DE102022003203A1 - Hybrid drive system for a motor vehicle, in particular for a motor vehicle, and motor vehicle - Google Patents

Abstract

The invention relates to a hybrid drive system (10) for a motor vehicle, with an internal combustion engine (16), which has a crankshaft (22), with an electric machine (26), which has a rotor (30), with an axle gear (36) and with a gear (44) with a first sub-gear (46) and a second sub-gear (48), the first sub-gear (46) having a first planetary gear set (50) with a first element (52), a second element (54) and a third element (56); and a second planetary gear set (58) having a fourth element (60), a fifth element (62) and a sixth element (64). The second partial transmission (48) comprises an output shaft (72) and a first spur gear stage (74), which has a first output gear (78), which is arranged coaxially to the output shaft (72) and with a rotationally fixed with the third element (56). connected or connectable, first input gear (76) of the first spur gear stage (74) meshes.

Description

The invention relates to a hybrid drive system for a motor vehicle, in particular for a motor vehicle, according to the preamble of patent claim 1. Furthermore, the invention relates to a motor vehicle, in particular a motor vehicle, with such a hybrid drive system.

The DE 10 2017 006 082 A1 discloses a hybrid drive device, with an internal combustion engine, with an electric machine having a rotor, and with a planetary gear.

The object of the present invention is to create a hybrid drive system for a motor vehicle, in particular for a motor vehicle, and a motor vehicle, in particular a motor vehicle, so that a particularly efficient operation of the hybrid drive system and particularly advantageous drivability can be realized.

This object is achieved by a hybrid drive system with the features of patent claim 1 and by a motor vehicle with the features of patent claim 10. Advantageous embodiments with useful developments of the invention are specified in the remaining claims.

A first aspect of the invention relates to a hybrid drive system, also referred to as a hybrid drive device or designed as a hybrid drive device, for a motor vehicle, also simply referred to as a vehicle. This means that the motor vehicle, which is preferably designed as a motor vehicle, in particular as a passenger car, has the hybrid drive system in its fully manufactured state and can be driven by means of the hybrid drive system. For example, in its fully manufactured state, the motor vehicle has at least or exactly two vehicle axles, which are arranged one after the other in the longitudinal direction of the motor vehicle and are therefore simply referred to as axles. The respective vehicle axle has, for example, at least or exactly two vehicle wheels, also simply referred to as wheels. The vehicle wheels are ground contact elements via which the motor vehicle can be supported or supported downwards on a ground in the vertical direction of the motor vehicle. The respective vehicle wheels of the respective vehicle axle are arranged, for example, on sides of the motor vehicle that are opposite one another in the transverse direction of the motor vehicle. If the motor vehicle is driven along the ground while the motor vehicle is supported on the ground in the vertical direction of the vehicle downwards via the ground contact elements, the vehicle wheels roll, in particular directly, on the ground. By means of the hybrid drive system, for example, the vehicle wheels of at least or exactly one of the vehicle axles can be driven, or the vehicle wheels of both vehicle axles can be driven by means of the hybrid drive system. The vehicle wheels that can be driven by the hybrid drive system are also referred to as drive wheels, drivable wheels or driven wheels. When we talk about the vehicle wheels below, this refers to the drive wheels unless otherwise stated.

The hybrid drive system has an internal combustion engine, which is also referred to as an internal combustion engine. The internal combustion engine has a crankshaft, via which the internal combustion engine can provide first drive torques for driving the motor vehicle, in particular for driving the drive wheels. The internal combustion engine is therefore designed, for example, as a reciprocating piston engine. The hybrid drive system also includes an electric machine that has a rotor. The electric machine can provide second drive torque via the rotor for driving the motor vehicle, in particular for driving the vehicle wheels. For example, the motor vehicle can be driven electrically, in particular purely electrically, by means of the electric machine. Since the motor vehicle can be driven by means of the internal combustion engine and by means of the electric machine, the motor vehicle is preferably designed as a hybrid vehicle. Most preferably, the electrical machine is a high-voltage component whose electrical voltage, in particular electrical operating or nominal voltage, is, for example, greater than 50 volts, in particular greater than 60 volts, and most preferably is several hundred volts. For example, the electrical machine has a stator, by means of which the rotor can be driven and thereby rotated about a machine axis of rotation relative to the stator. The crankshaft can be rotated, for example, about a crankshaft rotation axis relative to a housing element of the internal combustion engine, which is designed, for example, as an engine block, in particular as a cylinder block. For example, the crankshaft and the rotor are arranged coaxially with one another, so that the machine axis of rotation coincides with the crankshaft axis of rotation.

The hybrid drive system also has an axle drive. In particular, the axle gear is assigned to the vehicle axle, the vehicle wheels of which can be driven by means of the internal combustion engine and by means of the electric machine. In particular, the vehicle wheels can be protected from combustion via the axle gear voltage engine, in particular by the crankshaft, as well as by the electrical machine, in particular by the rotor. In particular, the axle gear is a differential gear, also known as a differential. For example, a respective input torque resulting from the respective first drive torque and/or from the respective second drive torque can be transmitted to the axle drive. In other words, the respective input torque can be introduced into the axle gear, whereby the axle gear can be driven. For example, the respective input torque is the respective first drive torque and/or the respective second drive torque. In particular, for example, via the axle gear or by means of the axle gear, the respective input torque that is introduced or can be introduced into the axle gear can be divided and transmitted to the vehicle wheels, in particular in half, so that the vehicle wheels receive the respective input torque via the axle gear and thus from the internal combustion engine and / or from the electric machine can be driven. In particular, the axle gear has the function, which is already well known from the general state of the art, that the axle gear allows different speeds of the vehicle wheels when the motor vehicle is cornering, in particular in such a way that the vehicle wheel on the outside of the curve rotates or can rotate at a higher speed than the one on the inside of the curve Vehicle wheel, in particular while the vehicle wheels can be driven by the internal combustion engine and by the electric machine via the axle drive or are driven by the electric machine and/or by the internal combustion engine.

The hybrid drive system also has a transmission, in particular provided in addition to the axle gear, via which, for example, the axle gear can be driven by the electric machine and by the internal combustion engine, that is, by the rotor and the crankshaft. Thus, for example, the transmission can provide the respective input torque. For example, the respective first drive torque and the respective second drive torque can be introduced into the transmission. In other words, it is conceivable that a respective transmission torque resulting from the respective first drive torque and / or from the respective second drive torque can be introduced into the transmission in order to thereby drive the transmission, for example the transmission the respective, from which respective transmission torque can provide resulting input torque. Thus, for example, based on a torque flow, via which a respective torque that can be provided or provided by the rotor and the crankshaft can be transferred to the axle gear in order to drive the axle gear and the vehicle wheels via the axle gear, the axle gear is arranged in the torque flow, whereby also the transmission is arranged in the torque flow, and wherein, for example, the transmission is arranged upstream of the axle gear and downstream of the rotor, wherein the gear is arranged upstream of the axle gear and downstream of the crankshaft.

The transmission has a first partial transmission and a second partial transmission. The first partial transmission has a first planetary gear set, which is also referred to as the first planetary gear set. For example, the first planetary gear set has a first sun gear, a first planet carrier, also referred to as a first web, and a first ring gear. Furthermore, for example, the first planetary gear set has at least one first planetary gear, which meshes, in particular simultaneously, with the first ring gear and with the first sun gear, whereby, for example, the first sun gear does not mesh with the first ring gear. In particular, the first planet gear is rotatably held on the first planet carrier. The first sun gear, the first ring gear and the first planet carrier are also referred to as gear elements of the first planetary gear set or are gear elements of the first planetary gear set. The first planetary gear set has a first element, a second element and a third element. For example, the first element is a first of the gear elements, for example the second element is a second of the gear elements, and for example the third element is a third of the gear elements.

The first partial transmission also has a second planetary gear set, which is also referred to as a second planetary gear set. For example, the second planetary gear set, which is preferably provided in addition to the first planetary gear set, has a second sun gear, in particular in addition to the first sun gear, a second planet carrier, in particular in addition to the first planet carrier, and a second, in particular in addition to the first ring gear Ring gear, whereby the second planet carrier is also referred to as the second web. For example, the second planetary gear set has at least one second planet gear, which is rotatably held on the second planet carrier. In particular, the second planet gear meshes with the second sun gear and with the second ring gear, in particular simultaneously, with the second sun gear not meshing with the second ring gear, for example. The second sun gear, the second planet carrier and that Second ring gears are also referred to as planetary gear elements or are planetary gear elements of the second planetary gear set. The second planetary gear set has a fourth element, a fifth element and a sixth element. In particular, the fourth element is a first of the planetary gear elements, for example the fifth element is a second of the planetary gear elements, and for example the sixth element is a third of the planetary gear elements of the second planetary gear set.

The hybrid drive system has, for example, a housing, wherein, for example, the first partial transmission, thus the first planetary gear set and/or the second planetary gear set, can be at least partially arranged in the housing. In particular, if the respective gear element is not connected to the housing in a rotationally fixed manner, the respective gear element can be rotated about a gear element rotation axis relative to the housing, in particular by driving the respective gear element. The gear element rotation axis is also referred to as the first planetary gear set rotation axis. In particular, if the respective planetary gear element is not connected to the housing in a rotationally fixed manner, the respective planetary gear element can be rotated about a planetary gear element rotation axis relative to the housing, in particular by driving the respective planetary gear element. The planetary gear element rotation axis is also referred to as the second planetary gear set rotation axis. In particular, it is conceivable that the planetary gear sets are arranged coaxially to one another, so that the planetary gear set rotation axes coincide, and therefore the gear element rotation axis then coincides with the planetary gear element rotation axis. In particular, it is conceivable that the internal combustion engine and/or the electric machine are arranged coaxially with the first planetary gear set and/or coaxially with the second planetary gear set. In particular, the respective planetary gear set rotation axis runs in the axial direction of the transmission and the hybrid drive system as a whole, with, for example, the axial direction of the transmission, in particular of the hybrid drive system as a whole, coinciding with the respective planetary gear set rotation axis or running parallel to the respective planetary gear set rotation axis. Furthermore, it is conceivable that the axial direction of the transmission runs in the axial direction of the axle drive, in particular coinciding with the axial direction of the axle drive.

The second partial transmission has an output shaft, via which, for example, the second partial transmission and thus in particular the transmission can provide the respective input torque.

The second partial transmission has a first spur gear stage, which is provided in particular in addition to the planetary gear sets and which has a first output gear as the first spur gear. The first output gear is arranged coaxially with the output shaft. In addition, the first output gear meshes with a first input gear of the first spur gear stage which is non-rotatably connected or connectable to the third element, the first input gear being designed, for example, as a second spur gear of the first spur gear stage. In particular, the first output gear and the first input gear mesh directly with one another. For example, based on the aforementioned torque flow, along which the respective input torque can be transferred from the transmission to the axle transmission, the first output gear and the first input gear are arranged in the torque flow, such that the first output gear is arranged downstream of the first input gear.

The second partial transmission also has a second spur gear stage, which is provided in addition to the first spur gear stage and has a second output gear as a third spur gear, which is arranged coaxially to the output shaft and with a second input gear connected, in particular permanently, in a rotationally fixed manner to the fifth element the second spur gear stage meshes. In particular, the second input gear is a fourth spur gear of the second spur gear stage. In particular, the second input gear and the second output gear mesh directly with one another. Based on the aforementioned torque flow, for example, the second input gear and the second output gear are arranged in the torque flow, such that the second output gear is arranged downstream of the second input gear. In particular, with respect to the torque flow, the partial transmissions are arranged in the torque flow, in particular in such a way that the second partial transmission is arranged downstream of the first partial transmission, so that the axle transmission can be driven by the first partial transmission via the second partial transmission. In particular, with respect to the torque flow, the output shaft is arranged in the torque flow, in particular in such a way that the output shaft is arranged upstream of the axle gear and downstream of the spur gear stages.

The hybrid drive system further has an output gear, which is provided in particular in addition to the input gears and in addition to the output gears. In particular, the output shaft can be driven by the first output gear and by the second output gear, so that, for example, the output shaft can be driven via the first output gear the first input gear and can be driven by the second input gear via the second output gear. Thus, for example, the respective output gear is or can be connected to the output shaft in a rotationally fixed manner. In particular, it is conceivable that the respective output gear can be permanently connected to the output shaft in a rotationally fixed manner.

The output gear is permanently connected to the output shaft in a rotationally fixed manner. In addition, the output gear constantly meshes with an axle drive input gear, which is designed as a gear. The feature that the output gear constantly meshes with the axle gear input gear is to be understood as meaning that the hybrid drive system does not switch between a meshing state in which the output gear meshes with the axle gear input gear and a non-meshing state in which the output gear does not mesh with the axle gear input gear meshes, is switchable, but the output gear and the axle gear input gear always, that is always and therefore permanently, mesh with each other. Thus, for example, the respective input torque can be provided by the output gear and, in particular directly, transmitted to the axle gear input gear and thereby introduced into the axle gear, whereby the axle gear can be driven, for example, and thereby in particular rotatable about an axle gear rotation axis relative to the housing. By driving the axle gear, the vehicle wheels can be driven.

The hybrid drive system further comprises a first switching element, which is designed to connect the crankshaft to the first element in a rotationally fixed manner. This means that the crankshaft can be connected to the first element in a rotationally fixed manner by means of the first switching element. The first switching element can be switched, for example, between a first coupling state and a first decoupling state. In the first coupling state, the crankshaft is connected to the first element in a rotationally fixed manner by means of the first switching element. In the first decoupling state, the first switching element releases the crankshaft for rotation about the crankshaft axis of rotation or about the transmission element rotation axis and relative to the first element, so that in the first decoupling state the crankshaft and the first element can be rotated relative to one another about the crankshaft rotation axis or about the transmission element rotation axis are, and so that, in particular in the first decoupling state, no torques can be transmitted via the first switching element between the crankshaft and the first element. For example, the first switching element can be moved, in particular relative to the housing and/or translationally, between at least one first coupling position causing the first coupling state and at least one first decoupling position causing the first decoupling position.

The rotor of the electric machine is coupled or can be coupled to the third element, in particular in a torque-transmitting manner and in particular in a rotationally fixed manner, in such a way that the respective first drive torque provided or able to be provided by the electrical machine via the rotor is transmitted to the third element, that is to say via the third Element can be introduced into the transmission. In other words, the rotor of the electric machine is coupled or can be coupled to the third element in such a way that torques, starting from the electric machine or from the rotor, can be introduced into the transmission on the third element and in particular via the third element.

In order to be able to realize particularly efficient operation of the hybrid drive system as well as particularly advantageous drivability, it is provided according to the invention that the second element is permanently connected to the fourth element in a rotationally fixed manner. Furthermore, it is provided according to the invention that the hybrid drive system comprises a second switching element, which is designed to connect the sixth element to the housing of the hybrid drive system in a rotationally fixed manner. This means that the sixth element can be connected to the housing in a rotationally fixed manner by means of the second switching element. For example, the second switching element can be switched between a second coupling state and a second decoupling state. In the second coupling state, the sixth element is rotatably connected to the housing by means of the second switching element, and is therefore fixed to the housing in a rotationally fixed manner, so that the sixth element cannot rotate about the planetary gear element rotation axis relative to the housing. In the second decoupling state, the second switching element releases the sixth element for rotation about the planetary gear element rotation axis and relative to the housing, so that in the second decoupling state the sixth element can be rotated about the planetary gear element rotation axis relative to the housing, and so in the second decoupling state no torques can be transmitted via the second switching element between the sixth element and the housing. For example, the second switching element can, in particular translationally and/or relative to the housing, between at least one second coupling position which brings about the second coupling state and at least one of the second decoupling positions can be moved to the second decoupling position.

In the context of the present disclosure, the feature that two components such as the third element and the first input gear are connected to one another in a rotationally fixed manner is to be understood to mean that the components connected to one another in a rotationally fixed manner are arranged coaxially to one another and are in particular when the components are driven , rotate together or simultaneously about a component rotation axis common to the components, such as the gear element rotation axis, with the same angular velocity, in particular relative to the housing. In other words, “rotatably fixed” means the following: Two rotatably mounted elements are connected to one another in a rotationally fixed manner when they are arranged coaxially to one another and are connected to one another in such a way that they rotate at the same angular speed, in particular around the component rotation axis and relative to the housing, when the elements are driven. The feature that two components such as the rotor and the third element are connected to each other 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, whereby the components are rotationally fixed are connected to each other, the components are also connected to each other to transmit torque. The feature that two components are permanently connected to one another in a torque-transmitting manner means that a switching element is not provided which can be switched between a coupling state that connects the components to one another in a torque-transmitting manner and a decoupling state in which no torques are transmitted between the components via the switching element can be transmitted, but the components are always or always and therefore permanently torque-transmitting, that is to say connected to one another in such a way that a 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 two components such as the output shaft and the output gear are permanently connected to one another in a rotationally fixed manner means that a switching element is not provided which can be switched between a coupling state that connects 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 torques can be transmitted between the components via the switching element, but rather the components are always, or always, therefore permanently, connected or coupled to one another in a rotationally fixed manner.

The feature that two components can be connected or coupled to one another in a rotationally fixed or torque-transmitting manner means, in particular, that the components are assigned a switching element which can be switched between at least one coupling state and a decoupling state. In the coupling state, the components are connected to one another in a rotationally fixed or torque-transmitting manner by means of the switching element. In the decoupling state, the components are decoupled from one another, so that in the decoupling state the components are rotatable relative to one another, in particular about the component rotation axis, and in particular so that no torques can be transmitted between the components via the switching element.

In the context of the present disclosure, ordinal words referred to as ordinals, such as "first", "first", "second", "second", etc., are not necessarily used to indicate a number or set of elements to which the ordinal words refer. to indicate or imply, but in order to be able to clearly refer to terms or elements to which the ordinal number words are assigned or to which the ordinal number words refer.

Furthermore, the terms “axial” and “coaxial” refer in particular to the respective planetary gear set rotation axis, with the planetary gear set rotation axes coinciding. Furthermore, “axially overlapping” is to be understood as meaning the following: Two elements are arranged axially overlapping, in particular relative to one another, if the elements are arranged in areas of the same axial coordinates, in particular in the axial direction of the hybrid drive system and thus in particular viewed along the planetary gear set rotation axis. For example, in the case of two elements arranged axially overlapping one another, there is at least one radially arranged straight line, i.e. running in the radial direction of the hybrid drive system and thus perpendicular to the axial direction of the hybrid drive system, which penetrates or intersects both one and the other of the elements arranged axially overlapping one another.

The axle gear input wheel is preferably a gear which is, for example, permanently, non-rotatably connected to a differential cage of the axle gear, also referred to as a differential cage.

In order to be able to realize a particularly compact design and a particularly efficient operation and thus to advantageously keep the power loss low, it is provided in one embodiment of the invention that a total of exactly two planetary gear sets are provided, namely the first planetary gear set and the second planetary gear set.

A further embodiment is characterized by a third switching element, which is designed to connect the first input gear to the third element in a rotationally fixed manner. In other words, the first input gear can be connected to the third element in a rotationally fixed manner, for example by means of the third switching element. Alternatively, the third switching element is designed to connect the first output gear to the output shaft in a rotationally fixed manner. In other words, it is conceivable that the first output gear can be connected to the output shaft in a rotationally fixed manner by means of the third switching element. Expressed again in other words, the hybrid drive system preferably has the third switching element, by means of which two connecting parts of the hybrid drive system can be connected to one another in a rotationally fixed manner. A first of the connecting parts is the first input gear, with the second connecting part then being the third element. Alternatively, the first connecting part is the first output gear, with the second connecting part then being the output shaft. For example, the third switching element can be switched between a third coupling state and a third decoupling state. In the third coupling state, the connecting parts are connected to one another in a rotationally fixed manner by means of the third switching element. In the third decoupling state, the third switching element releases the connecting parts for rotation about the gear element rotation axis and relative to one another, in particular when the connecting parts are the first input gear and the third element. For example, the output shaft is rotatable about an output shaft rotation axis relative to the housing. If the connecting parts are the first output gear and the output shaft, then in the third decoupling state the third switching element releases the connecting parts for rotation about the output shaft axis of rotation and relative to one another, so that in the third decoupling state the connecting parts are about the gear element rotation axis or around the Output shaft rotation axis can be rotated relative to each other. Preferably, the output shaft axis of rotation runs parallel to the respective planetary gear set rotation axis, the output shaft rotation axis being spaced from the respective planetary gear set rotation axis. For example, the third switching element can be moved, in particular translationally and/or relative to the housing, between a third coupling position causing the third coupling state and at least one third decoupling position causing the third decoupling state. By using the third switching element, advantageous switching and thus drivability can be achieved.

In order to be able to realize particularly efficient operation and particularly advantageous drivability, it is provided in a further embodiment of the invention that the hybrid drive system has a fourth switching element, which is designed to connect the third element to the sixth element in a rotationally fixed manner. In other words, the third element can be connected to the sixth element in a rotationally fixed manner by means of the fourth switching element. For example, the fourth switching element can be switched between a fourth coupling state and a fourth decoupling state. In the fourth coupling state, the third element is connected to the sixth element in a rotationally fixed manner by means of the fourth switching element. In the fourth decoupling state, the fourth switching element releases the third element for rotation about the respective planetary gear set rotation axis and relative to the sixth element, so that in the fourth decoupling state the third element and the sixth element are rotatable relative to each other about the respective planetary gear set rotation axis. For example, the fourth switching element can be moved, in particular translationally and/or relative to the housing, between at least one fourth coupling position causing the fourth coupling state and at least one fourth decoupling position causing the fourth decoupling state.

In a particularly advantageous embodiment of the invention, the hybrid drive system comprises a fifth switching element, which is designed to connect the first element to the housing in a rotationally fixed manner. In other words, the first element can be connected to the housing in a rotationally fixed manner by means of the fifth switching element. For example, the fifth switching element can be switched between a fifth coupling state and a fifth decoupling state. In the fifth coupling state, the first element is connected to the housing in a rotationally fixed manner by means of the fifth switching element. In the fifth decoupling state, the fifth switching element releases the first element for rotation about the first planetary gear set rotation axis relative to the housing, so that in the fifth decoupling state the first element can be rotated about the first planetary gear set rotation axis relative to the housing. For example, the fifth switching element can, in particular translationally and/or relative to the housing, between at least one fifth coupling position causing the fifth coupling state and at least one fifth coupling position bringing about the fifth decoupling state Decoupling position can be moved. In this way, for example, gears of the hybrid drive system can be switched as needed, so that particularly advantageous shiftability and thus particularly advantageous drivability can be achieved.

In order to be able to realize particularly efficient operation and advantageous drivability in a particularly space- and weight-efficient manner, a sixth switching element is provided in a further embodiment of the invention, which is designed to connect the crankshaft to the second element in a rotationally fixed manner. In other words, the crankshaft can be connected to the second element in a rotationally fixed manner by means of the sixth switching element. For example, the sixth switching element can be switched between a sixth coupling state and a sixth decoupling state. In the sixth coupling state, the crankshaft is connected to the second element in a rotationally fixed manner by means of the sixth switching element. In the sixth decoupling state, the sixth switching element releases the crankshaft for rotation about the crankshaft axis of rotation and relative to the second element, so that in the sixth decoupling state the crankshaft and the second element can be rotated relative to one another about the crankshaft axis of rotation or about the first planetary gear set rotation axis. For example, the sixth switching element is movable between at least one sixth coupling position causing the sixth coupling state and at least one sixth decoupling position causing the sixth decoupling state, in particular relative to the housing and/or translationally.

In a further, particularly advantageous embodiment of the invention, it is provided that, viewed in an axial direction of the hybrid drive system, that is to say in the axial direction of the hybrid drive system and thus viewed along the respective planetary gear set rotation axis, the second spur gear stage is on a side of the first partial transmission facing away from the first spur gear stage is arranged. This allows a particularly space-efficient and low-loss design of the hybrid drive system to be achieved.

In order to be able to realize a particularly compact design, particularly when viewed in the axial direction of the hybrid drive system 10, it is provided in a further embodiment of the invention that the crankshaft is arranged coaxially to the first partial transmission, with the output gear axially, that is to say in the axial direction of the hybrid drive system, is arranged between the internal combustion engine and the first sub-transmission, in particular the first planetary gear set.

In order to keep the installation space requirement of the hybrid drive system particularly low, especially when viewed in the axial direction of the hybrid drive system, and thus to be able to realize a particularly compact and efficient design, it is provided in a further embodiment of the invention that the electric machine overlaps axially with at least one of the planetary gear sets, in particular at least with the first planetary gear set is arranged.

A second aspect of the invention relates to a motor vehicle, which is preferably designed as a motor vehicle, in particular as a passenger car, and is also simply referred to as a vehicle, which has a hybrid drive system according to the first aspect of the invention and can be driven by means of the hybrid drive system. Advantages and advantageous refinements of the first aspect of the invention are to be viewed as advantages and advantageous refinements of the second aspect of the invention and vice versa.

Through the invention, the hybrid drive system, in particular the transmission and in particular the first sub-transmission, can be implemented as a multi-stage transmission based on coupled planetary gear sets, namely the first planetary gear set and the second planetary gear set, in particular in an axially parallel design, whereby the power loss can be kept particularly low . For example, up to six hybrid and/or internal combustion engine forward gears, one internal combustion engine reverse gear and at least three electric gears and various continuously variable driving ranges can be represented. A large spread can be achieved. The planetary gear sets are preferably designed as simple planetary gear sets, i.e. as single planetary gear sets. At least one of the switching elements, in particular at least two of the switching elements, can be designed as positive switching elements, in particular as claw clutches, in particular with or without a synchronizing unit, in order to keep losses particularly low. Good gearing efficiencies can be achieved. A coaxial planetary gear set design with two axially parallel outputs can be created, which is particularly advantageous for a front-transverse drive. The electrical machine can be arranged coaxially or laterally, i.e. in a so-called side-by-side arrangement. In particular when the electrical machine is arranged coaxially, it is possible to place at least one or more of the switching elements in the electrical machine. Further claw switching elements are conceivable, in particular through the use of the electric machine.

Further advantages, features and details of the invention result from the following description of preferred exemplary embodiments. 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 in the figures alone can be used not only in the combination specified in each case, but also in other combinations or on their own, without the scope of to abandon invention.

• 1 eine schematische Darstellung einer ersten Ausführungsform eines Hybridantriebssystems für ein Kraftfahrzeug;
• 2 eine schematische Darstellung einer zweiten Ausführungsform des Hybridantriebssystems; und
• 3 eine schematische Darstellung einer dritten Ausführungsform des Hybridantriebssystems.

The drawing shows in:

• 1 a schematic representation of a first embodiment of a hybrid drive system for a motor vehicle;
• 2 a schematic representation of a second embodiment of the hybrid drive system; and
• 3 a schematic representation of a third embodiment of the hybrid drive system.

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

1 shows a schematic representation of a first embodiment of a hybrid drive system 10 for a motor vehicle, also simply referred to as a vehicle, which is preferably designed as a motor vehicle, in particular as a passenger car. The motor vehicle has at least or exactly two vehicle axles arranged one behind the other in the longitudinal direction of the vehicle and thus sequentially, the respective vehicle axle having at least or exactly two vehicle wheels. The respective vehicle wheels of the respective vehicle axle are arranged on sides of the vehicle that are opposite one another in the transverse direction of the vehicle. By means of the hybrid drive system 10, the vehicle wheels of at least one of the vehicle axles can be driven, the vehicle wheels that can be driven by means of the hybrid drive system 10 being in 1 shown particularly schematically and labeled 12 and 14. The hybrid drive system 10 has an internal combustion engine 16, also referred to as an internal combustion engine, which is designed as a reciprocating piston engine. The internal combustion engine 16 has an engine block 18 designed as a cylinder block, which has or forms a plurality of cylinders 20. A respective combustion chamber is at least partially delimited by the respective cylinder 20, with combustion processes taking place in the respective combustion chamber during fired operation of the internal combustion engine 16. The internal combustion engine 16 has a crankshaft 22, via which the internal combustion engine 16 can provide first drive torques for driving the vehicle wheels 12 and 14 and thus for driving the motor vehicle. The crankshaft 22 is rotatable about a crankshaft rotation axis 24 relative to the engine block 18.

The hybrid drive system 10 also has an electric machine 26, which has a stator 28 and a rotor 30. The rotor 30 can be driven by means of the stator 28 and can therefore be rotated about a machine axis of rotation 32 relative to the stator 28. In the first embodiment, the electric machine 26 and the internal combustion engine 16 are arranged coaxially to one another, so that the crankshaft axis of rotation 24 and the engine axis of rotation 32 coincide. Via its rotor 30, the electric machine 26 can provide second drive torques for driving the vehicle wheels 12 and 14 and thus for driving the motor vehicle. The respective drive torque is also referred to as torque or is a respective torque.

The vehicle axle having the vehicle wheels 12 and 14 is in 1 marked 34. The vehicle axle 34 also has an axle gear 36, which is part of the hybrid drive system 10. A respective input torque can be introduced into the axle gear 36, whereby the axle gear 36 can be driven and in particular rotatable about an axle gear rotation axis, in particular relative to a housing 38 of the hybrid drive system 10. In the present case, the axle gear axis of rotation runs parallel to the crankshaft axis of rotation 24 and parallel to the machine axis of rotation 32 and is spaced from the crankshaft axis of rotation 24 and from the machine axis of rotation 32. In 1 is illustrated by arrows 40 and 42 that the respective input torque that can be introduced or introduced into the axle gear 36 can be divided and transmitted, in particular in half, to the vehicle wheels 12 and 14 by means of the axle gear 36, so that the vehicle wheels 12 and 12 are transmitted via the axle gear 36 14 can be driven by the internal combustion engine 16 and by the electrical machine 26. The respective input torque results from the respective first drive torque and from the respective second drive torque, in particular when the internal combustion engine 16 provides the first drive torque and at the same time the electric machine 26 provides the second drive torque. For example, if the internal combustion engine 16 provides the first drive torque while the electric machine 26 does not provide the second drive torque, the respective input torque results from the respective first drive torque. For example, if the electric machine 26 provides the second drive torque while the ver Internal combustion engine 16 does not provide the first drive torque, for example the respective input torque results from the respective second drive torque.

The hybrid drive system 10 also has a transmission 44 provided in addition to the axle transmission 36, which includes a first partial transmission 46 and a second partial transmission 48. The first partial transmission 46 has a first planetary gear set 50, which has a first sun gear 52, a first planet carrier 54 and a first ring gear 56. The sun gear 52 is also referred to as the first element, the planet carrier 54 is also referred to as the second element and the ring gear 56 is also referred to as the third element. In other words, the in 1 In the first embodiment shown, the sun gear 52 is a first element, the planet carrier 54 is a second element and the ring gear 56 is a third element of the first planetary gear set 50. Generally speaking, the sun gear 52, the planet carrier 54 and the ring gear 56 are transmission elements of the first planetary gear set 50, where the first element is a first of the gear elements, the second element is a second of the gear elements and the third element is a third of the gear elements.

The first partial transmission 46 also has a second planetary gear set 58, which has a second sun gear 60, a second planet carrier 62 and a second ring gear 64. In the first embodiment, the sun gear 60 is a fourth element, the planet carrier 62 is a fifth element, and the ring gear 64 is a sixth element. Generally speaking, the sun gear 60, the planet carrier 62 and the ring gear 64 are planetary gear elements of the planetary gear set 58, a first of the planetary gear elements being the fourth element, a second of the planetary gear elements being the fifth element and a third of the planetary gear elements being the sixth element. It can be seen that the planetary gear sets 50 and 58 are arranged coaxially with one another. In particular, if the respective element is not connected to the housing 38 in a rotationally fixed manner, the respective element is rotatable about a planetary gear set rotation axis 66 relative to the housing 18. In the present case, the planetary gear sets 50 and 58 are arranged coaxially to the internal combustion engine 16 and coaxially to the electrical machine 26.

The first planetary gear set 50 has at least one first planetary gear 68, which meshes with the first sun gear 52 and with the first ring gear 56, in particular simultaneously. The planet gear 68 is rotatably held on the first planet carrier 54. The second planetary gear set 58 has at least one second planetary gear 70, which meshes, in particular simultaneously, with the second sun gear 60 and with the second ring gear 64. The planet gear 70 is rotatably held on the second planet carrier 62. It can be seen that the planetary gear sets 50 and 58 are not stacked, but rather the planetary gear sets 50 and 58 follow one another completely in the axial direction of the respective planetary gear set 50, 58 and thus viewed along the planetary gear set rotation axis 66.

The second partial transmission 48 has an output shaft 72, which is rotatable about an output shaft rotation axis relative to the housing 38. The crankshaft axis of rotation 24, the machine axis of rotation 32 and the planetary gear set axis of rotation 66 are also collectively referred to as axes of rotation because they coincide here. The output shaft rotation axis runs parallel to the rotation axis and is spaced from the rotation axis. The axle gear rotation axis runs parallel to the rotation axis and is spaced from the rotation axis. The axle gear axis of rotation runs parallel to the output shaft axis of rotation and is spaced from the output shaft axis of rotation and vice versa. For example, the transmission 44, in particular the second partial transmission 48, can provide the respective input torque via the output shaft 72.

The second partial transmission 48 has a first spur gear stage 74, which has a first input gear 76 as a first spur gear and a first output gear 78 as a second spur gear. The first spur gear and the second spur gear mesh directly with each other, that is, they are in direct engagement with one another. The output gear 78 is arranged coaxially with the output shaft 72, the output shaft 72 being drivable by the output gear 78. At the in 1 First embodiment shown, the output gear 78 is connected, in particular permanently, in a rotationally fixed manner to the output shaft 72. In the first embodiment, the first input gear 76 can be connected in a rotationally fixed manner to the third element, and therefore to the first ring gear 56. For this purpose, in the first embodiment, a third switching element S3 is provided, by means of which the first input gear 76 can be connected to the third element in a rotationally fixed manner.

The second partial transmission 48 has a second spur gear stage 80, which has a second input gear 82 as a third spur gear and a second output gear 84 as a fourth spur gear. The third spur gear and the fourth spur gear are in direct engagement with one another and therefore mesh directly with one another. The output gear 84 is arranged coaxially with the output shaft 72, the output shaft 72 being drivable by the output gear 84. At the in 1 First embodiment shown, the output gear 84 is connected, in particular permanently, in a rotationally fixed manner to the output shaft 72. The input gear 82 is, in particular permanently, non-rotatably connected to the fifth element, therefore to the second planet carrier 62.

An output gear 86 is also provided, which is, for example, a fifth spur gear. The output gear 86 is arranged coaxially to the output shaft 72, the output gear 86 being drivable by the output shaft 72. At the in 1 In the first embodiment shown, the output gear 86 is permanently connected to the output shaft 72 in a rotationally fixed manner. It can be seen that the output gears 78 and 84 and the output gear 86 are arranged sequentially in the axial direction of the output shaft 72 and thus viewed along the output shaft axis of rotation and are thereby arranged coaxially to one another.

The output gear 86 meshes permanently with an axle gear input gear 88 of the axle gear 36, the axle gear input gear 88 of which can be designed as a further gear, in particular as a sixth spur gear. The axle gear input gear 88 is also referred to as a gear wheel or gear. It can be seen that the gear wheel is connected or can be connected in a rotationally fixed manner to a housing element 90 of the axle drive 36. In the first embodiment, the axle gear input gear 88 is permanently connected to the housing element 90 in a rotationally fixed manner. The housing element 90 is a differential cage, also known as a differential cage, which, like the axle gear input gear 88, is rotatable about the axle gear rotation axis relative to the housing 38.

In the first embodiment, the axle gear 36 includes compensating gears 92, which are rotatably held on the housing element 90 relative to the housing element 90 about a common compensating axis of rotation running perpendicular to the axle gear rotation axis. Furthermore, the axle gear 36 includes output gears 94, which are rotatable about the axle gear rotation axis relative to the housing 38 and, for example, also relative to the housing element 90 and, for example, relative to one another. For example, a first side shaft can be driven by a first of the output gears 94, in particular in that the first of the output gears 94 is connected, in particular permanently, in a rotationally fixed manner to the first side shaft. For example, the vehicle wheel 12 can be driven by the first side shaft. For example, a second side shaft can be driven by a second of the output gears 94, in particular in that the second of the output gears 94 is connected, in particular permanently, in a rotationally fixed manner to the second side shaft. For example, the second side shaft can drive the vehicle wheel 14. It can be seen that the output gears 94 mesh, in particular permanently, with the compensating gears 92. At the in 1 In the exemplary embodiment shown, the axle gear 36 is designed as a bevel gear differential, so that the compensating gears 92 and the output gears 94 meshing therewith are designed as bevel gears. Alternative designs of the axle gear 36 are conceivable, whereby the axle gear 36 can be designed, for example, as a spur gear differential, in particular as a planetary gear differential. For example, the axle gear 36 is a final gear ratio, also known as final drive, and therefore, based on a torque flow running from the output shaft 72 via the axle gear 36 to the vehicle wheels 12 and 14, it is the last gear ratio before the respective vehicle wheel 12, 14.

The hybrid drive system 10 has a first switching element S1, by means of which the crankshaft 22 can be connected in a rotationally fixed manner to the first element, therefore to the first sun gear 52. Furthermore, the rotor 30 is coupled or can be coupled to the third element, therefore to the first ring gear 56, in such a way that the respective second drive torque that can be provided or provided by the electric machine 26 via its rotor 30 is applied to the third element and via the third Element can be introduced into the transmission 44, in particular the first partial transmission 46. In the first embodiment, the rotor 30 is, in particular permanently, non-rotatably connected to the third element, that is, coupled.

In order to be able to realize a particularly compact design as well as a particularly advantageous drivability and a particularly efficient operation of the hybrid drive system 10, the second element, i.e. the first planet carrier 54, is permanently connected in a rotationally fixed manner to the fourth element, i.e. to the second sun gear 60. In addition, a second switching element S2 is provided, by means of which the sixth element, therefore the second ring gear 64, can be connected in a rotationally fixed manner to the housing 38 of the hybrid drive system 10.

In order to be able to keep the installation space requirements, the weight and the costs of the hybrid drive system 10 particularly low, a total of exactly two planetary gear sets are provided, namely the first planetary gear set 50 and the second planetary gear set 58.

A fourth switching element S4 is also provided, by means of which the third element can be connected to the sixth element in a rotationally fixed manner. The hybrid drive system 10 also has a fifth switching element S5, by means of which the first element can be connected to the housing 38 in a rotationally fixed manner. Furthermore, a sixth switching element S6 is provided, by means of which the crankshaft 22 can be connected to the second element in a rotationally fixed manner. Around In order to realize a particularly compact and efficient design, it is also provided that, viewed in the axial direction of the hybrid drive system 10 and thus along the planetary gear set rotation axis 66, the second spur gear stage 80 is on a side SE1 of the first facing away from the first spur gear stage 74 in the axial direction of the hybrid drive system 10 Partial transmission 46, in particular the second planetary gear set 58, is arranged, so that in the first embodiment the planetary gear sets 50 and 58 are arranged in the axial direction of the hybrid drive system 10 between the spur gear stages 74 and 80. The page SE1 is also referred to as the first page. The spur gear stage 74, viewed in the axial direction of the hybrid drive system 10, is arranged on a second side SE2 of the first partial transmission 46, in particular of the first planetary gear set 50, which faces away from the spur gear stage 80 in the axial direction of the hybrid drive system 10, with the sides SE1 and SE2 in the axial direction of the Hybrid drive system 10 lie opposite each other or face away from each other. In addition, the electric machine 26 is arranged to overlap axially with the planetary gear set 50.

2 shows a schematic representation of a second embodiment of the hybrid drive system 10. In the second embodiment, the first input gear 76 is connected, in particular permanently, in a rotationally fixed manner to the third element (first ring gear 56). In the second embodiment, the switching element S3 is designed to connect the first output gear 78 to the output shaft 72 in a rotationally fixed manner. Thus, in the second embodiment, the output gear 78 is designed as an idler gear, which is arranged on the output shaft 72 so that it can rotate, in particular about the output shaft axis of rotation. By means of the switching element S3, the first output gear 78 can be connected to the output shaft 72 in a rotationally fixed manner.

Furthermore, in the second embodiment it is provided that the machine axis of rotation 32 is spaced from the planetary gear set rotation axis 66 and from the crankshaft rotation axis 24 and runs parallel to the crankshaft rotation axis 24 and parallel to the planetary gear set rotation axis 66, the crankshaft rotation axis 24 and the planetary gear set rotation axis 66 coinciding. In 2 is illustrated by a dashed line 96 that the rotor 30 is coupled or can be coupled to the third element in a torque-transmitting manner, specifically in the second embodiment via the first input gear 76. In the second embodiment, the rotor 30 is permanently coupled to the third element in a torque-transmitting manner , in the present case via the first input gear 76, so that in the second embodiment the rotor 30 is permanently coupled to the input gear 76 in a torque-transmitting manner and to the third element via the input gear 76. In the second embodiment, too, the electric machine 26 is arranged axially overlapping the first planetary gear set 50. In an embodiment not shown in the figures and also referred to as the first variant, it is provided, for example, that the first variant corresponds to the second embodiment, only with the difference that the electric machine 26 is coaxial to the planetary gear sets 50 and 58 and coaxial to the Internal combustion engine 16 is arranged and that the rotor 30 is permanently connected to the third element in a rotationally fixed manner. In an embodiment not shown in the figures and also referred to as a second variant, it is conceivable that the second variant corresponds to the second embodiment, with the only difference being that the rotor 30 is permanently coupled to the third element in a torque-transmitting manner, bypassing the input gear 76 . For this purpose, for example, a coupling wheel designed in particular as a further gear, in particular as a further spur gear, is provided, which is provided in addition to the input gear 76 and also in addition to the output gear 78, in addition to the output gear 84 and in addition to the input gear 82. The coupling wheel is, for example, permanently connected to the third element in a rotationally fixed manner, with the rotor 30 being permanently connected to the coupling wheel in a torque-transmitting manner. Out of 2 It can be seen that in the second embodiment a gear 98 is provided, which is connected, in particular permanently, in a rotationally fixed manner to the rotor 30. In the second embodiment, for example, the gear 98 meshes, in particular directly, with the input gear 76, or, for example, an intermediate gear is provided, which meshes directly with the input gear 76 and directly with the gear 98, with direct meshing of the gear 98 with the input gear 76 omitted. In the second variant, it is conceivable that the gear 98 meshes, in particular directly, with the coupling wheel, or an intermediate gear is provided which meshes directly with the coupling wheel and directly with the gear 98, for example direct meshing of the gear 98 the coupling wheel is omitted.

Finally shows 3 a third embodiment of the hybrid drive system 10. In the third embodiment, both spur gear stages 74 and 80 connect in the axial direction of the hybrid drive system 10 to the first partial transmission 46, thus to the planetary gear sets 50 and 58, such that in the axial direction of the hybrid drive system 10, the first Spur gear stage 74 is arranged between the partial gear 46 and the second spur gear stage 80. Thus, for example, the spur gear stage 74 is viewed in the axial direction of the hybrid drive system 10 on one in the axial direction of the hybrid The drive system 10 is arranged on the side SE3 of the second spur gear stage 80 facing the partial transmission 46. In the third embodiment, the electric machine 26 is arranged axially overlapping both planetary gear sets 50 and 58. Furthermore, in the third embodiment it is provided that the switching elements S2 and S4 are arranged in the axial direction of the hybrid drive system 10 between the spur gear stages 74 and 80, so that, for example, the switching elements S2 and S4 are arranged on the side SE3 of the spur gear stage 80. The switching element S3 is also arranged, for example, in the axial direction of the hybrid drive system 10 between the spur gear stages 74 and 80. In an embodiment not shown in the figures and designated, for example, as a third variant, it is possible that the third variant according to the third embodiment 3 corresponds, with the only difference that the switching elements S2 and S4, viewed in the axial direction of the hybrid drive system 10, are arranged on a side SE4 of the spur gear stage 74 facing away from the spur gear stage 80 in the axial direction of the hybrid drive system 10 and facing the partial transmission 46, in particular in such a way that the switching elements S2 and S4 are arranged in the axial direction of the hybrid drive system 10 between the partial transmission 46 and the spur gear stage 74, in particular between the second planetary gear set 58 and the spur gear stage 74.

In the third embodiment, it is also provided that the output gear 86 is arranged axially, that is, viewed in the axial direction of the hybrid drive system 10, between the internal combustion engine 16 and the first partial transmission 46, in particular between the internal combustion engine 16 and the first planetary gear set 50.

Reference symbol list

10

Hybrid drive system

12

vehicle wheel

14

vehicle wheel

16

Internal combustion engine

18

Engine block

20

cylinder

22

crankshaft

24

Crankshaft rotation axis

26

electric machine

28

stator

30

rotor

32

Machine rotation axis

34

Vehicle axle

36

Axle gear

38

Housing

40

Arrow

42

Arrow

44

transmission

46

first partial transmission

48

second partial transmission

50

first planetary gear set

52

first sun wheel

54

first planetary carrier

56

first ring gear

58

second planetary gear set

60

second sun wheel

62

second planet carrier

64

second ring gear

66

Planetary gear set rotation axis

68

first planetary gear

70

second planetary gear

72

output shaft

74

first spur gear stage

76

first input gear

78

first output gear

80

second spur gear stage

82

second input gear

84

second output gear

86

output gear

88

Axle gear input gear

90

Housing element

92

Balance gear

94

output gear

96

dashed line

98

gear

S1

first switching element

S2

second switching element

S3

third switching element

S4

fourth switching element

S5

fifth switching element

S6

sixth switching element

SE1

Page

SE2

Page

SE3

Page

SE4

Page

QUOTES INCLUDED IN THE DESCRIPTION

This list of documents listed by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102017006082 A1 [0002]

Claims (10)

Hybrid drive system (10) for a motor vehicle, with an internal combustion engine (16), which has a crankshaft (22), with an electric machine (26), which has a rotor (30), with an axle gear (36) and with a transmission ( 44) with a first sub-gear (46) and a second sub-gear (48), wherein: - the first sub-gear (46) has: o a first planetary gear set (50) with a first element (52), a second element (54) and a third element (56); and o a second planetary gear set (58) having a fourth element (60), a fifth element (62) and a sixth element (64); - the second partial transmission (48) has: o an output shaft (72); o a first spur gear stage (74), which has a first output gear (78), which is arranged coaxially to the output shaft (72) and with a first input gear (76) of the first spur gear stage which is connected or can be connected in a rotationally fixed manner to the third element (56). (74) combs; and o a second spur gear stage (80), which has a second output gear (84), which is arranged coaxially to the output shaft (72) and with a second input gear (82) of the second spur gear stage ( 80) combs; - an output gear (86) is permanently connected to the output shaft (72) in a rotationally fixed manner and permanently meshes with an axle drive input gear (88); - a first switching element (S1) is provided, which is designed to connect the crankshaft (22) to the first element (52) in a rotationally fixed manner; - The rotor (30) is coupled or can be coupled to the third element (56) in such a way that torques on the third element (56) that can be provided by the electric machine (26) via the rotor (30) can be introduced into the transmission (44). ; characterized in that : - the second element (54) is permanently connected to the fourth element (60) in a rotationally fixed manner; and - a second switching element (S2) is provided, which is designed to connect the sixth element (64) in a rotationally fixed manner to a housing (38) of the hybrid drive system (10). Hybrid drive system (10). Claim 1 , characterized in that a total of exactly two planetary gear sets (50, 58) are provided, namely the first planetary gear set (50) and the second planetary gear set (58). Hybrid drive system (10). Claim 1 or 2 , characterized by a third switching element (S3), which is designed to: - connect the first input gear (76) to the third element (56) in a rotationally fixed manner; or - to connect the first output gear (78) to the output shaft (72) in a rotationally fixed manner. Hybrid drive system (10) according to one of the preceding claims, characterized by a fourth switching element (S4), which is designed to connect the third element (56) to the sixth element (64) in a rotationally fixed manner. Hybrid drive system (10) according to one of the preceding claims, characterized by a fifth switching element (S5), which is designed to connect the first element (52) to the housing (38) in a rotationally fixed manner. Hybrid drive system (10) according to one of the preceding claims, characterized by a sixth switching element (S6), which is designed to connect the crankshaft (22) to the second element (54) in a rotationally fixed manner. Hybrid drive system (10) according to one of the preceding claims, characterized in that , viewed in an axial direction of the hybrid drive system (10), the second spur gear stage (80) is on a side (SE1) of the first partial transmission (46) facing away from the first spur gear stage (74). is arranged. Hybrid drive system (10) according to one of the preceding claims, characterized in that the crankshaft (22) is arranged coaxially to the first partial transmission (46), the output gear (86) being arranged axially between the internal combustion engine (16) and the first partial transmission (46). is. Hybrid drive system (10) according to one of the preceding claims, characterized in that the electric machine (26) is arranged axially overlapping at least one of the planetary gear sets (50, 58). Motor vehicle, with a hybrid drive system (10) according to one of the preceding claims.

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