DE102022208156A1 - Electric drive device for a vehicle - Google Patents

Abstract

Electrical drive device comprising a single electric machine (EM), which is connected to a switchable planetary gear via a transmission input shaft (1), the planetary gear having exactly four switching elements for shifting four gears and a stepped planetary gear set (SP) with a first sun gear shaft (SR1). , a second sun gear shaft (SR2), a first ring gear shaft (HR1), a second ring gear shaft (HR2) and a web shaft (ST) with a plurality of stepped planetary gears rotatably arranged thereon, wherein the first ring gear shaft (HR1) of the stepped planetary gear set (SP) by means of the first Switching element (A) can be connected in a rotationally fixed manner to a housing (G), wherein the web shaft (ST) of the stepped planetary gear set (SP) can be connected in a rotationally fixed manner to the housing (G) by means of the second switching element (B), the first sun gear shaft (SR1) of the Stepped planetary gear set (SP) can be connected in a rotationally fixed manner to the housing (G) by means of the third switching element (C), wherein the first sun gear shaft (SR1) of the stepped planetary gear set (SP) can be connected in a rotationally fixed manner to the transmission input shaft (1) by means of the fourth switching element (D), wherein the second sun gear shaft (SR2) of the stepped planetary gear set (SP) is connected in a rotationally fixed manner to the transmission input shaft (1), wherein the second ring gear shaft (HR2) of the stepped planetary gear set (SP) is at least indirectly connected to a transmission output shaft (2).

Description

The invention relates to an electric drive device for a vehicle and a vehicle with such an electric drive device.

From the publication WO 2014/139 744 A1 a drive train for a vehicle is known, with at least one electric drive, which can be coupled via a drive shaft with at least a first gear ratio and a second gear ratio. At least one switching device is provided for switching the gear ratio stages, wherein the switching device for carrying out power shifts comprises at least one positive switching element and at least one frictional switching element. Each of the transmission stages can be switched with the positive switching element, with at least one of the transmission stages being switchable both with the positive switching element and with the frictional switching element.

The object of the present invention is to propose an alternative drive device with a 4-speed transmission. In particular, the drive device should be designed to be efficient and compact, with the transmission of the drive device should have increased conversion and spread. The task is solved by a drive device with the features of patent claim 1. Advantageous embodiments are the subject of the dependent claims, the following description and the figures.

An electric drive device according to the invention for a vehicle comprises a single electric machine which is connected to a switchable planetary gear via a transmission input shaft, the planetary gear having a first switching element for switching a first gear, a second switching element for switching a second gear, and a third switching element for switching a third gear, a fourth switching element for switching a fourth gear and a stepped planetary gear set with a first sun gear shaft, a second sun gear shaft, a first ring gear shaft, a second ring gear shaft and a web shaft with a plurality of stepped planetary gears rotatably arranged thereon, a first gear of the respective stepped planetary gear being included the first sun gear shaft and the first ring gear shaft of the stepped planetary gear set are in meshing engagement and are non-rotatably connected to a second gear of the respective stepped planetary gear, the second gear of the respective stepped planetary gear being in meshing engagement with the second sun gear shaft and the second ring gear shaft of the stepped planetary gear set, the first ring gear shaft of the Stepped planetary gear set can be connected in a rotationally fixed manner to a housing by means of the first switching element, wherein the web shaft of the stepped planetary gear set can be connected in a rotationally fixed manner to the housing by means of the second switching element, wherein the first sun gear shaft of the stepped planetary gear set can be connected in a rotationally fixed manner to the housing by means of the third switching element, the first sun gear shaft of the Stepped planetary gear set can be connected in a rotationally fixed manner to the transmission input shaft by means of the fourth switching element, the second sun gear shaft of the stepped planetary gear set being non-rotatably connected to the transmission input shaft, the second ring gear shaft of the stepped planetary gear set being at least indirectly connected to a transmission output shaft, at least the transmission input shaft, the transmission output shaft and the switchable planetary gear are arranged on a common first axis of rotation.

The drive device therefore has exactly one electrical machine that can be operated as a drive motor for driving the vehicle and as a generator for recuperating electrical energy. The electric machine includes a rotor and a stator, the rotor being connected to the transmission input shaft for driving purposes. Furthermore, the electrical machine is electrically connected to an electrical energy storage device in order to extract electrical energy for the drive and to feed in recuperated electrical energy.

An “indirect connection” or a “drive connection” of a shaft or a device with another shaft or with another device is to be understood as meaning that these shafts or devices are either directly connected to one another, for example connected to one another in a rotationally fixed manner, or indirectly via at least one further component, in particular via further shafts and gears, can be connected to one another.

For example, the rotor shaft of the electric machine is connected in a drive-effective manner to the transmission input shaft directly or via at least one further shaft. For example, the rotor shaft of the electric machine is connected in a drive-effective manner to the second transmission input shaft via at least one further shaft, via several gear wheels and/or via a traction means. The electric machine can be arranged on the first axis of rotation and thus be designed coaxially with the transmission input shaft, in which case the rotor shaft is preferably connected in a rotationally fixed manner to the transmission input shaft. Alternatively, the electric machine can be designed axially parallel to the transmission input shaft, whereby then the rotor shaft is indirectly connected to the transmission input shaft.

A “shaft” does not only mean, for example, a cylindrical, rotatably mounted gear element for transmitting torque, but rather it also refers to general connecting elements that connect individual components or elements to one another, in particular connecting elements that connect several elements to one another in a rotationally fixed manner. Two shafts that are connected to one another in a rotationally fixed manner can be designed in one piece.

The stepped planetary gear set is composed of the elements first sun gear shaft, second sun gear shaft, first ring gear shaft, second ring gear shaft and web shaft, with the web shaft rotatably supporting a plurality of stepped planetary gears, with each stepped planetary gear having two gears which are connected to one another in a rotationally fixed manner. In other words, each stepped planetary gear has two toothed sections which are connected to one another in a rotationally fixed manner and which have different diameters. The first toothed section or the first gear meshes with the first sun gear shaft and the first ring gear shaft, wherein the second toothed section or the second gear meshes with the second sun gear shaft and the second ring gear shaft. The second gear preferably has a larger diameter than the first gear, whereby a higher gear ratio can be achieved.

The electric drive device preferably has exactly four switching elements. Each switching element can be switched by a respective actuator. A “switching element” is to be understood as meaning a switchable device which, in a closed state, connects two shafts or a shaft and a non-rotatable component in a rotationally fixed manner and in an open state decouples the two shafts or the shaft and the non-rotatable component from one another. A “non-rotatable component” is to be understood as meaning a component that is fixed in a stationary manner, in particular non-rotatable or connected in one piece to a part of a housing in a non-rotatable manner. The switching elements of the drive device are designed as gear shifting elements and are therefore set up to shift gears.

The first, second and third switching elements are each designed to fix a respective shaft of the stepped planetary gear set, in particular the first ring gear shaft, the web shaft or the first sun gear shaft, stationary to the housing of the planetary gear in the closed state in order to form the respective gear. When the first switching element is closed and the second switching element, the third switching element and the fourth switching element are open, a first gear with a first translation is realized, in which case the first ring gear shaft of the stepped planetary gear set is connected to the housing in a rotationally fixed manner. When the second switching element is closed and the first switching element, the third switching element and the fourth switching element are open, a second gear with a second gear ratio is realized, in which case the web shaft of the stepped planetary gear set is connected to the housing in a rotationally fixed manner. When the third switching element is closed and the first switching element, the second switching element and the fourth switching element are open, a third gear with a third gear ratio is realized, in which case the first sun gear shaft of the stepped planetary gear set is connected to the housing in a rotationally fixed manner.

In contrast, the fourth switching element is designed to connect the first sun gear shaft of the stepped planetary gear set to the transmission input shaft in the closed state, the second sun gear shaft of the stepped planetary gear set being permanently connected in a rotationally fixed manner to the transmission input shaft. If the fourth switching element is closed and the first switching element, the second switching element and the third switching element are open, a fourth gear with a fourth gear ratio is realized, in which case the first sun gear shaft of the stepped planetary gear set is connected to the transmission input shaft and thus also to the second sun gear shaft of the stepped planetary gear set is connected in a rotationally fixed manner. As a result, the stepped planetary gear set is blocked and is therefore in a block rotation. By blocking the stepped planetary gear set, the translation is independent of the number of teeth of the meshing elements of the first planetary gear set i=1.

The combination of the electric machine with the stepped planetary gear set and the four switching elements creates a particularly efficient drive device with four gears and increased conversion and spread. The planetary gear has exactly five shafts, namely the first sun gear shaft of the stepped planetary gear set, the second sun gear shaft of the stepped planetary gear set, which is non-rotatably or integrally connected to the transmission input shaft, the first ring gear shaft of the stepped planetary gear set, the second ring gear shaft of the stepped planetary gear set, which is non-rotatably or integrally connected to the transmission output shaft, and the Bridge shaft. None of the shafts of the planetary gear are permanently fixed in a stationary manner, i.e. connected to the housing in a rotationally fixed manner.

According to a preferred embodiment, the four switching elements can be actuated by a single actuator using a single switching sleeve. For example, the switching sleeve is arranged in an axially displaceable manner in the planetary gear and has seven switching positions. In the first shift position of the shift sleeve, which represents a gear position, the first ring gear shaft of the stepped planetary gear set is connected to the housing in a rotationally fixed manner. In the second switching position of the switching sleeve, which represents a neutral position, the switching sleeve is only connected to the housing. In the third shift position of the shift sleeve, which represents a gear position, the web shaft of the stepped planetary gear set is connected to the housing in a rotationally fixed manner. In the fourth switching position of the switching sleeve, which represents a neutral position, the switching sleeve is only connected to the housing. In the fifth shift position of the shift sleeve, which represents a gear position, the first sun gear shaft of the stepped planetary gear set is connected to the housing in a rotationally fixed manner. In the sixth switching position of the switching sleeve, which represents a neutral position, the switching sleeve is only connected to the first sun gear shaft of the stepped planetary gear set. In the seventh switching position of the shift sleeve, which represents a gear position, the first sun gear shaft of the stepped planetary gear set is connected in a rotationally fixed manner to the transmission input shaft and thus also to the second sun gear shaft of the stepped planetary gear set. This creates a sequential switching order. The only actuator therefore moves the switching sleeve in the axial direction, first on the housing and then on the first sun gear shaft into the respective switching position. The shift sleeve preferably has claws which interact in a form-fitting manner with corresponding claw teeth in the respective gear position, in particular in the first, third, fifth and seventh shift positions. The respective claw teeth with which the switching sleeve interacts in a form-fitting manner is therefore to be understood as a switching element, i.e. as a first, second, third and fourth switching element. In particular, the shift sleeve is arranged axially between two gear positions in a respective neutral position, i.e. in the second, fourth and sixth shift position, so that a change between the gears, in particular between the first, third, fifth and seventh shift position, always requires a pass through a neutral position.

All four switching elements are preferably designed as positive switching elements, for example as claw clutches. Alternatively, at least one switching element is designed as a frictional switching element, for example as a multi-plate clutch or cone clutch. According to a preferred embodiment, the first switching element and the second switching element are combined to form a common first double switching element, with the third switching element and the fourth switching element being combined to form a common second double switching element. A “double switching element” means that two switching elements are arranged axially directly next to each other and are combined into a unit that can be switched using a single actuator. The respective double switching element is preferably designed as a positive switching element and includes, for example, claws that are intended for positive engagement. Through positive switching elements, the efficiency of the drive device can be increased due to reduced drag losses. In particular, positive-locking switching elements are designed to be more compact and optimized in terms of efficiency and have a cost advantage over friction-locking switching elements. However, load switching with positive switching elements is not possible. Therefore, synchronization must take place before a positive switching element is closed.

According to a preferred embodiment, at least the third and fourth switching elements are arranged at least partially or completely radially within the electrical machine. The electrical machine is preferably arranged on the first axis of rotation. In particular, the drive device is thereby designed to be axially more compact.

According to a preferred embodiment, the electric drive device further has a planetary gear set arranged on the first axis of rotation with the elements sun gear shaft, ring gear shaft and web shaft, a first element of the planetary gear set being connected in a rotationally fixed manner to the second ring gear shaft of the stepped planetary gear set, a second element of the planetary gear set being connected to the Housing is connected in a rotationally fixed manner, with a third element of the planetary gear set being connected in a rotationally fixed manner with the transmission output shaft. Several planet gears are rotatably arranged on the web shaft of the planetary gear set, each planet gear being in mesh with the sun gear shaft and the ring gear shaft of the planetary gear set. The second ring gear shaft of the stepped planetary gear set is therefore indirectly connected to the transmission output shaft via the planetary gear set designed as a negative planetary gear set. The planetary gear set is therefore designed as a rear-mounted gear set and is intended to increase the gear ratio. For example, the first element of the planetary gear set is the sun gear shaft, the second element of the planetary gear set is the ring gear shaft, and the third element of the planetary gear set is the web shaft. Alternatively, the first element of the planetary gear set is the ring gear shaft, the second element of the planetary gear set is the sun gear shaft, the third element of the planetary gear set is the web shaft.

According to a preferred embodiment, the electric drive device has a differential with a differential input and two differential output shafts, the differential input being at least indirectly connected to the transmission output shaft. For example, the differential input is designed as a differential input shaft and is connected to the transmission output shaft in a rotationally fixed manner. The drive power fed into the differential via the differential input is distributed to the two differential output shafts, the respective differential output shaft being connected in a driving manner to a respective drive wheel of an electric drive axle of the vehicle.

According to a preferred embodiment, the differential is arranged on the first axis of rotation, with the transmission input shaft and the transmission output shaft being designed as hollow shafts, and with one of the two differential output shafts extending axially through the planetary gear. As a result, the drive device is designed to be more compact, particularly in the radial direction.

According to a preferred embodiment, the differential is arranged on a second axis of rotation, the second axis of rotation being designed axially parallel to the first axis of rotation, the differential input being connected to the transmission output shaft via a spur gear stage. As a result, the drive device is designed to be more compact, particularly in the axial direction, with a gear ratio being able to be increased via the spur gear stage. In particular, the spur gear stage has two spur gears that mesh with one another, one spur gear being arranged on the first axis of rotation, the other spur gear being arranged on the second axis of rotation.

According to a preferred embodiment, the differential is arranged on a second axis of rotation, wherein the second axis of rotation is designed axially parallel to the first axis of rotation, with an intermediate shaft being arranged on a third axis of rotation, wherein the intermediate shaft is designed axially parallel to the first and second axes of rotation, the differential input via a first spur gear stage is connected to the intermediate shaft, the intermediate shaft being connected to the transmission output shaft via a second spur gear stage. As a result, the drive device is designed to be more compact, particularly in the axial direction, with the two spur gear stages allowing a gear ratio to be increased more than with one spur gear stage. In particular, each of the two spur gear stages has two spur gears that mesh with one another, with a respective spur gear of the respective spur gear stage being connected in a rotationally fixed manner to the intermediate shaft.

According to a preferred embodiment, the differential is designed as a bevel gear differential. A differential designed as a bevel gear differential has two wheel-side output elements, in particular a first output gear and a second output gear. The two driven wheels each mesh with a compensating element. The compensating elements are mounted in a differential cage so that they can rotate about their own axis. The respective output gear is connected to the respective output shaft in a rotationally fixed manner. The differential is driven via the differential carrier. Furthermore, alternative forms of design of the differential are also conceivable, for example as a spur gear differential or planetary differential, in particular a plus planetary differential.

According to a preferred embodiment, the differential is designed as an integral differential. An “integral differential” is to be understood as meaning a differential with a first planetary gear set and a second planetary gear set that is operatively connected to the first planetary gear set. The first planetary gear set is drivingly connected to the transmission output shaft, to the second planetary gear set and at least indirectly to the first differential output shaft. The second planetary gear set is also connected in a driving manner to the second differential output shaft and is supported on a stationary component, in particular on a housing component. By means of such an integral differential, the input torque on the transmission output shaft can be changed and divided into the two differential output shafts in a defined ratio. Preferably, half of the input torque is transmitted to the differential output shafts.

A vehicle according to the invention comprises a drive device according to the invention. In particular, the vehicle is designed as an electric vehicle and has an electric drive axle with the drive device according to the invention. The above definitions and statements on technical effects, advantages and advantageous embodiments of the drive device according to the invention also apply mutatis mutandis to the vehicle according to the invention.

• 1 eine stark abstrahierte schematische Ansicht eines Fahrzeugs mit einer erfindungsgemäßen elektrischen Antriebsvorrichtung;
• 2 eine stark abstrahierte schematische Ansicht einer erfindungsgemäßen Antriebsvorrichtung gemäß einer ersten Ausführungsform;
• 3 eine stark abstrahierte schematische Ansicht einer erfindungsgemäßen Antriebsvorrichtung gemäß einer zweiten Ausführungsform;
• 4 eine stark abstrahierte schematische Ansicht einer erfindungsgemäßen Antriebsvorrichtung gemäß einer dritten Ausführungsform;
• 5 eine stark abstrahierte schematische Ansicht einer erfindungsgemäßen Antriebsvorrichtung gemäß einer vierten Ausführungsform;
• 6 eine stark abstrahierte schematische Ansicht einer erfindungsgemäßen Antriebsvorrichtung gemäß einer fünften Ausführungsform;
• 7 eine stark abstrahierte schematische Ansicht einer erfindungsgemäßen Antriebsvorrichtung gemäß einer sechsten Ausführungsform;
• 8 eine stark abstrahierte schematische Ansicht einer erfindungsgemäßen Antriebsvorrichtung gemäß einer siebten Ausführungsform; und
• 9 eine stark abstrahierte schematische Ansicht einer erfindungsgemäßen Antriebsvorrichtung gemäß einer achten Ausführungsform.

Advantageous embodiments of the invention, which are explained below, are shown in the drawings, with the same elements being provided with the same reference numerals. Show it:

• 1 a highly abstracted schematic view of a vehicle with an electric drive device according to the invention;
• 2 a highly abstracted schematic view of a drive device according to the invention according to a first embodiment;
• 3 a highly abstracted schematic view of a drive device according to the invention according to a second embodiment;
• 4 a highly abstracted schematic view of a drive device according to the invention according to a third embodiment;
• 5 a highly abstracted schematic view of a drive device according to the invention according to a fourth embodiment;
• 6 a highly abstracted schematic view of a drive device according to the invention according to a fifth embodiment;
• 7 a highly abstracted schematic view of a drive device according to the invention according to a sixth embodiment;
• 8th a highly abstracted schematic view of a drive device according to the invention according to a seventh embodiment; and
• 9 a highly abstracted schematic view of a drive device according to the invention according to an eighth embodiment.

1 shows the vehicle 100 with a first drive axle 101 with two wheels R1, R2 and a second drive axle 102 with two wheels R3, R4. In the present case, the first drive axle 101 is designed as a front axle of the vehicle 100 and is equipped with an electric drive device according to the invention, which has a single electric machine EM and a planetary gear with a stepped planetary gear set SP and a differential 3. The vehicle 100 is therefore designed as an electric vehicle. The drive device is arranged transversely to the longitudinal direction of the vehicle and is effectively connected to the wheels R1, R2 of the first drive axle 101. In the present case, no further drive device is arranged on the second drive axle 102, i.e. on the rear axle of the vehicle 100, which saves costs, weight and installation space. To implement an all-wheel drive system, a further drive device can be arranged on the second axle and connected to the wheels R3, R4 of the second drive axle 102 in a drive-effective manner.

2 shows schematically an electric drive device according to a first embodiment, wherein the drive device has a single electric machine EM, which is connected to a switchable planetary gear via a transmission input shaft 1. The planetary gear has a first shifting element A for shifting a first gear, a second shifting element B for shifting a second gear, a third shifting element C for shifting a third gear, a fourth shifting element D for shifting a fourth gear and a stepped planetary gear set SP.

The stepped planetary gear set SP has a first sun gear shaft SR1, a second sun gear shaft SR2, a first ring gear shaft HR1, a second ring gear shaft HR2 and a web shaft ST with a plurality of stepped planetary gears rotatably arranged thereon. A first gear Z1 of the respective stepped planetary gear is in mesh with the first sun gear shaft SR1 and the first ring gear shaft HR1 of the stepped planetary gear set SP. The first gear Z1 of the respective stepped planetary gear is connected in a rotationally fixed manner to a second gear Z2 of the respective stepped planetary gear, the second gear Z2 of the respective stepped planetary gear being in mesh with the second sun gear shaft SR2 and the second ring gear shaft HR2 of the stepped planetary gear set SP. The second gear Z2 has a larger diameter than the first gear Z1. The second sun gear shaft SR2 of the stepped planetary gear set SP is connected to the transmission input shaft 1 in a rotationally fixed manner. The second ring gear shaft HR2 of the stepped planetary gear set SP is connected to the transmission output shaft 2 in a rotationally fixed manner. The electric machine EM, the transmission input shaft 1, the transmission output shaft 2 and the switchable planetary gear are arranged on a common first rotation axis A1.

In the present case, all four switching elements A, B, C, D are designed as positive switching elements and can be actuated by means of a single switching sleeve SM, which is axially displaced by a single actuator, not shown. The first ring gear shaft HR1 of the stepped planetary gear set SP can be connected in a rotationally fixed manner to a housing G of the planetary gear by means of the first switching element A. The web shaft ST of the stepped planetary gear set SP can be connected in a rotationally fixed manner to the housing G of the planetary gear by means of the second switching element B. The first sun gear shaft SR1 of the stepped planetary gear set SP can be connected in a rotationally fixed manner to the housing G of the planetary gear by means of the third switching element C. The first sun gear shaft SR1 of the stepped planetary gear set SP can be connected in a rotationally fixed manner to the transmission input shaft 1 by means of the fourth switching element D.

The switching sleeve SM is arranged in an axially displaceable manner in the planetary gear and in this case has seven switching positions. In the first switching position of the switching sleeve SM, represented by the first switching element A, the first ring gear shaft HR1 of the stepped planetary gear set SP is with the housing G non-rotatably connected. In the second switching position of the switching sleeve SM, which represents a neutral position, the switching sleeve SM is only connected to the housing G. In the third switching position of the switching sleeve SM, represented by the second switching element B, the web shaft ST of the stepped planetary gear set SP is connected to the housing G in a rotationally fixed manner. In the fourth switching position of the switching sleeve SM, which represents a neutral position, the switching sleeve SM is only connected to the housing G. In the fifth switching position of the switching sleeve SM, represented by the third switching element C, the first sun gear shaft SR1 of the stepped planetary gear set SP is connected to the housing G in a rotationally fixed manner. In the sixth switching position of the switching sleeve SM, which represents a neutral position, the switching sleeve SM is only connected to the first sun gear shaft SR1 of the stepped planetary gear set SP. In the seventh switching position of the switching sleeve SM, represented by the fourth switching element D, the first sun gear shaft SR1 of the stepped planetary gear set SP is connected in a rotationally fixed manner to the transmission input shaft 1 and thus also to the second sun gear shaft SR2 of the stepped planetary gear set SP. This creates a sequential switching order. In the present case, the shift sleeve SM has claws which interact in a form-fitting manner with corresponding claw teeth on the shift elements A, B, C, D in the respective gear position, in particular in the first, third, fifth and seventh shift positions of the sliding sleeve SM. The respective claw toothing with which the switching sleeve SM interacts in a form-fitting manner is therefore to be understood as the first, second, third and fourth switching elements A, B, C, D. In particular, the shift sleeve SM is arranged axially between two gear positions in a respective neutral position, i.e. in the second, fourth and sixth shift position, so that a change between the four gears, in particular between the first, third, fifth and seventh shift position, always involves a pass through a neutral position requires.

According to an axial sequence, the fourth switching element D is arranged axially adjacent to the electrical machine EM, wherein the third switching element C is arranged axially adjacent to the fourth switching element D, wherein the second switching element B is arranged axially adjacent to the third switching element C, wherein the first switching element A is arranged axially adjacent to the second switching element B, wherein the stepped planetary gear set SP is arranged axially adjacent to the first switching element A. This makes the drive device compact.

3 shows a second embodiment of a drive device according to the invention. The drive device according to 3 essentially corresponds to the drive device according to 2 , whereby the difference between these two embodiments lies in the design of the four switching elements A, B, C, D. In the present case, the first switching element A and the second switching element B are combined to form a common first double switching element DS1, with the third switching element C and the fourth switching element D being combined to form a common second double switching element DS2. The first double switching element DS1 is actuated, for example, by a first actuator, not shown, with the second double switching element DS2 being actuated, for example, by a second actuator, not shown. Alternatively, the switching elements can be actuated using a shift drum with two shift forks. Advantageous in this embodiment compared to the embodiment according to 2 is that the compulsory sequential walking sequence is no longer necessary. In other words, for example, you can shift directly from first gear to third gear. Otherwise, the exemplary embodiment corresponds to 3 according to the exemplary embodiment 2 , which is referred to.

4 shows a third embodiment of a drive device according to the invention. The drive device according to 4 essentially corresponds to the drive device according to 2 , with a difference between these two embodiments being the arrangement of a differential 3 on the transmission output shaft 2. The differential 3 has a differential input 4 and two differential output shafts 5, 6, the differential input 4 being connected to the transmission output shaft 2 in a rotationally fixed manner. Furthermore, the differential 3 is arranged on the first axis of rotation R1, with the transmission input shaft 1 and the transmission output shaft 2 being designed as hollow shafts, and with the first differential output shaft 5 extending axially through the planetary gear and the electric machine EM. The differential 3 is designed here as a bevel gear differential. The bevel gear differential has two wheel-side output elements, which are designed as a first output gear 3a and a second output gear 3b. The driven wheels 3a, 3b each mesh with a compensating element 3c, 3d. The compensating elements 3c, 3d are rotatably mounted about their own axis on a differential input 4 designed as a differential cage. The first driven gear 3a is non-rotatably connected to the first differential output shaft 5 and the second driven gear 3b is non-rotatably connected to the second differential output shaft 6. The differential carrier is connected to the transmission output shaft 2 in a rotationally fixed manner. Furthermore, the third and fourth switching elements C, D are arranged radially within the electrical machine EM and thus protrude axially into the electrical machine EM. This makes the drive unit axially more compact. Alternatively, only the fourth switching element D can be arranged radially within the electrical machine EM, i.e. overlap axially with the electrical machine EM.

According to an axial sequence, the second switching element B is arranged axially adjacent to the third switching element C and the electric machine EM, wherein the first switching element A is arranged axially adjacent to the second switching element B, wherein the stepped planetary gear set SP is arranged axially adjacent to the first switching element A is, wherein the differential 3 is arranged axially adjacent to the stepped planetary gear set SP. As a result, the drive device is designed to be compact. Otherwise, the exemplary embodiment corresponds to 4 according to the exemplary embodiment 2 , which is referred to.

5 shows a fourth embodiment of a drive device according to the invention. The drive device according to 5 essentially corresponds to the drive device according to 4 , the difference between these two embodiments being the arrangement of a planetary gear set P3. The drive device therefore has the stepped planetary gear set SP and the planetary gear set P3, which is designed as a minus planetary gear set and has the elements sun gear shaft SR3, ring gear shaft HR3 and web shaft ST3. A plurality of planet gears are rotatably arranged on the web shaft ST3 of the planetary gear set P3, each planet gear meshing with the sun gear shaft SR3 and the ring gear shaft HR3 of the planetary gear set P3. The first element of the planetary gear set P3 is designed as a sun gear shaft SR3 and is connected in a rotationally fixed manner to the second ring gear shaft HR2 of the stepped planetary gear set SP. The second element of the planetary gear set P3 is designed as a ring gear shaft HR3 and is connected in a rotationally fixed manner to the housing G of the planetary gear. The third element of the planetary gear set P3 is designed as a web shaft ST3 and is connected to the transmission output shaft 2 in a rotationally fixed manner. The ring gear shaft HR2 of the stepped planetary gear set SP is therefore indirectly connected to the transmission output shaft 2 via the planetary gear set P3, the planetary gear set P3 being arranged axially between the stepped planetary gear set SP and the differential 3. Otherwise, the exemplary embodiment corresponds to 5 according to the exemplary embodiment 4 , which is referred to.

6 shows a fifth embodiment of a drive device according to the invention. The drive device according to 6 essentially corresponds to the drive device according to 5 , whereby the difference between these two embodiments lies in the connection of the planetary gear set P3. In the present case, the ring gear shaft HR3 of the planetary gear set P3 is connected in a rotationally fixed manner to the second ring gear shaft HR2 of the stepped planetary gear set SP, the sun gear shaft SR3 of the planetary gear set P3 being connected in a rotationally fixed manner with the housing G of the planetary gear. The first element of the planetary gear set P3 is therefore designed as a ring gear shaft HR3 and is connected in a rotationally fixed manner to the second ring gear shaft HR2 of the stepped planetary gear set SP. Furthermore, the second element of the planetary gear set P3 is designed as a sun gear shaft SR3 and is connected in a rotationally fixed manner to the housing G of the planetary gear. The third element of the planetary gear set P3 is designed as a web shaft ST3 and is connected to the transmission output shaft 2 in a rotationally fixed manner. The second ring gear shaft HR2 of the stepped planetary gear set SP is therefore indirectly connected to the transmission output shaft 2 via the planetary gear set P3. Otherwise, the exemplary embodiment corresponds to 6 according to the exemplary embodiment 5 , which is referred to.

7 shows a sixth embodiment of a drive device according to the invention. The drive device according to 7 essentially corresponds to the drive device according to 4 , with a difference between these two embodiments being the arrangement of the differential 3. In the present case, the differential 3 is arranged on a second axis of rotation A2, which is designed axially parallel to the first axis of rotation A1, the differential input 4 being connected to the transmission output shaft 2 via a spur gear stage 7. The two differential output shafts 5, 6 are therefore arranged axially parallel to the planetary gear and the electric machine EM, whereby the drive device is designed to be more compact in the axial direction and a higher output ratio is made possible. The spur gear stage 7 consists of a first fixed gear F1, which is arranged on the first rotation axis A1 and is connected in a rotationally fixed manner to the transmission output shaft 2, and a second fixed gear F2, which is arranged on the second rotation axis A2 and is connected in a rotationally fixed manner to the differential input 4. The differential 3 is designed as a bevel gear differential, with the second fixed gear F2 advantageously being designed as a toothing on the differential carrier. Using the diameters of the fixed gears F1, F2, not only a translation of the spur gear stage 7 can be adjusted, but also the center distance between the two rotation axes A1, A2. Otherwise, the exemplary embodiment corresponds to 7 according to the exemplary embodiment 4 , which is referred to.

8th shows a seventh embodiment of a drive device according to the invention. The Drive device according to 8th essentially corresponds to the drive device according to 7 , with a difference between these two embodiments being the arrangement of an intermediate shaft 10. In the present case, the differential 3 is arranged on the second axis of rotation A2, which is designed axially parallel to the first axis of rotation A1, with the intermediate shaft 10 being arranged on a third axis of rotation A3, which is designed axially parallel to the first and second axes of rotation A1, A2. The differential input 4 is connected to the intermediate shaft 10 via a first spur gear stage 8, the intermediate shaft 10 being connected to the transmission output shaft 2 via a second spur gear stage 9. The two differential output shafts 5, 6 are arranged axially parallel to the planetary gear, to the electrical machine EM and to the intermediate shaft 10, whereby the drive device is designed to be more compact in the axial direction and a higher output ratio is made possible.

The first spur gear stage 8 consists of a first fixed gear F11, which is arranged on the third axis of rotation A3 and is connected in a rotationally fixed manner to the intermediate shaft 10, and a second fixed gear F12, which is arranged on the second axis of rotation A2 and is connected in a rotationally fixed manner to the differential input 4. The differential 3 is designed as a bevel gear differential, with the second fixed gear F12 of the first spur gear stage 8 advantageously being designed as a toothing on the differential cage. Not only a translation of the first spur gear stage 8 can be adjusted via the diameter of the fixed gears F11, F12, but also the center distance between the second and third rotation axes A2, A3. The second spur gear stage 9 consists of a first fixed gear F21, which is arranged on the third axis of rotation A3 and is connected in a rotationally fixed manner to the intermediate shaft 10, and a second fixed gear F22, which is arranged on the first axis of rotation A1 and is connected in a rotationally fixed manner to the transmission output shaft 2. Not only a translation of the second spur gear stage 9 can be adjusted via the diameter of the fixed gears F21, F22, but also the center distance between the first and third rotation axes A1, A3. Otherwise, the exemplary embodiment corresponds to 8th according to the exemplary embodiment 7 , which is referred to.

9 shows an eighth embodiment of a drive device according to the invention. The drive device according to 9 essentially corresponds to the drive device according to 4 , whereby a difference between these two embodiments lies in the design of the differential 3. In the present case, the differential 3 is designed as an integral differential with a first planetary gear set 30 and a second planetary gear set 40, the integral differential increasing the final gear ratio and enabling a differential function. The two planetary gear sets 30, 40 can be arranged either axially next to one another or radially one above the other, i.e. radially stacked, depending on the requirements of the integral differential, in particular the translation of the integral differential to be realized. In the present case, the planetary gear sets 30, 40 are arranged radially one above the other, thereby saving axial installation space. A sun gear 31 of the first planetary gear set 30 is designed as an input shaft of the integral differential and is connected in a rotationally fixed manner to the transmission output shaft 2. The output on the integral differential takes place via the two differential output shafts 5, 6, with a web shaft 33 of the first planetary gear set 30 being connected in a rotationally fixed manner to the first differential output shaft 5, with a ring gear 42 of the second planetary gear set 40 being connected in a rotationally fixed manner with the second differential output shaft 6. The sun gear 41 of the second planetary gear set 40 is designed to be non-rotatable with the ring gear 32 of the first planetary gear set 30 and in the present case is designed as an intermediate gear with internal teeth and external teeth. The web shaft 43 of the second planetary gear set 40 carries a plurality of planet gears 44, which mesh with the sun gear 41 and the ring gear 42, and is connected to the housing G in a rotationally fixed manner. Furthermore, the web shaft 33 of the first planetary gear set 30 carries a plurality of planetary gears 34 which mesh with the sun gear 31 and the ring gear 32.

By means of the first planetary gear set 30, a first output torque can be transferred to the first differential output shaft 5. A supporting torque of the first planetary gear set 30, which acts in the opposite direction to the first output torque, is transferred to the second planetary gear set 40 and is convertible in the second planetary gear set 40 in such a way that a second output torque corresponding to the first output torque can be transferred to the second differential output shaft 6. In other words, a drive power fed in via the sun gear 31 of the first planetary gear set 30 is distributed to the two differential output shafts 5, 6 by means of the integral differential. In the present case, the first differential output shaft 5 extends through the planetary gear and the electric machine EM. The second differential output shaft 6 extends away from the driving device in the opposite direction. Otherwise, the exemplary embodiment corresponds to 9 according to the exemplary embodiment 4 , which is referred to.

Reference symbols

1

Transmission input shaft

2

Transmission output shaft

3

differential

3a

first driven gear

3b

second driven gear

3c

first compensating element

3d

second compensating element

4

Differential input

5

Differential output shaft

6

Differential output shaft

7

Spur gear stage

8th

first spur gear stage

9

second spur gear stage

10

Intermediate shaft

30

first planetary gear set of the integral differential

31

sun gear

32

ring gear

33

Bridge shaft

34

Planetary gear

40

second planetary gear set of the integral differential

41

sun gear

42

ring gear

43

Bridge shaft

44

Planetary gear

G

Housing

SP

Stepped planetary gear set

SR1

first sun gear shaft

SR2

second sun gear shaft

HR1

first ring gear shaft

HR2

second ring gear shaft

ST

Bridge shaft

Z1

first gear

Z2

second gear

P3

Planetary gear set

SR3

sun gear shaft

HR3

ring gear shaft

ST3

Bridge shaft

100

vehicle

101

first drive axle

102

second drive axle

R1

wheel

R2

wheel

R3

wheel

R4

wheel

E.M

electric machine

F1

first fixed gear

F2

second fixed gear

Q11

first fixed gear

F12

second fixed gear

F21

first fixed gear

F22

second fixed gear

A

first switching element

b

second switching element

C

third switching element

D

fourth switching element

DS1

Double switching element

DS2

Double switching element

SM

switching sleeve

A1

first axis of rotation

A2

second axis of rotation

A3

third axis of rotation

QUOTES INCLUDED IN THE DESCRIPTION

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

Cited patent literature

• WO 2014139744 A1 [0002]

Claims (14)

Electric drive device for a vehicle (100), comprising a single electric machine (EM), which is connected to a switchable planetary gear via a transmission input shaft (1), the planetary gear having a first switching element (A) for switching a first gear, a second switching element (B) for shifting a second gear, a third shifting element (C) for shifting a third gear, a fourth shifting element (D) for shifting a fourth gear and a stepped planetary gear set (SP) with a first sun gear shaft (SR1), a second sun gear shaft ( SR2), a first ring gear shaft (HR1), a second ring gear shaft (HR2) and a web shaft (ST) with a plurality of stepped planetary gears rotatably arranged thereon, a first gear (Z1) of the respective stepped planetary gear being connected to the first sun gear shaft (SR1) and the first The ring gear shaft (HR1) of the stepped planetary gear set (SP) is in tooth mesh and is non-rotatably connected to a second gear (Z2) of the respective stepped planetary gear, the second gear (Z2) of the respective stepped planetary gear being connected to the second sun gear shaft (SR2) and the second ring gear shaft (HR2 ) of the stepped planetary gear set (SP) is in mesh, wherein the first ring gear shaft (HR1) of the stepped planetary gear set (SP) can be connected in a rotationally fixed manner to a housing (G) by means of the first switching element (A), wherein the web shaft (ST) of the stepped planetary gear set (SP) can be connected in a rotationally fixed manner to the housing (G) by means of the second switching element (B), wherein the first sun gear shaft (SR1) of the stepped planetary gear set (SP) can be connected in a rotationally fixed manner to the housing (G) by means of the third switching element (C), wherein the first sun gear shaft (SR1) of the stepped planetary gear set (SP) can be connected in a rotationally fixed manner to the transmission input shaft (1) by means of the fourth switching element (D), wherein the second sun gear shaft (SR2) of the stepped planetary gear set (SP) is connected in a rotationally fixed manner to the transmission input shaft (1). , wherein the second ring gear shaft (HR2) of the stepped planetary gear set (SP) is at least indirectly connected to a transmission output shaft (2), wherein at least the transmission input shaft (1), the transmission output shaft (2) and the switchable planetary gear are arranged on a common first axis of rotation (A1). Electric drive device according to Claim 1 , whereby the four switching elements (A, B, C, D) can be actuated by a single actuator using a single switching sleeve (SM). Electric drive device according to Claim 1 , wherein the first switching element (A) and the second switching element (B) are combined to form a common first double switching element (DS1), wherein the third switching element (C) and the fourth switching element (D) are combined to form a common second double switching element (DS2). are trained. Electric drive device according to one of the preceding claims, wherein all four switching elements (A, B, C, D) are designed as positive switching elements. Electric drive device according to one of the preceding claims, wherein the electric machine (EM) is arranged on the common first axis of rotation (A1). Electrical drive device according to one of the preceding claims, wherein at least the third and fourth switching elements (C, D) are arranged radially within the electrical machine (EM). Electric drive device according to one of the preceding claims, further comprising a planetary gear set (P3) arranged on the first axis of rotation (A1) with the elements sun gear shaft (SR3), ring gear shaft (HR3) and web shaft (ST3), wherein a first element of the planetary gear set (P3) is connected in a rotationally fixed manner to the second ring gear shaft (HR2) of the stepped planetary gear set (SP), a second element of the planetary gear set (P3) being connected in a rotationally fixed manner to the housing (G), a third element of the planetary gear set (P3) being connected to the transmission output shaft (2) is connected in a rotationally fixed manner. Electric drive device according to one of the preceding claims, further comprising a differential (3) with a differential input (4) and two differential output shafts (5, 6), the differential input (4) being at least indirectly connected to the transmission output shaft (2). Electric drive device according to Claim 8 , wherein the differential (3) is arranged on the first axis of rotation (A1), wherein the transmission input shaft (1) and the transmission output shaft (2) are designed as hollow shafts, and one of the two differential output shafts (5, 6) extends axially through the planetary gear extends. Electric drive device according to Claim 8 , wherein the differential (3) is arranged on a second axis of rotation (A2), which is axially parallel to the first axis of rotation (A1), the differential input (4) via a Spur gear stage (7) is connected to the transmission output shaft (2). Electric drive device according to Claim 8 , wherein the differential (3) is arranged on a second axis of rotation (A2), which is axially parallel to the first axis of rotation (A1), wherein an intermediate shaft (10) is arranged on a third axis of rotation (A3), which is axially parallel to the first and second Rotation axis (A1, A2) is formed, the differential input (4) being connected to the intermediate shaft (10) via a first spur gear stage (8), the intermediate shaft (10) being connected to the transmission output shaft (2) via a second spur gear stage (9). connected is. Electric drive device according to one of the Claims 9 until 11 , whereby the differential (3) is designed as a bevel gear differential. Electric drive device according to one of the Claims 9 until 11 , whereby the differential (3) is designed as an integral differential. Vehicle (100) with a drive device according to one of the preceding claims.

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