Electric drive module, chassis platform, and wheeled transport machinery

Abstract

The present disclosure relates to an electric drive module, a chassis platform, and a wheeled transport machine. The chassis platform comprises a frame and at least one pair of identical electric drive modules connected to the frame; each electric drive module is configured to independently drive one wheel of a wheeled transport machine; each electric drive module comprises a driving assembly, a steering assembly, and a suspension assembly; the driving assembly is configured to be connected between the frame and the wheel to drive the wheel to rotate; the steering assembly is configured to be connected between the frame and the wheel to drive the wheel to turn; and the suspension assembly is configured to be connected between the frame and the steering assembly. The chassis platform comprises at least one pair of the electric drive modules. The wheeled transport machine comprises the electric drive modules or the chassis platform.

Description

ELECTRIC DRIVE MODULE, CHASSIS PLATFORM, AND WHEELED TRANSPORT MACHINERY CROSS-REFERENCE TO RELATED APPLICATIONS The present disclosure is based on a Chinese application filed on December 30, 2024 with an application number of 202411970475.3, and claims the priority right thereof, the entire contents of which are hereby incorporated by reference. TECHNICAL FIELD The present disclosure relates to an electric drive module, a chassis platform and a wheeled transport machinery. BACKGROUND ART In the related art, wheeled transport machinery, such as off-highway wide-body dump trucks and mining dump trucks, usually faces the problem of poor universality of parts of the power transmission system, especially in the matching of core parts such as engines, motors, gearboxes and drive axles. For example, mining trucks of different tonnages not only need to be equipped with engines of corresponding power according to their load capacity, but also need to be fitted with motors of matching torque and adapted drive axles. This not only increases the production, procurement and management costs of parts of equipment manufacturers, but also raises the manufacturing costs of products. In addition, the costs of spare parts management and maintenance borne by users during operation are also increased accordingly. It should be noted that the information disclosed in the background art of the present disclosure is only intended to enhance the understanding of the overall background of the present disclosure, and shall not be deemed as an acknowledgement or any form of implication that such information constitutes the prior art already known to those skilled in the art. CONTENT OF THE INVENTION The present disclosure provides an electric drive module, a chassis platform and a wheeled transport machinery, achieving a modular design for the drive system of the transport machinery. In a first aspect of the present disclosure, an electric drive module for a chassis platform of a wheeled transport machinery is provided, where the chassis platform includes a frame and at least one pair of identical electric drive modules connected to the frame. Each of the electric drive modules is configured to independently drive one wheel of the wheeled transport machinery, and each of the electric drive modules includes: a drive assembly configured to be connected between the frame and the wheel for driving the wheel to rotate; a steering assembly configured to be connected between the frame and the wheel for driving the wheel to steer; and a suspension assembly configured to be connected between the frame and the steering assembly. In some embodiments, the drive assembly is symmetrical about a radial cross-section of the wheel; and / or the suspension assembly is symmetrical about a radial cross-section of the wheel. In some embodiments, the steering assembly includes a steering knuckle, which is symmetrical about a radial cross-section of the wheel and is fixedly connected to the wheel. In some embodiments, the steering assembly further includes a steering mechanism, which is movably connected between the frame and the steering knuckle. In some embodiments, the steering mechanism includes a steering knuckle arm and a steering cylinder, the steering knuckle arm being fixedly connected to the steering knuckle, and both ends of the steering cylinder being hingedly connected to the steering knuckle arm and the frame, respectively. In some embodiments, the suspension assembly is hingedly connected with the steering knuckle. In some embodiments, the suspension assembly includes a suspension cylinder, both ends of which are hingedly connected to the frame and the steering knuckle, respectively. In some embodiments, the suspension assembly includes a first fork arm, the steering knuckle is provided with a first hinge portion, and both ends of the first fork arm are hingedly connected to the frame and the first hinge portion, respectively. In some embodiments, the suspension assembly further includes a second fork arm, the steering knuckle is provided with a second hinge portion spaced apart from the first hinge portion in a vertical direction, and both ends of the second fork arm are hingedly connected to the frame and the second hinge portion, respectively. In some embodiments, the first fork arm is spherically hinged to the first hinge portion; and / or the second fork arm is spherically hinged to the second hinge portion. In some embodiments, the drive assembly includes a motor and a transmission shaft, the motor is mounted inside the frame, and both ends of the transmission shaft are connected to the motor and the wheel, respectively. In some embodiments, the frame includes a support beam and a torsion-resistant tube connected to the support beam, and the motor is mounted inside the torsion resistant tube. In some embodiments, the steering knuckle is provided with a through-hole extending along an axial direction of the wheel, and the transmission shaft is inserted through the through-hole. In some embodiments, the drive assembly further includes a reducer, which is connected between the transmission shaft and the wheel. In some embodiments, the reducer includes a spur gear reducer. In some embodiments, the drive assembly further includes a braking device integrated onto the reducer. In some embodiments, the drive assembly is removably connected to both the frame and the wheel; and / or the steering assembly is removably connected to both the frame and the wheel; and / or the suspension assembly is removably connected to the frame. According to a second aspect of the present disclosure, a chassis platform for a wheeled transport machinery is provided, which includes at least one pair of the electric drive modules for a chassis platform of a wheeled transport machinery as mentioned above, wherein each of the electric drive modules is configured to independently drive one wheel of the wheeled transport machinery. In some embodiments, the chassis platform further includes a power module configured to supply electrical energy to the drive assembly, and a hydraulic module configured to supply hydraulic energy to the steering assembly and / or the suspension assembly. In some embodiments, the chassis platform further includes a controller, which is in signal connection with the power module and the hydraulic module, and is configured to output instructions to the power module and / or the hydraulic module to control action of at least one of the drive assembly, the steering assembly and the suspension assembly. According to a third aspect of the present disclosure, a wheeled transport machinery is provided, which includes the abovementioned electric drive module for a chassis platform of a wheeled transport machinery, or the abovementioned chassis platform for a wheeled transport machinery. Based on the above technical solution, an electric drive module is provided in the present disclosure to independently drive wheels, wherein the electric drive module integrates the functions of driving, steering and suspension. This, on one hand, can reduce the number of components that need to be assembled separately, thereby simplifying the production and assembling processes and reducing the complexity of maintenance and repair, and on the other hand, can effectively control independent rotation and steering of the wheel driven by it, and can provide a shock absorption function at each wheel, thereby contributing to enhancing the overall maneuverability and operational stability of the wheeled transport machinery. BRIEF DESCRIPTION OF THE DRAWINGS The accompanying drawings described herein are provided to facilitate a further understanding of the present disclosure and constitute a part of this application. The illustrative embodiments of the present disclosure and their descriptions are used to explain the present disclosure and shall not be construed as unduly limiting the same. In the accompanying drawings: FIG. 1 is a schematic structural view of a wheeled transport machinery according to an embodiment of the present disclosure. FIG. 2 is a schematic structural view of an electric drive module according to an embodiment of the present disclosure. FIG. 3 is a partial cross-sectional view of the electric drive module according to an embodiment of the present disclosure. FIG. 4 is a schematic view showing the symmetrical arrangement of a suspension assembly and a steering knuckle in the electric drive module according to an embodiment of the present disclosure. FIG. 5 is a schematic structural view of a chassis platform according to an embodiment of the present disclosure. FIG. 6 is a schematic structural view of the chassis platform according to another embodiment of the present disclosure. FIG. 7 is a schematic structural view of the chassis platform according to a further embodiment of the present disclosure. Explanation of the reference signs 1. frame; 11. support beam; 12. torsion-resistant tube; 2. wheel; 3. drive assembly; 31. motor; 32. transmission shaft; 33. reducer; 4.steering assembly; 41. steering knuckle; 411. first hinge portion; 412. second hinge pa; 413. first ball joint; 414. second ball joint; 415. through hole; 42. steering knuckle arm; 43. steering cylinder; 44. steering pin shaft; 5. suspension assembly; 51. suspension cylinder; 52. first fork arm; 521. first ball socket; 522. first support arm; 53. second fork arm; 531. second ball socket; 532. second support arm; 6.power module; 7. hydraulic module; 8. controller; 9. cargo box. EMBODIMENTS Various exemplary embodiments of the present disclosure will now be described in detail with reference to the accompanying drawings. The description of the exemplary embodiments is merely illustrative, and shall in no way constitute any limitation on the present disclosure, its application or use. The present disclosure may be implemented in many different ways, and is not limited to the embodiments described herein. These embodiments are provided to make the present disclosure thorough and complete, and to fully convey the scope of the present disclosure to those skilled in the art. It should be noted that, unless specifically stated otherwise, the relative arrangement of components and steps, the composition of materials, numerical expressions and values set forth in these embodiments shall be construed as merely exemplary rather than restrictive. The terms "first", "second" and similar words used in the present disclosure do not denote any order, quantity or importance, but are merely used to distinguish different portions. The terms such as "comprise" or "include" mean that the elements preceding the term cover the elements listed after the term, without excluding the possibility of also encompassing other elements. The terms such as "upper", "lower", "left", "right" and the like are only used to indicate relative positional relationships; when the absolute position of the object described changes, this relative positional relationship may also change accordingly. In the present disclosure, when a specific device is described as being located between a first device and a second device, there may or may not be an intermediate device between the specific device and the first device or the second device. When a specific device is described as being connected to other devices, the specific device may be directly connected to said other devices without any intermediate device, or may be connected to said other devices indirectly through an intermediate device. All the terms used in the present disclosure (including technical and scientific terms) have the meanings as normally understood by a person skilled in the art, unless otherwise defined. It should also be understood that terms, for example, defined in general dictionaries shall be interpreted as having meanings consistent with their contextual meanings in the related art, and shall not be interpreted in an idealized or overly formalized sense unless explicitly defined as such herein. The techniques, methods and devices known to a person of ordinary skill in the relevant art may not be discussed in detail, but where appropriate, such techniques, methods and devices shall be deemed as part of the specification. Based on the various embodiments of the present disclosure described above, the technical features of one embodiment may be beneficially combined with those of one or more other embodiments, provided that there is no explicit negation or conflict. In the related art, the chassis system of the wheeled transport machinery has the defects of poor universality of key parts and high maintenance costs. For example, the wheeled transport machinery of different types or tonnages typically requires parts such as steering axles, drive axles, gearboxes, suspension cylinders and link-guide mechanisms of different specifications. This significantly increases the development and manufacturing costs of parts of the wheeled transport machinery, and makes it inconvenient for users to use and maintain these parts. In order to address at least some of the aforementioned problems, the present disclosure adopts a modular design for the drive system of the wheeled transport machinery, such that the driving requirements of the wheeled transport machineries of different types or tonnages can be met by configuring different numbers of the drive modules and / or arranging the multiple drive modules in adaptable layouts. FIG.1 is a schematic view of a wheeled transport machinery. In a first aspect of the present disclosure, an electric drive module for a chassis platform of the wheeled transport machinery is provided. The chassis platform includes a frame 1 and at least one pair of identical electric drive modules connected to the frame 1. Each electric drive module is configured to independently drive one wheel 2 of the wheeled transport machinery. Each electric drive module includes a drive assembly 3, a steering assembly 4 and a suspension assembly 5. The drive assembly 3 is configured to be connected between the frame 1 and the wheel 2 for driving the wheel 2 to rotate. The steering assembly 4 is configured to be connected between the frame 1 and the wheel 2 for driving the wheel 2 to steer. The suspension assembly 5 is configured to be connected between the frame 1 and the steering assembly. Herein, the drive assembly 3 drives the wheels 2 to enable the wheeled transport machinery to move forward and backward; the steering assembly 4 drives the wheels 2 to enable leftward and rightward steering of the wheeled transport machinery; and the suspension assembly 5 is connected between the frame 1 and the steering assembly to provide at least a shock absorption function for the frame 1, especially when the wheeled transport machinery is traveling on rough or uneven ground. In the embodiments of the present disclosure, each electric drive module independently drives one wheel 2, thereby capable of effectively controlling independent rotation and steering of the wheel 2 driven by it, and can provide a shock absorption function at each wheel 2, which contributes to enhancing the overall maneuverability and operational stability of the wheeled transport machinery. The electric drive module provided in the embodiments of the present disclosure integrates the functions of driving, steering and suspension, which helps simplify the design of the vehicle chassis. Unlike the related art where such functional components are separately arranged, the integrated electric drive module in the present disclosure can reduce the number of components that need to be assembled separately, thereby simplifying the production and assembling processes and reducing the complexity of maintenance and repair. According to the embodiments of the present disclosure, when facing the load-bearing requirements of the wheeled transport machinery of different tonnages, the electric drive modules can be combined in different quantities to form a series of chassis platforms suitable for the wheeled transport machinery of different tonnages, thus effectively shortening the research and development cycle of new products. Referring to FIG. 4, in some embodiments, the drive assembly 3 is symmetrical with respect to a radial cross-section of the wheel 2. The suspension assembly 5 is symmetrical with respect to the radial cross-section of the wheel 2. Specifically, the symmetrical arrangement in the present disclosure is different from the chassis design in the related art. In the related art, parts such as transmission gears and thrust rods of the chassis are designed with a primary load-bearing direction, i.e. these parts can withstand higher loads during forward movement but have lower load-bearing capacity during backward movement, such that the chassis structure in the related art adopts a differentiated design for the forward and backward directions, making it an asymmetric structural design. In the embodiments of the present disclosure, by arranging the drive assembly 3 and / or the suspension assembly 5 to be symmetrical with respect to the radial cross-section of the wheel 2, the loads acting on the drive assembly 3 and the suspension assembly 5 in the front-and-rear direction are uniformly distributed during both forward and reverse travel of the wheeled transport machinery. This enables high load-bearing capacity and high-power braking energy recovery for bidirectional travel (i.e., travel in both forward and reverse directions), and can also help reduce asymmetric wear that occurs when the machinery travels in different directions, thereby prolonging the service life of components such as the drive assembly 3, the suspension assembly 5 and the wheel 2. Herein, the suspension assembly 5 and the steering knuckle 41 are symmetrical with respect to the radial cross-section of the wheel 2, especially refers to a radial cross-section when the wheeled transport machinery is in a state where the frame 1 is horizontal and the orientation of the wheel 2 is consistent with the travel direction of the frame 1, and in this case, the radial cross-section refers to a radial cross-section of the wheel 2 extending along the direction of gravity. It should be understood that during the travel of the wheeled transport machinery, the relative positions of partial structures of the drive assembly 3 and the suspension assembly 5 relative to the wheel 2 may change dynamically due to changes in the travel direction, road conditions and other factors. However, the projections of the connection positions between the drive assembly 3 and the wheel 2, as well as between the suspension assembly 5 and the wheel 2, onto the radial plane of the wheel 2 always coincide with the center of the wheel 2. This arrangement ensures that the transmission paths of the interaction forces between the drive assembly 3 and the wheel 2, as well as between the suspension assembly 5 and the wheel 2, all pass through their geometric centers, thereby helping to ensure uniform stress distribution at different positions of the aforementioned components. Referring to FIG. 2, in some embodiments, the steering assembly 4 includes a steering knuckle 41. The steering knuckle 41 is symmetrical with respect to the radial cross-section of the wheel 2 and is fixedly connected to the wheel 2. As an example, the steering knuckle 41 may be fixedly connected to a rim of the wheel 2. Referring to FIG. 2, in some embodiments, the steering assembly 4 further includes a steering mechanism, which is movably connected between the frame 1 and the steering knuckle 41. On this basis, the wheel 2 can undergo a relative position change relative to the frame 1, thereby enabling the steering of the wheel 2. Referring to FIG. 2, in some embodiments, the steering mechanism includes a steering knuckle arm 42 and a steering cylinder 43. The steering knuckle arm 42 is fixedly connected to the steering knuckle 41, and both ends of the steering cylinder 43 are hingedly connected to the steering knuckle arm 42 and the frame 1, respectively. Based on this configuration, the extension or retraction of the steering cylinder 43 can achieve positional change of the wheel 2 relative to the frame 1, thereby achieving steering of the wheel 2. As shown in FIG. 2, in some examples, the steering mechanism further includes a steering pin shaft 44. The steering pin shaft 44 is used to connect the steering cylinder 43 and the frame 1, and both the steering cylinder 43 and the frame 1 are configured to be rotatable relative to the steering pin shaft 44. In some embodiments, the suspension assembly 5 is hingedly connected to the steering knuckle 41. The hinged connection between the suspension assembly 5 and the steering knuckle 41 enables relative rotation between the suspension assembly 5 and the steering knuckle 41, so as to accommodate the change in relative position between the frame 1 and the wheel 2 during movement of the wheeled transport machinery, thereby enhancing the stability of the frame 1 and the load-bearing device (e.g., the cargo box 9 shown in FIG. 1) for the loaded articles thereon during running of the wheeled transport machinery. Referring to FIG. 2, in some embodiments, the suspension assembly 5 includes a suspension cylinder 51. Both ends of the suspension cylinder 51 are hingedly connected to the frame 1 and the steering knuckle 41, respectively. Based on this configuration, the extension and retraction of the suspension cylinder 51 enables relative positional change between the frame 1 and the steering knuckle 41, that is, the relative positional change between the frame 1 and the wheel 2. This helps absorb vibrations caused by uneven road surfaces during the running of the wheeled transport machinery, provides cushioning, and improves the overall stability of the transport machinery. In one example, the suspension cylinder 51 is arranged approximately along a Z-direction to improve the vibration resistance of the frame 1 in the Z-direction. The Z-direction may, for instance, be a vertical direction. Referring to FIG 2, in some embodiments, the suspension assembly 5 includes a first fork arm 52. The steering knuckle 41 is provided with a first hinge portion 411, and both ends of the first fork arm 52 are hinged to the frame 1 and the first hinge portion 411, respectively. As an example, the first fork arm 52 includes two first support arms 522 arranged at intervals substantially along an X-direction. The two first support arms 522 are both hingedly connected with the frame 1, for instance, connected to the frame 1 via rotatable pin shafts. The two first support arms 522 can disperse the impact force from the wheel 2, thereby avoiding the problem of stress concentration on the frame 1 that would arise from a single-point connection means. The X-direction may be, for example, a horizontal direction or a longitudinal direction of the chassis platform. In a specific example, the first fork arm 52 connects the frame 1 and the first hinge portion 411 substantially along a Y-direction. The Y-direction may be, for example, a direction perpendicular to the X-direction and the Z-direction or a transverse direction of the chassis platform. Referring to FIG. 2, in some embodiments, the suspension assembly 5 further includes a second fork arm 53. The steering knuckle 41 is provided with a second hinge portion 412, which is spaced apart from the first hinge portion 411 in the Z-direction or the vertical direction. Both ends of the second fork arm 53 are hinged to the frame 1 and the second hinge portion 412, respectively. As an example, the second fork arm 53 includes two second support arms 532 arranged at intervals substantially along the X-direction. The two second support arms 532 are both hingedly connected to the frame 1, for instance, connected to the frame 1 through rotatable pin shafts. The two second support arms 532 can disperse impact forces from the wheel 2, thereby avoiding the problem of stress concentration on the frame 1 that would arise from a singlepoint connection means. In a specific example, the second fork arm 53 connects the frame 1 and the second hinge portion 412 substantially along the Y-direction. In some embodiments where the suspension assembly 5 includes the first fork arm 52 and the second fork arm 53, the first fork arm 52 and the second fork arm 53 jointly form a double-fork arm suspension structure. Compared to a single-fork arm suspension structure, the double-fork arm suspension structure can more effectively absorb the impact force from ground, and thus reduces vibration of the frame 1 and provides better traveling stability for the wheeled transport machinery. In the embodiments described above, by providing, on the fork arm, two support arms arranged at intervals in the X-direction for hinged connection with the frame 1, the frame 1 is allowed to swing relative to the wheel 2 in the Z-direction, thereby cushioning the impact force applied to the frame 1 in the Z-direction, such as the impact force resulting from uneven road surfaces. Referring to FIG. 2, as an example, the first fork arm 52 is disposed above the second fork arm 53 in the Z-direction. In some embodiments, the first fork arm 52 is spherically hinged to the first hinge portion 411. The second fork arm 53 is spherically hinged to the second hinge portion 412. Such spherical hinge connection can offer a large rotatable range, thereby providing sufficient degrees of freedom and flexibility for the relative movement between the first fork arm 52 and the steering knuckle 41 and / or between the second fork arm 53 and the steering knuckle 41, so as to adapt to complex environments or road conditions. Especially when the wheeled transport machinery encounters rough and uneven road surfaces, the resulting impact forces usually act on the wheels 2 in multiple directions. The spherical hinge connection can better adapt to these multi-directional impact forces, enabling the suspension assembly 5 to better cushion such impact forces and helping to improve the overall movement stability of the wheeled transport machinery. In addition, the spherical fitting structure of the spherical hinge connection is helpful to reduce the impact and wear on the relevant components of the suspension assembly 5 and the steering assembly 4, thereby prolonging their service life. Specifically, in some embodiments, as shown in FIG. 3, the steering knuckle 41 is provided with a first ball joint 413 and a second ball joint 414. The first fork arm 52 is provided with a first ball socket 521 that engages with the first ball joint 413, and the second fork arm 53 is provided with a second ball socket 531 that engages with the second ball joint 414. The first ball socket 521 is fitted over the outer periphery of the first ball joint 413, and the first ball socket 521 and the first ball joint 413 are configured to allow relative rotation therebetween. The second ball socket 531 is fitted over the outer periphery of the second ball joint 414, and the second ball socket 531 and the second ball joint 414 are configured to allow relative rotation therebetween. In some embodiments where the suspension assembly 5 includes the suspension cylinder 51, the first fork arm 52, and the second fork arm 53, the first fork arm 52 is positioned above the second fork arm 53, and the suspension cylinder 51 is hingedly connected to the first ball socket 521 of the first fork arm 52. Through the coordinated action of the suspension cylinder 51, the first fork arm 52 and the second fork arm 53, relative swinging, relative rotation and other movements between the frame 1 and the wheels 2 can be achieved, thereby meeting the requirements for driving flexibility and stability of the wheeled transport machinery. Referring to FIG. 2, in some embodiments, the drive assembly 3 includes a motor 31 and a transmission shaft 32. The motor 31 is mounted inside the frame 1, and both ends of the transmission shaft 32 are connected to the motor 31 and the wheel 2, respectively. Based on this configuration, the transmission shaft 32 can transmit the torque output by the motor 31 to the wheel 2, thereby achieving the driving of the wheel 2. Mounting the motor 31 inside the frame 1 can, on one hand, prevent the motor 31 from direct exposure to the external environment to reduce the erosion and impact of sediment, rainwater, dust and the like on the motor 31, thereby prolonging the service life of the motor 31; and on the other hand, can help reduce the unsprung mass of the chassis platform of the wheeled transport machinery, thereby enhancing the shock absorption performance of the chassis platform. As an example, the frame 1 is provided therein with a mounting base, on which the motor 31 is mounted. Referring to FIG. 1, in some embodiments, the frame 1 includes a support beam 11 and a torsion-resistant tube 12 connected to the support beam 11. The motor 31 is mounted inside the torsion-resistant tube 12. As a sprung component, the torsion-resistant tube 12 is subject to little impact and vibration from road surfaces, resulting in a low failure rate, and thus can provide a sufficiently robust casing protection for the motor 31 to thereby enhance the reliability of the drive assembly 3. As an example, the torsion-resistant tube 12 may be configured as a circular tube, a U-shaped tube, or a polygonal tube with a cavity, with the cavity being used to accommodate the motor 31. Referring to FIG. 3, in some embodiments, the steering knuckle 41 is provided with a through-hole 415 extending along an axial direction of the wheel 2, and the transmission shaft 32 is inserted through the through-hole 415. Providing the through-hole 415 in the steering knuckle 41 to allow the transmission shaft 32 to pass directly through the steering knuckle 41 and transmit power to the wheel 2 can eliminate the need for additional arrangement of mounting structures or power transmission structures. This, on one hand, can improve power transmission efficiency, and on the other hand, can effectively reduce the spatial occupation between the components, and achieve a compact layout of the entire electric drive module. Referring to FIGS. 1 and 2, in some embodiments, the drive assembly 3 further includes a reducer 33. The reducer 33 is connected between the transmission shaft 32 and the wheel 2. As an example, an end of the transmission shaft 32 away from the motor 31 passes through the through-hole 415 and is connected to an input flange of the reducer 33. The reducer 33, configured in accordance with the characteristics of the motor 31, can convert the output speed and torque of the motor 31 (e.g., high speed and low torque) into speed and torque suitable for driving the wheel 2 (e.g., low speed and high torque) for output, thereby achieving effective matching between the drive assembly 3 and the operational conditions of the wheeled transport machinery. Furthermore, compared with the use of a gearbox for transmission in the related art, the reducer 33 has the characteristics of simple structure, small volume and low mechanical losses, which contributes to reducing the use and maintenance costs of the drive assembly 3. In some embodiments, the motor 31, the transmission shaft 32 and the reducer 33 are designed based on the requirements for travelling in both forward and backward directions, so that the load on the wheels 2 and the aforementioned relevant components remains consistent during the forward and reverse travelling of the wheeled transport machinery. Unlike the related art, where structural limitations of components such as drive axles, main reducers and the like result in the inability to achieve full-power braking and thus affect energy recovery efficiency, the motor 31, transmission shaft 32 and reducer 33 provided in the embodiments of the present disclosure are designed based on the requirements for travelling in both forward and backward directions, for example, designed as a structure symmetrical with respect to the wheels 2, such that the load on these components are consistent during forward and reverse travel, which helps improve energy recovery efficiency and extend the service life of the wheeled transport machinery during forward and reverse travel. Specifically, in some examples, the reducer 33 includes a spur gear reducer. The meshing characteristics of the spur gears remain consistent during both clockwise and counterclockwise rotation, ensuring that the power transmission stability of the spur gear reducer may not vary due to the change in travel direction (forward or reverse direction). Consequently, the wheel 2 can obtain identical power performance under the working conditions of forward and reverse traveling of the wheeled transport machinery, thereby reducing the problem of unbalanced wearing of related components caused by load variations under different working conditions. In some embodiments, the drive assembly 3 further includes a braking device integrated onto the gear reducer 33. Integrating the braking device onto the reducer 33 can improve braking efficiency and the structural compactness of the drive assembly as a whole, which helps to realize the miniaturized design of the electric drive module. In addition, within the electric drive module, the integration of the braking device and the reducer 33 helps optimize the energy recovery process of the motor, and can improve the overall energy efficiency of the vehicle by achieving dynamic distribution of braking force and energy recovery efficiency. The specific form and structure of the braking device can be selected based on the structure of the reducer 33, the braking requirements of the wheeled transport machinery, and so on. For example, in some examples, the braking device includes a wet brake, particularly an integrated service-and-parking wet brake. In some embodiments, a hydraulic module is employed to supply hydraulic energy to the wet brake. In some specific examples, the braking device may share a hydraulic module with hydraulic components in the steering assembly 4 (such as the steering cylinder 43), thus facilitating to achieve a compact design of the electric drive device. In some embodiments, as shown in FIGS. 1 and 2, the integrated braking device and reducer 33 may be arranged radially inside the rim of wheel 2, thus further saving mounting space and achieving an integrated layout. As an example, an output end of the reducer 33 is fixedly connected to the rim of the wheel 2. In some embodiments, the drive assembly 3 is removably connected both to the frame 1 and to the wheels 2; and / or the steering assembly 4 is removably connected both to the frame 1 and to the wheels 2; and / or the suspension assembly 5 is removably connected to the frame 1. The removable connection design allows individual assemblies of the electric drive module, such as the drive, steering and suspension assemblies, to be dismounted and replaced independently, and also facilitates the entire electric drive module to be mounted and dismounted relative to the chassis platform of the wheeled transport machinery, making regular maintenance and servicing more convenient. Specifically, when the electric drive module encounters a fault that is difficult to resolve in a short period during operation, the removable connection design allows for the rapid removal of the faulty assembly (such as the drive assembly 3, steering assembly 4, or suspension assembly 5), enabling quick replacement of the electric drive module or the related faulty assembly, and avoiding prolonged downtime of the wheeled transport machinery. Herein, the present disclosure does not limit the specific form of the removable connection. For instance, various detachable connection means such as pin connections or bolt connections may be selected according to actual conditions. As an example, the motor 31 of the drive assembly 3 is detachably mounted on the mounting base inside the frame 1. The output flange of the motor 31 is connected to the transmission shaft 32 via bolts, and an output housing of the reducer 33 of the drive assembly 3 is connected to the rim of the wheel 2 through bolts. As an example, the steering cylinder 43 of the steering assembly 4 is connected to the frame 1 via a steering pin shaft 44, and the steering cylinder 43 may also be connected to the steering knuckle 41 through a pin shaft. As an example, the suspension cylinder 51 of the suspension assembly 5 is connected to the frame 1 through a pin shaft, and both the first fork arm 52 and the second fork arm 53 of the suspension assembly 5 are connected to the frame 1 via pin shafts. According to a second aspect of the present disclosure, a chassis platform for the wheeled transport machinery is provided. The chassis platform includes at least one pair of the aforementioned electric drive modules, with each electric drive module being configured to separately drive one wheel of the wheeled transport machinery. As each wheel is driven by an independent electric drive module, the wheeled transport machinery can perform customized operations in various working environments. For example, the distribution of driving force or the steering angles of different wheels can be adjusted as required to adapt to different work tasks, such as traction, handling, transportation and so on. Further, the electric drive module can be flexibly applied to the chassis platforms of different types of the wheeled transport machineries. Specifically, the number and positions of the electric drive modules arranged on the chassis platform can be adaptively set according to the type, specification or load requirements of the wheeled transport machinery. For example, two, four, six or eight electric drive modules may be arranged, and for another example, a pair of electric drive modules may be arranged on the front wheels or rear wheels of the wheeled transport machinery, or a certain number of electric drive modules may be distributed relative to the entire chassis platform, so as to independently drive different numbers of the wheels 2 or the wheels 2 at different positions, thereby meeting different transportation requirements. In order to more clearly explain the means of designing the electric drive module in practical applications, a specific embodiment in which the wheeled transport machinery is configured as a mining truck is described herein. In this specific embodiment, when facing the load-bearing requirements of the mining trucks of different tonnages, the electric drive modules may be combined in different quantities to form a series of chassis platforms suitable for the mining trucks of different tonnages, thus effectively shortening the research and development cycle of new products. Among them, the main parts of the electric drive modules (such as the motor, the reducer, the suspension cylinder, the steering cylinder, etc.) may adopt unified specifications, models and interface dimensions, thereby reducing the development and manufacturing costs of these parts, greatly simplifying the inventory and spare parts management for manufacturers and users, and improving the maintenance efficiency of the relevant products during use. Referring to FIG. 5, in some embodiments, the chassis platform further includes a power module 6 and a hydraulic module 7. The power module 6 is configured to supply electrical energy to the drive assembly 3. The hydraulic module 7 is configured to supply hydraulic energy to the steering assembly 4 and / or the suspension assembly 5. Configuring the power module 6 and the hydraulic module 7 as independent modules respectively facilitates the separate maintenance and management of any one of the modules, and thus can reduce repair time and maintenance costs. Among them, each electric drive module may be configured with a separate power module 6 or hydraulic module 7 for energy supply. Alternatively, the chassis platform may be equipped with only one power module 6 or one hydraulic module 7, which then supplies energy to all the electric drive modules individually. As shown in FIG. 5, in some embodiments, the chassis platform further includes a controller 8, which is in signal connection with the power module 6 and the hydraulic module 7 and is configured to output instructions to the power module 6 and / or the hydraulic module 7 to control the actions of at least one of the drive assembly 3, the steering assembly 4 and the suspension assembly 5. The controller 8 functions to control each module of the chassis platform, including but not limited to the power module 6 and the hydraulic module 7 mentioned above. For example, the controller 8 can control the output parameters of the power module 6 and the hydraulic module 7 according to the real-time operational requirements of the wheeled transport machinery, thereby coordinately controlling the drive assembly 3, the steering assembly 4 and the suspension assembly 5 in the electric drive module, realizing the action control during running of the wheeled transport machinery and improving the maneuverability of the wheeled transport machinery. Further, in order to more clearly illustrate the method for selecting the quantity and arranging the layout of the electric drive modules in practical applications, a process of designing the chassis platform for mining trucks of different tonnages is described herein as an example. Taking a mining truck with a chassis platform featuring a 4*4 distributed electric drive structure as the design basis, the mining truck is equipped with a cargo box and a lifting system to fulfill the material transportation function of the mining truck. Herein, the term 4*4 means that the mining truck includes four wheels, with one electric drive module correspondingly arranged for each wheel. If it is necessary to enhance the load-bearing and transportation capacity on the basis of this mining truck, two or more sets of electric drive modules may be added to form a chassis platform with 6*6 distributed electric drive (refer to FIG. 6), a chassis platform with 8*8 distributed electric drive (refer to FIG. 7), or a chassis platform with 10*10 distributed electric drive, and the volume of the cargo box is synchronously increased to thereby achieve an improvement in the load-bearing and transportation capacity. To take a specific example, assuming that the load-bearing capacity of a single electric drive module is 15 tons, the chassis platform with 4*4 configuration can bear 60 tons, the chassis platform with 6*6 configuration can bear 90 tons, the chassis platform with 8*8 configuration can bear 120 tons, and the chassis platform with 10*10 configuration can bear 150 tons. The chassis platforms of different tonnages adopt completely identical electric drive modules, thus realizing the universalization of the parts. Of course, the load-bearing capacity of a single electric drive module is not limited to the aforementioned 15 tons, but can also be designed to 10 tons, 20 tons, 30 tons, or other tonnages to meet the requirements of a series of chassis platforms and mining trucks with different tonnage load-bearing capacities. It should be understood here that if a chassis platform with a multi-wheel drive structure does not require four-wheel or all-wheel drive, the electric drive module as mentioned above may correspondingly have its parts reduced and downgraded. For example, the parts such as the motor 31, the transmission shaft 32 or the reducer 33 may be removed to form a 4*2 chassis platform with a two-wheel drive structure. Herein, the term 4*2 means that the chassis platform is equipped with four wheels, but only two electric drive modules with driving capability are adopted to drive two of the wheels. Alternatively, in practical applications, various other combination forms can also be designed, which can also enable the wheeled transport machinery to travel in both forward and reverse directions while ensuring corresponding transportation and load-bearing capacities. In the embodiments of the present disclosure, the power module 6, the hydraulic module 7 and the controller 8 may be arranged between two opposing support beams 11 of the frame 1. The different modules may be separated by additional support beams 11 or the torsion-resistant tubes 12 according to the spatial layout requirements of the chassis platform. For specific layout arrangements, reference may be made to FIGS. 5 to 7 respectively. According to a third aspect of the present disclosure, a wheeled transport machinery is provided, which includes the aforementioned electric drive module or chassis platform. The wheeled transport machinery provided in the embodiments of the present disclosure includes conveying machinery, especially a heavy-duty transport machinery. The positive technical effects possessed by the electric drive module or chassis platform in each of the above embodiments are also applicable to the wheeled transport machinery, and will not be repeated herein. 5       The electric drive module, chassis platform and wheeled transport machinery provided by the present disclosure have been described in detail above. Specific embodiments are applied herein to illustrate the principles and implementation modes of the present disclosure. The descriptions of the above embodiments are only intended to facilitate the understanding of the methods 10 and core ideas of the present disclosure. It should be noted that, for those skilled in the art, several improvements and modifications can be made to the present disclosure without departing from the principles of the present disclosure, and these improvements and modifications also fall within the scope of protection of the claims of the present disclosure. 15

Claims

1. An electric drive module for a chassis platform of a wheeled transport machinery, the chassis platform comprising a frame (1) and at least one pair of the same electric drive modules connected to the frame (1), wherein each of the electric drive modules is configured to independently drive one wheel (2) of the wheeled transport machinery, and each of the electric drive modules comprises:a drive assembly (3) configured to be connected between the frame (1) and the wheel (2) for driving the wheel (2) to rotate;a steering assembly (4) configured to be connected between the frame (1) and the wheel (2) for driving the wheel (2) to steer; anda suspension assembly (5) configured to be connected between the frame (1) and the steering assembly.

2. The electric drive module for a chassis platform of a wheeled transport machinery according to claim 1, whereinthe drive assembly (3) is symmetrical about a radial cross-section of the wheel (2); and / orthe suspension assembly (5) is symmetrical about a radial cross-section of the wheel (2).

3. The electric drive module for a chassis platform of a wheeled transport machinery according to claim 1 or 2, wherein the steering assembly (4) comprises a steering knuckle (41), which is symmetrical about a radial cross-section of the wheel (2) and is fixedly connected to the wheel (2).

4. The electric drive module for a chassis platform of a wheeled transport machinery according to claim 3, wherein the steering assembly (4) further comprises a steering mechanism, which is movably connected between the frame (1) and thesteering knuckle (41).

5. The electric drive module for a chassis platform of a wheeled transport machinery according to claim 4, wherein the steering mechanism comprises a steering knuckle arm (42) and a steering cylinder (43), the steering knuckle arm (42) being fixedly connected to the steering knuckle (41), and both ends of the steering cylinder (43) being hingedly connected to the steering knuckle arm (42) and the frame (1), respectively.

6. The electric drive module for a chassis platform of a wheeled transport machinery according to any one of claims 3 to 5, wherein the suspension assembly (5) is hingedly connected with the steering knuckle (41).

7. The electric drive module for a chassis platform of a wheeled transport machinery according to any one of claims 3 to 6, wherein the suspension assembly (5) comprises a suspension cylinder (51), both ends of which are hingedly connected to the frame (1) and the steering knuckle (41), respectively.

8. The electric drive module for a chassis platform of a wheeled transport machinery according to any one of claims 3 to 7, wherein the suspension assembly (5) comprises a first fork arm (52), the steering knuckle (41) is provided with a first hinge portion (411), and both ends of the first fork arm (52) are hingedly connected to the frame (1) and the first hinge portion (411), respectively.

9. The electric drive module for a chassis platform of a wheeled transport machinery according to claim 8, wherein the suspension assembly (5) further comprises a second fork arm (53), the steering knuckle (41) is provided with a second hinge portion (412) spaced apart from the first hinge portion (411) in a vertical direction, and both ends of the second fork arm (53) are hingedly connected to the frame (1) and the second hinge portion (412), respectively.

10. The electric drive module for a chassis platform of a wheeled transport machinery according to claim 9, whereinthe first fork arm (52) is spherically hinged to the first hinge portion (411); and / orthe second fork arm (53) is spherically hinged to the second hinge portion (412).

11. The electric drive module for a chassis platform of a wheeled transport machinery according to any one of claims 3 to 10, wherein the drive assembly (3) comprises a motor (31) and a transmission shaft (32), the motor (31) is mounted inside the frame (1), and both ends of the transmission shaft (32) are connected to the motor (31) and the wheel (2), respectively.

12. The electric drive module for a chassis platform of a wheeled transport machinery according to claim 11, wherein the frame (1) comprises a support beam (11) and a torsion-resistant tube (12) connected to the support beam (11), and the motor (31) is mounted inside the torsion-resistant tube (12).

13. The electric drive module for a chassis platform of a wheeled transport machinery according to claim 11 or 12, wherein the steering knuckle (41) is provided with a through-hole (415) extending along an axial direction of the wheel (2), and the transmission shaft (32) is inserted through the through-hole (415).

14. The electric drive module for a chassis platform of a wheeled transport machinery according to any one of claims 11 to 13, wherein the drive assembly (3) further comprises a reducer (33), which is connected between the transmission shaft (32) and the wheel (2).

15. The electric drive module for a chassis platform of a wheeled transport machinery according to claim 14, wherein the reducer (33) comprises a spur gear reducer.

16. The electric drive module for a chassis platform of a wheeled transport machinery according to claim 14 or 15, wherein the drive assembly (3) further comprises a braking device integrated onto the reducer (33).

17. The electric drive module for a chassis platform of a wheeled transport machinery according to any one of claims 1 to 16, whereinthe drive assembly (3) is removably connected to both the frame (1) and the wheel (2); and / orthe steering assembly (4) is removably connected to both the frame (1) and the wheel (2); and / orthe suspension assembly (5) is removably connected to the frame (1).

18. A chassis platform for a wheeled transport machinery, comprising at least one pair of the electric drive modules for a chassis platform of a wheeled transport machinery according to any one of claims 1 to 17, each of the electric drive modules being configured to independently drive one wheel of the wheeled transport machinery.

19. The chassis platform for a wheeled transport machinery according to claim 18, wherein the chassis platform further comprises a power module (6) configured to supply electrical energy to the drive assembly (3), and a hydraulic module (7) configured to supply hydraulic energy to the steering assembly (4) and / or the suspension assembly (5).

20. The chassis platform for a wheeled transport machinery according to claim 19, wherein the chassis platform further comprises a controller (8), which is in signal connection with the power module (6) and the hydraulic module (7), and is configured to output instructions to the power module (6) and / or the hydraulic module (7) to control action of at least one of the drive assembly (3), the steering assembly (4) and the suspension assembly (5).

21. A wheeled transport machinery, comprising the electric drive module for a chassis platform of a wheeled transport machinery according to any one of claims 1 to 17, or the chassis platform for a wheeled transport machinery according to any one of claims 18 to 20.

Images