Drive arrangement for a vehicle

Abstract

The proposal relates to a drive arrangement (10) for a vehicle comprising a first planetary gear (P1) with at least three rotatable gear elements (1a; 2a; 3a) and a second planetary gear (P2) with at least three rotatable gear elements (1b; 2b; 3b), wherein a first gear element (1a) of the first planetary gear (P1) is connected in a rotationally fixed manner to a first output shaft (A1) of the drive arrangement (10), wherein a first gear element (1b) of the second planetary gear (P2) is connected in a rotationally fixed manner to a second output shaft (A2) of the drive arrangement (10), wherein a second gear element (2a) of the first planetary gear (P1) is connected in a rotationally fixed manner to a second gear element (2b) of the second planetary gear (P2), and wherein a third gear element (3a) of the first planetary gear (P1) is connected in a rotationally fixed manner to a drive shaft (A) of the drive arrangement (10).To implement a connect and disconnect function, it is proposed to provide a switching element (S) by means of which a third gear element (3b) of the second planetary gear (P2) can be coupled in a rotationally fixed manner to a housing (G) of the drive arrangement (10) and can be decoupled from the housing (G), so that in the decoupled state the first planetary gear (P1) and the second planetary gear (P2) can rotate in a block.

Description

Prior ArtIn the related art, electric drive assemblies for, for example, electric vehicles or hybrid vehicles are implemented in various configurations. Typically, drive assemblies including an electric machine (E-machine), an inverter, and a transmission are sold as a so-called E-axis. The transmission generally contains a differential function, by means of which a torque can be transmitted to two output shafts of the vehicle. It is possible to design the two output shafts coaxially or offset axially with respect to the shaft of the electric machine. Coaxial arrangements, in which the axis of rotation of an output shaft of the electric machine is arranged parallel to the axis of rotation of the two output shafts, can be realized, for example, with planetary gears or spur gear gears, wherein planetary gears offer some advantages with regard to the installation space and the power density. The transmission can be connected to the output shaft of the electric machine, for example, in an axial extension thereof, without requiring any outward radial installation space. By a suitable combination of two planetary gears or a gear with two planetary stages, a differential function can also be realized without additional components being required for this purpose, such as a motor vehicle differential with differential cage and differential gears.From U.S. Pat. No. 5,845,732 A, for example, a drive arrangement for a vehicle is known, which has a first planetary gear with at least three rotatable gear elements and a second planetary gear with at least three rotatable gear elements. A first transmission element of the first planetary gear is connected in a rotationally fixed manner to a first output shaft and a first transmission element of the second planetary gear is connected in a rotationally fixed manner to a second output shaft of the drive arrangement. A second transmission element of the first planetary gear set is connected in a rotationally fixed manner to a second transmission element of the second planetary gear set, as a result of which the two planetary gear sets are coupled. A third transmission element of the first planetary gear is connected in a rotationally fixed manner to a drive shaft of the drive arrangement. U.S. Pat. No. 5,845,732 A discloses numerous exemplary embodiments with different variations, in which in each case different transmission elements of the first planetary transmission are coupled to different transmission elements of the second planetary transmission in order to achieve a speed and torque equality on both output shafts. In all embodiments, a transmission element of the second planetary gear is always connected fixed to the housing in order to be able to support the torque input via the drive shaft at all times.Furthermore, DE 10 2021 207 998 A1 discloses a drive arrangement for a vehicle having a differential function, which, in addition to two coupled planetary gears or planetary stages, which are each coupled to one of two output shafts of a vehicle, additionally has a shift element which provides three shift positions: closed torque flow, interrupted torque flow and blocked torque flow (parking lock). With this drive arrangement, an interruption of the torque flow from the electric machine to the output shafts (so-called "disconnect" function) is possible in order to achieve a minimization of the drag losses and / or a limitation of the maximum rotational speed of the electric machine. In all the embodiments of DE 10 2021 207 998 A1, the planet carrier of the first planetary gear is always fixedly connected to the stator of the electric machine fixed to the housing.Disclosure of the InventionThe invention relates to a drive arrangement for a vehicle comprising a first planetary gear with at least three rotatable gear elements and a second planetary gear with at least three rotatable gear elements, wherein a first gear element of the first planetary gear is connected in a rotationally fixed manner to a first output shaft of the drive arrangement, wherein a first gear element of the second planetary gear is connected in a rotationally fixed manner to a second output shaft of the drive arrangement, wherein a second gear element of the first planetary gear is connected in a rotationally fixed manner to a second gear element of the second planetary gear, wherein a third gear element of the first planetary gear is connected in a rotationally fixed manner to a drive shaft of the drive arrangement. According to the invention, it is provided that a shifting element is provided, by means of which a third transmission element of the second planetary gearing can be coupled to a housing of the drive arrangement in a rotationally fixed manner and can be decoupled from the housing.In the context of the present application, a housing is understood to mean a component installed in a stationary manner in a vehicle, which component moves itself neither in translation nor in rotation relative to the vehicle. The housing can be, for example, a transmission housing or a component fastened to the transmission housing. However, it can also be another component that is stationary relative to the vehicle.A coaxial arrangement of rotatable elements is understood to mean an arrangement in which the rotatable elements rotate about the same axis of rotation during a rotation or rotation.A planetary gear or a planetary stage with at least three rotatable gear elements is understood to mean a gear or partial gear which has as gear elements at least one sun gear, a ring gear and a planetary carrier with at least one set of planetary gears which are in engagement with tooth flanks which mesh with one another in pairs both with the sun gear and with the ring gear, regardless of whether individual gear elements of the first planetary gear are structurally combined with gear elements of the second planetary gear or not. Thus, for example, it is possible in particular for a ring gear with internal toothing to simultaneously have external toothing and to serve as the sun gear of a further planetary gearing. It is also possible for a planet carrier to have two sets of planet gears, wherein the planet gears of the first planetary gear set mesh with the gears of the second planetary gear set and the planet gears of the first planetary gear set mesh with the sun gear, while the planet gears of the second planetary gear set mesh with the ring gear. In the context of the application, a planet carrier with the planetary gears arranged thereon is understood as a transmission element rotatable about the axis of the planetary carrier, wherein the planet gears can naturally rotate relative to the associated planetary carrier.A differential function is understood to mean a transmission function which has or simulates the function of a conventional differential. A transmission with differential function does not have to have a conventional differential with differential gears, ring gears and differential cage and can also comprise, for example, two planetary gears coupled to one another. The purpose of the differential function is to set the most equal possible output torque on the two output shafts or the wheels connected thereto. The differential function enables both the parallel drive of two output shafts with the same rotational speed and a rotation of the two output shafts with different rotational speeds or rotational speeds relative to one another (for example in the case of a slip).A revolution in the block is understood to mean a state in which all the transmission elements involved in the block rotate about the same common axis at the same or almost the same rotational speed or rotational speed and no relative movements occur between the transmission elements. The drive arrangement according to the invention enables all gear elements of the two planetary gear sets to rotate together with the input shaft and the two output shafts in the block in the "disconnect" state, wherein all these elements can rotate at the same or almost the same rotational speed about the axis of the two output shafts and the input shaft coaxial thereto with the rotor of the electric machine. Since the drive arrangement according to the invention also has a differential function, a state in which the first planetary gear and the second planetary gear initially rotate together with the input shaft and the output shafts in the block does not exclude that, for example, by the subsequent initiation of a cornering of the vehicle or by a suddenly occurring slip of a wheel on one of the output shafts, a relative movement between the output shafts can start, which causes some transmission elements to begin to rotate relative to one another and the block rotation is thus at least temporarily canceled.A "disconnect" state is understood to mean a state in which no torque is transmitted from the drive shaft of the drive arrangement to the output shafts. In contrast, in a "connect" state, torque can be transmitted from the input shaft to the output shafts.A rotationally fixed connection of two transmission elements is understood to mean a mechanically rigid connection of the two transmission elements, such that the two transmission elements cannot rotate relative to one another. However, the rotationally fixed transmission elements can rotate about a common axis.Advantages of the InventionThe invention describes a compact drive arrangement which enables a coaxial construction of a transmission in the drive arrangement, wherein a torque ratio and a differential function are advantageously provided and at the same time a "connect" and "disconnect" state can be set.In the "disconnect" state, when the coupling between the third transmission element of the second planetary transmission and the housing is canceled, the drag losses can be minimized. If, for example, the vehicle is to roll when the electric machine is deactivated or else is to be driven by a second drive axle, then the first output shaft and the second output shaft can rotate at the same rotational speed in accordance with the wheel rotational speed of the wheels of the moving vehicle. As a result of the torque support of the third transmission element of the second planetary gear mechanism on the housing being canceled by means of the shifting element, the two planetary gear mechanisms can rotate together with the input shaft and the two output shafts at the same rotational speed in the block in this state, as has already been explained. As a result, advantageously no losses arise in the toothed engagements and the planetary gear bearings of the two planetary gear sets. If the rotor of the electric machine is connected to the drive shaft in a rotationally fixed manner, then the rotor and its bearing also rotates at this wheel speed and therefore only generates low losses, since the block circulation takes place at the wheel speed or the rotational speed of the output shafts. Depending on the design of the electric machine, the electromagnetic losses in the electric machine can also be reduced due to the low rotor rotational speed in the disconnect state, so that the drag losses are substantially only influenced by the bearing friction of the rotor shaft and of the output shafts.When the rotor shaft is completely stopped when the vehicle is moving, there is usually the risk of damage to the standstill at the rotor shaft bearings due to vibrations introduced by the vehicle. Since, by means of the present invention, in the "disconnect" state, the bearings of the rotor shaft always rotate at the wheel speed, damage to standstill at the rotor shaft bearings can advantageously be prevented.In the above-described prior art driving arrangements, it is usually necessary to accelerate a rotor of the electric machine coupled to the input shaft to a synchronous speed as quickly as possible when the vehicle is running and the electric machine is activated to transmit torque to the output shafts. In this case, the rotor is accelerated to the synchronous rotational speed with a very high rotational speed gradient. Damage to the bearings can occur if the rolling bodies of the bearings do not roll cleanly under high rotational speed gradients because of their inertia. In the drive arrangement according to the invention, the rotor of the electric machine does not have to accelerate from zero to the synchronous rotational speed during the transition from the "disconnect" state to the "connect" state, but only from the wheel rotational speed (n_rad) of the wheels of the vehicle coupled to the output shafts to the synchronous rotational speed (n_sync=n_rad*i_transmission), wherein i_transmission is the transmission ratio of the transmission. This advantageously reduces, on the one hand, the time interval and the energy consumption for the synchronization. In addition, in the solution according to the invention, an elasto-hydrodynamic lubrication film is also maintained in the "disconnect" state in the bearings, which reduces the risk of wear or other damage during synchronization.Furthermore, the installation space of the transmission can advantageously be reduced by the coaxial arrangement.Advantageous embodiments and further developments of the invention make possible the features contained in the dependent claims.The first planetary gear can advantageously have at least one first sun gear, at least one first planetary carrier with first planetary gears which mesh with the first sun gear, and at least one first ring gear which meshes with the first planetary gears, while the second planetary gear can have at least one second sun gear, at least one second planetary carrier with second planetary gears which mesh with the second sun gear, and at least one second ring gear, wherein the second ring gear either meshes directly with the second planetary gears or meshes with third planetary gears which are arranged on the second planetary carrier and in turn mesh with the second planetary gears.In an advantageous exemplary embodiment, it is provided that the first planet carrier, as the first transmission element of the first planetary gear mechanism, is connected to the first output shaft of the drive arrangement in a rotationally fixed manner. The first sun gear can be connected in a rotationally fixed manner as the third transmission element of the first planetary gear mechanism to the drive shaft of the drive arrangement, while the first ring gear as the second transmission element of the first planetary gear mechanism is connected in a rotationally fixed manner to the second sun gear as the second transmission element of the second planetary gear mechanism. This construction of the drive arrangement can be implemented easily and inexpensively as a coaxial construction.In a first embodiment of this exemplary embodiment, the second planet carrier as the first transmission element of the second planetary gear mechanism can be connected to the second output shaft in a rotationally fixed manner and the second ring gear as the third transmission element of the second planetary gear mechanism can be coupled to the housing of the drive arrangement in a rotationally fixed manner by means of the shift element or can be decoupled from the housing.In a second embodiment of this exemplary embodiment, alternatively, the second ring gear as the first transmission element of the second planetary gear mechanism can be connected to the second output shaft in a rotationally fixed manner, and the second planetary carrier as the third transmission element of the second planetary gear mechanism can be coupled to the housing of the drive arrangement in a rotationally fixed manner by means of the shift element or can be decoupled from the housing.The drive arrangement according to the invention advantageously enables a full differential function in that the first planetary gear and the second planetary gear are coupled to one another in such a way that rotation of the first output shaft at a first rotational speed and rotation of the second output shaft at a second rotational speed different from the first rotational speed are possible.Brief Description of the DrawingsPossible embodiments of the invention are explained below with reference to the attached figures. In the drawing, the following are shown: FIG. 1 shows a schematic illustration of a first exemplary embodiment of the drive arrangement according to the invention in a "connect" state, FIG. 2 shows the drive arrangement from FIG. 1 in the "disconnect" state, FIG. 3 shows a schematic illustration of a second exemplary embodiment of a drive arrangement according to the invention in a "connect" state, FIG. 4 shows a schematic illustration of a third exemplary embodiment of a drive arrangement according to the invention in a "connect" state.Embodiments of the InventionFIG. 1 discloses a schematic illustration of a drive arrangement 10 according to the invention in a "connect" state. The drive arrangement 10 can be installed, for example, in a vehicle, not shown, and drive the latter. The drive arrangement 10 can have an electric machine E, a transmission which comprises a first planetary gear P 1 and a second planetary gear P 2 or two planetary stages, and two output shafts A 1, A 2 which can transmit a torque to a vehicle wheel, which is not shown.The drive arrangement 10 further comprises a housing G, in particular a transmission housing, which can be installed in a stationary manner in a vehicle, for example. The drive arrangement 10 has a drive shaft A, which is preferably connected to a rotor RO of the electric machine E of the drive arrangement 10 in a rotationally fixed manner. The electric machine E also has a stationary stator ST. The input shaft A functions as an input shaft of a transmission which comprises the two planetary gear sets P 1 and P 2. The first planetary gear P 1 has a first sun gear S 1, a first planetary carrier PT 1 having first planetary gears PR 1, which mesh with the first sun gear S 1, and a first ring gear H 1 meshing with the first planetary gears PR 1. The second planetary gear P 2 has a second sun gear S 2, a second planetary carrier PT 2 with second planetary gears PR 2, which mesh with the second sun gear S 2, and at least one second ring gear H 2, wherein the second ring gear H 2 in FIGS. 1 and 2 meshes with third planetary gears PR 3 arranged on the second planetary carrier PT 2, which in turn mesh with the second planetary gears PT 2.As is illustrated in FIG. 1, the first planet carrier PT 1, for example, can be connected in a rotationally fixed manner as the first transmission element 1 aof the first planetary transmission P 1 to the first output shaft A 1 of the drive arrangement. The first sun gear S 1 can be connected, for example, as the third transmission element 3 aof the first planetary gear P 1 to the drive shaft A of the drive arrangement 10 in a rotationally fixed manner. The first ring gear H 1 can be connected, for example, as the second transmission element 2 aof the first planetary transmission P 1 to the second sun gear S 2 as the second transmission element 2 bof the second planetary transmission P 2 in a rotationally fixed manner. In the exemplary embodiment shown in FIG. 1, the second planetary carrier PT 2 as the first transmission element 1 bof the second planetary gear set P 2 is connected to the second output shaft A 2 in a rotationally fixed manner, while the second ring gear H 2 as the third transmission element 3 bof the second planetary gear set P 2 is coupled to the housing G of the drive arrangement 10 in a rotationally fixed manner by means of a shift element S. The shifting element S makes it possible, for example, to shift an external toothing Z or a claw engagement of the second ring gear H 2 into positive engagement with the stationary component on the housing G. In this case, the shifting element S can be designed, for example, as a claw clutch and, by axial displacement from the position shown in FIG. 1 into the position shown in FIG. 2, can cancel the positive engagement in the external toothing Z of the second ring gear H 2.In the position of the shift element S shown in FIG. 1, the second ring gear H 2 is supported on the housing G and is connected thereto in a rotationally fixed manner. A torque introduced from the electric machine E onto the input shaft A is therefore transmitted by the first planetary gear P 1 and the second planetary gear P 2 coupled thereto and transmitted to the first output shaft A 1 and the second output shaft A 2. In this case, the transmission elements of the first planetary gear P 1 and the transmission elements of the second planetary gear P 2 can preferably be designed such that the first output shaft A 1 and the second output shaft A 1 rotate at the same rotational speed. For example, when a slip occurs at one of the vehicle wheels connected to the first output shaft A 1 or the second output shaft A 2, the first output shaft A 1 may rotate at a different rotational speed relative to the second output shaft A 2, as is easily seen in FIG. 1. That is, the two planetary gear sets P 1 and P 2 coupled to each other inherently also have a differential function.FIG. 2 shows the drive arrangement 10 from FIG. 1 in the "disconnect" state in which the switching element S releases the second ring gear H 2. That is, the second ring gear H 2 is decoupled from the housing G. As a result, the second ring gear H 2 is now not supported on the housing G and can rotate relative thereto. If, in this state, a torque were still transmitted from the electric machine E to the input shaft A, this torque would no longer be transmitted to the first output shaft A 1 and the second output shaft A 2. The drive train is thus interrupted and the "disconnect" state is set. If, for example, the electric machine is now additionally deactivated during straight-ahead travel of the vehicle and no input torque is transmitted to the drive shaft A, the two output shafts A 1, A 2 can rotate together with the planetary gears P 1 and P 2 and the drive shaft A with the rotor RO in the block if the vehicle rolls or were driven by a second drive shaft, not shown, as can be easily visualized with reference to FIG. 2. Without the switching element S and the decoupling of the second ring gear H 2 from the housing G, this would not be possible.FIG. 3 shows a second exemplary embodiment of a drive arrangement 10 according to the invention in a "connect" state. Identical parts are provided with identical reference numerals. In the following, the difference from the first exemplary embodiment in FIGS. 1 and 2 will be discussed with regard to the center of gravity. In the drive arrangement in FIG. 3, the second planetary gear P 2 has, similar to FIG. 1, a second sun gear S 2, which is coupled to the first ring gear H 1 of the first planetary gear P 1 in a rotationally fixed manner via a shaft connection. However, the second planet carrier PT2 has only one set of planet gears PR2 which mesh with both the second sun gear S2 and the second ring gear H2. In contrast to the exemplary embodiment from FIGS. 1 and 2, however, in the second exemplary embodiment in FIG. 3, the second ring gear H 2 of the second planetary gear set P 2 is connected to the second output shaft A 2 in a rotationally fixed manner as the second gear element 1 bof the second planetary gear set P 2. As a further difference, the second planetary carrier PT 2 now has an external toothing Z or claws, which can be positively locked by means of the shifting element S, so that the planetary carrier PT 2 as the third transmission element 3 bof the second planetary transmission P 2 can be coupled to the housing G in a rotationally fixed manner via the axially displaceable shifting element S and can be decoupled therefrom. In this exemplary embodiment, too, decoupling the third transmission element 3 bof the second planetary gear P 2 from the housing G ensures that the output shafts A 1 and A 2 can rotate together with the first planetary gear P 1 and the second planetary gear P 2 in a block.FIG. 4 shows a third exemplary embodiment of the drive arrangement 10 according to the invention. In this exemplary embodiment, as in the exemplary embodiment from FIG. 3, the second ring gear H 2 of the second planetary gear set P 2 is connected in a rotationally fixed manner to the second output shaft A 2 as the third gear element 1 bof the second planetary gear set P 2, and the second planetary carrier PT 2 likewise has only one set of planetary gears PR 2 which mesh both with the second sun gear S 2 and with the second ring gear H 2. The second planetary carrier PT 2 also again has an external toothing Z or claws, which can be positively connected to the shift element S in the "connect" state, so that the second planetary carrier PT 2 can be coupled to the housing G again as the third transmission element 3 bof the second planetary transmission P 2 via the axially displaceable shift element S in a rotationally fixed manner and can be decoupled therefrom. Furthermore, as in FIG. 3 and in FIG. 1, the second sun gear S 2 of the second planetary gear set P 2 is coupled rotationally fixedly to the first ring gear H 1 of the first planetary gear set P 1. Unlike in FIGS. 1 and 3, however, this rotationally fixed coupling in FIG. 4 is not effected by a shaft connection, but rather by the fact that the first ring gear H 1 has a toothing on its outer circumference, which toothing forms the second sun gear S 2. The first ring gear H1 and the second sun gear S2 are thus structurally combined to form a toothed ring disc with internal toothing and external toothing. The remaining functionality corresponds to that of FIG. 3.It is understood that within the scope of the present invention illustrated further combinations of the transmission elements 1 a, 2 aand 3 aof the first planetary gear P 1 with the transmission elements 1 b, 2 band 3 bof the second planetary gear P 2 are conceivable, which represent a drive arrangement with the features of the independent claim and which are characterized in that a shifting element S is provided by means of which a third transmission element 3 bof the second planetary gear, which is not connected to the second output shaft A 2 and which is not connected to a transmission element of the first planetary gear P 1 in a rotationally fixed manner, can be coupled to a housing G of the drive arrangement 10 in a rotationally fixed manner and can be decoupled from the housing G.References included in the specificationThis list of documents cited by the applicant has been produced in an automated manner and is only included for the better information of the reader. The list is not part of the German patent application or utility model application. The DPMA does not take any adhesion for any faults or omissions.Patent Literature citedU.S. Pat. No. 5,845,732 A

[0002] DE 10 2021 207 998 A1

[0003]

Claims

Drive arrangement (10) for a vehicle, comprising a first planetary gear (P1) with at least three rotatable gear elements (1a; 2a; 3a) and a second planetary gear (P2) with at least three rotatable gear elements (1b; 2b; 3b), wherein a first gear element (1a) of the first planetary gear (P1) is connected in a rotationally fixed manner to a first output shaft (A1) of the drive arrangement (10), wherein a first gear element (1b) of the second planetary gear (P2) is connected in a rotationally fixed manner to a second output shaft (A2) of the drive arrangement (10), wherein a second gear element (2a) of the first planetary gear (P1) is connected in a rotationally fixed manner to a second gear element (2b) of the second planetary gear (P2), wherein a third transmission element (3a) of the first planetary gearing (P1) is connected to a drive shaft (A) of the drive arrangement (10) in a rotationally fixed manner, characterized in that a shifting element (S) is provided, by means of which a third transmission element (3b) of the second planetary gearing (P2) can be coupled to a housing (G) of the drive arrangement (10) in a rotationally fixed manner and can be decoupled from the housing (G).Drive arrangement according to Claim 1, characterized in that, in a state of the drive arrangement (10) in which no torque of the electric machine (E) acts on the drive shaft (A) and the first output shaft (A1) and the second output shaft (A2) execute a rotational movement at the same rotational speed, and in a switching state of the switching element (S) in which the third transmission element (3b) of the second planetary transmission (P2) is decoupled from the housing (G) of the drive arrangement (10), the first planetary transmission (P1) and the second planetary transmission (P2) rotate together with the drive shaft (A) in the block.Drive arrangement according to Claim 1 or Claim 2, characterized in that the drive arrangement (10) furthermore comprises an electric machine (E) having a rotor (RO) and a stator (ST), the rotor (RO) being coupled to the drive shaft (A) in a rotationally fixed manner.Drive arrangement according to one of the preceding claims, characterized in that the first planetary transmission (P1) has at least one first sun wheel (S1), at least one first planetary carrier (PT1) with first planetary wheels (PR1) which mesh with the first sun wheel (S1), and at least one first ring wheel (H1) which meshes with the first planetary wheels (PR1), and in that the second planetary transmission (P2) has at least one second sun wheel (S2), at least one second planetary carrier (PT2) with second planetary wheels (PR2) which mesh with the second sun wheel (S2), and at least one second ring wheel (H2), wherein the second ring gear (H2) either directly meshes with the second planetary gears (PR2) or meshes with third planetary gears (PR3) arranged on the second planetary carrier (PT2), which in turn mesh with the second planetary gears (PT2).Drive arrangement according to Claim 4, characterized in that the first planet carrier (PT1), as the first transmission element (1a) of the first planetary gearing (P1), is connected to the first output shaft (A1) of the drive arrangement in a rotationally fixed manner.Drive arrangement according to Claim 4 or 5, characterized in that the first sun wheel (S1), as the third transmission element (3a) of the first planetary transmission (P1), is connected to the drive shaft (A) of the drive arrangement (10) in a rotationally fixed manner.Drive arrangement according to one of Claims 4 to 6, characterized in that the first ring gear (H1) as the second transmission element (2a) of the first planetary gearing (P1) is connected in a rotationally fixed manner to the second sun gear (S2) as the second transmission element (2b) of the second planetary gearing (P2).Drive arrangement according to one of Claims 4 to 7, characterized in that the second planet carrier (PT2), as the first transmission element (1b) of the second planetary transmission (P2), is connected to the second output shaft (A2) in a rotationally fixed manner, and in that the second ring gear (H2), as the third transmission element (3b) of the second planetary transmission (P2), can be coupled to the housing (G) of the drive arrangement (10) in a rotationally fixed manner by means of the shift element (S) and can be decoupled from the housing (G).Drive arrangement according to one of Claims 4 to 7, characterized in that the second ring gear (H2) as the first transmission element (1b) of the second planetary gearing (P2) is connected to the second output shaft (A2) in a rotationally fixed manner, and the second planet carrier (PT2) as the third transmission element (3b) of the second planetary gearing (P2) can be coupled to the housing (G) of the drive arrangement in a rotationally fixed manner by means of the shift element (S) and can be decoupled from the housing (G).Drive arrangement according to one of the preceding claims, characterized in that the first planetary gear (P1) and the second planetary gear (P2) are coupled to one another in such a way that rotation of the first output shaft (A1) at a first rotational speed and rotation of the second output shaft (A2) at a second rotational speed different from the first rotational speed are possible in order to achieve a differential function.

Images