicle wheels 16 can be driven by driving the axle drive 60, which can be driven by means of the hybrid drive system 20.In particular, the respective vehicle wheel 16 can be driven by the axle transmission 60 via a respective side shaft 62.

[0033] The second driven axle, not shown in the figures, has a second electric machine by means of which the vehicle wheels of the second driven axle can be driven. Fig. In the first embodiment of the drive device 10 shown in Figure 1, the first electric machine 30, in particular its rotor 34, is coupled to the ring gear 52 in a torque-transmitting manner and thus to the shaft 42, which is, in particular, permanently and non-rotatably connected to the ring gear 52. Thus, in the first embodiment, the ring gear 52 or the shaft 42 is the first differential shaft of the planetary gear 38. Particularly advantageously, the rotor 34 is permanently coupled to the ring gear 52 in a torque-transmitting manner.

[0034] In order to be able to realize a particularly advantageous operation of the drive device 10, it is provided in the first embodiment that the internal combustion engine 22, in particular the output shaft 28, is or can be coupled in a rotationally fixed manner to the sum shaft of the planetary gear 38. In the Fig. In the first embodiment shown in Figure 1, the internal combustion engine 22, in particular the output shaft 28, can be coupled to the master shaft of the planetary gear 38. In this case, the master shaft of the planetary gear 38 in the first embodiment is the shaft 44, which is in particular permanently coupled or connected in a rotationally fixed manner to the planet carrier 54, so that the internal combustion engine 22, in particular the output shaft 28, can be coupled in a rotationally fixed manner to the shaft 44 and thus to the carrier. For this purpose, a coupling element K0 is provided, which is also referred to as a first clutch. In the first embodiment, for example, the coupling element K0 is designed as a frictional or non-positive switching element, wherein the coupling element K0 can be designed, for example, as a friction clutch, in particular as a multi-plate clutch. By means of the coupling element K0, the internal combustion engine 22, in particular the output shaft 28, can be connected in a rotationally fixed manner to the shaft 44 and thus to the carrier.The coupling element K0 can be switched between at least one first coupling state and at least one first decoupling state. In the first coupling state, the output shaft 28 is connected in a rotationally fixed manner to the shaft 44 (sum shaft) by means of the coupling element K0, and, for example, in the first decoupling state, the output shaft 28 is decoupled from the shaft 44. This is to be understood in particular that in the first coupling state, a maximum of a third torque can be transmitted between the output shaft 28 and the shaft 44 via the coupling element K0, in particular such that in the first coupling state, the output shaft 28 is connected in a rotationally fixed manner to the shaft 44 by means of the coupling element K0. In the decoupling state, a maximum of a fourth torque, which is lower than the third torque, can be transmitted between the output shaft 28 and the shaft 44 via the coupling element K0, wherein the fourth torque is preferably 0.In particular, in the first decoupling state, the coupling element K0 allows relative rotations between the output shaft 28 and the shaft 44 about the rotation axis 46. In other words, in the first coupling state, the output shaft 28 is more strongly coupled to the shaft 44 by means of the coupling element K0 than in the first decoupling state.

[0035] Since in the first embodiment, shaft 44 is the sum shaft and shaft 42 is the first differential shaft of the planetary gear 38, shaft 40 is the second differential shaft of the planetary gear 38. The second differential shaft (shaft 40) of the planetary gear 38 is coupled to the axle drive, in particular in a torque-transmitting and very particularly permanently torque-transmitting manner, in such a way that torques, also referred to as output torques, can be diverted from the planetary gear 38 via the second differential shaft and introduced into the axle drive 60, whereby the axle drive 60 can be driven and thus driven about the axle drive rotation axis 61 relative to the housing 48. In particular, the axle drive 60 can be driven by means of the output torques, or the axle drive 60 can be driven by means of fifth torques resulting from the output torques.The drive device 10 comprises a second coupling element K1, which is also referred to as a locking clutch or locking element. The coupling element K1 is designed to connect the two differential shafts of the planetary gear 38, i.e., the shafts 40 and 42, in a rotationally fixed manner. Furthermore, . Fig. 1 that the axle drive rotation axis 61 runs parallel to the rotation axis 46 and is spaced from the rotation axis 46. Furthermore, the output shaft 28 is arranged coaxially to the rotation axis 46. This means, in particular, that the output shaft 28 is rotatable about an output shaft rotation axis relative to the motor housing 24, also referred to as the engine block, wherein the output shaft rotation axis coincides with the rotation axis 46. Furthermore, it is provided that the machine rotation axis 36 runs parallel to the rotation axis 46 and parallel to the axle drive rotation axis 61 and is spaced from the rotation axis 46 and the axle drive rotation axis 61.

[0036] Furthermore, the drive device 10 has a countershaft 64, which is provided in particular in addition to the shafts 40, 42, and 44 and in addition to the side shafts 62 and is rotatable about a countershaft rotation axis 66, in particular relative to the housing 48. The countershaft 64 runs parallel to the axle drive rotation axis 61, parallel to the rotation axis 46, and parallel to the machine rotation axis 36, and is spaced apart from them. In other words, the countershaft 64 is arranged, in particular about its countershaft rotation axis 66, parallel and axially offset from the rotation axis 46 of the master shaft of the planetary gear 38 and parallel and axially offset from the axle drive rotation axis 61 of the axle drive 60. In this case, the second differential shaft (shaft 40) is connected or coupled to the countershaft 64 by means of at least one first spur gear stage 68 in a torque-transmitting manner.In the present case, the shaft 40 and the countershaft 64 are permanently coupled to one another in a torque-transmitting manner by means of the first spur gear stage 68. For this purpose, the first spur gear stage 68 has a first gear 70 as the first spur gear and a second gear 72 as the second spur gear, with the gears 70 and 72 meshing directly with one another. The gear 70 is, in particular permanently, connected in a rotationally fixed manner to the shaft 40, and the gear 72 is, in particular permanently, connected in a rotationally fixed manner to the countershaft 64. Viewed along the rotational axis 46 of the master shaft, the planetary gear 38 is arranged downstream of the internal combustion engine 22, the coupling element K1 downstream of the planetary gear 38, and the first spur gear stage 68 downstream of the coupling element K1.

[0037] Furthermore, the drive device 10 comprises a second spur gear stage provided in addition to the first spur gear stage 68, which is referred to as the final gear spur gear stage 74. The axle drive 60 is coupled, in particular permanently, in a torque-transmitting manner to the countershaft 64 by means of at least one spur gear stage, or in this case exactly one spur gear stage, which in this case is the final gear spur gear stage 74. For this purpose, the final gear spur gear stage 74 comprises a third gear 75 and a fourth gear 76, wherein the gear 75 and / or the gear 76 can be designed, for example, as spur gears. In particular, it is conceivable for the gear 76 to be a ring gear, wherein, for example, the gear 75 can be a pinion and / or a bevel gear. The gears 75 and 76 mesh directly with one another.The gear 75 is, in particular permanently, connected in a rotationally fixed manner to the countershaft 64, wherein the gear 75 follows the gear 72 in the axial direction of the countershaft 64 and thus along the countershaft rotation axis 66. The gear 76 is, in particular permanently, connected in a rotationally fixed manner to the axle drive 60, in particular to a differential housing and / or a differential carrier of the axle drive 60. It can be seen that the final ratio spur gear stage 74, viewed along the rotation axis 46 of the summing shaft, is arranged at least partially, in particular at least predominantly or completely, between the planetary gear 38 and the coupling element K1. In particular, the final ratio spur gear stage 74, viewed along the rotation axis 46, is arranged between the first spur gear stage 68, in particular the coupling element K1, and the internal combustion engine 22, in particular the coupling element K0.

[0038] The drive device 10 can have an input spur gear stage 77, provided in particular in addition to the spur gear stages 68 and 74, via which the rotor 34 is coupled, in particular permanently, to the ring gear 52 and thus to the shaft 42 in a torque-transmitting manner. In particular, it is conceivable for the shaft 42 or the ring gear 52 to be coupled, in particular permanently, to the rotor 34 in a torque-transmitting manner via exactly one spur gear stage, for which the input spur gear stage 77 is used in the first embodiment. The input spur gear stage 77 has a fifth gear 78 and a sixth gear 80, wherein the gear 78 and / or the gear 80 can be a spur gear. The gears 78 and 80 mesh directly with one another. The gear 78 is, in particular permanently, connected in a rotationally fixed manner to the rotor 34, and the gear 80 is, in particular permanently, connected in a rotationally fixed manner to the ring gear 52.It is conceivable that the gear 80 is formed integrally with the ring gear 52. The input spur gear stage 77 is arranged along the rotational axis 46 such that the input spur gear stage 77 is arranged at least partially at the same height as the final gear ratio spur gear stage 74. Alternatively or additionally, it is provided that, viewed along the rotational axis 46, the input spur gear stage 77 is arranged between the internal combustion engine 22, in particular the coupling element K0, and the first spur gear stage 68, in particular the coupling element K1. This allows the installation space requirement to be kept particularly low.

[0039] The coupling element K1 can be a positive-locking coupling element, in particular a claw clutch, or the coupling element K1 is a frictional or non-positive coupling element such as a friction clutch, in particular a multi-disk clutch.

[0040] Fig. 2 shows a second embodiment of the drive device 10. For better clarity, Fig. 2, the axle drive 60, the side shafts 62, and the vehicle wheels 16 are not shown. Furthermore, in the second embodiment, the coupling element K1 is designed as a positive-locking coupling element, in particular as a claw clutch. In the second embodiment, the shaft 40, which is connected in a rotationally fixed manner to the ring gear 52, is the second differential shaft. In contrast to the first embodiment, however, in the second embodiment, the sum shaft of the planetary gear 38 is the shaft 44, which is connected, in particular permanently, in a rotationally fixed manner to the carrier (planetary carrier 54) and is also referred to as the carrier shaft, to which the output shaft 28 can be connected in a rotationally fixed manner by means of the coupling element K0. Accordingly, the first differential shaft of the planetary gear 38 in the second embodiment is the shaft 40, which is connected, in particular permanently, in a rotationally fixed manner to the sun gear 50 and to which the rotor 34 of the first electric machine 30 is coupled, in particular permanently, in a torque-transmitting manner.In the second embodiment, the second differential shaft is shaft 42.

[0041] In the first embodiment, the spur gear stage 77 is an input spur gear stage, by means of which the electric machine 30, in particular the rotor 34, is coupled, in particular permanently, to the ring gear 52 and thus to the shaft 42 in a torque-transmitting manner.

[0042] In the second embodiment, viewed along the axis of rotation 46, the coupling element K1 is arranged between the internal combustion engine 22, in particular the coupling element K0, very particularly the spur gear stage 77, and the planetary gear 38. While in the first embodiment the planetary gear 38 is arranged at the front and the coupling element K1 at the rear, in the second embodiment the planetary gear 38 is arranged at the front and the coupling element K1 at the front. In the first and second embodiments, the electric machine 30 is arranged axially parallel. This means in particular that the machine axis of rotation 36 runs parallel to the output shaft axis of rotation and thus to the axis of rotation 46. Furthermore, in the first and second embodiments, the planetary gear 38, in particular its planetary gear set 56, is designed as a simple planetary gear set.

[0043] In the second embodiment, the input spur gear stage 77 comprises the gears 78 and 80, wherein the gear 78 is connected, in particular permanently, in a rotationally fixed manner to the rotor 34. In the second embodiment, the gear 80 is connected, in particular permanently, in a rotationally fixed manner to the shaft 40. In the second embodiment, the gears 78 and 80 do not mesh directly with one another, but in the second embodiment, an intermediate gear 82, designed in particular as a further spur gear, and an intermediate shaft 84 are provided. Preferably, the intermediate gear 82 and the intermediate shaft 84 are components of the input spur gear stage 77. It can be seen that the intermediate gear 82 is connected, in particular permanently, in a rotationally fixed manner to the intermediate shaft 84, wherein the intermediate gear 82 meshes, in particular simultaneously, with the gears 78 and 80, in particular directly.The intermediate shaft 84 is rotatable about an intermediate shaft rotation axis, in particular relative to the housing 48, wherein the intermediate shaft rotation axis runs parallel to the rotation axis 46 and thus parallel to the machine rotation axis 36, parallel to the countershaft rotation axis 66 and parallel to the axle transmission rotation axis 61 and is spaced from the machine rotation axis 36, from the rotation axis 46, from the countershaft rotation axis 66 and from the axle transmission rotation axis 61.

[0044] Fig. 3 shows a third embodiment of the drive device 10, not falling under claim 1. In the third embodiment, the coupling element K1 is arranged at the front and the planetary gear 38 is arranged at the rear. Furthermore, in the third embodiment, it is provided that the electric machine 30, in particular its rotor 34, is connected in a rotationally fixed manner, in particular permanently, to the ring gear 52 and thus to the shaft 42, which is connected in a rotationally fixed manner, in particular permanently, to the ring gear 52, so that in the third embodiment, the shaft 42 is the first differential shaft. The shaft 40, which is connected in a rotationally fixed manner, in particular permanently, to the sun gear 50, is the second differential shaft in the third embodiment and thus an output of the planetary gear 38.Accordingly, in the third embodiment, the shaft 44, which is connected, in particular permanently, in a rotationally fixed manner to the web, is the sum shaft, which can be coupled, i.e. connected, in particular via the coupling element K0, in a rotationally fixed manner to the output shaft 28 and thus to the internal combustion engine 22.

[0045] Fig. 4 shows a fourth embodiment of the drive device 10, which does not fall under claim 1. The fourth embodiment basically corresponds to the third embodiment or builds on the third embodiment, since in the fourth embodiment, as in the third embodiment, the electric machine 30, i.e. the rotor 34, is arranged coaxially with the planetary gear 38 and the output shaft 28. Thus, the machine axis of rotation 36 coincides with the axis of rotation 46 and with the output shaft axis of rotation. Furthermore, in the fourth embodiment too, the rotor 34 is connected, in particular permanently, in a rotationally fixed manner to the first differential shaft of the planetary gear 38, although in the fourth embodiment the first differential shaft of the planetary gear 38 is the web. The second differential shaft of the planetary gear 38 in the fourth embodiment is the shaft 40, which is connected, in particular permanently, in a rotationally fixed manner to the sun gear 50.Thus, the shaft 40 is the output of the planetary gear set 38 in the fourth embodiment. Furthermore, in the fourth embodiment, the sum shaft of the planetary gear set 38 is the shaft 42, which is connected, in particular permanently, in a rotationally fixed manner to the ring gear 52. Furthermore, in the fourth embodiment, the planetary gear set 38, in particular the planetary gear set 56, is designed as a double planetary gear set. This means that the planetary gear set 56 has a first number of planet gears 58 and a second number of planet gears 59, wherein the first number and / or the second number is preferably an even number, thus an even number and very preferably greater than 1. For example, it is provided that the first number corresponds to the second number, so that the first number and the second number form a total number or total number of planet gears 58 and 59.The first number is a first half and the second number is the second half of the total number. The, in particular all, planet gears 58, i.e. the first half of the total number, mesh directly with the sun gear 50 on the one hand and directly with the, in particular all, planet gears 59 and thus with the second half of the total number, wherein meshing of the, in particular all, planet gears 58 and thus the first number with the ring gear 52 is omitted. The, in particular all, planet gears 59 and thus the second number of the total number, mesh directly with the ring gear 52 on the one hand and directly with the first half of the total number, wherein meshing of the, in particular all, planet gears 59 with the sun gear 50 is omitted.

[0046] In the fourth embodiment, viewed along the axis of rotation 46, the planetary gear 38 is arranged between the internal combustion engine 22, in particular between the coupling element K0 and very particularly between the final transmission spur gear stage 74, and the coupling element K1. Furthermore, in the third and fourth embodiments, it is provided that the planetary gear 38 is arranged at least partially, in particular at least predominantly and thus at least half or completely, at the same height as the electric machine 30, viewed in the axial direction of the summing shaft or along the axis of rotation 46, in particular such that the planetary gear 38 is at least partially, in particular at least predominantly or completely, overlapped or covered by the electric machine 30, in particular by the rotor 34 and / or the stator 32, viewed outwards in the radial direction of the summing shaft.Furthermore, it is provided, in particular at least in the fourth embodiment, that the coupling element K1, which in the fourth embodiment can be designed as a frictional coupling element, in particular as a friction clutch, for example, is arranged at least partially, in particular at least predominantly and thus at least more than half or completely, at the same height as the electric machine 30 in the axial direction of the summing shaft and thus along the axis of rotation 46, so that the coupling element K1 is at least partially, in particular at least predominantly or completely, overlapped and thus covered by the electric machine 30, in particular by the rotor 34 and / or the stator 32, in the radial direction of the summing shaft.

[0047] Finally, Fig. 5 shows a switching table 86 for illustrating operating states or operating modes of the drive device 10. In a column S1 of the switching table 86, operating modes of the drive device 10, also referred to as states Z1, Z2, Z3 and Z4, are entered. In a cell ZE1 of the switching table 86, "K0" is entered, and in a cell ZE2, "K1" is entered. Below the cell ZE1 and related to the image plane of Fig. 5 To the right of column S1 are cells ZEK, and below cell ZE2 and related to the image plane of Fig. 5 To the right of cells ZEK are cells ZEK2. In the respective cell ZEK or ZEK2, either a solid circle or a dash is entered. A solid circle located below cell ZE1 means that the coupling element K0 is closed, and thus in its coupling state. A reference to the image plane of Fig. 5 A dash located below cell ZE1 means that the coupling element K0 is in its decoupling state, i.e., open. Accordingly, a dash related to the image planes of Fig.5 A dash arranged below cell ZE2 indicates that the coupling element K1 is open, and therefore in its uncoupling state, and accordingly a filled circle arranged below cell ZE2 means that the coupling element K1 is closed, and therefore in its coupling state. Therefore, to set state Z1 of the drive device 10, the coupling element K0 is closed while the coupling element K1 is open. To set state Z2, both coupling elements K0 and K1 are open simultaneously. To set state Z3, the coupling element K0 is open while the coupling element K1 is closed. To set state Z4, both coupling elements K0 and K1 are open. The first state Z1 is an EVT state, creating an electrically continuously variable transmission (EVT). The second state Z2 is a fixed gear, in particular for implementing a parallel hybrid.The third state Z3 enables a drive, in particular a purely electric drive, on the first vehicle axle 14, thus the vehicle wheels 16. In the fourth state Z4, the first vehicle axle 14 is switched to neutral, i.e., decoupled. This means, in particular, that the vehicle wheels 16 cannot be driven or are not driven.

[0048] In the following, further operating states of the drive device 10, also referred to as operating modes, are described in particular: In a first of the operating states, a start-up, in particular of the initially stationary motor vehicle, takes place by means of the internal combustion engine 22. If the coupling element K0 is closed and the coupling element K1 is open, the speed of the internal combustion engine 22 can be continuously adjusted or adjusted in a driving state of the motor vehicle by, in particular, continuously adjusting the speed of the electric machine 30. In this first operating state, for example, the motor vehicle can be started from a standstill with the first vehicle axle 14 driven. Any power loss is not fed into a starting clutch, such as the coupling element K0, which is designed, for example, as a separating clutch, but into the electric machine 30.An electrical power generated in or by means of the first electrical machine 30 in the first operating state feeds the second electrical machine, by means of which the second vehicle axle or the vehicle wheels of the second vehicle axle is or are driven. Furthermore, it is conceivable, particularly in the first operating state, that an electrical power generated in or by means of the first electrical machine 30 when starting off is used to charge a battery of the motor vehicle, also referred to as the vehicle battery. In a second of the operating states, the coupling element K0 is open and the coupling element K1 is closed, as a result of which, for example, the first vehicle axle 14 or its vehicle wheels 16 can be or are driven via the first electrical machine 30.In a third operating state, for example, the coupling elements K0 and K1 are open, whereby the first electric machine 30 and the combustion engine 22 are decoupled from the vehicle drive, i.e., from the vehicle axle 14 and the vehicle wheels 16, respectively. Thus, at a vehicle speed other than 0, the electric machine 30 and the combustion engine 22 can themselves have a speed of 0 or any other speeds, which do not have to be identical to one another. In a fourth operating state, the coupling elements K1 and K0 are closed, whereby the combustion engine 22 is coupled to the first vehicle axle 14 via a fixed, i.e., fixed or non-variable, gear ratio. In this fourth operating state, which corresponds to a parallel hybrid mode, the first electric machine 30 can optionally have three machine operating states.A first of the machine operating states is a generator mode, in which the electric machine 30 is operated as a generator. A second of the machine operating states is a motor mode, in which the electric machine 30 is operated as an electric motor. The third machine operating state is a no-load state. Thus, it is provided in particular that the previously described first operating state is the first state Z1, the previously described second operating state is the third state Z3, the previously described third operating state is the fourth state Z4, and the previously described fourth operating state is the second state Z2. List of reference symbols 10 Drive device 12 double arrow 14 vehicle axle 16 vehicle wheel 18 Double arrow 20 Hybrid drive system 22 combustion engine 24 Engine block 26 cylinders 28 Output shaft 30 electric machine 32 Stator 34 Rotor 36 Machine rotation axis 38 planetary gears 40 wave 42 Wave 44 Wave 46 axis of rotation 48 housings 50 sun gear 52 ring gear 54 planet carriers 56 planetary gear set 58 Planetary gear 59 Planetary gear 60 axle drives 61 Axle gear rotary axis 62 side shaft 64 Countershaft 66 Countershaft rotation axis 68 First spur gear stage 70 gear 72 gear 74 Final gear ratio spur gear stage 75 gear 76 gear 77 Input spur gear stage 78 gear 80 gear 82 intermediate gear 84 Intermediate shaft 86 Switching table K0 coupling element K1 coupling element S1 column Z1 condition Z2 condition Z3 condition Z4 condition ZE1 cell ZE2 cell ZEK cells ZEK2 cells

Claims

[1] Drive device (10) for a motor vehicle, with a first driven axle (14) which has a hybrid drive system (20) with an internal combustion engine (22), a first electric machine (30), a planetary gear (38) with exactly three shafts (40, 42, 44), namely a sum shaft, a first differential shaft and a second differential shaft, and a first axle gear (60), and with a second driven axle which has a second electric machine, wherein the first electric machine (30) is coupled or can be coupled to the first differential shaft of the planetary gear (38) in a torque-transmitting manner, wherein: - the internal combustion engine (22) is or can be coupled in a rotationally fixed manner to the sum shaft of the planetary gear (38), and - the second differential shaft of the planetary gear (38) is coupled to the axle gear (60) in such a way that torques can be diverted from the planetary gear (38) via the second differential shaft and introduced into the axle gear (60), - a final transmission spur gear stage (74) is provided, which comprises a gear (76) which is permanently connected in a rotationally fixed manner to a differential housing of the first axle transmission (60), characterized by an input spur gear stage (77) by means of which the first electric machine (30) is coupled to the first differential shaft in a torque-transmitting manner, wherein the input spur gear stage (77) is arranged along a rotational axis (46) of the sum shaft such that the input spur gear stage (77) is arranged at least partially at the same height as the final transmission spur gear stage (74). [2] Drive device (10) according to claim 1, characterized bya blocking coupling (K1) which is designed to connect two of the exactly three shafts (40, 42, 44) to one another in a rotationally fixed manner. [3] Drive device (10) according to claim 2, characterized by a countershaft (64) which is arranged parallel and axially offset to a rotational axis (46) of the sum shaft of the planetary gear (38) and parallel and axially offset to a rotational axis (61) of the axle gear (60), wherein the second differential shaft and the countershaft (64) are coupled to one another in a torque-transmitting manner by means of a first spur gear stage (68). [4] Drive device (10) according to claim 3, characterized by that, viewed along the axis of rotation (46) of the sum shaft, the planetary gear (38) is arranged after the internal combustion engine (22), the blocking clutch (K1) after the planetary gear (38) and the first spur gear stage (68) after the blocking clutch (K1). [5] Drive device (10) according to claim 4, characterized bythat the final transmission spur gear stage (74) is arranged between the planetary gear (38) and the locking clutch (K1) when viewed along the axis of rotation (46) of the sum shaft. [6] Drive device (10) according to claim 3, characterized by that, viewed along the axis of rotation (46) of the sum shaft, the input spur gear stage (77) is arranged after the internal combustion engine (22), the blocking clutch (K1) after the input spur gear stage (77), the planetary gear (38) after the blocking clutch (K1) and the first spur gear stage (68) after the planetary gear (38).

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