Drive device for a working machine

Abstract

Drive device (10) for a working machine, wherein the drive device (10) comprises a first electric machine (EM1) with a first motor shaft (12) configured to provide a first drive power at the first motor shaft (12), a second electric machine (EM2) with a second motor shaft (14) configured to provide a second drive power at the second motor shaft (14), a first drive output shaft (16), a first power take-off shaft (40) and a second power take-off shaft (42), wherein the first motor shaft (12) is mechanically operatively connected to the first drive output shaft (16) by means of a drive transmission (32), and wherein the second motor shaft (14) is mechanically operatively connected to the first power take-off shaft (40) and to the second power take-off shaft (42), wherein the drive transmission (32) comprises an input shaft (34), an output shaft (36), a first planetary gear set (FP1) with a first sun gear (72),a first planet carrier (74) and a first ring gear (76), a second planetary gear set (FP2) with a second sun gear (82), a second planet carrier and a second ring gear (86), a drive shift element (FS), a first brake (B2) and a second brake (B1), wherein the first sun gear (72) is permanently and rotationally fixed to the input shaft (34) of the drive transmission (32), wherein the first planet carrier (74) is permanently and rotationally fixed to the second ring gear (86), wherein the first ring gear (76) can be locked by means of the first brake (B2) of the drive transmission (32), wherein the second sun gear (82) is permanently and rotationally fixed to the input shaft (34) of the drive transmission (32), wherein the second planet carrier (84) is permanently and rotationally fixed to the output shaft (36) of the drive transmission (32),wherein the second ring gear (86) can be locked by means of the second brake (B1) of the drive transmission (32) and wherein the second planetary gear set (FP2) can be locked by means of the drive switching element (FS).

Description

Technical field

[0001] The present invention relates to a drive device for a working machine which has two electric machines. State of the art

[0002] Drive systems for construction machinery must enable efficient and reliable operation under varying soil conditions and work cycles. If the machinery is powered solely by an internal combustion engine, complex, expensive, and bulky mechanical components, and alternatively or additionally hydraulic components, are necessary.

[0003] German patent application DE 10 2013 201 095 A1 describes a multi-scalable transmission system. The transmission system has an input configured to receive torque from a variable-speed drive device and an output coupled to the input. The transmission system also has a selectable clutch coupled between the input and the output. Furthermore, a planetary gear unit is provided, coupled to both the input and the output, and comprising at least one planetary gear set and a brake.

[0004] In WO 2020 / 074 340 A1, a drive train for a working machine is described which has a planetary gearbox and two electric drive motors to replace a drive train with an internal combustion engine.

[0005] US Patent 2010 / 0170732A1 describes a drive system for a working machine, comprising an electric generator and two electric machines. The generator can be driven by a drive motor of the working machine to provide electrical energy for the operation of the two electric machines. Description of the invention

[0006] A first aspect of the invention relates to a drive device for a working machine. A drive device can, for example, form part of a drive train. The working machine can be designed as an agricultural machine, e.g., a tractor, as construction equipment, or as a special-purpose vehicle. Examples of working machines are a wheel loader and a tractor, in which the respective wheels can be driven by a drive power from the drive device. Attachments can typically be mounted on working machines, which can also be driven by the working machine. For this purpose, the working machine can provide a power source.

[0007] The drive device comprises a first electric machine with a first motor shaft. The first electric machine is configured to provide a first drive power at the first motor shaft. The drive device comprises a second electric machine with a second motor shaft. The second electric machine is configured to provide a second drive power at the second motor shaft. Each of the electric machines may, for example, have only one motor shaft. The designation "second motor shaft" serves to identify it as belonging to the second electric machine.

[0008] The electric machines can be configured to convert electrical energy into mechanical energy. Optionally, each electric machine can be equipped for recuperation. An electric machine can be, for example, an asynchronous motor or a synchronous motor. The drive unit includes an energy source, such as a rechargeable battery. This energy source supplies both electric machines with power for their operation. The drive unit can have an associated inverter for each electric machine, which controls the drive power output. Each electric machine in the drive unit can also have its own associated energy source.

[0009] The drive unit has a first drive output shaft. At the first drive output shaft, for example, a portion of the drive power generated by the electric motors can be output, for instance, to an associated drive axle of the machine. The first drive output shaft can, for example, be mechanically connected to a rear axle of the machine. A drive output shaft can, for example, be mechanically connected to the associated drive axle of the machine via an axle differential. Alternatively or additionally, a mechanical connection via bevel gears is also possible. A drive output shaft can form an output shaft of the drive unit. The drive unit can be designed to transmit drive power from the first motor shaft to the first drive output shaft.

[0010] The first engine shaft is mechanically connected to the first drive output shaft by means of a drive transmission. The drive unit can include the drive transmission. The drive transmission can be configured to provide different gear ratios between the first engine shaft and the first drive output shaft. The drive transmission can also be configured to interrupt torque transmission from the first engine shaft to the first drive output shaft, for example, at a specific shift point. This allows for neutral operation.

[0011] The drive unit has a first power take-off (PTO) shaft and a second PTO shaft. Power can be supplied to one PTO shaft. The first PTO shaft can, for example, be a front PTO shaft. The second PTO shaft can be a rear PTO shaft. Implements can be supplied with mechanical power from the machine at each PTO shaft. The drive unit can, for example, be designed to drive the PTO shaft at a substantially constant speed, such as one of two preset PTO speeds. Alternatively or additionally, the drive unit can, for example, be designed to drive the PTO shaft at a variable speed. The drive unit can be designed to selectively disconnect the power transmission to either one or both PTO shafts.

[0012] The second motor shaft can be mechanically connected to both the first and second power take-off (PTO) shafts. For example, in a first switching state, the second motor shaft can only be mechanically connected to the first PTO shaft. Similarly, in a second switching state, the second motor shaft can only be mechanically connected to the second PTO shaft. Finally, in a fourth switching state, the second motor shaft can be mechanically connected to both the first and second PTO shafts. In this fourth switching state, the second electric motor can drive auxiliary units, such as hydraulic pumps, without driving an implement or either PTO shaft.In the fourth switching state, the second electric machine can also, in certain embodiments, alternatively or additionally drive a drive shaft without driving an attachment.

[0013] The drive transmission comprises an input shaft, an output shaft, a first planetary gear set, a second planetary gear set, a drive selector, a first brake, and a second brake. The first planetary gear set includes a first sun gear, a first planet carrier, and a first ring gear. The second planetary gear set includes a second sun gear, a second planet carrier, and a second ring gear. A planetary gear set can be designed as a standard planetary gear set and is designated as such, for example, only for identification purposes. Similarly, each planetary gear set can have only three rotating elements. A planetary gear set has a sun gear, a planet carrier, and a ring gear as rotating elements. The designation, for example, as a second sun gear, serves only to identify it as belonging to the second planetary gear set. Accordingly, the second planetary gear set can, for example, have only one sun gear.One or more planet gears can be rotatably mounted on each planet carrier. Each planet gear set can, for example, be designed as a negative planet gear set. In a negative planet gear set, each planet gear meshes with the sun gear and the ring gear. One or both planet gear sets can also be designed as a positive planet gear set, in which two sets of planet gears are rotatably mounted on the planet carrier. These planet gears then mesh with each other in pairs. One of the planet gears in each pair additionally meshes with the sun gear, and another of the planet gears in each pair additionally meshes with the ring gear. The drive switching element is designed, for example, as a friction-fit switching element. The term "drive switching element" serves to assign a function. Drive switching elements can be designed like other switching elements.A brake in the transmission can be a switching element by means of which a rotating element of a planetary gear set of the transmission can be locked to a stationary component. The two brakes can, for example, be designed as friction-fit switching elements.

[0014] The first sun gear is permanently and non-rotatably connected to the input shaft of the drive unit. The first planet carrier is permanently and non-rotatably connected to the second ring gear, for example, by means of a hollow shaft. The first ring gear can be locked by means of the first brake of the drive unit, for example, by a non-rotatable connection to a stationary component of the drive system. The second sun gear is permanently and non-rotatably connected to the input shaft of the drive unit. The second planet carrier is permanently and non-rotatably connected to the output shaft of the drive unit. The second ring gear can be locked by means of the second brake of the drive unit, for example, by a non-rotatable connection to a stationary component of the drive system. The second planetary gear set can be locked by means of the drive control element.For locking, the drive switching element can be designed to connect two rotating elements of the second planetary gear set in a rotationally fixed manner. In the locked state, all rotating elements of a planetary gear set rotate at the same angular velocity.

[0015] This results in a compact drive transmission that provides three highly efficient gear ratios, making it ideal for construction machinery. The transmission incorporates a high number of brakes, which can be more cost-effective than shift elements that connect two rotating components. This allows the transmission to provide three gear ratios in a particularly cost-effective manner. Furthermore, a wide gear ratio spread can be achieved with minimal radial space requirements. By interlocking the gears, the transmission eliminates gear meshing in the highest speed range, enabling highly efficient operation even under high power demands. The transmission also features a neutral position.

[0016] The drive system takes advantage of the fact that electric motors, compared to those powered solely by an internal combustion engine, allow for more flexible use of the machine's installation space. This enables the machine to have two power take-off (PTO) shafts, with only one or both PTO shafts being driven during operation. This allows for the simultaneous use, or at least the attachment, of two implements. The two implements are then driven, for example, by only the second electric motor. Thus, even with a mechanical design otherwise largely identical to that of a machine powered solely by an internal combustion engine, no additional motor is required to drive the second PTO shaft. An additional power interface for the second PTO shaft can be provided. The drive for both PTO shafts can be integrated into a central drive unit.

[0017] The drive device can have a first power take-off gearbox and, alternatively or additionally, a second power take-off gearbox. A power take-off gearbox can be designed to provide a mechanical connection between a power take-off shaft and an implement, for example, with different gear ratios. This allows the first power take-off shaft to operate at a different speed than the second, even when both shafts are driven simultaneously. Furthermore, this makes it possible to operate the second electric motor at a particularly efficient operating point. For example, each power take-off gearbox can be designed to provide two different gear ratios.

[0018] The drive unit can be designed to be modularly expanded. This allows a standardized drive unit to be adapted to different customer requirements. Examples of modular expansions can be found in the embodiments described below. The modular expansion of the drive unit can be carried out before installation in the machine. In another embodiment, the modular expansion can also be carried out after the drive unit has been installed in the machine.

[0019] If two elements are mechanically connected, they are coupled to each other directly or indirectly in such a way that a movement of one element causes a reaction of the other. For example, a mechanical connection can be provided by a positive-locking or friction-locking connection. In a mechanical connection, one or more spur gear stages can be involved in the drive power transmission. For example, the mechanical connection can correspond to the meshing of corresponding gear teeth of two elements. Further elements, such as one or more spur gear stages, can be provided between the elements.

[0020] A permanently rotationally fixed connection between two elements is understood to be a connection in which the two elements are essentially rigidly coupled to each other in all intended states. This also includes a friction-fit connection, in which intentional or unintentional slippage can occur. Permanently rotationally fixed elements can exist as rotationally fixed individual components or as a single piece.

[0021] A connection between two elements via another element can mean that this additional element is involved in an indirect interaction between the two elements. For example, this element can be positioned in the force flow between these two elements. A connection between two elements via two or more elements can mean that these additional elements are all involved in an indirect interaction between the two elements.

[0022] A switchable connection can, in one state, enable torque transmission between two elements, for example through a rigid coupling, and in another state essentially interrupt this torque transmission. A corresponding switching element can be provided between the two elements for this purpose.

[0023] If torque can be transmitted from one element to another, this may require the actuation of a switching element, for example, to establish a mechanical connection. However, if torque can be transmitted from one element to another, this may also be possible in all intended states of the drive device, i.e., for example, independently of the respective switching states of the individual switching elements.

[0024] A spur gear stage can be single-stage or multi-stage. A single-stage spur gear stage can, for example, have two meshing gears. A two-stage spur gear stage can, for example, have three meshing gears.

[0025] A switching element can be designed, for example, as a friction-fit or positive-fit element. A multi-plate clutch is an example of a friction-fit switching element. A jaw clutch is an example of a positive-fit switching element. A switching element can be closed, for example, by actuation. For instance, a switching element can be actuated with oil pressure to enable torque transmission between two elements. A switching element can be designed to disconnect a mechanical connection between two elements in a specific state. A switching element can also be designed as a double switching element, which optionally connects a first element to a second or third element. A double switching element can optionally have a neutral position. The drive device can include a control device for controlling the switching elements and thus switching between the respective operating modes.

[0026] In a further embodiment of the drive device, the drive device comprises an intermediate power take-off (PTO) shaft and a first spur gear stage. The intermediate PTO shaft can be mechanically connected to the first PTO shaft by means of a first PTO switching element. For example, the intermediate PTO shaft can be rotationally fixed to the first PTO shaft by means of the first PTO switching element. The intermediate PTO shaft can be mechanically connected to the second PTO shaft by means of a second PTO switching element. For example, the intermediate PTO shaft can be rotationally fixed to the second PTO shaft by means of the second PTO switching element. The second motor shaft can be mechanically connected to the intermediate PTO shaft by means of the first spur gear stage. Thus, only one output shaft and, alternatively or additionally, one power interface on the second electric motor are necessary to selectively drive both PTO shafts.A simple and space-saving design can be achieved. The term "PTO switching element" serves to assign a function. PTO switching elements can be designed like other switching elements. For example, the two PTO switching elements are designed with friction to allow starting and, alternatively or additionally, the engagement of one of the two PTO shafts when the other PTO shaft is already driven via the intermediate PTO shaft.

[0027] The drive device can include an internal combustion engine with a combustion engine shaft, which is designed to provide combustion drive power at the combustion engine shaft. The internal combustion engine can, for example, be a diesel engine. The combustion engine shaft can, for example, be mechanically connected to the power take-off intermediate shaft by means of a combustion switching element. For example, the combustion engine shaft can be rotationally fixed to the power take-off intermediate shaft by means of the combustion switching element. The term combustion switching element serves to identify the function. The combustion switching element can be designed like other switching elements. For example, the combustion switching element is designed for frictional engagement. For example, the first power take-off shaft can be mechanically connected to the power take-off intermediate shaft via the combustion engine shaft, the combustion switching element, and the first power take-off switching element.For example, the first power take-off (PTO) shaft can be connected to the combustion engine shaft in a rotationally fixed manner using the first PTO switching element. This allows the combustion engine to drive one or both PTO shafts alone or in conjunction with the second electric motor. This configuration can result in a particularly high PTO power output. Alternatively, the combustion engine can be powered independently, yet the first PTO shaft can still be driven by the second electric motor via the combustion engine shaft. The combustion engine can also drive the second electric motor to generate electricity for an energy storage device or the first electric motor. In this case, the second electric motor functions as a generator. The combustion engine shaft can, for example, extend through the combustion engine, allowing for the connection of additional components at both axial ends.

[0028] In a further embodiment of the drive device, it is provided that the drive device has a second drive output shaft. The second drive output shaft can, for example, be mechanically connected to a front axle of the machine. The drive device can be configured to transmit drive power from the first engine shaft to the second drive output shaft. The second drive output shaft enables the drive device to provide all-wheel drive.

[0029] The drive unit can be designed to transmit torque from the first to the second drive output shaft. This allows for the simple provision of an unregulated all-wheel drive. Furthermore, the drive power can be easily transmitted to both drive output shafts via the transmission. The second drive output shaft can be mechanically connected to the first drive output shaft. Alternatively, the second drive output shaft can be mechanically connected to the first drive output shaft. The drive unit can, for example, include an all-wheel drive spur gear stage and an all-wheel drive shift element, whereby the first drive output shaft is mechanically connected to the second drive output shaft via the all-wheel drive spur gear stage and the all-wheel drive shift element. The terms "all-wheel drive shift element" and "all-wheel drive spur gear stage" serve to clarify their functions.The all-wheel drive switching element can be designed like other switching elements, and the all-wheel drive spur gear stage can be designed like other spur gear stages. For example, the all-wheel drive switching element is friction-fit and the all-wheel drive spur gear stage is single-stage.

[0030] In a further embodiment of the drive device, it is provided that the drive device comprises an all-wheel drive spur gear stage, an all-wheel drive switching element, an auxiliary power switching element, and a third electric motor with a third motor shaft, which is configured to provide a third drive power at the third motor shaft. The third motor shaft can be mechanically connected to the second drive output shaft via the all-wheel drive spur gear stage using the all-wheel drive switching element. This allows the third electric motor to assist the first electric motor during propulsion when all-wheel drive is activated. When driving with all-wheel drive, driving efficiency may be reduced, so greater power may be required.The third electric motor can then provide this power without the first electric motor needing to be specifically designed for the rarely occurring peak loads when driving with all-wheel drive. Furthermore, by distributing the power between the first and third electric motors, the available installation space can be used efficiently and flexibly, either alternatively or additionally.

[0031] In a further embodiment of the drive device, the drive device comprises a summing gearbox, a brake, and a third electric motor with a third motor shaft, which is configured to provide a third drive power at the third motor shaft. A summing gearbox can, for example, have several input shafts and one output shaft, at which the drive power supplied to the input shafts is provided collectively. The summing gearbox can, for example, be designed as a planetary gear set. A brake can be a switching element by means of which a rotatable element can be locked to a stationary component. The brake can, for example, be designed as a friction-based switching element. The planetary gear set can comprise a sun gear, a planet carrier, and a ring gear. One or more planet gears can be rotatably mounted on the planet carrier.The planetary gear set is designed, for example, as a negative planetary gear set. In a negative planetary gear set, each planet gear meshes with both the ring gear and the sun gear. Torque can be transmitted from the third motor shaft to a first input shaft of the summing gearbox. The first input shaft of the summing gearbox can, for example, be designed as a sun gear. The first drive output shaft can be mechanically connected to a second input shaft of the summing gearbox. Similarly, the second input shaft of the summing gearbox can be mechanically connected to the first motor shaft via the drive gearbox and the first drive output shaft. The second input shaft of the summing gearbox can, for example, be designed as a ring gear. An output shaft of the summing gearbox can be permanently and rotationally fixed to the second drive output shaft. The output shaft of the summing gearbox can, for example, be designed as a planet carrier.The third electric motor allows the gear ratio of the summing gearbox to be changed. This results in a controllable all-wheel drive, optionally also in a power-split configuration. The first input shaft of the summing gearbox can be locked using the brake. This allows for a rigid all-wheel drive, which can be particularly efficient. When using the rigid all-wheel drive, the third electric motor can, for example, be deactivated.

[0032] In a further embodiment of the drive device, the drive device includes a motor coupling switching element. The term "motor coupling switching element" serves to identify its function. Motor coupling switching elements can be designed like other switching elements. For example, they can be frictionally engaged. The first motor shaft can be mechanically connected to the second motor shaft by means of the motor coupling switching element, for example, via a spur gear stage. The connection can also be at least partially made via a spur gear stage, through which the first motor shaft can be mechanically connected to the first drive output shaft. The motor coupling switching element can, for example, be arranged coaxially on the power take-off intermediate shaft, with the first motor shaft being mechanically connected to the power take-off intermediate shaft by means of the motor coupling switching element.The motor coupling switching element allows the first electric motor to assist the second electric motor in driving the power take-off (PTO) shafts. This also allows the second electric motor to assist the first electric motor in driving the drive shafts. This results in new operating modes. Furthermore, the individual electric motors can be smaller, since at maximum PTO load, the machine is typically operated at low speeds or stationary. Similarly, at maximum driving speed, little or no PTO load is usually required. Additionally, this allows for the provision of a ground-speed PTO function.

[0033] In a further embodiment of the drive device, the drive device comprises a first motor coupling element and a second motor coupling element. The third motor shaft can be mechanically connected to the second motor shaft via the first motor coupling element. The first motor shaft can also be mechanically connected to the third motor shaft via the second motor coupling element. The third electric motor can thus, for example, assist the second electric motor independently of the first. The first electric motor can, for example, only assist the second electric motor if this is also possible through the third electric motor, i.e., if the first motor coupling element is closed. For the mechanical connection of the first motor shaft to the second motor shaft, for example, both the first and second motor coupling elements must be closed.The first motor coupling switching element can therefore function similarly to the motor coupling switching element described in the previous embodiment. Through the two motor coupling switching elements, the first electric motor and the third electric motor can assist the second electric motor in driving the power take-off (PTO) shafts. In addition, the third electric motor can also assist the second electric motor in driving the PTO shafts on its own, while the first electric motor only drives the drive of the machine. Through the two motor coupling switching elements, the second electric motor can also assist the first electric motor in driving the drive shafts. This results in new operating modes and a ground-speed PTO function.

[0034] In a further embodiment of the drive device, it is provided that the drive device comprises a working hydraulic supply device, a system hydraulic supply device, and an auxiliary electric motor with an auxiliary motor shaft. The auxiliary electric motor can be designed as a standard electric motor. The auxiliary electric motor can, for example, be significantly less powerful than the first and second electric motors, and optionally also compared to other electric motors described herein. The auxiliary motor shaft can be a standard motor shaft, designated as such only for identification purposes. The working hydraulic supply device can be configured to supply the working hydraulics with pressure. The working hydraulics can be used, for example, to operate various tools of the machine, such as a bucket.A working hydraulic supply device can, for example, include a fixed-displacement pump and a variable-displacement pump, both driven by a single shaft. Alternatively, a working hydraulic supply device can also include only a variable-displacement pump. The system hydraulic supply device can be configured to supply pressure to the respective control hydraulics. For example, the system hydraulic supply device can provide transmission oil pressure and pressure for actuating the respective switching elements of the drive system. The system hydraulic supply device can, for example, include a fixed-displacement pump for the transmission oil pressure and a fixed-displacement pump for the switching element actuation pressure, both driven by a single shaft. Alternatively, the system hydraulic supply device can include only a fixed-displacement pump.The system hydraulic supply device and the working hydraulic device can be separate units. The respective oil circuits supplied by them can be fluidically separated, at least in one pressure range. The system hydraulic supply device can, for example, be mechanically connected to the second engine shaft via a spur gear stage and the intermediate power take-off shaft.

[0035] For example, the auxiliary electric motor is always operated at a predetermined minimum speed during the operation of the driven machine to enable the actuation of the respective switching elements. The second electric motor can therefore remain stationary during certain operating states of the driven machine, which can be efficient. Furthermore, a module consisting of the auxiliary electric motor and the system hydraulic supply unit can allow for flexible use of installation space, independent of other components of the drive system. Additionally, the second electric motor can be dimensioned with lower power output. The auxiliary electric motor and the second electric motor can thus be operated particularly efficiently, for example, less frequently at inefficient operating points during typical operating cycles of the driven machine. The auxiliary motor shaft can be permanently and rotationally fixed to an input shaft of the system hydraulic supply unit.A module constructed in this way can be free of switching elements and spur gear stages. If, on the other hand, the system hydraulic supply device is driven by the second electric motor, the second electric motor can, for example, always be operated at a predetermined minimum speed during operation of the driven machine in order to enable the actuation of the respective switching elements.

[0036] In a further embodiment of the drive device, it is provided that the drive device comprises a working hydraulic supply device and a system hydraulic supply device. The second motor shaft can be mechanically connected to both the working hydraulic supply device and the system hydraulic supply device. This eliminates the need for an auxiliary electric motor. The drive device can thus be particularly compact and require fewer electric motors. In this configuration, the second electric motor can, for example, always operate at a minimum speed during the operation of the working machine.

[0037] In a further embodiment of the drive device, the drive device is provided with a second spur gear stage. The working hydraulic supply device can be permanently and rotationally fixed to a shaft of the first spur gear stage. The working hydraulic supply device can be arranged in the torque flow of the second drive power upstream of the PTO intermediate shaft. The system hydraulic supply device can be mechanically operatively connected to the second motor shaft via the first and second spur gear stages. Particularly efficient speed ratios can be achieved, even though the second electric motor drives both the system hydraulic supply device and the working hydraulic supply device. The first and second spur gear stages can have a common gear, which, for example, is permanently and rotationally fixed to the PTO intermediate shaft.This allows the drive device to have a particularly small number of gears.

[0038] In another embodiment of the drive device, the first motor shaft is mechanically connected to the second motor shaft via the second spur gear stage using the motor coupling switching element. This eliminates the need for an additional spur gear stage, or at least additional gears, to couple the first and second motor shafts. Instead, a mechanical connection between the first and second motor shafts can utilize the second spur gear stage. Alternatively or additionally, this allows the drive device to be very compact axially. The motor coupling switching element can, for example, be arranged coaxially with an input shaft of the system hydraulic supply device. This results in a very compact design.

[0039] In another embodiment of the drive device, the second planet carrier is provided to be rotationally fixed to the second sun gear by means of the drive switching element. This allows the second planet gear set to be easily locked in place by the drive switching element. For example, no additional hollow shafts are required.

[0040] In a further embodiment of the drive device, the first planetary gear set is designed as a negative planetary gear set. Alternatively or additionally, the second planetary gear set can also be designed as a negative planetary gear set. This can result in a structurally simple and efficient drive system with gear ratios particularly suitable for working machines.

[0041] A second aspect concerns a working machine. This working machine has a drive device as described in the first aspect. The respective advantages and further characteristics can be found in the description of the first aspect, whereby embodiments of the first aspect also constitute embodiments of the second aspect and vice versa.

[0042] The machine has one drive axle and, in a further embodiment, an additional drive axle. Torque can be transmitted from the first drive axle to the first drive axle. Torque can be transmitted from the second drive axle, if present, to the additional drive axle. The first drive axle is, for example, the rear axle of the machine. The additional drive axle is, for example, the front axle of the machine. Wheels are arranged at opposite ends of each drive axle. Each drive axle can have an axle differential and, alternatively or additionally, a wheel drive for each wheel. The machine can have a service brake, which is, for example, located on the rear axle. The machine can also have a service brake for each drive axle. Brief description of the characters Fig. Figure 1 schematically illustrates a first embodiment of a drive device for a working machine with two electric machines and a drive transmission. Fig. Figure 2 schematically illustrates a second embodiment of a drive device for a working machine, which additionally has an internal combustion engine. Fig. Figure 3 schematically illustrates one of the two electric machines with the associated drive mechanism of the drive device. Fig. Figure 4 schematically illustrates a switching matrix of the drive transmission of the drive device. Fig. Figure 5 schematically illustrates a third embodiment of a drive device for a working machine, in which the electric motors are connected differently compared to the first embodiment. Fig. Figure 6 schematically illustrates a fourth embodiment of a drive device for a working machine, in which a working hydraulic supply device and a system hydraulic supply device are connected differently compared to the first embodiment. Fig. Figure 7 schematically illustrates a fifth embodiment of a drive device for a working machine, in which a first motor shaft and a second motor shaft can be mechanically connected to each other. Fig. Figure 8 schematically illustrates a sixth embodiment of a drive device for a working machine, in which the first motor shaft and the second motor shaft are mechanically interconnected, unlike in the fifth embodiment. Fig. Figure 9 schematically illustrates a seventh embodiment of a drive device for a working machine, which has an auxiliary electric machine by means of which the system hydraulic supply device can be driven. Fig. Figure 10 schematically illustrates an eighth embodiment of a drive device for a working machine, which has a third electric machine by means of which a second drive output shaft can also be driven. Fig. Figure 11 schematically illustrates a ninth embodiment of a drive device for a working machine, in which, compared to the eighth embodiment, the motor shafts can be connected differently. Fig. Figure 12 schematically illustrates a tenth embodiment of a drive device for a working machine, which has a third electric machine and a summing gearbox to provide a controllable all-wheel drive in a power-split configuration. Fig. Figure 13 schematically illustrates an eleventh embodiment of a drive device for a working machine, in which, compared to the tenth embodiment, the third motor shaft is mechanically connectable to the second motor shaft and the first motor shaft is mechanically connectable to the third motor shaft. Detailed description of embodiments

[0043] Fig. Figure 1 schematically illustrates a drive device 10 of a machine. The drive device 10 comprises a first electric machine EM1 with a first motor shaft 12, which is configured to provide a first drive power at the first motor shaft 12. The drive device 10 comprises a second electric machine EM2 with a second motor shaft 14, which is configured to provide a second drive power at the second motor shaft 14. In the illustrated embodiment of the first design, the two electric machines EM1 and EM2 are designed for the same rotational speed and have essentially the same power output. The drive device comprises a first drive output shaft 16 and a second drive output shaft 18. The first drive output shaft 16 is mechanically connected to a rear axle 20.The rear axle 20 has an axle differential 22, a service brake 24 on each side, a wheel gearbox 26 on each side, and a wheel 28 on each side. The rear axle 20 can be driven for propulsion by the working machine via the first drive output shaft 16. The second drive output shaft 18 is mechanically connected to a front axle (not shown). The second drive output shaft 18 is mechanically connected to the first drive output shaft 16 via an all-wheel drive spur gear stage 30 and an all-wheel drive shift element AS. This allows a rigid all-wheel drive to be engaged, enabling the working machine to be driven with both the rear axle 20 and the front axle simultaneously.

[0044] The first motor shaft 12 is mechanically connected to the first drive output shaft 16 by means of a drive transmission 32. The drive transmission 32 has an input shaft 34, which is mechanically connected to the first motor shaft 12. In the first embodiment of the drive device 10, the input shaft 34 of the drive transmission 32 is permanently and rotationally fixed to the first motor shaft 12. The drive transmission 32 has an output shaft 36, which is permanently and rotationally fixed to the first drive output shaft 16. Furthermore, the drive transmission 32 has a first planetary gear set FP1, a second planetary gear set FP2, a drive switching element FS, a first brake B1, and a second brake B2. The first planetary gear set FP1 has a first sun gear 72, a first planet carrier 74, and a first ring gear 76 and is designed as a negative planetary gear set.Several planet gears 78 are rotatably mounted on the first planet carrier 74, each meshing with the first sun gear 72 and the first ring gear 76. The second planetary gear set FP2 has a second sun gear 82, a second planet carrier 84, and a second ring gear 86 and is designed as a negative planetary gear set. Several planet gears 88 are rotatably mounted on the second planet carrier 84, each meshing with the second sun gear 82 and the second ring gear 86.

[0045] The first sun gear 72 is permanently and rotationally fixedly connected to the input shaft 34 of the drive unit 32. The first planet carrier 74 is permanently and rotationally fixedly connected to the second ring gear 86 by means of a hollow shaft 90. The first ring gear 76 can be rotationally fixedly connected to a stationary component of the drive unit 10 by means of the first brake B1 of the drive unit 32 and thus locked in place. The second sun gear 82 is permanently and rotationally fixedly connected to the input shaft 34 of the drive unit 32. The second planet carrier 84 is permanently and rotationally fixedly connected to the output shaft 36 of the drive unit 32. The second ring gear 86 can be connected to the stationary component of the drive unit and thus locked in place by means of the second brake B2 of the drive unit 32. The second planetary gear set FP2 can be locked by means of the drive switching element FS by means of the second planet carrier 84 being rotationally fixedly connected to the second sun gear 82.

[0046] Based on the Fig. 3, which shows only the first electric motor 12 and the drive transmission 32 connected to the first motor shaft 12, as well as based on the Fig. Figure 4, which shows a switching matrix of the drive transmission 32, clearly illustrates the operation of the drive transmission 32. The drive transmission 32 provides three compact transmission stages suitable for working machines. In the switching matrix, each row corresponds to a transmission stage labeled V1 to V3. Actuated and therefore closed brakes B1, B2, and an actuated and therefore closed drive switching element FS are shown in the Fig. Figure 4 is illustrated with an "x". In a first gear ratio V1, which corresponds to a gear for slow driving, only the first brake B1 is engaged. This allows the planet gears 88 of the second planetary gear set FP2 to roll against the second ring gear 86 and thus transmit drive power from the second sun gear 82 to the second planet carrier 84. In a second gear ratio V2, which corresponds to a gear for medium driving speeds, only the second brake B2 is engaged. This allows the planet gears 78 of the first planetary gear set FP1 to roll against the first ring gear 76 and thus transmit drive power from the first sun gear 72 via the hollow shaft 90 to the second planetary gear set FP2, in which the second ring gear 86 rotates at the same speed as the first planet carrier 74. In the second planetary gear set FP2, the second sun gear 82 rotates at the speed of the input shaft 34 of the drive unit 32.Accordingly, a gear reduction occurs at the second planet carrier 84. In a third gear ratio stage V3, which corresponds to a high-speed gear, only the drive shift element FS is closed. The second planetary gear set FP2 is thus locked, so that the planet gears 88 of the second planetary gear set FP2 do not roll against either the second sun gear 82 or the second ring gear 86. Consequently, the output shaft 36 of the drive transmission 32 rotates without loss, just like the input shaft 34 of the drive transmission 32, enabling particularly efficient operation at high speeds.

[0047] The drive unit has a first power take-off (PTO) shaft 40 and a second PTO shaft 42. The first PTO shaft 40 is designed as a front PTO shaft. The second PTO shaft 42 is designed as a rear PTO shaft. A two-stage PTO gearbox 60 is connected to the second PTO shaft 42. A further PTO gearbox (not shown) is connected to the first PTO shaft 40. Two implements can be supplied with PTO power via the two PTO shafts 40 and 42. For this purpose, the second engine shaft 14 is mechanically operatively connected to the first PTO shaft 40 and to the second PTO shaft 42. The second engine shaft 14 is mechanically operatively connected to an intermediate PTO shaft 46 by means of a first spur gear stage 44. The intermediate PTO shaft 46 is rotationally fixed to the front of the first PTO shaft 40 by means of a first PTO switching element ZF1. The intermediate power take-off shaft 46 can be connected at the rear to the second power take-off shaft 42 by means of a second power take-off switching element ZF2 in a rotationally fixed manner.

[0048] The drive unit 10 comprises a working hydraulic supply unit 48 and a system hydraulic supply unit 50. The working hydraulic supply unit 48 comprises a constant-speed pump 52 and a variable-speed pump 54. The working hydraulic supply unit 48 is designed to supply pressure to the working hydraulics in order to hydraulically actuate a tool. The system hydraulic supply unit 50 comprises two constant-speed pumps 56. The system hydraulic supply unit 50 is designed to provide system pressure for actuating the switching elements of the drive unit 10 and for actuating a steering system, as well as to provide transmission oil pressure. The system hydraulic supply unit 50 and the working hydraulic supply unit 48 are mechanically connected to the second engine shaft 14 via a spur gear stage 58, the intermediate power take-off shaft 46, and the first spur gear stage 44.In the first embodiment, the second electric machine EM2 always runs at a minimum speed during operation of the working machine in order to provide a minimum system pressure.

[0049] Fig. Figure 2 shows a second embodiment of the drive device 10, which is similar to the first embodiment. Only the differences are described.

[0050] In the second embodiment of the drive device 10, an internal combustion engine 200 with an internal combustion engine shaft 202, which extends axially through the internal combustion engine 200, is additionally provided. The internal combustion engine shaft 202 can be connected to the power take-off intermediate shaft 46 in a rotationally fixed manner by means of an internal combustion engine switching element VS. Thus, the second electric machine EM2 can be driven by the internal combustion engine 200 as a generator. The first power take-off shaft 40 can be connected to the internal combustion engine shaft 202 in a rotationally fixed manner by means of the first power take-off switching element ZF1. Thus, the first power take-off shaft 40 can be driven by the internal combustion engine 200 or, with the internal combustion engine switching element VS closed, also by the second electric machine EM2. The internal combustion engine 200 can be further configured in other embodiments, which are described in the Fig. 5 to Fig. 13 are shown, so it should also be provided.

[0051] Fig. Figure 5 shows a third embodiment of the drive device 10, which is similar to the first embodiment. Only the differences are described.

[0052] In the third embodiment, the first motor shaft 12 is not permanently rotationally fixed to the input shaft 34, but is mechanically connected via a single-stage spur gear stage 500. The first spur gear stage 44, which mechanically connects the second motor shaft 14 to the intermediate power take-off shaft 46, is designed as a two-stage stage in the third embodiment instead of a single-stage stage as in the first embodiment.

[0053] This additional gear ratio allows the two electric motors EM1 and EM2 in the third embodiment to be designed for a higher rotational speed compared to the first embodiment. As a result, the two electric motors EM1 and EM2 are radially more compact in the third embodiment. In contrast, the two electric motors EM1 and EM2 are axially shorter in the first embodiment.

[0054] Fig. Figure 6 shows a fourth embodiment of the drive device 10, which is similar to the third embodiment. Only the differences are described.

[0055] In the fourth embodiment, the working hydraulic supply device 48 is permanently and rotationally fixedly connected to a shaft 600 of the two-stage first spur gear stage 44. The system hydraulic supply device 50 is mechanically connected to the second motor shaft 14 via the first spur gear stage 44 and a second spur gear stage 602. The first spur gear stage 44 and the second spur gear stage 602 share a common gear 604, which is permanently and rotationally fixedly connected to the intermediate power take-off shaft 46. Furthermore, in the fourth embodiment of the drive device 10, the spur gear stage 500, which connects the first motor shaft 12 to the input shaft 34 of the drive transmission 32, is multi-stage.

[0056] This results in a more pronounced radial nesting, so that the sixth embodiment of the drive device 10 has a very short axial profile. This utilizes a radial installation space that, in conventional combustion engine-powered machinery, is occupied by a fuel tank. Furthermore, improved speed levels are achieved at the working hydraulic supply device 48 and the system hydraulic supply device 50. Accordingly, two different gear ratios in the PTO gearbox 60 can be omitted. Therefore, in the fourth embodiment, the PTO gearbox 60 is designed as a simple spur gear stage without a switching element. In the fourth embodiment, the second electric motor EM2 is designed for higher speeds than the first electric motor EM1.

[0057] Fig. Figure 7 shows a fifth embodiment of the drive device 10, which is similar to the fourth embodiment. Only the differences are described.

[0058] In the fifth embodiment of the drive device 10, a first motor coupling switching element MS1 is additionally provided. The first motor shaft 12 is mechanically connected to the second motor shaft 14 by means of the first motor coupling switching element MS1. In the embodiment shown, a spur gear stage 700 is connected to a middle shaft 702 of the spur gear stage 500, by means of which the first motor shaft 12 is mechanically connected to the input shaft 34 of the drive transmission 32. The first motor coupling switching element MS1 is arranged on the power take-off intermediate shaft 46 and is designed to connect the spur gear stage 700 to the power take-off intermediate shaft 46.

[0059] Accordingly, the first electric machine 12 and the second electric machine 14 can mutually support each other in driving the two power take-off shafts 40, 42 and the two drive output shafts 16, 18. This allows for a lower overall system power output, since the machine typically does not need to provide maximum power take-off and maximum drive power simultaneously. In the example shown, the second electric machine EM2 is therefore designed for a lower maximum power output than the first electric machine EM1. Consequently, the second electric machine EM2 is particularly small in the seventh embodiment. Furthermore, this provides a ground-driven power take-off function.

[0060] Fig. Figure 8 shows a sixth embodiment of the drive device 10, which is similar to the fifth embodiment. Only the differences are described.

[0061] In the sixth embodiment of the drive device 10, the mechanical connection between the first motor shaft 12 and the second motor shaft 14 is designed differently. The first motor coupling switching element MS1 is arranged coaxially with a drive shaft of the system hydraulic supply device 50. Instead of the spur gear stage 700, which provides a switchable mechanical connection between the spur gear stage 500 and the intermediate power take-off shaft 46, a spur gear stage 800 is provided. The spur gear stage 800 provides a mechanical connection between the input shaft 34 of the drive transmission 32 and the drive shaft of the system hydraulic supply device 50 when the motor coupling switching element is closed. Accordingly, the first motor shaft 12 can be mechanically connected to the second motor shaft 14 via the second spur gear stage 602 by means of the first motor coupling switching element 12. As a result, the drive device 10 according to the sixth embodiment is particularly short axially.

[0062] Fig. Figure 9 shows a seventh embodiment of the drive device 10, which is similar to the fifth embodiment. Only the differences are described.

[0063] In the seventh embodiment of the drive device 10, the system hydraulic supply device 50 is not driven by the second electric machine EM2. Accordingly, the second spur gear stage 602 is also omitted. Instead, the seventh embodiment of the drive device 10 has an auxiliary electric machine HM with an auxiliary motor shaft 900. The auxiliary motor shaft 900 is mechanically connected to the system hydraulic supply device 50, in the example shown by being permanently and rotationally fixed to the drive shaft of the system hydraulic supply device 50. This allows the system hydraulic supply device 50 to be arranged and driven independently. This improves flexibility in terms of installation space utilization. Furthermore, the second electric machine EM2 can be switched off when no hydraulic power or drive assistance from the second electric machine EM2 is required.The auxiliary electric machine HM is operated at a minimum speed instead of the second electric machine EM2 during operation of the driven machine. This allows the second electric machine EM2 to operate more frequently at its efficient operating point. The maximum power output of the auxiliary electric machine HM is significantly lower than that of the two electric machines EM1 and EM2 combined.

[0064] Fig. Figure 10 shows an eighth embodiment of the drive device 10, which is similar to the fifth embodiment. Only the differences are described.

[0065] The eighth embodiment of the drive device 10 additionally features a third electric motor EM3 with a third motor shaft 1000. The third electric motor EM3 is designed to provide a third drive power at the third motor shaft. The third motor shaft 1000 is mechanically connected to the second drive output shaft 18 via a multi-stage spur gear stage 1002 and an additional power switching element ZL. The third electric motor EM3 is designed for a lower power output than the first electric motor EM1.

[0066] In the eighth embodiment of the drive device 10, an adjustable all-wheel drive function can be provided in addition to a rigid all-wheel drive function. When the all-wheel drive switching element AS is engaged, the two drive axles are driven at a fixed speed ratio. By engaging the auxiliary power switching element ZL and with the all-wheel drive switching element AS closed, the third electric motor EM3 can assist the first electric motor EM1 in driving both the two power take-off shafts 40, 42 and the two drive output shafts 16, 18. Accordingly, the first electric motor in this embodiment can be designed for lower power, thus saving installation space and costs. With the all-wheel drive switching element AS disengaged but the auxiliary power switching element ZL engaged, the third electric motor EM3 can drive the second drive output shaft 18 independently of the first drive output shaft 16.This allows the speed ratio of the second drive output shaft 18 to the first drive output shaft 16 to be varied for a controllable all-wheel drive.

[0067] Fig. Figure 11 shows a ninth embodiment of the drive device 10, which is similar to the eighth embodiment. Only the differences are described.

[0068] In the ninth embodiment, the third motor shaft 1000 is mechanically connected to the second motor shaft 14. The third motor shaft 1000 is mechanically connected to the PTO intermediate shaft 46 via a spur gear stage 1100 by means of the first motor coupling switching element MS1. In the ninth embodiment, the first motor shaft 12 can also still be mechanically connected to the second motor shaft 14. For this purpose, a second motor coupling switching element MS2 is provided, by means of which the second motor shaft 14 is connected to the motor shaft 12. Fig. In the embodiment shown in Figure 11, the third motor shaft 1000 can be mechanically connected via the spur gear stage 1100. Thus, if the first motor coupling switching element MS1 and the second motor coupling switching element MS2 are actuated, the drive power from the first electric motor EM1 can be transmitted to the PTO intermediate shaft 46. Furthermore, the ninth embodiment allows an operating mode in which the third electric motor EM3 assists the second electric motor EM2 in driving the PTO shafts, and the first electric motor EM1 drives the respective drive output shafts 16 and 18 on its own. In this operating mode, the second motor coupling switching element MS2 and the auxiliary power switching element ZL are unactuated, while the first motor coupling switching element MS1 is actuated.

[0069] In the ninth embodiment, the first electric motor EM1 and the third electric motor EM3 are designed such that only together can the maximum required driving power be provided. This makes the drive device 10 of the ninth embodiment compact and cost-effective.

[0070] Fig. Figure 12 shows a tenth embodiment of the drive device 10, which is similar to the eighth embodiment. Only the differences are described.

[0071] In the tenth embodiment, the first electric motor EM1 and the third electric motor EM3 are connected such that the drive device 10 is electrically power-split and can provide variable all-wheel drive. The auxiliary power switching element ZL is omitted. Additionally, a summing gear 1200 is provided, which is designed as a negative planetary gear set with a sun gear 1202 as the first input shaft, a ring gear 1204 as the second input shaft, and a planet carrier 1206 as the output shaft. Several planet gears 1208 are rotatably mounted on the planet carrier, each meshing with the sun gear 1202 and the ring gear 1204.

[0072] The third motor shaft 1000 is mechanically connected to the sun gear 1202 via the spur gear stage 1002. The first drive output shaft 16 is mechanically connected to the ring gear 1204 via the all-wheel drive spur gear stage 30, so that torque can be transmitted from the first motor shaft 12 to the second input shaft of the summing gearbox 1200 via the drive transmission 32. The planet carrier 1206 is permanently and rotationally fixed to the second drive output shaft 18. The third electric motor EM3 thus allows the transmission ratio at the summing gearbox 1204 to be varied. The third electric motor EM3 is designed for low loads, as it essentially only varies the transmission ratio.

[0073] The sun gear 1202 of the summing gearbox 1200 can be locked by means of an additional brake 1210. This allows a rigid all-wheel drive to be provided, which enables efficient driving without supports thanks to the third electric motor EM3.

[0074] Fig. Figure 13 shows an eleventh embodiment of the drive device 10, which is essentially a combination of the ninth and tenth embodiments. Only the differences are described.

[0075] In the eleventh embodiment, the first motor coupling switching element MS1 and the second motor coupling switching element MS2 are also provided, as in the ninth embodiment. The third motor shaft 1000 can thus be mechanically connected to the second motor shaft 14 by means of the first motor coupling switching element MS1. The first motor shaft 12 can thus be mechanically connected to the third motor shaft 1000 by means of the second motor coupling switching element MS2.

[0076] Furthermore, the eleventh embodiment includes the summing gearbox 1200, as in the tenth embodiment. The third motor shaft 1000 is mechanically connected to the sun gear 1202 via the spur gear stage 1002 and an additional switching element 1300. As in the tenth embodiment, the first drive output shaft 16 is mechanically connected to the ring gear 1204 via the all-wheel drive spur gear stage 30, so that torque can be transmitted from the first motor shaft 12 to the second input shaft of the summing gearbox 1200 via the drive transmission 32. The planet carrier 1206 is permanently and rotationally fixed to the second drive output shaft 18.

[0077] The additional switching element 1300 allows the third motor shaft 1000 to be disconnected from the summing gearbox 1200. This allows the third electric motor EM3, with the additional switching element 1300 disengaged, to assist the second electric motor EM2 in driving the power take-off shafts 40 and 42, while the first electric motor drives the drive output shafts 16 and 18 independently and without any influence of the third electric motor EM3 on the gear ratio. Reference sign 10 Drive device 12, 14, 1000 motor shafts 16, 18 drive output shafts 20 Rear axle 22 axle differential 24 Driving brake 26 wheel gearboxes 28-inch wheel 30 All-wheel drive spur gear stage 32 Driving gear 34 Input shaft 36 Output shaft 40, 42 PTO shafts 44, 58, 500, 602, 700, 800, 1002, 1100 Spur gear stage 46 PTO intermediate shaft 48 Working hydraulic supply device 50 System hydraulic supply device 52, 56 Constant pump 54 Variable displacement pump 60 Dispensing gearboxes 72, 82 Sun gear of the drive transmission 74, 84 Planetary carrier of the drive transmission 76, 86 Hollow gears of the drive transmission 78, 88 planetary gears of the track planetary gear sets 90 Hollow shaft 200 internal combustion engine 202 internal combustion engine shaft 600 wave 604 gear 702 medium wave 900 Auxiliary motor shaft 1200 summing gearbox 1202 Sun wheel 1204 Ring gear 1206 Planetary Carriers 1208 planetary gears 1210 Brake 1300 switching element EM1-EM3 Electrical Machines HM Auxiliary Electric Machine AS all-wheel drive switching element FP1, FP2 planetary wheelsets FS drive control element B1, B2 Brakes of the transmission ZF1, ZF2 dispensing switching elements V1-V3 gear ratio stages of the drive transmission VS combustion control element MS1, MS2 motor coupling switching elements ZL Additional Power Switching Element

Claims

[1] Drive device (10) for a working machine, wherein the drive device (10) comprises a first electric machine (EM1) with a first motor shaft (12) configured to provide a first drive power at the first motor shaft (12), a second electric machine (EM2) with a second motor shaft (14) configured to provide a second drive power at the second motor shaft (14), a first drive output shaft (16), a first power take-off shaft (40) and a second power take-off shaft (42), wherein the first motor shaft (12) is mechanically connectable to the first drive output shaft (16) by means of a drive transmission (32), and wherein the second motor shaft (14) is mechanically connectable to the first power take-off shaft (40) and to the second power take-off shaft (42), wherein the drive transmission (32) comprises an input shaft (34), an output shaft (36), a first planetary gear set (FP1) with a first sun gear (72),a first planet carrier (74) and a first ring gear (76), a second planetary gear set (FP2) with a second sun gear (82), a second planet carrier and a second ring gear (86), a drive shift element (FS), a first brake (B2) and a second brake (B1), wherein the first sun gear (72) is permanently and non-rotatably connected to the input shaft (34) of the drive transmission (32), wherein the first planet carrier (74) is permanently and non-rotatably connected to the second ring gear (86), wherein the first ring gear (76) can be locked by means of the first brake (B2) of the drive transmission (32), wherein the second sun gear (82) is permanently and non-rotatably connected to the input shaft (34) of the drive transmission (32), wherein the second planet carrier (84) is permanently and non-rotatably connected to the output shaft (36) of the drive transmission (32),wherein the second ring gear (86) can be locked by means of the second brake (B1) of the drive transmission (32) and wherein the second planetary gear set (FP2) can be locked by means of the drive switching element (FS). [2] Drive device (10) according to claim 1, characterized by , that the drive device (10) has a PTO intermediate shaft (46) and a first spur gear stage (44), wherein the second motor shaft (14) is mechanically connected to the PTO intermediate shaft (46) by means of the first spur gear stage (44), wherein the PTO intermediate shaft (46) can be mechanically connected to the first PTO shaft (40) by means of a first PTO switching element (ZF1) and the PTO intermediate shaft (46) can be mechanically connected to the second PTO shaft (42) by means of a second PTO switching element (ZF2). [3] Drive device (10) according to claim 1 or 2, characterized by, that the drive device (10) has a second drive output shaft (18), wherein a torque can be transmitted from the first drive output shaft (16) to the second drive output shaft (18). [4] Drive device (10) according to claim 3, characterized by , that the drive device (10) comprises an all-wheel drive spur gear stage (30), an all-wheel drive switching element (AS), an additional power switching element (ZL) and a third electric machine (EM3) with a third motor shaft (1000) which is designed to provide a third drive power at the third motor shaft (1000), wherein the third motor shaft (1000) is mechanically interconnected with the second drive output shaft (18) by means of the additional power switching element (ZL) and wherein the first drive output shaft (16) is mechanically interconnected with the second drive output shaft (18) via the all-wheel drive spur gear stage (30) by means of the all-wheel drive switching element (AS). [5] Drive device (10) according to claim 3, characterized by, that the drive device (10) comprises a summing gearbox (1200), a brake (1210) and a third electric machine (EM3) with a third motor shaft (1000), which is designed to provide a third drive power at the third motor shaft (1000), wherein a torque can be transmitted from the third motor shaft (1000) to a first input shaft (1202) of the summing gearbox (1200), wherein the first drive output shaft (16) is mechanically connected to a second input shaft (1204) of the summing gearbox (1200), wherein an output shaft (1206) of the summing gearbox (1200) is permanently rotationally fixed to the second drive output shaft (18) and wherein the first input shaft (1202) of the summing gearbox (1200) can be locked by means of the brake (1210). [6] Drive device (10) according to any of the preceding claims, characterized by, that the drive device (10) has a motor coupling switching element (MS1), wherein the first motor shaft (12) can be mechanically connected to the second motor shaft (14) by means of the motor coupling switching element (MS1). [7] Drive device (10) according to claim 4 or 5, characterized by , that the drive device (10) has a first motor coupling switching element (MS1) and a second motor coupling switching element (MS2), wherein the third motor shaft (1000) can be mechanically connected to the second motor shaft (14) by means of the first motor coupling switching element (MS1) and wherein the first motor shaft (12) can be mechanically connected to the third motor shaft (1000) by means of the second motor coupling switching element (MS2). [8] Drive device (10) according to any of the preceding claims, characterized by, that the drive device (10) comprises a working hydraulic supply device (48), a system hydraulic supply device (50) and an auxiliary electric machine (HM) with an auxiliary motor shaft (900), wherein the second motor shaft (14) is mechanically connected to the working hydraulic supply device (48) and wherein the auxiliary motor shaft (900) is mechanically connected to the system hydraulic supply device (50). [9] Drive device (10) according to any one of the preceding claims 1 to 7, characterized by , that the drive device (10) has a working hydraulic supply device (48) and a system hydraulic supply device (50), wherein the second motor shaft (14) is mechanically connected to the working hydraulic supply device (48) and to the system hydraulic supply device (50). [10] Drive device (10) according to claim 9, characterized by, that the drive device (10) has a second spur gear stage (602), wherein the working hydraulic supply device (48) is permanently rotationally fixed to a shaft (600) of the first spur gear stage (44), and wherein the system hydraulic supply device (50) is mechanically operatively connected to the second motor shaft (14) via the first spur gear stage (44) and the second spur gear stage (602), wherein the first spur gear stage (44) and the second spur gear stage (602) have a common gear (604). [11] Drive device (10) according to claims 6 and 10, characterized by , that the first motor shaft (12) can be mechanically connected to the second motor shaft (14) by means of the motor coupling switching element (MS1) via the second spur gear stage (602). [12] Drive device (10) according to any of the preceding claims, characterized by , that the second planet carrier (84) can be connected to the second sun gear (82) in a rotationally fixed manner by means of the drive switching element (FS). [13] Drive device (10) according to any of the preceding claims, characterized by , that the first planetary wheelset (FP1) is designed as a negative planetary wheelset. [14] Drive device (10) according to any of the preceding claims, characterized by , that the second planetary wheelset (FP2) is designed as a negative planetary wheelset. [15] Working machine with a drive axle and a drive device (10) according to one of the preceding claims, wherein a torque can be transmitted from the first drive output shaft (16) to the drive axle.

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