Work vehicle drive with multiple electric machines and torque combination assembly

Abstract

A drive assembly for a work vehicle comprises an electric machine input arrangement with a first electric machine configured to generate a first power source, an electric machine input gear arrangement configured to receive the first power source from the first electric machine, and a second electric machine configured to generate a second power source. The drive assembly further comprises a combination gear arrangement coupled to selectively receive the first power source from the electric machine input gear arrangement and the second power source from the second electric machine to generate a combined power; and an electric machine output arrangement configured to receive and transmit the combined power from the combination gear arrangement.

Description

AREA OF REVELATION

[0001] This disclosure relates to drive systems for work vehicles, including drive assemblies for producing multi-speed rotary outputs in implementations such as wheel final drives. BACKGROUND OF THE REVELATION

[0002] Work vehicles, such as those used in agriculture, construction, and forestry, and other conventional vehicles can be powered by an internal combustion engine (e.g., a diesel engine) and / or one or more electrical power sources (e.g., electric motors). Various drive assemblies can be used in the vehicle to effect power transmission from the primary or secondary power source. For example, the vehicle's propulsion system and drivetrain may include one or more drive assemblies to produce one or more output speeds for operating specific vehicle components. For example, wheel final drives, axle drives, and the like may provide one or more gear ratios to transmit final or near-final power to the vehicle's ground-engaging traction wheels or tracks.Efficient and smooth operation across the speed and torque ranges required by such drives is desirable. SUMMARY OF THE REVELATION

[0003] This disclosure provides a multi-gear drive assembly such as can be used in work vehicles (e.g. as towing wheel drives).

[0004] In one aspect, the disclosure provides a drive assembly for a work vehicle comprising an electric machine input arrangement with a first electric machine configured to generate a first power source, an input gear assembly for the electric machine configured to receive the first power source from the first electric machine, and a second electric machine configured to generate a second power source.The drive assembly further includes a combination gear assembly coupled to selectively receive the first power source from the electric machine input gear assembly and the second power source from the second electric machine to produce a combined power; and an electric machine output assembly configured to receive and transmit the combined power from the combination gear assembly.

[0005] In another aspect, the disclosure provides a drive assembly for a work vehicle comprising an electric machine input arrangement with a first electric machine configured to generate a first power source, an electric machine input gear arrangement configured to receive and condition the first power source from the first electric machine according to a variety of gear ratios, and a second electric machine configured to generate a second power source.The drive assembly further includes a combination gear assembly coupled to selectively receive the first power source from the input gear assembly for the electric machine and the second power source from the second electric machine to produce a combined power; an output arrangement of the electric machine configured to receive and transmit the combined power from the combination gear assembly; and a control system coupled to the electric machine input gear assembly.The control system is configured to operate the electric machine input gear arrangement selectively in at least one of: a low state in which the electric machine input gear arrangement transmits the first power source to the combination gear arrangement with a reduced gear ratio, a direct state in which the electric machine input gear arrangement transmits the first power source to the combination gear arrangement with a direct gear ratio, and a disconnected state in which the electric machine input gear arrangement disconnects the first power source through the electric machine input gear arrangement.The control system is configured to operate the electric machine input arrangement selectively in at least one of: a first mode in which the first electric machine is activated, the second electric machine is activated and the electric machine input gear arrangement is put into the low state; a second mode in which the first electric machine is deactivated, the second electric machine is activated and the electric machine input gear arrangement is put into the disconnected state; and a third mode in which the first electric machine is activated, the second electric machine is activated and the electric machine input gear arrangement is put into the direct state.

[0006] In further respects, the disclosure provides a wheel final drive coupled to a wheel of a working vehicle, comprising an electric machine input arrangement with a first electric machine configured to generate a first power source, an electric machine input gear arrangement configured to receive the first power source from the first electric machine, and a second electric machine configured to generate a second power source.The wheel final drive further includes a combination gear assembly coupled to selectively receive the first power source from the electric machine input gear assembly and the second power source from the second electric machine to produce a combined power; an electric machine output assembly configured to receive and transmit the combined power from the combination gear assembly; and a wheel final planetary gear set coupled to receive the combined power from the electric machine output assembly and transmit it to the wheel of the working vehicle.

[0007] The details of one or more embodiments are set forth in the accompanying drawings and the following description. Other features and advantages will become apparent from the description, the drawings, and the claims. BRIEF DESCRIPTION OF THE DRAWINGS Fig. Figure 1 is a schematic side view of an exemplary work vehicle in the form of a wheel loader in which the disclosed drive assembly can be used; Fig. 2A is a schematic representation of certain components of a power transmission and drive train for the exemplary work vehicle of Fig. 1; Fig. 2B is a schematic representation of an exemplary implementation of the disclosed wheel final drive, which is incorporated into the exemplary work vehicle from Fig. 1 can be integrated; Fig. Figure 3 is a partially isometric view of the wheel final drive, showing an electric machine input arrangement and a combination gear arrangement used in the work vehicle of Fig. 1 can be implemented; Fig. Figure 4 is a cross-sectional view of the electrical machine input arrangement and the combination gear arrangement used in the work vehicle of Fig. 1 can be implemented; Fig. Figure 5 is a more detailed cross-sectional view of a first electrical machine input gear arrangement of the electrical machine input arrangement of the Fig. 3 and Fig. 4; Fig. Figure 6 is a partial exploded view of the electrical machine input arrangement and the combination gear arrangement of the Fig. 3 and Fig. 4; and the Fig. 7 and Fig. Figure 8 shows isometric exploded side views of a direct coupling device of the electrical machine input assembly. Fig. 3 and Fig. 4.

[0008] Identical reference symbols in the different drawings denote the same elements. DETAILED DESCRIPTION

[0009] One or more exemplary embodiments of the disclosed drive assembly as a wheel end drive are described below, as shown in the accompanying figures of the drawings briefly described above. Various modifications of the exemplary embodiments may be considered by those skilled in the field.

[0010] As used herein, lists of elements separated by conjunctive expressions (e.g., "and") and preceded by the phrase "one or more of" or "at least one of" denote configurations or arrangements that may include individual elements of the list or a combination thereof. For example, "at least one of A, B, and C" or "one or more of A, B, and C" indicates the possibilities of only A, only B, only C, or any combination of two or more of A, B, and C (e.g., A and B; B and C; A and C; or A, B, and C).

[0011] As used here, the term "axial" refers to a dimension that is, in principle, parallel to an axis of rotation, an axis of symmetry, or a centerline of one or more components. For example, in a cylinder or disk with a centerline and opposite, generally round, ends or faces, the "axial" dimension may refer to the dimension that extends, in principle, parallel to the centerline between the opposite ends or faces. In certain cases, the term "axial" may be used in relation to components that are not cylindrical (or otherwise radially symmetrical). For example, the "axial" dimension for a rectangular housing with a rotating shaft may be considered to be a dimension that is, in principle, parallel to the axis of rotation of the shaft.Furthermore, the term "radial" as used herein may refer to a dimension or a relationship of components with respect to a line extending outward from a common centerline, axis, or similar reference, for example, in a plane of a cylinder or disk perpendicular to the centerline or axis. In certain cases, components may be considered to be "radially" aligned even though one or both components are not cylindrical (or otherwise radially symmetrical). Moreover, the terms "axial" and "radial" (and any derivatives thereof) may encompass directional relationships that are not exactly aligned with the true axial and radial dimensions (e.g., oblique to them), provided that the relationship is predominant in the respective nominal axial or radial dimension.Additionally, the term "circumferential" can refer to a collective tangential dimension that is perpendicular to the radial and axial dimensions around an axis.

[0012] In general, the disclosure provides a drive assembly as a wheel final drive that can be operated selectively or alternatively with dual electric machines at the input side of the drive. Without fundamental changes to many of the internal or external components of the wheel final drive and / or other aspects of the drive train, the drive assembly can receive rotary input power and transmit rotary output power at various speeds and torques in each direction, as desired.Several such drive assemblies with shared internal and external hardware can thus be used for opposing shafts that must rotate in opposite directions to jointly effect movement of the vehicle or a subsystem thereof. This could be used, for example, to provide traction to wheels or tracks on opposite sides of the vehicle that engage the ground, propelling the vehicle forward or backward. In one exemplary implementation, the wheel final drive can be used in a common configuration for all wheels of the vehicle.

[0013] As noted, in certain embodiments, the drive assembly is or includes a wheel final drive power transmission arrangement with one or more gear sets driven by a power source, such as two or more electric machines. The gear set transmits torque from the electric machines directly or via an intermediate or input gear arrangement to an arrangement that combines the torques and transmits them to a rotating output element. The output element may be another intermediate component or directly connected to the driven component. The one or more gear sets may effect gear ratio changes between the input power sources and the output element, transmit power directly without a change in the gear ratio, or a combination thereof.The output element can thus rotate at the same speed or at one or more different speeds than the input power source or input shaft. The gear sets can take any number of different forms, including arrangements with meshing spur gears or other gears, as well as arrangements with one or more planetary gear sets. The drive assembly allows for high reduction ratios, enabling the use of single or interacting electric machines, which can be operated at suitable speeds to provide one or more speed and torque outputs.

[0014] Furthermore, the drive assembly can automatically and / or selectively switch gear ratios (i.e., switch between power flow paths with different gear ratios) as a wheel final drive, particularly in the input gear arrangement associated with one or more of the electric machines. The drive assembly can include one or more active engagement components that engage or disengage to effect power transmission via a power flow path. In this way, clutch configurations can be used to execute the gear ratio changes with appropriate control hardware and logic. By selectively engaging the multiple clutch elements via the actuating components, the drive assembly can thus output multiple speeds and torques.

[0015] In one example, the input coupling devices include a first and second coupling device that are selectively actuated to engage a planetary gear set to modify the power flow of at least one of the electric machines. Engagement of the first coupling device grounds one component of the planetary gear set to produce a first gear ratio and output speed and torque; and engagement of the second coupling device locks other components of the planetary gear set to produce a second gear ratio and output speed and torque. Such a multi-gear drive assembly can thus produce power at different speeds and torques.

[0016] In certain embodiments, a gear assembly is assigned to one of the electric machines on the input side of the wheel final drive. The gear assembly makes it possible to condition the power of the first electric machine before it is combined with power from one or more other electric machines.Such an arrangement provides an input configuration in which the electric machines can be used individually or collectively depending on speed and torque requirements, including a low-speed / high-torque mode in which the torque of the first electric machine is multiplied by the gear ratio of the input gear assembly before being combined with the torque of the second electric machine; an unassisted high-speed mode in which the first electric machine is disconnected and direct power is transferred from the second electric machine through the final drive; and an assisted high-speed mode in which direct power torque from the first electric machine is combined with the torque of the second electric machine.

[0017] The drive assembly disclosed herein may be useful for any number of work or construction vehicle applications, or conventional vehicle applications. In the work vehicle context, the drive assembly may power various subsystems, including different aspects of the vehicle's power transmission and drivetrain. As an example, the drive assembly may be, or be integrated into, a wheel final drive to provide traction power to the vehicle's ground-engaging wheels or tracks. The drive assembly may be integrated into the power and drivetrain at the wheel / track ends (e.g., one on each ground-engaging wheel or track), in which case the drive assembly may be considered an "axle drive" that couples directly, or via a downstream gear set, to the wheel or track carrier hub, as described mainly below.However, the examples discussed below are also applicable to a drive assembly that is positioned at an intermediate position between the wheels / tracks and the drive motor or gearbox.

[0018] The following describes one or more exemplary implementations of the disclosed drive assembly as a wheel final drive. The explanation contained herein may sometimes focus on the exemplary application of a wheel final drive assembly of a wheel loader, but the disclosed drive assembly can also be used for other types of drives, components, and work vehicles, including various other construction machines (e.g., bulldozers, motor graders, dump trucks) as well as various agricultural or forestry machines (e.g., combine harvesters, harvesters, balers, mowers, forestry tractors, and so on) and utility vehicles.

[0019] With reference to Fig. 1. In some embodiments, the disclosed work vehicle 100 can be a wheel loader, although, as noted, the drive assembly described herein can be applied to a variety of machines. As shown, the work vehicle 100 can include a main structural frame or chassis 102 supporting a work attachment 104, which is selectively positioned by various combinations of structural elements (e.g., arms, crossbeams, swivel joints, etc.) and can be moved controllably using any number of actuators, such as hydraulic cylinders. The work vehicle 100 can further be equipped with an operator's cab 106, a power transmission and drive train 108, a control system 110, and a hydraulic system 112. The work vehicle 100 can be supported above the ground by ground-engaging wheels or crawler tracks.In the illustrated example, the work vehicle 100 includes a front axle with steerable front wheels 114 (one on each left or right side of the work vehicle 100) and a rear axle with non-steerable rear wheels 114 (one or more on each left or right side of the work vehicle 100).

[0020] Referring also to Fig. 2A The power transmission and drivetrain 108 includes wheel steering components 118, including various devices (e.g., power steering pumps and lines, steering mechanisms, and the like) that couple manual (e.g., operator steering controls or wheels) and / or automated (via the control system 110) steering inputs to the wheels, such as the steerable wheels 114. The power transmission and drivetrain 108 includes a drive motor, such as an engine 120, which supplies power to the work vehicle 100, either as direct mechanical power or after conversion to electrical or hydraulic power. In one example, the engine 120 is an internal combustion engine, such as a diesel engine, which has a crankshaft for outputting mechanical power. The engine 120 is controlled by an engine control module (not shown) of the control system 110.It should be noted that the use of an internal combustion engine is merely an example and the main power source could be one or more fuel cells, electric motors, hybrid gas-electric motors, or other power-generating devices. As noted below, the motor 120 can, in particular, provide electrical power to one or more wheel final drives 130 assigned to one or more wheels 114.

[0021] The motor 120 provides power to onboard mechanical, electrical, and hydraulic subsystems of the work vehicle 100, which control functions such as tractive power to propel the work vehicle 100 and the delivery of power to other subsystems remote from the work vehicle 100. For example, the motor 120 can provide mechanical power that is converted into an electrical format to operate the electronics of the control system 110 and one or more electric drives of the work vehicle 100. The control system 110 can thus include mechanical-to-electrical power conversion components 124, one or more batteries 126, and associated electronics, including various alternators, generators, voltage regulators, rectifiers, inverters, and the like.The control system 110 can be configured as a computing device or electronic control unit (ECU) with associated processor devices and memory architectures, as a hard-wired computing circuit (or circuits), as a programmable circuit, as a hydraulic, electrical or electrohydraulic control.

[0022] The control system 110 can be configured to perform various computer-based and control functions with respect to the work vehicle 100, including various devices associated with the power and drive train 108, the hydraulic system 112, and various additional components of the work vehicle 100. In some embodiments, the control system 110 can be configured to receive command signals in various formats (e.g., hydraulic signals, voltage signals, etc.) and to output command signals in various formats (e.g., hydraulic signals, voltage signals, current signals, mechanical movements such as rotation, etc.). The control system 110 is configured to operate various aspects of the disclosed drive assembly, including electromechanical actuators (e.g.,Solenoids), which may form part of the power transmission and drive train 108 or part of another subsystem of the working vehicle 100, such as in the wheel final drives 130 discussed below.

[0023] In some embodiments, the control system 110 can receive input commands from a human-machine interface or an operator interface (not shown) and various sensors, units, and systems on board or remotely from the work vehicle 100, or be configured to receive these input commands or otherwise communicate with them. In response, the control system 110 can generate one or more types of commands for implementation by various systems of the work vehicle 100. Additionally or alternatively, the control system 110 can operate autonomously without input from a human operator, communicating with other systems or devices (including other controllers) in various known ways, including via a CAN bus (not shown), wireless or hydraulic communication means, or otherwise.In one example, and as discussed in more detail below, the control system 110 can command current to electromagnets assigned to an actuator assembly to engage and / or disengage various clutches within the drive train 108.

[0024] The motor 120 can also provide mechanical power that is converted into a hydraulic format to drive various hydraulic actuators, pumps, and compressors that pressurize fluid to drive various actuators of the hydraulic system 112 to power components of the work vehicle 100, such as the work attachment 104, the steering and braking of the wheels, a towed work attachment (not shown), or the like. In this example, the work vehicle 100 supports the mounting of the work attachment 104 as a loader with connecting boom arms and a bucket that can be raised and lowered during operation by one or more hydraulic piston-cylinder devices. The hydraulic system 112 can operate autonomously with the control system 110 or in response to commands from an operator input device (e.g., operator controls, operator display device, etc.).The hydraulic system 112 can be connected to and operated from the cab 106 or remotely from the work vehicle 100. It can also include other components (e.g., valves, flow lines, pistons / cylinders, seals / gaskets, etc.) so that various devices can be controlled with and based on hydraulic, mechanical, or other signals and movements.

[0025] As noted above, the drive assembly of this disclosure can be implemented in various subsystems within the work vehicle context and supplied with power in one or more formats. An exemplary drive assembly is described below, implemented and integrated as an electric wheel final drive 130, which forms part of the drive train 108. Such a wheel final drive 130 is installed immediately upstream of each of the four wheels 114 of the work vehicle 100. Each wheel final drive 130 itself, or one or more components thereof, can thus be considered an "axle drive" due to its position near the associated wheel 114 and its function of providing the final or near-final gear ratio for the associated wheel 114. The wheel final drives 130 can be different on each or pairs (e.g., front and rear) of the wheels 114.Due to the bidirectional functionality of the drive assembly, the wheel final drives 130 are identical for all wheels 114, and as such, only one is described below. Although the exemplary wheel final drive 130 is electric, it can also be operated by a different input power format (e.g., hydraulic or mechanical). The exemplary wheel final drive 130 is also described herein as operating with multiple (e.g., two) electric machines for input power. However, the wheel final drive 130 can be operated with more than two electric machines. As described below, various types of intermediate input gearboxes can be used or omitted depending on the operating parameters (e.g., speed and torque) of the electric machines and / or the drive assembly itself and the wheels 114.As described, the exemplary wheel final drive 130 is a multi-mode drive that can be operated to output several speed and torque ranges for traction power to the wheels 114. While the motor 120 thus provides primary power for the electric machine(s), the wheel final drives 130 are the primary power (and speed and torque) influencing factors to the wheels 114, so that a central gearbox, axles, or other upstream speed and torque conversion device can be omitted in the work vehicle 100 and is therefore not included in the exemplary implementation.

[0026] Referring also to Fig. Figure 2B includes as its main components an electric machine input assembly 140, a combination gear assembly 160, an electric machine output assembly 170, and a wheel end planetary gear set 180, which are arranged partially or completely within a final drive housing 132. In general, the wheel final drive 130 can be mounted on the vehicle chassis 102, for example by means of a mounting flange 134 of the housing 132, in a fixed orientation in the case of the rear wheels 114, or pivotably about an upright, generally vertical or vertically inclined steering axis (not shown) in the case of the steered front wheels 114. In general, the outer wheel final drive 130 can be configured in any way suitable for mounting the associated wheel 114.

[0027] In one example, the electrical machine input arrangement 140 includes a first electrical machine (or “motor”) 142 and a second electrical machine (or “motor”) 144. The first electrical machine 142 is coupled to the combination gear arrangement 160 via a first electrical machine input gear arrangement 146 and shafts 148, 150. Generally, the second electrical machine 144 is coupled to the combination gear arrangement 160 via a drive shaft 152. Thus, the torque from the first electrical machine 142 has a transmission ratio set by the electrical machine input gear arrangement 146, and the second electrical machine 144 has a direct (or 1:1) transmission ratio. The electrical machines 142, 144 may be the same or different relative to each other and / or have the same or different speed and / or torque capabilities.

[0028] As described in more detail below, the first electric machine input gear arrangement 146 can include a planetary gear set 220 within a housing 200, which selectively modifies the torque and / or speed of power from the first electric machine 142 depending on the positions of one or more coupling devices 240, 250. In general, the electric machine input gear arrangement 146 enables an improved ability to transmit the range and power of the wheel final drive 130 from the individual and / or interacting electric machines 142, 144 (e.g., without requiring more expensive electric machines and / or gear arrangements). Further details regarding the electric machine input arrangement 146 are provided below.

[0029] The combination gear assembly 160 generally operates to combine the power inputs from the first and second electric machines 142, 144 of the electric machine input assembly 140. In one example, the combination gear assembly 160 includes a first outer gear 162, which receives power from the first electric machine 142 (via the first electric machine input gear assembly 146), and a second outer gear 164, which receives power from the second electric machine 144. The outer gears 162, 164 mesh with a central gear 166, which is mounted on a drive shaft 168, serving to combine the torque from the first and second electric machines 142, 144.

[0030] The output assembly of the electric machine 170 is configured to receive power from the combination gear assembly 160 and transmit the power to the wheel end planetary gear set 180, as discussed below. In one example, the output assembly of the electric machine 170 includes an output gear set 172 of the electric machine 170 to modify the characteristics of the power output. A wheel end drive shaft 174 can couple the output of the electric machine 170 to the wheel end planetary gear set 180, which in turn transmits the power to the associated wheel 114.

[0031] Depending on the speed and torque requirements, the wheel end planetary gear set 180 can take various forms or be omitted. In one example, the wheel end planetary gear set 180 is a single-stage planetary gear set with a sun gear 182 and a carrier 184 that carries planet gears 186 which are meshed with a ring gear 188. In one example, the carrier 184 can be attached directly to a wheel hub (not shown) of the associated wheel 114, or the carrier 184 can be contained within an outer wheel end housing section 136 of the housing 132 that is coupled to the wheel hub. The ring gear 188 can be attached to the mounting flange 134 introduced above or formed integrally with it.Thus, the exemplary outer gear set 180 is a sun gear-in, carrier-out planetary arrangement, although various other configurations are provided, including the omission of an outer gear set or the carrier and / or the outer wheel end housing section 136 formed by or directly coupled to the wheel hub of the wheel 114. The wheel end drive 130 further comprises one or more wheel bearings 190 within the housing 132 to enable the carrier 184 and / or the outer wheel end housing section 136 to rotate relative to the vehicle chassis 102 about a general lateral or side-by-side fixed or pivoting drive or axis of rotation.

[0032] With reference to the Fig. Reference 3-8 provides the following additional details regarding the electrical machine input arrangement 140 and the combination gear arrangement 160, which may be implemented in the wheel final drive 130 introduced above.

[0033] In one example, Fig. 3 in particular the first electric machine 142, which is coupled to the combination gear arrangement 160 via the first electric machine input gear arrangement 146, and the second electric machine 144, which is coupled directly (e.g. without an intermediate gear arrangement to modify speed and / or torque) to the combination gear arrangement 160. In the view of Fig. 3. The housings (e.g., housing 200) were made of Fig. 2B) of the first electric machine input gear assembly 146 and the combination gear assembly 160 for illustration. As shown, the electric machine input gear assembly 146 is coupled to drive the first outer gear 162 of the combination gear assembly 160 with power from the first electric machine 142; and the second outer gear 164 is driven directly by the second electric machine 144. In turn, the first and second outer gears 162 and 164 are each coupled to the central gear 166 of the combination gear assembly 160, which serves to combine the torques from the electric machines 142 and 144 to output the power via the drive shaft 168 to the output arrangement of the electric machine 170 discussed above.In this way, the first and second electric machines 142, 144 can provide output power through the combination gear arrangement 160 in different modes, in which the electric machines 142, 144 operate in combination with each other or individually, depending on the torque and speed requirements for the wheel final drive 130. In this example, the first electric machine input gear arrangement 146 enables a variation or conditioning of the power at the output arrangement of the electric machine 170 (. Fig. 2B), which would otherwise pose a challenge for the two electrical machines 142, 144, as explained in more detail below.

[0034] Now, the focus will shift to... Fig. 4 Reference is made to Figure 4, which shows a cross-sectional view of the electrical machine input arrangement 140 and the combination gear arrangement 160, and to Figure 4. Fig. Figure 5 shows a detailed view of the first electric machine input gear arrangement 146. As in Fig. 3. The housings (e.g., housing 200) of the electrical machine input assembly 140 and the combination gear assembly 160 were placed in the Fig. 4 and Fig. Number 5 has been omitted for illustrative purposes.

[0035] As shown, the first electric machine input gear arrangement 146 can receive power from the first electric machine 142 via an input shaft (or drive shaft) 210 coupled to the shaft 150 of the electric machine, and deliver power via an output shaft 230 (or other type of output element) coupled to or integral with the shaft 152 of the combination gear arrangement 160. As presented above, the first electric machine input gear arrangement 146 in this example includes an input planetary gear set 220 to selectively condition the power between the input and output shafts 210, 230.

[0036] Depending on the speed and torque requirements, the input planetary gear set 220 can take various forms. In one example, the input planetary gear set 220 is a single-stage planetary gear set with a sun gear 222 and a carrier 224 that carries planet gears 226, which are positioned to mesh with a ring gear 228. In another example, the sun gear 222 is integrally attached to the input shaft 210 or otherwise connected to it, and the carrier 224 can be attached to or toothed on the gear set output shaft 230. Thus, the exemplary input planetary gear set 220 is a sun-gear-in, carrier-out planetary arrangement, although various other configurations can be provided.

[0037] Power through the input planetary gear set 220 can be enabled and / or modified by one or more of the coupling devices, including a first (or low-) coupling device 240 and a second (or direct or high-) coupling device 250. It is further noted that Fig. 6. Referenced, which is an exploded view, generally the view of Fig. 3 and corresponds and the Fig. 7 and Fig. 8, the exploded views of each side of the direct coupling device 250 are shown.

[0038] In general, the low-coupling device 240 is formed by a bidirectional coupling element (or “driver”) 242 that selectively engages with the ring gear 228. In one example, the coupling element 242 is generally annular with one or more rows of splined teeth and / or other engagement elements (which, for example, represent a combination of cavities, projections, teeth, or drivers configured for circumferential engagement). In particular, the low-coupling device 240 is formed by a first set of splined teeth that allow axial movement within the housing 200 ( Fig. 2B) towards and away from the ring gear 228, fixed or locked to the stationary housing 200 in a rotationally fixed manner. As introduced above, the housing 200 of the assembly 146 acts as a reaction element that is fixed axially and radially with respect to the axis of rotation against which forces can be exerted. The low-disengagement device 240 has a disengaged position in which the low-disengagement device 240 is separated from the ring gear 228, so that the ring gear 228 can rotate relative to the housing 200 ( Fig. 2B); and the low-coupling device 240 has an engaged position in which the engagement elements of the low-coupling device 240 engage with the ring gear 228, so that the low-coupling device 240 locks the ring gear 228 relative to the housing 200 ( Fig. 2B) (e.g., to prevent rotation). In general, the low-disengagement device 240 can be axially repositioned between the engaged and disengaged positions by one or more actuators to implement a modification of the speed ratio and torque through the input planetary gear set 220. As discussed below, the engaged position of the low-disengagement device 240 allows power to flow through the gear set 220 at a lower (e.g., higher) gear ratio.

[0039] Although not shown in detail, the low-coupling device 240 can be axially repositioned by one or more suitable actuators, wherein one or more electromechanical solenoids, hydraulic actuators and / or springs are arranged inside and / or outside the housing 200 ( Fig. 2B). Such actuators can be commanded based on signals from the control system 110.

[0040] The direct coupling device 250 is formed by one or more support elements 252, which support a first coupling element (or “driver”) 254 and a second coupling element (or “driver”) 256. As shown, the first and second coupling elements 254, 256 are annular and generally concentric with each other, with the first coupling element 254 positioned radially inside the second coupling element 256. In fact, the first and second low-profile coupling elements 254, 256 can be considered a forked coupling arrangement to influence the power flow in individual directions of rotation.

[0041] The first and second coupling elements 254, 256 are arranged within a coupling frame 258. As is best done in Fig. As shown in Figure 8, the coupling frame 258 has an outer cylindrical flange with internal splines and an inner cylindrical flange with internal and external splines. The first coupling element 254 has external splines that engage with corresponding internal splines along the outer cylindrical flange of the coupling frame 258; and the second coupling element 256 has internal splines that engage with corresponding external splines along the inner cylindrical flange of the coupling frame 258. The spline arrangements allow the first and second coupling elements 254, 256 to move axially within the coupling frame 258 between their respective engaged and disengaged positions, which are discussed below.

[0042] In addition to the splined couplings between the first and second coupling elements 254, 256 and the coupling frame 258, the internal splines on the inner cylindrical flange of the coupling frame 258 also engage with corresponding splines on the input shaft 210. As a result, the first and second coupling elements 254, 256 and the coupling frame 258 are interlocked and configured to rotate with the input shaft 210.

[0043] The direct coupling device 250 further includes a coupling frame cover 260 and a coupling locking element 262, which are positioned on the other axial side of the coupling frame 258 relative to the first and second coupling elements 254, 256, e.g. axially between the coupling elements 254, 256 and the planetary gear set 220. The coupling frame cover 260 is attached to the coupling locking element 262 and the coupling locking element 262 is attached to the ring gear 228, as best shown in Fig. 5 shown.

[0044] In one embodiment, each of the coupling elements 254, 256 is provided with engagement elements (which, for example, represent a combination of cavities, projections, teeth, or drivers configured for circumferential engagement) that are oriented toward the coupling frame cover 260. In this example, each of the engagement elements of the coupling elements 254, 256 is a projection with a square or perpendicular side and an inclined side. The square sides of the engagement elements of the first coupling element 254 are oriented in a direction of rotation opposite to the square sides of the engagement elements of the second coupling element 256. In this way, the coupling elements 254, 256 are oriented to be selectively engaged in different directions of rotation.

[0045] The coupling frame cover 260 includes circumferential rows of engagement elements (which are, for example, a combination of cavities, projections, teeth, or lugs configured for circumferential engagement) corresponding to the radial positions of the engagement elements extending from the coupling elements 254, 256. While the engagement elements of the coupling elements 254, 256 are projecting vertical and inclined structures, as noted above, the engagement elements of the coupling frame cover 260 are recesses or slots, each of which has a corresponding square or perpendicular side and an inclined side facing circumferentially to the radially paired set of engagement elements of the coupling elements 254, 256, which engage selectively in a single direction of rotation for each element 254, 256.

[0046] As a result of this arrangement, each of the coupling elements 254, 256 can selectively interact with the coupling frame cover 260 in engaged and disengaged positions, e.g., so that the input shaft 210 can selectively interact with the ring gear 228. In each disengaged position, the respective coupling element 254, 256 is positioned axially at a distance from the coupling frame cover 260; and in each engaged position, the respective coupling element 254, 256 is moved towards the coupling frame cover 260, so that the engagement elements of the respective coupling element 254, 256 and the coupling frame cover 260 engage with each other.

[0047] Although not shown in detail, the direct coupling device 250 can be axially repositioned by one or more suitable actuators, wherein one or more electromechanical solenoids, hydraulic actuators and / or springs are arranged inside and / or outside the housing 200 ( Fig. 2B). Such actuators can be commanded based on signals from the control system 110.

[0048] In the disengaged positions, the coupling elements 254 and 256 can rotate independently of the coupling frame cover 260. However, when the first coupling element 254 is in the engaged position, it is locked to the coupling frame cover 260 in the first direction of rotation. Due to the inclined engagement elements, when the first coupling element 254 is in the engaged position, it can override the coupling frame cover 260 in the second direction of rotation. Similarly, when the second coupling element 256 is in the engaged position, it is locked to the coupling frame cover 260 in the second direction of rotation; and due to the inclined engagement elements, when the second coupling element 256 is in the engaged position, it can override the coupling frame cover 260 in the first direction of rotation.When both coupling elements 254, 256 are engaged, the coupling elements 254, 256 are locked together with the coupling frame cover 260 in both directions of rotation.

[0049] As noted above, the coupling elements 254 and 256 are toothed with the coupling frame 258, which in turn is toothed with the input shaft 210; and the coupling frame cover 260 is attached to the coupling locking element 262, which in turn is attached to the ring gear 228. Thus, when the first coupling element 254 and / or the second coupling element 256 are in the engaged position(s), the ring gear 228 is fixed against rotation on the input shaft 210 in the corresponding direction(s) of rotation. Consequently, these engagement positions allow the entire planetary gear set 220 (e.g., the sun gear 222, the carrier 224, the planet gears 226, and the ring gear 228) to rotate as a unit with the input shaft 210 about an axis defined by the input shaft 210.In other words, the inset positions of the coupling elements 254, 256 allow a direct or 1:1 ratio of the first electric machine 142 and the input shaft 210 relative to the output shaft 230.

[0050] As a result of the configuration of the coupling devices 240, 250 and the planetary gear set 220, it can be assumed that the electric machine input gear arrangement 146 has at least three states, including a disconnected state, a low state and a direct state.

[0051] In the disengaged state, the low-coupling device 240 and the direct-coupling device 250 are in the disengaged position. As a result, any torque from the first electric machine 142 is effectively prevented from being transmitted through the electric machine input gear assembly 146 to the combination gear assembly 160 and the downstream components. The disengaged state can be used, for example, when power from the first electric machine 142 is not required or desired for the wheel final drive 130.

[0052] In the low-speed state, the low-speed coupling device 240 is in the engaged position, and the direct-speed coupling device 250 is in the disengaged position in each direction of rotation. As a result of this configuration, power flows from the first electric motor 142 through the input shaft 210 to the sun gear 222 and the planet gears 226. Since the ring gear 228 is further locked to the housing 200 by the low-speed coupling device 240, the power flows through the planet gears 226 to drive the planet carrier 224 and the output shaft 230. Thus, the speed of the power is reduced by the gear ratio between the sun gear 222, the planet gears 226, and the planet carrier 224, thereby reducing the speed of the power while increasing the torque output. As an example, the reduction through this power flow path can be 4:1, 5:1, or higher or lower gear ratios.

[0053] In the direct state, the low-coupling device 240 is positioned in the disengaged position, and the direct-coupling device 250 is positioned in the engaged position in at least the commanded direction of rotation. As noted above, the first coupling element 254 is arranged in the engaged position to transmit power in the first direction of rotation, and the second coupling element 256 is arranged in the engaged position to transmit power in the second direction of rotation. As also noted above, the engagement of the direct-coupling device 250 allows the entire input planetary gear set 220 to rotate as a single unit, resulting in a direct (or 1:1) transmission ratio.

[0054] The different states of the first electric machine 142 and the combination of the first electric machine 142 and the second electric machine 144 enable the electric machine input arrangement 140 to operate in one or more operating modes, including a low speed / high torque (or first) mode, a non-supported high speed (or second) mode and a supportive high speed (or third) mode.

[0055] In one example, the low-speed / high-torque mode can be useful during situations where the vehicle operates at relatively low speeds and / or where greater torque is required, such as when starting and / or climbing an incline. In the low-speed / high-torque mode, the electric machine input gear arrangement 146 is brought into the low state (e.g., with the low-speed clutch device 240 engaged and the direct-speed clutch device 250 disengaged), and each electric machine 142, 144 is activated. As a result of this arrangement, the output speed is reduced by the gear ratio resulting from the engagement of the low-speed clutch device 240, thereby increasing the torque at a corresponding gear ratio (e.g., by a multiple of 4 or 5 in the example discussed above).In the combination gear arrangement 160, the torque of the first electric machine 142 is combined with the torque of the second electric machine 144 by the electric machine input gear arrangement 146, as reflected by the following output torque equation for the low speed / high torque mode:. TO=(TM1)(GR)+TM2 where: T O the output torque is; T M1 the torque of the first electric machine is; GR is the torque multiplier, which results from the gear ratio; and T M2 The torque is from the second electric machine.

[0056] In one example, the unsupported high-speed mode can be useful in situations where the rotational speeds are higher than those of the low-speed / high-torque mode and / or when the additional torque from the first electric machine 142 is not required for the requested or desired application. In the unsupported high-speed mode, the electric machine input gear assembly 146 is placed in the disengaged state (e.g., when the low-speed clutch device 240 and the direct-speed clutch device 250 are disengaged), the first electric machine 142 is deactivated, and the second electric machine 144 is activated. As a result of this arrangement, only the torque of the second electric machine 144 is transmitted through the combination gear assembly 160, as reflected by the following output torque equation for the unsupported high-speed mode: TO=TM2 where: T Othe output torque is; and T M2 The torque is from the second electric machine.

[0057] In one example, the assisted high-speed mode can be useful in situations where the rotational speeds are higher than those of the low-speed / high-torque mode and / or when the additional torque from the first electric machine 142 is required or advantageous for the requested or desired application. In the assisted high-speed mode, the electric machine input gear assembly 146 is placed in the direct state (e.g., when the low-speed clutch device 240 is disengaged and the direct-speed clutch device 250 is engaged in at least the commanded direction of rotation), and each electric machine 142, 144 is activated. As a result of this arrangement, the torques of both electric machines 142, 144 are combined in the combination gear assembly, as reflected by the following output torque equation for the assisted high-speed mode: TO=TM1+TM2 where: T Othe output torque is; T M1 the torque of the first electric machine is; and T M2 The torque is from the second electric machine.

[0058] Accordingly, the exemplary embodiments discussed above provide a drive assembly as a wheel final drive for a work vehicle. The dual electric machines on the input side of the wheel final drive can be operated individually and cooperatively, as desired or required, to provide a single output with a full torque and speed range. In particular, the wheel final drive discussed above allows the use of two electric machines with relatively low torque (e.g., at a relatively lower cost) for the same output as a single high-torque motor.

[0059] Furthermore, the following examples are provided, which are numbered for ease of reference. 1. A drive assembly for a work vehicle, comprising: an electric machine input arrangement, comprising: a first electric machine configured to generate a first energy source, an electric machine input gear arrangement configured to receive the first energy source from the first electric machine, and a second electric machine configured to generate a second energy source; a combination gear arrangement coupled to selectively receive the first energy source from the electric machine input gear arrangement and the second energy source from the second electric machine to generate a combined energy; and an electric machine output arrangement configured to receive and transmit the combined energy from the combination gear arrangement. 2. The drive assembly according to Example 1, wherein the electric machine input gear arrangement is configured to selectively condition the first power source for the combination gear arrangement according to a variety of gear ratios, and wherein the combination gear arrangement is configured to directly receive the second power source from the second electric machine. 3. The drive assembly according to Example 1, further comprising a control system coupled to and configured with the electric machine input gear arrangement to selectively operate the electric machine input gear arrangement in at least one low state, in which the electric machine input gear arrangement transmits the first power source to the combination gear arrangement in a reduced gear ratio, and a direct state, in which the electric machine input gear arrangement transmits the first power source to the combination gear arrangement in a direct gear ratio. 4. The drive assembly according to Example 3, wherein the control system is further configured to operate the electric machine input gear arrangement in a disconnected state in which the electric machine input gear arrangement disconnects the first power source through the electric machine input gear arrangement. 5. The drive assembly according to Example 4, wherein the control system is configured to operate the electric machine input arrangement selectively in at least one of: a first mode in which the first electric machine is activated, the second electric machine is activated and the electric machine input gear arrangement is placed in the low state, and a second mode in which the first electric machine is deactivated, the second electric machine is activated and the electric machine input gear arrangement is placed in the disconnected state. 6. The drive assembly according to Example 5, wherein the control system is further configured to selectively operate the electric machine input arrangement in a third mode in which the first electric machine is activated, the second electric machine is activated, and the electric machine input gear arrangement is put into the direct state. 7. The drive assembly according to Example 6, wherein the electrical input arrangement comprises: a housing containing a first housing element forming a reaction element; a drive shaft rotatable about a drive axis relative to the reaction element in a first direction of rotation and alternatively in a second direction of rotation; a planetary gear set coupled to the drive shaft and configured to selectively rotate an output element in the first direction of rotation and in the second direction of rotation; a first coupling device coupled to the reaction element and configured to connect the planetary gear set to the reaction element to impart a first rotational speed to the output element in the first direction of rotation and in the second direction of rotation;and a second coupling device coupled to form an interface with the planetary gear set to selectively effect a second rotational speed of the output element in the first direction of rotation and in the second direction of rotation. 8. The drive assembly according to Example 7, wherein the first coupling device includes a bidirectional coupling element that selectively engages with the planetary gear set. 9. The drive assembly according to Example 8, wherein the second coupling device includes a first coupling element configured to form an interface with the planetary gear set in the first direction of rotation, and a second coupling element configured to form an interface with the planetary gear set in the second direction of rotation. 10. The drive assembly according to Example 9, wherein the planetary gear set includes at least one sun gear attached to the drive shaft, at least one planet gear meshing with the sun gear, at least one carrier supporting the at least one planet gear, and at least one ring gear meshing with the at least one planet gear; and wherein the first coupling device is configured to communicate with the planetary gear set by locking the ring gear to the housing. 11. Drive assembly according to Example 10, wherein the second coupling device is configured to communicate with the planetary gear set by rotatably attaching the drive shaft to the at least one planet carrier. 12. The drive assembly according to Example 11, wherein the second coupling device includes a coupling frame toothed with the drive shaft which radially supports the first coupling element and the second coupling element to move axially between respective engaged and disengaged positions in order to selectively interface with the planetary gear set. 13. The drive assembly according to Example 12, wherein the second coupling device further comprises: a coupling frame cover configured to accommodate at least one section of the first coupling element and the second coupling element when the second coupling device forms an interface with the planetary gear set, and a coupling lock securing the coupling frame cover to the ring gear. 14. The drive assembly according to Example 13, wherein the at least one planet carrier is rotatably fixed to the output element. 15. The drive assembly according to Example 1, wherein the drive assembly is a wheel final drive for a wheel of the work vehicle and wherein the output arrangement of the electric machine is coupled to transmit the combined power to the wheel.

[0060] According to a person skilled in the art, certain aspects of the disclosed subject matter can be implemented as a method, a system (e.g., a work vehicle control system included in a work vehicle), or a computer program product. Accordingly, certain embodiments can be implemented entirely as hardware, entirely as software (including firmware, resident software, microcode, etc.), or as a combination of software and hardware (and other) features. Furthermore, certain embodiments can be executed in the form of a computer program on a computer-compatible storage medium with computer-compatible program code embedded in the medium.

[0061] Any suitable computer-compatible or computer-readable medium may be used. The computer-compatible medium may be a computer-readable signaling medium or a computer-readable storage medium. A computer-compatible or computer-readable storage medium (including a storage device associated with a computer system or electronic client device) may, for example, be an electronic, magnetic, optical, electromagnetic, infrared, or semiconductor system, apparatus, device, or a suitable combination of the foregoing, but is not limited to such.More specific examples (a non-exhaustive list) of computer-readable medium would include: an electrical connection with one or more cables, a portable computer disk, a hard disk, random access memory (RAM), read-only memory (ROM), erasable programmable read-only memory (EPROM or flash memory), optical storage, portable read-only storage (CD-ROM), and an optical storage device. For the purposes of this document, computer-usable or computer-readable storage medium can be any physical medium capable of containing or storing a program for use by or in conjunction with the command-execution system, device, or apparatus.

[0062] A computer-readable signaling medium can include a propagating data signal containing computer-readable program code, for example, in the baseband or as part of a carrier wave. Such a propagating signal can take a variety of forms, including, but not limited to, electromagnetic, optical, or a suitable combination thereof. A computer-readable signaling medium can be non-transitory and can be any computer-readable medium that is not a computer-readable storage medium and that can communicate, propagate, or transport a program for use by or in conjunction with a command-execution system, device, or apparatus.

[0063] Aspects of certain embodiments described herein can be described with reference to flowchart representations and / or block diagrams of processes, devices (systems), and computer programs according to the embodiments of the invention. It is assumed that each block of such flowchart representations and / or block diagrams, and combinations of blocks in such flowchart representations and / or block diagrams, can be implemented by computer program instructions.These computer program instructions can be provided to a processor of a general-purpose computer, a special-purpose computer, or any other programmable data processing device for the manufacture of a machine, such that the instructions executed by the processor of the computer or other programmable data processing device create a device for performing the functions / actions specified in the flowchart and / or block diagram block or blocks.

[0064] These computer program instructions can also be stored in a computer-readable memory that can instruct a computer or other programmable data processing device to operate in a particular manner, such that the instructions stored in the computer-readable memory produce a manufactured item, including instructions that implement the function / action specified in the flowchart and / or block diagram or in blocks.

[0065] The computer program instructions can also be loaded into a computer or other programmable data processing device to initiate a series of operational steps that are executed on the computer or other programmable device to produce a computer-implemented process, so that the instructions executed on the computer or other programmable device provide steps to implement the functions / actions specified in the flowchart and / or block diagram block or blocks.

[0066] Each flowchart and block diagram in the figures or any similar preceding explanation may illustrate the architecture, functionality, and operation of possible implementations of systems, procedures, and computer program products according to various embodiments of the present disclosure. In this context, each block in the flowchart or block diagrams may represent a module, segment, or portion of code containing one or more executable instructions for implementing the specified logical functions. It should also be noted that in some alternative implementations, the functions specified in the block (or otherwise described herein) may appear in the order shown in the figures.For example, two consecutive blocks (or two consecutive operations) can essentially be executed concurrently, or the blocks (or operations) can sometimes be executed in reverse order, depending on the specific functionality. It should also be noted that each block of a block diagram and / or flowchart representation, and combinations of blocks within a block diagram and / or flowchart representation, can be implemented by specialized hardware-based systems that perform the specified functions or actions, or by combinations of hardware and computer instructions for specific purposes.

[0067] The terminology used herein serves solely to describe certain exemplary embodiments and is in no way intended to be restrictive. As used herein, the singular forms "a" and "the" are intended to include the plural forms unless the context clearly excludes this. Furthermore, it is understood that the terms "comprises" and / or "comprehensive," when used in this patent specification, indicate the presence of specified features, integers, steps, operations, elements, and / or components, but do not exclude the presence or addition of one or more other features, integers, steps, operations, elements, components, and / or groups thereof.

[0068] The description of the present disclosure is provided for illustrative and descriptive purposes, but is not intended to be exhaustive or limited to the disclosure as disclosed. Many modifications and variations are obvious to those skilled in the art without deviating from the scope and meaning of the disclosure. The embodiments expressly mentioned herein have been selected and described to best explain the principles of the disclosure and their practical application, and to enable other persons skilled in the art to understand the disclosure and to recognize many alternatives, modifications, and deviations from the examples described. Accordingly, various embodiments and implementations other than those explicitly described are within the scope of the following claims.

Claims

[1] Drive assembly (130) for a work vehicle (100), comprising: an electrical machine input arrangement (140), comprising: a first electrical machine (142) configured to generate a first power source, an electric machine input gear arrangement (146) configured to receive the first power source from the first electric machine (142), the first electric machine (142) being coupled to a combination gear arrangement (160) via the electric machine input gear arrangement (146) and shafts (148, 150), and a second electric machine (144) configured to generate a second power source, a stationary housing (200) which is fixed axially and radially with respect to a rotation axis of the shafts (148, 150) as a reaction element; an input shaft (210) with a drive shaft, wherein the input shaft (210) is rotatable relative to the reaction element in a first direction of rotation and alternatively in a second direction of rotation about its drive shaft; a planetary gear set (220) coupled to the input shaft (210) and configured to selectively rotate an output shaft (230) in the first direction of rotation or in the second direction of rotation; a first coupling device (240) coupled to the reaction element and configured to connect the planetary gear set (220) to the reaction element to effect a first rotational speed of the output shaft (230) in the first direction of rotation or in the second direction of rotation; and a second coupling device (250) which is coupled to form a connection with the planetary gear set (220) in order to selectively produce a second rotational speed of the output shaft (230) in the first direction of rotation or in the second direction of rotation; the combination gear arrangement (160) which is coupled to selectively receive the first power source from the electric machine input gear arrangement (146) and the second power source from the second electric machine (144) to generate a combined power; and an output arrangement of the electric machine (170) which is configured to receive and transmit the combined power from the combination gear arrangement (160). [2] Drive assembly (130) according to claim 1, wherein the electric machine input gear arrangement (146) is configured to selectively adapt the first power source to the combination gear arrangement (160) according to a plurality of gear ratios, and wherein the combination gear arrangement (160) is configured to receive the second power source directly from the second electric machine (144). [3] Drive assembly (130) according to claim 1 or 2, further comprising a control system (110) coupled to the electric machine input gear arrangement (146) and configured to selectively operate the electric machine input gear arrangement (146) in at least one low state in which the electric machine input gear arrangement (146) transmits the first power source to the combination gear arrangement (160) in a reduced transmission ratio, and a direct state in which the electric machine input arrangement (146) transmits the first power source to the combination gear arrangement (160) in a direct transmission ratio. [4] Drive assembly (130) according to claim 3, wherein the control system (110) is further configured to operate the electrical machine input gear arrangement (146) in a disconnected state in which the electrical machine input gear arrangement (146) disconnects the first power source through the electrical machine input gear arrangement (146). [5] Drive assembly (130) according to claim 4, wherein the control system (110) is configured to selectively control the electrical machine input arrangement (140) in at least one of: a first mode in which the first electric machine (142) is activated, the second electric machine (144) is activated and the electric machine input gear arrangement (146) is moved to the low state, and a second mode in which the first electric machine (142) is deactivated, the second electric machine (144) is activated and the electric machine input gear arrangement (146) is placed in the separated state. [6] Drive assembly (130) according to claim 5, wherein the control system (110) is further configured to selectively operate the electrical machine input arrangement (140) in a third mode in which the first electrical machine (142) is activated, the second electrical machine (144) is activated and the electrical machine input gear arrangement (146) is put into the direct state. [7] Drive assembly (130) according to claim 6, wherein the first coupling device (240) includes a bidirectional coupling element (242) that selectively engages with the planetary gear set (220). [8] Drive assembly (130) according to claim 7, wherein the second coupling device (250) includes a first coupling element (254) configured to engage with the planetary gear set (220) to form a connection in the first direction of rotation, and a second coupling element (256) is configured to form a connection with the planetary gear set (220) in the second direction of rotation. [9] Drive assembly (130) according to claim 8, wherein the planetary gear set (220) includes at least one sun gear (222) fixed to the drive shaft (210), at least one planet gear (226) meshing with the sun gear (222), at least one carrier (224) supporting the at least one planet gear (226), and at least one ring gear (228) meshing with the at least one planet gear (226); and wherein the first coupling device (240) is configured to establish a connection with the planetary gear set (220) by locking the ring gear (228) to the housing (200). [10] Drive assembly (130) according to claim 9, wherein the second coupling device (250) is configured to establish a connection with the planetary gear set (220) by rotatably attaching the input shaft (210) to the at least one planet carrier (224). [11] Drive assembly (130) according to claim 10, wherein the second coupling device (250) includes a coupling frame (258) which is toothed with the input shaft (210) and which radially supports the first coupling element (254) and the second coupling element (256) to move axially between their respective engaged and disengaged positions in order to selectively form a connection with the planetary gear set (220). [12] Drive assembly (130) according to claim 11, wherein the second coupling device (250) further comprises: a coupling frame cover (260) configured to accommodate at least one section of the first coupling element (254) and the second coupling element (256) when the second coupling device (250) forms an interface with the planetary gear set (220), and a coupling lock (262) that secures the coupling frame cover (260) to the ring gear (228). [13] Drive assembly (130) according to claim 12, wherein the at least one planet carrier (184) is rotatably fixed to the output shaft (230). [14] Drive assembly (130) according to any one of claims 1 to 13, wherein the drive assembly (130) is a wheel final drive for a wheel (114) of the work vehicle (100), and wherein the output arrangement of the electric machine (140) is coupled to transmit the combined power to the wheel (114).

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