Hybrid drive system for a motor vehicle, in particular for a motor vehicle, and motor vehicle

Abstract

Hybrid drive system (10) for a motor vehicle, comprising an internal combustion engine (16) having a crankshaft (22), an electric machine (26) having a rotor (30), an axle transmission (36) and a transmission (44) having a first partial transmission (46) and a second partial transmission (48), wherein: - the first partial transmission (46) comprises: ◯ a first planetary gear set (50) having a first sun gear (52), a first planet carrier (54) and a first ring gear (56); and ◯ a second planetary gear set (58) with a second sun gear (60), a second planet carrier (62) and a second ring gear (64); - the second partial transmission (48) comprises: ◯ an output shaft (72); ◯ a first spur gear stage (74) having a first output gear (78) arranged coaxially with the output shaft (72) and meshing with a first input gear (76) of the first spur gear stage (74) that is connected or connectable in a rotationally fixed manner to the first ring gear (56); and ◯ a second spur gear stage (80) having a second output gear (84) arranged coaxially to the output shaft (72) and meshing with a second input gear (82) of the second spur gear stage (80) which is connected in a rotationally fixed manner to the second planet carrier (62); - an output gear (86) is permanently connected to the output shaft (72) in a rotationally fixed manner and permanently meshes with an axle transmission input gear (88); - a first switching element (S1) is provided which is designed to connect the crankshaft (22) in a rotationally fixed manner to the first sun gear (52); - the rotor (30) is coupled or can be coupled to the first ring gear (56) in such a way that torques that can be provided by the electric machine (26) via the rotor (30) can be introduced into the transmission (44) at the first ring gear (56); characterized in that: - the first planet carrier (54) is permanently connected to the second sun gear (60) in a rotationally fixed manner; and - a second switching element (S2) is provided, which is designed to connect the second ring gear (64) in a rotationally fixed manner to a housing (38) of the hybrid drive system (10).

Description

[0001] 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.

[0002] US 2010 / 0 035 718 A1, DE 10 2016 213 713 A1, DE 10 2015 223 026 A1 and DE 10 2018 000 183 A1 show transmissions with a first partial transmission having a planetary gear and with a second partial transmission having at least one spur gear stage.

[0003] The generic DE 10 2017 006 082 A1 discloses a hybrid drive device, with an internal combustion engine, with an electric machine having a rotor, with a first partial transmission having a planetary gear and with a second partial transmission having a spur gear stage.

[0004] The object of the present invention is to provide 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 a particularly advantageous drivability can be realized.

[0005] This object is achieved by a hybrid drive system having the features of patent claim 1 and by a motor vehicle having the features of patent claim 10. Advantageous embodiments with expedient further developments of the invention are specified in the remaining claims.

[0006] A first aspect of the invention relates to a hybrid drive system, also referred to as a hybrid drive device or embodied as a hybrid drive device, for a motor vehicle, also simply referred to as a vehicle. This means that the motor vehicle, preferably embodied 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 arranged consecutively and thus one behind the other in the longitudinal direction of the motor vehicle, also 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 by means of which the motor vehicle can be or is supported downwards on the ground in the vertical direction of the motor vehicle. The respective vehicle wheels of the respective vehicle axle are arranged, for example, on opposite sides of the motor vehicle in the transverse direction of the motor vehicle. If the motor vehicle is driven along the ground while being supported downwards on the ground in the vertical direction of the vehicle 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 by means of the hybrid drive system the vehicle wheels of both vehicle axles can be driven. The vehicle wheels that can be driven by means of the hybrid drive system are also referred to as drive wheels, drivable wheels or driven wheels.When reference is made below to vehicle wheels, this refers to the drive wheels unless otherwise stated.

[0007] The hybrid drive system comprises an internal combustion engine, 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. Thus, the internal combustion engine is designed, for example, as a reciprocating piston engine. The hybrid drive system also comprises an electric machine having a rotor. The electric machine can provide second drive torques for driving the motor vehicle, in particular for driving the vehicle wheels, via the rotor. For example, the motor vehicle can be driven by means of the electric machine, in particular purely electrically.Since the motor vehicle can be driven by both the internal combustion engine and the electric machine, the motor vehicle is preferably designed as a hybrid vehicle. Very preferably, the electric machine is a high-voltage component whose electrical voltage, in particular the electrical operating or nominal voltage, is, for example, greater than 50 volts, in particular greater than 60 volts, and very preferably amounts to several hundred volts. For example, the electric machine has a stator, by means of which the rotor can be driven and is thus rotatable about a machine axis of rotation relative to the stator. The crankshaft is, for example, rotatable about a crankshaft axis of rotation relative to a housing element of the internal combustion engine, designed, for example, as an engine block, in particular as a cylinder block.For example, the crankshaft and the rotor are arranged coaxially to each other so that the machine rotation axis coincides with the crankshaft rotation axis.

[0008] The hybrid drive system also has an axle drive. In particular, the axle drive is assigned to the vehicle axle, whose vehicle wheels can be driven by the internal combustion engine and by the electric motor. In particular, the vehicle wheels can be driven via the axle drive by the internal combustion engine, in particular by the crankshaft, and by the electric motor, in particular by the rotor. Very particularly, the axle drive is a differential gear, also simply referred to 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 drive, whereby the axle drive can be driven.For example, the respective input torque is the respective first drive torque and / or the respective second drive torque. In particular, the respective input torque introduced or introduceable into the axle drive can be divided and transmitted to the vehicle wheels, in particular equally, via the axle drive or by means of the axle drive, so that the vehicle wheels can be driven by the respective input torque and thus by the internal combustion engine and / or the electric motor via the axle drive.In particular, the axle drive has the function already sufficiently known from the general state of the art that the axle drive allows different speeds of the vehicle wheels when the motor vehicle is cornering, in particular such that the vehicle wheel on the outside of the curve rotates or can rotate at a higher speed than the vehicle wheel on the inside of the curve, in particular while the vehicle wheels can be driven by the internal combustion engine and the electric machine via the axle drive or are driven by the electric machine and / or the internal combustion engine.

[0009] The hybrid drive system also has a transmission, in particular provided in addition to the axle transmission, via which the axle transmission can be driven, for example, by the electric machine and by the internal combustion engine, i.e., 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, wherein, for example, the transmission can provide the respective input torque resulting from the respective transmission torque.Thus, for example, with respect to a torque flow via which a respective torque that can be provided or is provided by the rotor and the crankshaft can be transmitted to the axle drive in order to drive the axle drive and, via the axle drive, the vehicle wheels, the axle drive is arranged in the torque flow, wherein the transmission is also arranged in the torque flow, and wherein, for example, the transmission is arranged upstream of the axle drive and downstream of the rotor, wherein the transmission is arranged upstream of the axle drive and downstream of the crankshaft.

[0010] The transmission has a first sub-transmission and a second sub-transmission. The first sub-transmission has a first planetary gear set, which is also referred to as the first planetary gear set. The first planetary gear set has a first sun gear, a first planet carrier, also referred to as the first web, and a first ring gear. Furthermore, the first planetary gear set has at least one first planet gear, which meshes, in particular simultaneously, with the first ring gear and with the first sun gear, wherein meshing of the first sun gear with the first ring gear is avoided. 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 transmission elements of the first planetary gear set or are transmission 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 transmission elements, for example, the second element is a second of the transmission elements, and for example, the third element is a third of the transmission elements.

[0011] The first sub-transmission also has a second planetary gear set, which is also referred to as a second planetary gear set. The second planetary gear set, which is preferably provided in addition to the first planetary gear set, has a second sun gear provided in addition to the first sun gear, a second planet carrier provided in addition to the first planet carrier, and a second ring gear provided in addition to the first ring gear, wherein the second planet carrier is also referred to as a second carrier. 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, wherein meshing of the second sun gear with the second ring gear does not occur.The second sun gear, the second planet carrier, and the second ring gear 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 the sixth element is a third of the planetary gear elements of the second planetary gear set.

[0012] 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 arranged at least partially in the housing. In particular when the respective transmission element is not connected to the housing in a rotationally fixed manner, the respective transmission element can be rotated about a transmission element rotation axis relative to the housing, in particular by driving the respective transmission element. The transmission element rotation axis is also referred to as the first planetary gear set rotation axis. In particular when 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 for the planetary gear sets to be arranged coaxially with one another, such that the planetary gear set axes of rotation coincide, and thus the transmission element axis of rotation coincides with the planetary gear element axis of rotation. In particular, it is conceivable for the internal combustion engine and / or the electric machine to be arranged coaxially with the first planetary gear set and / or coaxially with the second planetary gear set. In particular, the respective planetary gear set axis of rotation runs in the axial direction of the transmission and of the hybrid drive system as a whole, wherein, for example, the axial direction of the transmission, in particular of the hybrid drive system as a whole, coincides with the respective planetary gear set axis of rotation or runs parallel to the respective planetary gear set axis of rotation. Furthermore, it is conceivable for the axial direction of the transmission to run in the axial direction of the axle transmission, in particular coincides with the axial direction of the axle transmission.

[0013] 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.

[0014] The second sub-transmission has a first spur gear stage, which is provided in particular in addition to the planetary gear sets and has a first output gear as the first spur gear. The first output gear is arranged coaxially with the output shaft. Furthermore, the first output gear meshes with a first input gear of the first spur gear stage, which is connected or connectable in a rotationally fixed manner to the first ring gear, wherein the first input gear is 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, with respect to the aforementioned torque flow along which the respective input torque can be transmitted from the transmission to the axle drive, 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.

[0015] The second sub-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 the third spur gear, which is arranged coaxially to the output shaft and meshes with a second input gear of the second spur gear stage, which is connected, in particular permanently and non-rotatably, to the second planet carrier. 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. With respect to 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 sub-transmissions are arranged in the torque flow, in particular such that the second sub-transmission is arranged downstream of the first sub-transmission, so that the axle transmission can be driven by the first sub-transmission via the second sub-transmission. In particular, with respect to the torque flow, the output shaft is arranged in the torque flow, in particular such that the output shaft is arranged upstream of the axle transmission and downstream of the spur gear stages.

[0016] The hybrid drive system further comprises 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 by the first input gear via the first output gear and by the second input gear via the second output gear. Thus, for example, the respective output gear is or can be connected in a rotationally fixed manner to the output shaft. In particular, it is conceivable that the respective output gear can be permanently connected in a rotationally fixed manner to the output shaft.

[0017] The output gear is permanently connected to the output shaft in a rotationally fixed manner. Furthermore, the output gear permanently meshes with an axle drive input gear, which is designed as a gear. The feature that the output gear permanently meshes with the axle drive input gear means that the hybrid drive system cannot be switched between a meshing state, in which the output gear meshes with the axle drive input gear, and a non-mesh state, in which the output gear does not mesh with the axle drive input gear. Instead, the output gear and the axle drive input gear always mesh with each other, meaning that they always and therefore permanently mesh with each other.Thus, for example, the respective input torque can be provided by the output gear and transmitted, in particular directly, to the axle drive input gear and thus introduced into the axle drive, whereby the axle drive can be driven, for example, and thus rotated relative to the housing, in particular about an axle drive rotation axis. By driving the axle drive, the vehicle wheels can be driven.

[0018] The hybrid drive system further comprises a first shifting element configured to connect the crankshaft to the first sun gear in a rotationally fixed manner. This means that the crankshaft can be connected to the first sun gear in a rotationally fixed manner by means of the first shifting element. The first shifting element can, for example, be switched between a first coupled state and a first uncoupled state. In the first coupled state, the crankshaft is connected to the first sun gear in a rotationally fixed manner by means of the first shifting element.In the first decoupling state, the first shifting element releases the crankshaft for rotation about the crankshaft axis of rotation or about the transmission element axis of rotation and relative to the first sun gear, so that in the first decoupling state, the crankshaft and the first sun gear are rotatable relative to one another about the crankshaft axis of rotation or about the transmission element axis of rotation, and so that, in particular in the first decoupling state, no torque can be transmitted between the crankshaft and the first sun gear via the first shifting element. For example, the first shifting element can be moved, in particular relative to the housing and / or translationally, 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 position.

[0019] The rotor of the electric machine is or can be coupled to the first ring gear, in particular in a torque-transmitting and very particularly rotationally fixed manner, such that the respective first drive torque provided or capable of being provided by the electric machine via the rotor can be introduced at the first ring gear, i.e., into the transmission via the first ring gear. In other words, the rotor of the electric machine is or can be coupled to the first ring gear such that torques originating from the electric machine or the rotor can be introduced at the first ring gear and, in particular, into the transmission via the first ring gear.

[0020] In order to achieve particularly efficient operation of the hybrid drive system and particularly advantageous drivability, the invention provides that the first planet carrier is permanently connected to the second sun gear in a rotationally fixed manner. Furthermore, the invention provides that the hybrid drive system comprises a second switching element designed to connect the second ring gear to the housing of the hybrid drive system in a rotationally fixed manner. This means that the second ring gear 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 second ring gear is connected to the housing in a rotationally fixed manner by means of the second switching element, and is thus fixed to the housing in a rotationally fixed manner, such that the second ring gear cannot rotate about the planetary gear element axis of rotation relative to the housing. In the second decoupling state, the second switching element releases the second ring gear for rotation about the planetary gear element axis of rotation and relative to the housing, such that in the second decoupling state the second ring gear can be rotated about the planetary gear element axis of rotation relative to the housing, and such that in the second decoupling state no torque can be transmitted between the second ring gear and the housing via the second switching element.For example, the second switching element can be moved, in particular translationally and / or relative to the housing, between at least one second coupling position causing the second coupling state and at least one second decoupling position causing the second decoupling state.

[0021] 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 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, such as the transmission element rotation axis, at the same angular velocity, in particular relative to the housing. In other words, “rotationally fixed” is to be understood as follows: 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 velocity, in particular about 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 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, if the components are connected to one another in a rotationally fixed manner, the components are also connected to one another in a torque-transmitting manner.The feature that two components are permanently connected to one another in a torque-transmitting manner means that a switching element is not provided that can be switched between a coupled state connecting the components to one another in a torque-transmitting manner and a decoupling state in which no torque can be transmitted between the components via the switching element. Rather, the components are always and therefore permanently connected to one another in a torque-transmitting manner, i.e., they are connected 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 two components such as the output shaft and the output gear are permanently connected 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 connecting the components to one another in a rotationally fixed manner and a decoupling state in which the components are decoupled from one another and can be rotated relative to one another so that no torque can be transmitted between the components via the switching element, but rather the components are always, and therefore permanently, connected or coupled to one another in a rotationally fixed manner.

[0022] The feature that two components can be connected or coupled to one another in a rotationally fixed or torque-transmitting manner is to be understood in particular as meaning that the components are assigned a switching element that 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 torque can be transmitted between the components via the switching element.

[0023] In the context of the present disclosure, ordinal numerals, also referred to as ordinalia, such as "first", "first", "second", "second", etc., are not necessarily used to indicate or imply a number or quantity of elements to which the ordinal numerals refer, but rather to be able to unambiguously refer to concepts or elements to which the ordinal numerals are assigned or to which the ordinal numerals refer.

[0024] Furthermore, the terms “axial” and “coaxial” refer in particular to the respective planetary gear set rotational axis, wherein the planetary gear set rotational axes coincide. Furthermore, “axially overlapping” is to be understood as follows: Two elements are arranged axially overlapping, in particular with respect to one another, when the elements are arranged in regions 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 rotational axis. For example, in the case of two elements arranged axially overlapping with one another, there exists at least one radially arranged straight line running in the radial direction of the hybrid drive system and thus perpendicular to the axial direction of the hybrid drive system, which straight line penetrates or intersects both the one and the other of the axially overlapping elements.

[0025] The axle transmission input gear is preferably a gear which is, for example, in particular permanently, connected in a rotationally fixed manner to a differential cage of the axle transmission, also referred to as a differential carrier.

[0026] In order to realize a particularly compact design and a particularly efficient operation and thus to be able to keep the power loss advantageously 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.

[0027] A further embodiment is characterized by a third shifting element which is designed to connect the first input gearwheel in a rotationally fixed manner to the first ring gear. In other words, for example, the first input gearwheel can be connected in a rotationally fixed manner to the first ring gear by means of the third shifting element. Alternatively, the third shifting element is designed to connect the first output gearwheel in a rotationally fixed manner to the output shaft. In other words, it is conceivable that the first output gearwheel can be connected in a rotationally fixed manner to the output shaft by means of the third shifting element. Expressed again in other words, the hybrid drive system preferably has the third shifting 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 gearwheel, wherein the second connecting part is then the first ring gear.Alternatively, the first connecting part is the first output gear, in which case the second connecting part is 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 transmission element axis of rotation 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 axis of rotation relative to the housing.If the connecting parts are the first output gear and the output shaft, the third shifting element, in the third decoupling state, 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 rotatable about the transmission element axis of rotation or about the output shaft axis of rotation relative to one another. Preferably, the output shaft axis of rotation runs parallel to the respective planetary gear set axis of rotation, wherein the output shaft axis of rotation is spaced from the respective planetary gear set axis of rotation. For example, the third shifting element can be moved, in particular translationally and / or relative to the housing, between a third coupling position bringing about the third coupling state and at least one third decoupling position bringing about the third decoupling state.By using the third switching element, advantageous switchability and thus drivability can be achieved.

[0028] In order to achieve particularly efficient operation and particularly advantageous drivability, a further embodiment of the invention provides that the hybrid drive system has a fourth shifting element designed to connect the first ring gear to the second ring gear in a rotationally fixed manner. In other words, the first ring gear can be connected to the second ring gear in a rotationally fixed manner by means of the fourth shifting element. For example, the fourth shifting element can be switched between a fourth coupling state and a fourth decoupling state. In the fourth coupling state, the first ring gear is connected to the second ring gear in a rotationally fixed manner by means of the fourth shifting element.In the fourth decoupling state, the fourth shifting element releases the first ring gear for rotation about the respective planetary gearset rotational axis and relative to the second ring gear, so that in the fourth decoupling state, the first ring gear and the second ring gear are rotatable relative to one another about the respective planetary gearset rotational axis. For example, the fourth shifting element can be moved, in particular translationally and / or relative to the housing, between at least one fourth coupling position effecting the fourth coupling state and at least one fourth decoupling position effecting the fourth decoupling state.

[0029] In a particularly advantageous embodiment of the invention, the hybrid drive system comprises a fifth switching element which is designed to connect the first sun gear to the housing in a rotationally fixed manner. In other words, the first sun gear 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 sun gear 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 sun gear for rotation about the first planetary gear set axis of rotation relative to the housing, such that in the fifth decoupling state the first sun gear can be rotated about the first planetary gear set axis of rotation relative to the housing.For example, the fifth shifting element can be moved, in particular translationally and / or relative to the housing, between at least one fifth coupling position, which effects the fifth coupling state, and at least one fifth decoupling position, which effects the fifth decoupling state. This allows, for example, gears of the hybrid drive system to be shifted as needed, so that particularly advantageous shiftability and thus particularly advantageous drivability can be realized.

[0030] In order to achieve particularly efficient operation and advantageous drivability in a particularly space- and weight-efficient manner, a further embodiment of the invention provides a sixth switching element designed to connect the crankshaft to the first planet carrier in a rotationally fixed manner. In other words, the crankshaft can be connected to the first planet carrier in a rotationally fixed manner by means of the sixth switching element. For example, the sixth switching element can be switched between a sixth coupled state and a sixth uncoupled state. In the sixth coupled state, the crankshaft is connected to the first planet carrier in a rotationally fixed manner by means of the sixth switching element.In the sixth decoupling state, the sixth shifting element releases the crankshaft for rotation about the crankshaft rotational axis and relative to the first planetary carrier, so that in the sixth decoupling state, the crankshaft and the first planetary carrier can be rotated relative to one another about the crankshaft rotational axis or about the first planetary gear set rotational axis. For example, the sixth shifting element is movable, in particular relative to the housing and / or translationally, between at least one sixth coupling position effecting the sixth coupling state and at least one sixth decoupling position effecting the sixth decoupling state.

[0031] In a further, particularly advantageous embodiment of the invention, the second spur gear stage is arranged on a side of the first sub-transmission facing away from the first spur gear stage, viewed in an axial direction of the hybrid drive system, i.e., viewed in the axial direction of the hybrid drive system and thus along the respective planetary gear set rotation axis. This allows for a particularly space-efficient and low-loss design of the hybrid drive system.

[0032] In order to be able to realize a particularly compact design, particularly 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, wherein the output gear is arranged axially, that is to say in the axial direction of the hybrid drive system, between the internal combustion engine and the first partial transmission, in particular the first planetary gear set.

[0033] In order to keep the installation space requirement of the hybrid drive system particularly low, particularly 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 is arranged axially overlapping with at least one of the planetary gear sets, in particular at least with the first planetary gear set.

[0034] A second aspect of the invention relates to a motor vehicle, preferably designed as a motor vehicle, in particular as a passenger car, and 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 the hybrid drive system. Advantages and advantageous embodiments of the first aspect of the invention are to be regarded as advantages and advantageous embodiments of the second aspect of the invention, and vice versa.

[0035] The invention enables the hybrid drive system, in particular the transmission and especially the first sub-transmission, to 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 power loss can be kept particularly low. For example, up to six hybrid and / or combustion engine forward gears, one combustion engine reverse gear, and at least three electric gears and various continuously variable transmission ranges can be realized. A wide range of transmission ratios can be achieved. The planetary gear sets are preferably designed as simple planetary gear sets, thus as single planetary gear sets.At least one of the shifting elements, in particular at least two of the shifting elements, can be designed as positive-locking shifting 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 implemented, which is particularly advantageous for a front-transverse drive. The electric machine can be arranged coaxially or laterally, thus in a so-called side-by-side arrangement. In particular when the electric machine is arranged coaxially, it is possible to place at least one or more of the shifting elements in the electric machine. Additional claw shifting elements are conceivable, in particular via the use of the electric machine.

[0036] Further advantages, features, and details of the invention will become apparent from the following description of preferred embodiments. The features and feature combinations mentioned above in the description, as well as the features and feature combinations 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.

[0037] The drawing shows: Fig. 1 is a schematic representation of a first embodiment of a hybrid drive system for a motor vehicle; Fig. 2 is a schematic representation of a second embodiment of the hybrid drive system; and Fig. 3 a schematic representation of a third embodiment of the hybrid drive system.

[0038] In the figures, identical or functionally identical elements are provided with the same reference numerals.

[0039] Fig. 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 vehicle's longitudinal direction and thus sequentially, wherein the respective vehicle axle has at least or exactly two vehicle wheels. The respective vehicle wheels of the respective vehicle axle are arranged on opposite sides of the vehicle in the vehicle's transverse direction. By means of the hybrid drive system 10, the vehicle wheels of at least one of the vehicle axles can be driven, wherein the vehicle wheels drivable by means of the hybrid drive system 10 in Fig. 1 and are designated 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, wherein during fired operation of the internal combustion engine 16, combustion processes take place in the respective combustion chamber. 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.

[0040] The hybrid drive system 10 also includes an electric machine 26, which has a stator 28 and a rotor 30. The rotor 30 is drivable by means of the stator 28 and is thus rotatable about a machine rotation axis 32 relative to the stator 28. In the first embodiment, the electric machine 26 and the internal combustion engine 16 are arranged coaxially with one another, so that the crankshaft rotation axis 24 and the machine rotation axis 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.

[0041] The vehicle axle having the vehicle wheels 12 and 14 is in Fig. 1 with 34. The vehicle axle 34 also has an axle drive 36, which is a component of the hybrid drive system 10. A respective input torque can be introduced into the axle drive 36, whereby the axle drive 36 is drivable and, in particular, rotatable about an axle drive axis of rotation, in particular relative to a housing 38 of the hybrid drive system 10. In the present case, the axle drive axis of rotation runs parallel to the crankshaft axis of rotation 24 and parallel to the engine axis of rotation 32 and is spaced apart from the crankshaft axis of rotation 24 and the engine axis of rotation 32. In Fig. 1, arrows 40 and 42 illustrate that the respective input torque that can be introduced or is introduced into the axle drive 36 can be divided and transmitted, in particular half, to the vehicle wheels 12 and 14 by means of the axle drive 36, so that the vehicle wheels 12 and 14 can be driven by the internal combustion engine 16 and the electric machine 26 via the axle drive 36. 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 the electric machine 26 provides the second drive torque at the same time.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 internal combustion engine 16 does not provide the first drive torque, the respective input torque results from the respective second drive torque.

[0042] The hybrid drive system 10 also has a transmission 44 provided in addition to the axle transmission 36, which comprises 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, in the Fig. 1, 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, the first element being a first of the transmission elements, the second element being a second of the transmission elements, and the third element being a third of the transmission elements.

[0043] The first sub-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, with 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, when the respective element is not rotationally fixedly connected to the housing 38, 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 electric machine 26.

[0044] The first planetary gear set 50 has at least one first planet 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 mounted on the first planet carrier 54. The second planetary gear set 58 has at least one second planet 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 mounted on the second planet carrier 62. It can be seen that the planetary gear sets 50 and 58 are not stacked; 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 along the planetary gear set rotation axis 66.

[0045] The second sub-transmission 48 has an output shaft 72, which is rotatable about an output shaft rotation axis relative to the housing 38. The crankshaft rotation axis 24, the engine rotation axis 32, and the planetary gear set rotation axis 66 are collectively referred to as rotation axes, since they coincide in this case. The output shaft rotation axis runs parallel to the rotation axis and is spaced from the rotation axis. The axle transmission rotation axis runs parallel to the rotation axis and is spaced from the rotation axis. The axle transmission rotation axis runs parallel to the output shaft rotation axis and is spaced from the output shaft rotation axis, and vice versa. For example, the transmission 44, in particular the second sub-transmission 48, can provide the respective input torque via the output shaft 72.

[0046] The second partial transmission 48 has a first spur gear stage 74, which has a first input gear 76 as the first spur gear and a first output gear 78 as the second spur gear. The first spur gear and the second spur gear mesh directly with each other, i.e., they are directly engaged with each other. The output gear 78 is arranged coaxially with the output shaft 72, wherein the output shaft 72 is drivable by the output gear 78. In the Fig. In the first embodiment shown in Figure 1, 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 is rotationally fixedly connected to the third element, thus to the first ring gear 56. For this purpose, a third switching element S3 is provided in the first embodiment, by means of which the first input gear 76 is rotationally fixedly connected to the third element.

[0047] The second sub-gearbox 48 has a second spur gear stage 80, which has a second input gear 82 as the third spur gear and a second output gear 84 as the fourth spur gear. The third spur gear and the fourth spur gear are directly engaged with each other, thus meshing directly with each other. The output gear 84 is arranged coaxially with the output shaft 72, wherein the output shaft 72 is drivable by the output gear 84. In the Fig. In the first embodiment shown in Figure 1, the output gear 84 is connected, in particular permanently, in a rotationally fixed manner to the output shaft 72. The input gear 82 is connected, in particular permanently, in a rotationally fixed manner to the fifth element, thus to the second planet carrier 62.

[0048] Also provided is an output gear 86, which is, for example, a fifth spur gear. The output gear 86 is arranged coaxially to the output shaft 72, wherein the output gear 86 is drivable by the output shaft 72. In the Fig. In the first embodiment shown in Figure 1, 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 consecutively in the axial direction of the output shaft 72 and thus along the output shaft rotation axis and are arranged coaxially to one another.

[0049] The output gear 86 permanently meshes with an axle drive input gear 88 of the axle drive 36, whose axle drive input gear 88 can be designed as a further gear, in particular as a sixth spur gear. The axle drive input gear 88 is also referred to as a gear wheel or toothed wheel. It can be seen that the gear wheel is 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 drive input gear 88 is permanently connected in a rotationally fixed manner to the housing element 90. The housing element 90 is a differential cage, also referred to as a differential carrier, which, like the axle drive input gear 88, is rotatable about the axle drive rotation axis relative to the housing 38.

[0050] In the first embodiment, the axle drive 36 comprises compensating gears 92, which are mounted on the housing element 90 so as to be rotatable relative to the housing element 90 about a common compensating rotational axis running perpendicular to the axle drive rotational axis. Furthermore, the axle drive 36 comprises output gears 94, which are rotatable relative to the housing 38 about the axle drive rotational axis and, for example, also relative to the housing element 90, and, for example, relative to one another. For example, a first sideshaft can be driven by a first of the output gears 94, in particular by the first of the output gears 94 being connected, in particular permanently, in a rotationally fixed manner to the first sideshaft. For example, the vehicle wheel 12 can be driven by the first sideshaft.For example, a second side shaft can be driven by a second of the output gears 94, in particular by the second of the output gears 94 being connected, in particular permanently, to the second side shaft in a rotationally fixed manner. 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. In the embodiment shown in . Fig. In the embodiment shown in Figure 1, the axle drive 36 is designed as a bevel gear differential, so that the differential gears 92 and the meshing output gears 94 are designed as bevel gears. Alternative designs of the axle drive 36 are conceivable, wherein the axle drive 36 can be designed, for example, as a spur gear differential, in particular as a planetary gear differential. For example, the axle drive 36 is a final drive ratio, also referred to as a final drive ratio, thus, with respect to a torque flow running from the output shaft 72 via the axle drive 36 to the vehicle wheels 12 and 14, the last ratio before the respective vehicle wheel 12, 14.

[0051] The hybrid drive system 10 has a first shifting element S1, by means of which the crankshaft 22 can be connected in a rotationally fixed manner to the first element, thus to the first sun gear 52. Furthermore, the rotor 30 is or can be coupled to the third element, thus to the first ring gear 56, in such a way that the respective second drive torque, which can be provided or is provided by the electric machine 26 via its rotor 30, can be introduced at the third element and via the third element into the transmission 44, in particular the first sub-transmission 46. In the first embodiment, the rotor 30 is connected, in particular permanently, in a rotationally fixed manner to the third element, i.e., coupled.

[0052] In order to achieve a particularly compact design as well as particularly advantageous drivability and particularly efficient operation of the hybrid drive system 10, the second element, i.e., the first planetary carrier 54, is permanently connected in a rotationally fixed manner to the fourth element, i.e., the second sun gear 60. Furthermore, a second switching element S2 is provided, by means of which the sixth element, i.e., the second ring gear 64, can be connected in a rotationally fixed manner to the housing 38 of the hybrid drive system 10.

[0053] In order 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.

[0054] A fourth switching element S4 is also provided, by means of which the third element can be connected in a rotationally fixed manner to the sixth element. The hybrid drive system 10 further comprises a fifth switching element S5, by means of which the first element can be connected in a rotationally fixed manner to the housing 38. Furthermore, a sixth switching element S6 is provided, by means of which the crankshaft 22 can be connected in a rotationally fixed manner to the second element.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 arranged on a side SE1 of the first sub-transmission 46, in particular of the second planetary gear set 58, facing away from the first spur gear stage 74 in the axial direction of the hybrid drive system 10, 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 side SE1 is also referred to as the first side.The spur gear stage 74 is arranged on a second side SE2 of the first sub-transmission 46, in particular of the first planetary gear set 50, which is remote from the spur gear stage 80 in the axial direction of the hybrid drive system 10, wherein the sides SE1 and SE2 are opposite one another or remote from one another in the axial direction of the hybrid drive system 10. Furthermore, the electric machine 26 is arranged axially overlapping the planetary gear set 50.

[0055] Fig. 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 in a rotationally fixed manner to the output shaft 72. Thus, in the second embodiment, the output gear 78 is designed as a loose gear which is arranged on the output shaft 72 so as to be rotatable, in particular about the output shaft axis of rotation. By means of the switching element S3, the first output gear 78 can be connected in a rotationally fixed manner to the output shaft 72.

[0056] Furthermore, in the second embodiment, it is provided that the machine rotation axis 32 is spaced apart 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, wherein the crankshaft rotation axis 24 and the planetary gear set rotation axis 66 coincide. Fig. 2, a dashed line 96 illustrates that the rotor 30 is 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 this 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, the electric machine 26 is also arranged axially overlapping the first planetary gear set 50. In an embodiment shown in Figs.In an embodiment not shown and also referred to as the first variant, for example, it is provided that the first variant corresponds to the second embodiment, the only difference being that the electric machine 26 is arranged coaxially to the planetary gear sets 50 and 58 and coaxially to the internal combustion engine 16, 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 the second variant, it is conceivable that the second variant corresponds to the second embodiment, 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, a coupling gear is provided, for example, in particular as an additional gear, in particular as an additional spur gear, 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 gear is, for example, permanently connected in a rotationally fixed manner to the third element, wherein the rotor 30 is permanently connected to the coupling gear in a torque-transmitting manner. From . Fig. 2 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, wherein direct meshing of the gear 98 with the input gear 76 is omitted. In the second variant, it is conceivable that the gear 98 meshes, in particular directly, with the coupling gear, or an intermediate gear is provided which meshes directly with the coupling gear and directly with the gear 98, wherein, for example, direct meshing of the gear 98 with the coupling gear is omitted.

[0057] Finally, Fig. 3 shows a third embodiment of the hybrid drive system 10. In the third embodiment, both spur gear stages 74 and 80 adjoin the first partial transmission 46, and thus the planetary gear sets 50 and 58, in the axial direction of the hybrid drive system 10, such that the first spur gear stage 74 is arranged between the partial transmission 46 and the second spur gear stage 80 in the axial direction of the hybrid drive system 10. Thus, for example, the spur gear stage 74 is arranged on a side SE3 of the second spur gear stage 80 facing the partial transmission 46 in the axial direction of the hybrid drive system 10. 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 referred to, for example, as a third variant, it is possible for the third variant of the third embodiment to be according to. Fig.3, 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 and facing the partial transmission 46, in particular such 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.

[0058] In the third embodiment, it is also provided that the output gear 86 is arranged axially, that is to say 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. List of reference symbols 10 Hybrid drive system 12 vehicle wheel 14 vehicle wheel 16 Internal combustion engine 18 Engine block 20 cylinders 22 Crankshaft 24 Crankshaft rotation axis 26 electric machine 28 Stator 30 rotors 32 Machine rotation axis 34 vehicle axle 36 axle drives 38 housings 40 Arrow 42 Arrow 44 gearboxes 46 first partial transmission 48 second partial transmission 50 first planetary gear set 52 first sun gear 54 first planet carrier 56 first ring gear 58 second planetary gear set 60 second sun gear 62 second planet carrier 64 second ring gear 66 Planetary gear set rotation axis 68 first planetary gear 70 second planet 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 drive input gear 90 Housing element 92 differential 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

Claims

[1] Hybrid drive system (10) for a motor vehicle, comprising an internal combustion engine (16) having a crankshaft (22), an electric machine (26) having a rotor (30), an axle transmission (36) and a transmission (44) having a first partial transmission (46) and a second partial transmission (48), wherein: - the first partial transmission (46) comprises: ◯ a first planetary gear set (50) having a first sun gear (52), a first planet carrier (54) and a first ring gear (56); and ◯ a second planetary gear set (58) with a second sun gear (60), a second planet carrier (62) and a second ring gear (64); - the second partial transmission (48) comprises: ◯ an output shaft (72); ◯ a first spur gear stage (74) having a first output gear (78) arranged coaxially with the output shaft (72) and meshing with a first input gear (76) of the first spur gear stage (74) that is connected or connectable in a rotationally fixed manner to the first ring gear (56); and ◯ a second spur gear stage (80) having a second output gear (84) arranged coaxially to the output shaft (72) and meshing with a second input gear (82) of the second spur gear stage (80) which is connected in a rotationally fixed manner to the second planet carrier (62); - an output gear (86) is permanently connected to the output shaft (72) in a rotationally fixed manner and permanently meshes with an axle transmission input gear (88); - a first switching element (S1) is provided which is designed to connect the crankshaft (22) in a rotationally fixed manner to the first sun gear (52); - the rotor (30) is coupled or can be coupled to the first ring gear (56) in such a way that torques that can be provided by the electric machine (26) via the rotor (30) can be introduced into the transmission (44) at the first ring gear (56); characterized by , that: - the first planet carrier (54) is permanently connected to the second sun gear (60) in a rotationally fixed manner; and - a second switching element (S2) is provided, which is designed to connect the second ring gear (64) in a rotationally fixed manner to a housing (38) of the hybrid drive system (10). [2] Hybrid drive system (10) according to claim 1, characterized by 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). [3] Hybrid drive system (10) according to claim 1 or 2, characterized by a third switching element (S3) which is designed to: - to connect the first input gear (76) to the first ring gear (56) in a rotationally fixed manner; or - to connect the first output gear (78) to the output shaft (72) in a rotationally fixed manner. [4] Hybrid drive system (10) according to one of the preceding claims, characterized by a fourth switching element (S4) which is designed to connect the first ring gear (56) to the second ring gear (64) in a rotationally fixed manner. [5] 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 sun gear (52) to the housing (38) in a rotationally fixed manner. [6] 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) in a rotationally fixed manner to the first planet carrier (54). [7] Hybrid drive system (10) according to one of the preceding claims, characterized bythat, viewed in an axial direction of the hybrid drive system (10), the second spur gear stage (80) is arranged on a side (SE1) of the first partial transmission (46) facing away from the first spur gear stage (74). [8] Hybrid drive system (10) according to one of the preceding claims, characterized by that the crankshaft (22) is arranged coaxially to the first partial transmission (46), wherein the output gear (86) is arranged axially between the internal combustion engine (16) and the first partial transmission (46). [9] Hybrid drive system (10) according to one of the preceding claims, characterized by that the electric machine (26) is arranged axially overlapping at least one of the planetary gear sets (50, 58). [10] Motor vehicle, comprising a hybrid drive system (10) according to one of the preceding claims.

Images