DE102022001138A1 - Electric drive device for a motor vehicle, in particular for a motor vehicle - Google Patents

Abstract

The invention relates to an electric drive device (10) for a motor vehicle, having a housing (12) with a first planetary gear set (18) arranged in the housing (12) and having a first sun gear (22) and a first planetary carrier as the first elements (24) and a first ring gear (26), with a second planetary gear set (20) arranged in the housing (12), which as second elements has a second sun gear (30) coupled in a rotationally fixed manner to the first ring gear (26), a second planetary carrier (32) and a second ring gear (34) which is or can be coupled in a rotationally fixed manner to the first planetary carrier (24), with an electrical machine (40) which has a stator (42) and a rotor (44), with a An input shaft (50) that can be driven by the rotor (44) and is permanently non-rotatably connected to the first sun wheel (22), with an output shaft (52), with a differential gear (54), with a side shaft (76), and with a shifting element (56 ), which is designed to connect the first ring gear (26) to the housing (12) in a torque-proof manner.

Description

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

Such an electric drive device for a motor vehicle, in particular for a motor vehicle, is, for example, already DE 10 2018 008 939 B3 to be taken as known. The electric drive device has a housing and a first planetary gearset arranged in the housing, which has a first sun gear, a first planet carrier and a first ring gear as first elements. The electric drive device also includes a second planetary gear set arranged in the housing, which has as second elements a second sun gear non-rotatably coupled to the first ring gear, a second planet carrier and a second ring gear non-rotatably coupled or capable of being coupled to the first planet carrier. Also provided is an electrical machine which has a stator and a rotor. The electric drive device also includes an input shaft that can be driven by the rotor and is permanently connected to the first sun gear in a rotationally fixed manner, as well as an output shaft. A differential gear is also provided. The electric drive device also includes a side shaft and a first switching element, which is designed to connect the first ring gear to the housing in a rotationally fixed manner. A second switching element is also provided, which is designed to connect one of the second elements to the housing or to one of the first elements in a rotationally fixed manner. The rotor, the first planetary gear set, the second planetary gear set and the differential gear are arranged coaxially with one another.

The object of the present invention is to improve an electric drive device of the type mentioned at the outset.

This problem is solved by an electric drive device with the features of patent claim 1 . Advantageous configurations with expedient developments of the invention are specified in the remaining claims.

In order to improve an electric drive device of the type specified in the preamble of claim 1, the invention provides that the first planetary gear set and the second planetary gear set are stacked one on top of the other, with the second planetary gear set surrounding the first planetary gear set. In other words, the planetary gear sets are stacked radially one on top of the other in such a way that the second planetary gear set radially encloses the first planetary gear set. This means that at least one longitudinal region of the first planetary gearset running in the axial direction of the respective planetary gearset, viewed in the axial direction of the respective planetary gearset, is arranged within the second planetary gearset and is surrounded, in particular completely, circumferentially around the axial direction of the respective planetary gearset . Thus, viewed in the axial direction of the respective planetary gear set, at least the longitudinal area of the first planetary gear set is arranged at the same height as the second planetary gear set. To put it another way, at least the length of the first planetary gearset in the radial direction of the respective planetary gearset overlaps or covers the second planetary gearset to the outside. In other words, the second planetary gear set is arranged at least along the length of the first planetary gear set, ie on the first planetary gear set. The respective planetary gear set is also referred to as a gear set. Excessively high rotational speeds can be avoided by the invention, with a particularly high torque being able to be realized, in particular that can be provided or brought about by means of the electric machine. Because the planetary gear sets are stacked one on top of the other, the space requirement of the electric drive device can be kept particularly small, particularly in the axial direction of the respective planetary gear set. In addition, particularly long gear ratios can be displayed. Furthermore, particularly advantageous stationary translations of the planetary gear sets can be presented. In particular, it is conceivable that the first ring gear and the second sun gear are formed in one piece with one another, that is to say are formed by a one-piece body, consequently by a single piece and thus by a monoblock. In other words, it is preferably provided that the first ring gear and the second sun gear are not designed as components that are designed separately from one another and are connected to one another, but rather it is very preferably provided that the first ring gear and the second sun gear are made of a single piece and thus are formed by a monoblock. Very preferably, the differential gear is designed as a planetary differential.

In order to be able to keep the installation space requirement, and therefore the axial length of the electric drive device, particularly low, particularly when viewed in the axial direction of the respective planetary gear set, it is provided in an advantageous embodiment of the invention that the differential gear is arranged inside the rotor, with the side shaft between the differential gear and a motor vehicle wheel that can be driven by the sideshaft and is also simply referred to as a wheel vehicle is arranged and passes through the first planetary gear set and the second planetary gear set. The vehicle wheel is a ground contact element, via which the motor vehicle can be or is supported on a ground downwards in the vertical direction of the vehicle. If the motor vehicle is driven along the ground while the motor vehicle is supported on the ground via the ground contact element in the vertical direction of the vehicle, the vehicle wheel rolls, in particular directly, on the ground.

In a further embodiment of the invention, it is provided that the first shifting element is designed as a shiftable freewheel and the second shifting element is designed as a multi-plate clutch. As a result, for example, a common actuator, for example one that can be operated electrically, can be used in order to actuate, that is to switch, both the first switching element and the second switching element.

In a further embodiment of the invention, it is provided that a fixed gear ratio of the second planetary gear set is in a range from -2.2 to -1.2 inclusive, in particular to -1.4 inclusive. Furthermore, it is preferably provided that a torque/speed ratio of the electric machine has an advantageous value, in particular with the aim of using the electric machine as a high-torque electric machine with a correspondingly reduced or low speed.

Furthermore, it is preferably provided that, viewed in the axial direction of the respective planetary gear set, the electric machine, the planetary gear sets stacked on top of one another and the differential gear are arranged one after the other in the following order: The electric machine—the planetary gear sets stacked on top of one another—the differential gear.

Because the second planetary gear set is stacked on top of the first planetary gear set, the first planetary gear set is an inner planetary gear set and the second planetary gear set is an outer planetary gear set. Preferably, the stationary gear ratio of the second planetary gear set is between -2.5 and +1.2. Alternatively or additionally, for example, a stationary gear ratio of the first planetary gear set is between -3.5 and -2. It is also conceivable that the stationary translation of the first planetary gear set is between -2 and -1.3. For example, a quotient of the stationary translation of the first planetary gear set and the stationary translation of the second planetary gear set is -1.9/-1.5, this ratio also being referred to as the stationary translation combination. This can result in a gear ratio of 5.75/2.9, for example. As a result, for example, the electric machine is designed to provide a torque of 900 Newton meters, in particular via its rotor.

The invention is based in particular on the following findings and considerations: The stacking of planetary gear sets can require special proportions of the components involved, which can severely restrict a solution space for possible fixed ratio combinations. Only one standard translation combination outside of a stackable translation range can be possible with a request for translations. By optimizing the overall system, with the electric machine being designed for higher torques and lower maximum speeds, it is possible with the invention to choose a suitable stationary ratio combination that can be selected within possible stationary ratio combinations for stacking and also a tension field of a ratio choice and a step jump can optimize between gears. The stacking of the planetary gear sets causes an improvement in the gearing efficiency as a result of a ratio change. The efficiency map of the electric machine also improves due to the increased torque of the electric machine in combination with lower speeds. Furthermore, a further increase in efficiency is achieved through the interaction of changed translations and a changed efficiency map of the electric machine.

Further advantages, features and details of the invention result from the following description of preferred exemplary embodiments and from the drawing. The features and combinations of features mentioned above in the description and the features and combinations of features mentioned below in the description of the figures and/or shown alone in the figures can be used not only in the combination specified in each case, but also in other combinations or on their own, without going beyond the scope of the leave invention.

• 1 eine schematische Darstellung einer ersten Ausführungsform einer elektrischen Antriebsvorrichtung für ein Kraftfahrzeug;
• 2 eine schematische Darstellung einer zweiten Ausführungsform der elektrischen Antriebsvorrichtung;
• 3 eine schematische Darstellung einer dritten Ausführungsform der elektrischen Antriebsvorrichtung;
• 4 eine schematische Darstellung einer vierten Ausführungsform der elektrischen Antriebsvorrichtung;
• 5 eine schematische Darstellung einer fünften Ausführungsform der elektrischen Antriebsvorrichtung;
• 6 eine schematische Darstellung einer sechsten Ausführungsform der elektrischen Antriebsvorrichtung;
• 7 eine schematische Darstellung einer siebten Ausführungsform der elektrischen Antriebsvorrichtung;
• 8 eine schematische Darstellung einer achten Ausführungsform der elektrischen Antriebsvorrichtung;
• 9 eine schematische Darstellung einer neunten Ausführungsform der elektrischen Antriebsvorrichtung;
• 10 eine schematische Darstellung einer zehnten Ausführungsform der elektrischen Antriebsvorrichtung;
• 11 eine schematische Darstellung einer elften Ausführungsform der elektrischen Antriebsvorrichtung;
• 12 eine schematische Darstellung einer zwölften Ausführungsform der elektrischen Antriebsvorrichtung; und
• 13 eine schematische Darstellung einer dreizehnten Ausführungsform der elektrischen Antriebsvorrichtung.

The drawing shows in:

• 1 a schematic representation of a first embodiment of an electric drive device for a motor vehicle;
• 2 a schematic representation of a second embodiment of the electric drive device;
• 3 a schematic representation of a third embodiment of the electric drive device;
• 4 a schematic representation of a fourth embodiment of the electric drive device;
• 5 a schematic representation of a fifth embodiment of the electric drive device;
• 6 a schematic representation of a sixth embodiment of the electric drive device;
• 7 a schematic representation of a seventh embodiment of the electric drive device;
• 8th a schematic representation of an eighth embodiment of the electric drive device;
• 9 a schematic representation of a ninth embodiment of the electric drive device;
• 10 a schematic representation of a tenth embodiment of the electric drive device;
• 11 a schematic representation of an eleventh embodiment of the electric drive device;
• 12 a schematic representation of a twelfth embodiment of the electric drive device; and
• 13 a schematic representation of a thirteenth embodiment of the electric drive device.

Elements that are the same or have the same function are provided with the same reference symbols in the figures.

1 shows a schematic representation of a first embodiment of an electric drive device 10 for a motor vehicle, in particular for a motor vehicle preferably designed as a passenger vehicle. The motor vehicle is designed, for example, as an electric vehicle, in particular as a battery-electric vehicle, and can be driven, in particular purely electrically. In its fully manufactured state, the motor vehicle has, for example, at least or exactly two vehicle axles, also referred to simply as axles, one after the other in the longitudinal direction of the vehicle and thus arranged one behind the other. The respective axle has at least or exactly two vehicle wheels, also referred to simply as wheels, the respective vehicle wheels of the respective vehicle axle being arranged on opposite sides of the motor vehicle in the vehicle transverse direction. By means of the electric drive device 10, for example, the vehicle wheels can be driven electrically, in particular purely, at least or precisely one of the vehicle axles, as a result of which the motor vehicle can be driven, in particular purely electrically. The vehicle wheels that can be driven by the electric drive device 10 are also referred to as drivable wheels or driven wheels. When the wheels or the vehicle wheels are discussed below, unless otherwise stated, these are to be understood as meaning the vehicle wheels that can be driven by means of the drive device 10 . The vehicle wheels that can be driven by electric drive device 10 are in 1 shown particularly schematically and denoted by 11 and 13 , the vehicle axle including the vehicle wheels 11 and 13 being denoted by 15 . The vehicle wheels of the axles are ground contact elements, via which the motor vehicle, also simply referred to as a vehicle, can be or is supported on a ground downwards in the vertical direction of the vehicle. If the motor vehicle is driven along the ground while the motor vehicle is supported on the ground via its ground contact elements in the vehicle vertical direction, the vehicle wheels of the vehicle axles roll, in particular directly, on the ground.

The electric drive device 10 comprises an in 1 Housing 12, shown particularly schematically, which, in particular directly, delimits a receiving space 14, also referred to as a receiving area. The electric drive device 10 also includes a planetary gear 16 which is arranged or accommodated in the housing 12 and thus in the receiving space 14 . The planetary gear 16 and thus the drive device 10 include a first planetary gear set 18 and a second planetary gear set 20, which are arranged coaxially to one another. The first planetary gear set 18 has a first sun gear 22 , a first planet carrier 24 and a first ring gear 26 . The sun gear 22, the planet carrier 24 and the ring gear 26 are first elements of the planetary gear set 18 or are also referred to as first elements. In addition, the first planetary gear set 18 includes first planet gears 28 which are rotatably mounted on the first planetary carrier 24 . The respective planet gear 28 meshes simultaneously with the sun gear 22 and with the ring gear 26. The second planetary gear set 20 has a second sun gear 30, a second planet carrier 32 and a second ring gear 34. The sun gear 30, the planet carrier 32 and the ring gear 34 are second elements of the planetary gear set 20 or are also referred to as second elements. The sun gears 22 and 30, the planet carriers 24 and 32 and the ring gears 26 and 34 and the housing 12 are also referred to as components of the drive device 10. The planetary gear sets 18 and 20 are in the receiving space 14 and thus accommodated or arranged in the housing 12 . The second planetary gear set 20 also includes second planet gears 36 which are rotatably mounted on the second planet carrier 32 . In addition, the respective, second planet gear 36 meshes simultaneously with the sun gear 30 and with the ring gear 34. The planet carriers 24 and 32 are also referred to as webs.

In particular, if the respective element is not connected to the housing 12 in a rotationally fixed manner, the respective element can rotate about an axis of rotation, also referred to as the main axis of rotation, relative to the housing 12 or the respective element then rotates about the main axis of rotation relative to the housing 12 , when the respective planetary gear set 18, 20 is driven, that is, when a torque is introduced into the respective planetary gear set 18, 20. Alternatively or additionally, the respective components can rotate relative to one another about the main axis of rotation, in particular when the respective components are not connected to one another in a rotationally fixed manner. If, for example, second components are connected to one another in a rotationally fixed manner or coupled to one another in a rotationally fixed manner, the components connected to one another in a rotationally fixed manner are secured against rotations occurring about the main axis of rotation and relative to one another. If, for example, two of the elements are connected or coupled in a rotationally fixed manner, the planetary gear sets 18 and 20 are driven, the elements connected in a rotationally fixed manner rotate together and thus as a block about the main axis of rotation, in particular relative to the housing 12. This means that the rotationally fixed interconnected elements revolve as a block. If, for example, the respective element is connected or coupled to the housing 12 in a rotationally fixed manner, the respective element is secured against rotation relative to the housing 12 and about the main axis of rotation, so that the respective element connected in a rotationally fixed manner to the housing 12 cannot rotate relative to the housing 12 can rotate around the main axis of rotation.

Out of 1 it can be seen that the second sun gear 30 is, in particular permanently, non-rotatably connected to the first ring gear 26, so that in particular when the planetary gear sets 18 and 20 are driven, the ring gear 26 and the sun gear 30 together and thus as a block with the same Rotate angular velocity about the main axis of rotation relative to the housing 12, especially when the ring gear 26 and the sun gear 30 are not rotatably connected to the housing 12. Preferably, ring gear 26 and sun gear 30 are integral with each other, that is, formed by a single piece.

In addition, the second ring gear 34 is coupled or can be coupled in a rotationally fixed manner to the first planetary carrier 24 . At the in 1 The first embodiment shown, the second ring gear 34 is, in particular permanently, non-rotatably connected to the first planet carrier 24, i.e. coupled, so that the planet carrier 24 and the ring gear 34 rotate in particular together and thus as a block relative to the housing 12 about the main axis of rotation , when the planetary gear sets 18 and 20 are driven and the planet carrier 24 and ring gear 34 are not rotationally fixed to the housing 12.

The drive device 10 also includes an electric machine 40 which, in the first embodiment, is designed as an internal rotor machine or as a radial flux machine (RFM). The motor vehicle can be driven electrically by means of the electric machine 40 . In particular, the vehicle wheels 11 and 13 can be driven electrically, in particular purely electrically, by means of the electric machine 40 . By electrically driving the vehicle wheels 11 and 12, the motor vehicle can be electrically driven as a whole. For this purpose, the electrical machine 40 includes a stator 42 and a rotor 44 which can be driven by the stator 42 and is therefore rotatable about a machine axis of rotation relative to the stator 42 and relative to the housing 12 . The planetary gear sets 18 and 20 and the electric machine 40 are arranged coaxially with one another so that the main axis of rotation coincides with the axis of rotation of the machine. Via the rotor 44, the electric machine 40 can provide torques for, in particular purely, electric driving of the vehicle wheels 11 and 13 and thus of the motor vehicle.

The drive device 10, in particular the planetary gear 16, has an input shaft 50 that can be driven by the rotor 44 and is permanently non-rotatably connected to the first sun gear 22, which can be driven by the rotor 44 and is therefore rotatable about the main axis of rotation or the axis of rotation of the machine relative to the housing 12 . At the in 1 The first embodiment shown is the input shaft 50, in particular permanently, non-rotatably connected to the rotor 44. Furthermore, it is conceivable that the input shaft 50 can be connected to the rotor 44 in a rotationally fixed manner.

The drive device 10, in particular the planetary gear 16, has an output shaft 52 which is rotatable in particular about the main axis of rotation and thus in the first embodiment also about the machine axis of rotation relative to the housing 12, via which the planetary gear 16 generates torques in the form of output torques, in particular for driving the Vehicle wheels 11 and 13 can provide. The respective output In this case, the torque results from the respective torque which is provided by the electrical machine 40 in particular via its rotor 44 . The respective output torque can be dissipated or diverted from the planetary gear 16 via the output shaft 52 .

The drive device 10 also includes a differential gear 54, also referred to simply as a differential or axle gear. The vehicle wheels 11 and 13 of the vehicle axle 15 can be driven by the electric machine 40 via the differential gear 54 . Thus, the differential gear 54 has the function, which is well known from the general state of the art, of distributing or dividing the respective output torque that can be made available or made available by the output shaft 52 to the vehicle wheels 11 and 13, which in 1 illustrated by arrows 38 and 39. Furthermore, the differential gear 54 permits different speeds of the vehicle wheels 11 and 13 when the motor vehicle is cornering, for example, such that the vehicle wheel 11, 13 on the outside of the curve can rotate at a higher speed than the vehicle wheel 13, 11 on the inside of the curve, in particular while the vehicle wheels 11 and 13 can be driven or are driven by the output shaft 52 and thus by the electric machine 40 via the differential gear 54 .

The electric drive device 10 has a first switching element 56 which, in the first embodiment, is designed as a non-positive or frictional switching element, in particular as a multi-plate clutch. By means of the first switching element 56, the first ring gear 26 and thus the fact that the sun gear 30 is permanently non-rotatably connected to the ring gear 26, the sun gear 30 is non-rotatably connected to the housing 12. In addition, the drive device 10 has a second shifting element 58 which, in the first embodiment, is designed as a positive shifting element, in particular as a claw clutch. In the first embodiment, the second planet carrier 32 can be connected to the housing 12 in a torque-proof manner by means of the second switching element 58 . Furthermore, it is provided that the rotor 44, the first planetary gear set 18, the second planetary gear set 20 and the differential gear 54 are arranged coaxially to one another. In the first embodiment, the differential gear 54 is designed as a bevel gear differential and as a ball differential. The differential gear 54 has a differential housing 62 which is rotatable relative to the housing 12 about a differential gear axis of rotation. Since the differential gear 54 is coaxial with the rotor 44 and coaxial with the planetary gear sets 18 and 20, the differential gear axis of rotation is coincident with the engine axis of rotation and with the main axis of rotation. For example, the differential housing 62 is designed as a differential carrier or as a differential cage. In the first embodiment, the output shaft 52 is, in particular permanently, non-rotatably connected to the differential housing 62 . The ring gear 34 and in the present case also the planetary carrier 24 are connected, in particular permanently, in a rotationally fixed manner to the output shaft 52 and thus, in particular permanently, in a rotationally fixed manner to the differential housing 62 . The respective output torque provided or that can be provided by the output shaft 52 can be transmitted from the output shaft 52 to the differential housing 62 , as a result of which the differential housing 62 can be driven and thereby rotated about the differential gear axis of rotation relative to the housing 12 . Thus, by driving the differential housing 62 , the differential housing 62 is rotated about the main axis of rotation, in particular relative to the housing 12 .

The ball differential is characterized in particular by the fact that the differential housing 62 delimits a receiving space 64, also referred to as the receiving area, which is designed in the shape of a sphere or a segment of a sphere. The differential gear 54 designed as a bevel gear differential in the first embodiment has two differential gears 66 and 68 which are rotatably mounted on the differential housing 62 and which are rotatably mounted on the differential housing 62 in such a way that the differential gears 66 and 68 can rotate about a common differential gear axis of rotation relative to the differential housing 62 and can also rotate relative to each other. The axis of rotation of the differential gear runs perpendicular to the axis of rotation of the differential gear. In the first embodiment, the differential gears 66 and 68 are bevel gears. The differential gears 66 and 68 are arranged in the receiving space 64 . Furthermore, the differential gear 54 has two output wheels 70 and 72 which are also arranged in the receiving space 64 . The output gears 70 and 72 can be rotated about the differential gear axis of rotation that is common to the output gears 70 and 72 relative to the differential housing 62 and, for example, also relative to one another, with the respective output gear 70, 72 meshing with the differential gears 66 and 68, in particular simultaneously. The driven wheels 70 and 72 are arranged in the receiving space 64 . In the first embodiment, the driven gears 70 and 72 are bevel gears. In other words, the differential gears 66 and 68 as well as the output gears 70 and 72 are gears, which in the present case are designed as bevel gears. The gears are at least partially, in particular at least over predominantly or completely, in the receiving space 64 arranged. The output gears 70 and 72 are, in particular permanently, torque-transmitting, in particular non-rotatably, coupled or connected to respective side shafts 74 and 76, which are also simply referred to as shafts and are designed, for example, as articulated shafts. The vehicle wheels 11 and 13 can be driven by the electric machine 40 via the side shafts 74 and 76, so that the vehicle wheels 11 and 13 can be driven by the driven wheels 70 and 72 and thus by the differential gear 54 via the side shafts 74 and 76. Out of 1 it can be seen that the side shaft 74 is arranged between the vehicle wheel 11 and the differential gear 54 and can thus be driven by the side shaft 74, that is to say via the side shaft 74, by the driven wheel 70. The side shaft 76 is arranged between the vehicle wheel 13 and the differential gear 54 so that the vehicle wheel 13 can be driven by the side shaft 76 and thus by the driven wheel 72 via the side shaft 76 .

If the differential housing 62 is rotated about the main axis of rotation, in particular relative to the housing 12 , the differential gears 66 and 68 are rotated about the main axis of rotation, in particular relative to the housing 12 . Then, for example, the driven wheels 70 and 72 and, via them, the side shafts 74 and 76 and thus the vehicle wheels 11 and 13 are driven by the differential gears 66 and 68, as a result of which the motor vehicle can be driven as a whole. The differential housing 62 is here, in particular via the output shaft 52, permanently non-rotatably connected to the first planetary carrier 24 and in the present case also permanently non-rotatably connected to the ring gear 34 .

In order to be able to keep the length of the drive device 10, also referred to as the axial length, particularly short, particularly in the axial direction of the respective planetary gear set 18, 20 and thus viewed along the main axis of rotation, the first planetary gear set 18 and the second planetary gear set 20 are stacked on top of one another, with the second Planetary gear set 20 surrounds the first planetary gear set 18 .

In the first embodiment, the differential gear 54 is arranged within the rotor 44 , with the sideshaft 76 passing through both the planetary gear set 18 and the planetary gear set 20 between the differential gear 54 and the vehicle wheel 13 .

The drive device 10 also has a parking lock 96, via which the output shaft 52 and thus, for example, the differential housing 62 rotatably connected to the housing 12 and thus secured against relative rotations occurring about the main axis of rotation and relative to the housing 12. As a result, the vehicle wheels 11 and 13 of the motor vehicle can also be secured against undesired rotations, so that an undesired rolling away of the motor vehicle can be avoided, for example by means of the parking lock 96, particularly when the motor vehicle is parked on a slope.

In an embodiment not shown in the figures, the shifting element 58 is designed as a switchable freewheel, in particular while the shifting element 56 is designed as a non-positive or frictional shifting element, in particular as a multi-plate clutch.

2 12 shows a second embodiment of the drive device 10. In the second embodiment, a switching part 59 common to the switching elements is assigned to the switching elements 56 and 58, which is in the present case designed as a double claw or sliding sleeve. By means of the switching part 59, the switching element 56 and via this the first ring gear 26 or the switching element 58 and via this the second planetary carrier 32 can be connected to the housing 12 in a non-rotatable manner, in each case in a form-fitting manner. For this purpose, the switching part 59 can be moved, in particular relative to the housing 12 and/or translationally and/or along the main axis of rotation, between at least one first switching position and at least one second switching position. In the first shift position, the shifting element 56 and, via this, the ring gear 26 are connected by means of the shifting part 59, in the present case with a positive fit, in a rotationally fixed manner to the housing 12, in particular while the shifting element 58 and the planetary carrier 32 are rotatable about the main axis of rotation relative to the housing 12. In the second switching position, the switching element 58 and, via this, the planetary carrier 32 are connected by means of the switching part 59, in the present case in a form-fitting, non-rotatable manner to the housing 12, in particular while the ring gear 26 is rotatable in particular about the main axis of rotation relative to the housing 12. In the second embodiment, both the shifting element 56 and the shifting element 58 and also the shifting part 59 are form-locking shifting elements, in particular claw clutches.

3 12 shows a third embodiment of the drive device 10. The third embodiment basically corresponds to the first embodiment, but in the third embodiment the switching elements 56 and 58 are positioned differently than in the first embodiment. 4 shows a fourth embodiment of the drive device 10. The fourth embodiment basically corresponds to the second embodiment, A different positioning of the switching elements 56 and 58 is also provided in the fourth embodiment compared to the second embodiment. In a further embodiment not shown in the figures, it can be provided that this embodiment basically corresponds to the third embodiment, in particular with the difference that the switching element 58 is designed as a switchable freewheel, in particular while the switching element 56 is designed as a friction or non-positive switching element, in particular designed as a multi-disc brake or multi-disk clutch.

5 shows a fifth embodiment of the drive device 10. In the fifth embodiment, the differential gear 54 is arranged, in particular completely, outside of the rotor 44. Furthermore, it is provided in the fifth embodiment that the shifting element 58 is designed as a form-fitting shifting element, in particular as a claw clutch. In particular, the dog clutch can be designed as a sliding sleeve.

6 shows a sixth embodiment, which basically corresponds to the fifth embodiment, in particular with the difference that the switching element 58 is designed as a switchable freewheel.

7 12 shows a seventh embodiment of the drive device 10. The seventh embodiment basically corresponds to the fifth or sixth embodiment, with the difference that in the seventh embodiment the switching part 59 common to the switching elements 56 and 58 is provided.

8th shows an eighth embodiment of the drive device 10. In the eighth embodiment, the electrical machine 40 is designed as an axial flux machine (AFM). Here, the rotor 44 has two rotor elements 45 and 47, which are designed in particular as rotor disks. The rotor elements 45 and 47 are spaced apart from one another in the axial direction of the electrical machine 40 and thus viewed along the machine axis of rotation, with the stator 42 being arranged between rotor elements 45 and 47 in the axial direction of the electrical machine 40 . The rotor elements 45 and 47 are connected to the input shaft 50 in a torque-proof manner, in particular permanently.

While 9 a ninth embodiment of the drive device 10 shows shows 10 a tenth embodiment of the drive device 10. In the ninth embodiment, the shifting element 56 is designed as a non-positive or frictional shifting element, in particular as a multi-plate clutch, while the shifting element 58 is designed as a positive shifting element, in particular as a claw clutch. In the tenth embodiment, the shifting element 58 is designed as a positive shifting element, ie as a claw clutch, while the shifting element 56 is designed as a frictional or non-positive shifting element, in particular as a multi-plate clutch. In addition, in the tenth embodiment, a here non-switchable freewheel 61 is provided, which avoids relative rotations between the second ring gear 34 and the first planet carrier 24 occurring in a first direction of rotation about the main axis of rotation and relative rotations occurring in a second direction of rotation, opposite the first direction of rotation, about the main axis of rotation between the ring gear 34 and the planet carrier 24 allows. In other words, ring gear 34 can thus, for example, rotate about the main axis of rotation in the second direction of rotation relative to planet carrier 24, with rotation of ring gear 34 occurring about the main axis of rotation in the first direction of rotation relative to planet carrier 24 being prevented by means of non-shiftable freewheel 61 is.

While 11 an eleventh embodiment of the drive device 10 shows shows 12 a twelfth embodiment of the drive device 10.

Finally shows 13 a thirteenth embodiment of the drive device 10. In the thirteenth embodiment, the differential gear 54 is designed as a planetary differential, and therefore as a further planetary gear. Instead of the differential housing 62, the planetary differential has a third ring gear 98 which is connected to the output shaft 52 in a torque-proof manner, in particular permanently. The planetary differential also includes a third sun gear 100 and a third planetary carrier 102, which is designed as a double planetary carrier the respective planet gear 104 meshes with the ring gear 98, but not with the sun gear 100. The planet gears 104 and 106 are rotatably mounted on the third planet carrier 102, which is common to the planet gears 104 and 106 and is designed as a double planet carrier. It is conceivable that the planetary gears 104 mesh with the planetary gears 106 or that the planetary gears 104 do not mesh with the planetary gears 106 . Furthermore, it can be seen that the side shaft 76, by which the vehicle wheel 13 can be driven, is connected, in particular permanently, in a torque-transmitting manner, in particular in a torque-proof manner, to the planetary carrier 102 designed as a double planetary carrier. The sideshaft 74, from which the vehicle wheel 11 can be driven is connected, in particular permanently, to the sun gear 100 in a torque-transmitting manner, in particular in a torque-proof manner.

Advantageous rotor cooling of the electrical machine 40 can be realized by pulling out the differential gear 54, that is to say in particular when the differential gear 54 is not arranged inside the rotor 44 but outside the rotor 44. This is particularly advantageous if the electrical machine 40 is designed as an axial flux machine, since the overall length of the end windings is then eliminated and two walls can be formed with the wheel set plane and the rotor 44, which bring design advantages with regard to the overall length. In order to make sensible use of the available space, the switching elements 56 and 58 can be located radially above it. Advantageously, the differential gear 54 would then be configured as a planetary differential. In the thirteenth embodiment, the planetary differential is formed as a double planetary gear set. Alternatively, two sun gears can be provided. As a result, the axial length can be kept particularly short. A particular advantage is that the switching elements 56 and 58 can then be arranged well above the differential, so that they do not enter into the axial overall length.

Reference List

10

electric drive device

11

vehicle wheel

12

Housing

13

vehicle wheel

14

recording room

15

vehicle axle

16

planetary gear

18

first planetary gear set

20

second planetary gear set

22

first sun wheel

24

first planet carrier

26

first ring gear

28

first planet wheel

30

second sun wheel

32

second planet carrier

34

second ring gear

36

second planet gear

38

Arrow

39

Arrow

40

electric machine

42

stator

44

rotor

45

rotor element

47

rotor element

50

input shaft

52

output shaft

54

differential gear

56

first switching element

58

second switching element

59

switching part

61

non-switchable freewheel

62

differential case

64

recording room

66

balance wheel

68

balance wheel

70

output gear

72

wear wheel

74

sideshaft

76

sideshaft

96

parking lock

98

third ring gear

100

third sun wheel

102

third planet carrier

104

third planet gear

106

fourth planet gear

QUOTES INCLUDED IN DESCRIPTION

This list of documents cited 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.

Patent Literature Cited

• DE 102018008939 B3 [0002]

Claims (4)

Electric drive device (10) for a motor vehicle, having a housing (12), with a first planetary gear set (18) arranged in the housing (12), which as first elements has a first sun gear (22), a first planet carrier (24) and has a first ring gear (26), with a second planetary gear set (20) arranged in the housing (12), which as second elements comprises a second sun gear (30) coupled in a rotationally fixed manner to the first ring gear (26), a second planetary carrier (32 ) and a second ring gear (34) which is or can be coupled in a rotationally fixed manner to the first planetary carrier (24), with an electrical machine (40) which has a stator (42) and a rotor (44), with one of the rotor ( 44) drivable and permanently non-rotatably connected to the first sun gear (22) input shaft (50), with an output shaft (52), with a differential gear (54), with a side shaft (76), with a first shifting element (56) which is designed to connect the first ring gear (26) to the housing (12) in a rotationally fixed manner, and to a second switching element (58) which is designed to connect one of the second elements to the housing (12) or to one of the first elements in a rotationally fixed manner to connect, wherein the rotor (44), the first planetary gear set (18), the second planetary gear set (20) and the differential gear (54) are arranged coaxially to one another, characterized in that the first planetary gear set (18) and the second planetary gear set (20 ) are stacked on top of each other, with the second planetary gear set (20) surrounding the first planetary gear set (18). Electrical drive device (10) after claim 1 , characterized in that the differential gear (54) is arranged inside the rotor (44), the side shaft (76) being arranged between the differential gear (54) and a vehicle wheel (13) of the motor vehicle which can be driven by the side shaft (76) and the first planetary gear set (18) and second planetary gear set (20) interspersed. Electrical drive device (10) after claim 1 or 2 , characterized in that the first switching element (56) is designed as a switchable freewheel and the second switching element (58) as a multi-plate clutch. Electrical drive device (10) according to one of the preceding claims, characterized in that a stationary transmission ratio of the second planetary gear set (20) is in a range from -2.2 to -1.2 inclusive, in particular -1.4.

Images