Transmission device, steering mechanism, and vehicle

Abstract

A transmission device, a steering mechanism, and a vehicle. The transmission device comprises a mount, a bearing, a worm, and a worm gear; the bearing is disposed in an inner hole of the mount, the worm extends into an inner ring of the bearing, and the worm is in transmitting connection with the worm gear; the mount is further provided with an abutting part, the abutting part can abut against an outer ring of the bearing in the rotating axis direction of the worm, and the abutting part is used for limiting radial displacement caused when the worm and the worm gear are in fit transmission, thereby guaranteeing a fit clearance between the worm gear and the worm.

Description

Transmission, steering and vehicles

[0001] This application claims priority to the Chinese patent application filed with the China Patent Office on September 28, 2023, with application number 202311283171.5 and application name “Transmission device, steering mechanism and vehicle”, the entire contents of which are incorporated by reference into this application. Technical Field

[0002] The present application relates to the field of transmission, and in particular to a transmission device, a steering mechanism, and a vehicle comprising the steering mechanism. Background Art

[0003] In the transmission field, during the transmission process of the worm wheel and the worm, the interaction between the worm wheel and the worm easily causes the fit clearance between the worm wheel and the worm to become larger, thereby affecting the transmission accuracy of the worm wheel and the worm.

[0004] Summary of the Invention

[0005] In view of the above-mentioned deficiencies in the prior art, the purpose of this application is to provide a transmission device with improved transmission accuracy, and a vehicle including the transmission device. Specifically, the present application includes the following technical solutions:

[0006] In the first aspect, an embodiment of the present application provides a transmission device, including a support, a bearing, a worm and a worm wheel, the bearing being arranged in the inner hole of the support, the worm extending into the inner ring of the bearing, and the worm being connected to the worm wheel for transmission; the support is also provided with a supporting portion, which can support the outer ring of the bearing along the direction of the rotation axis of the worm, and the supporting portion is used to limit the radial displacement generated when the worm and the worm wheel are in cooperative transmission, so as to ensure the fitting clearance between the worm wheel and the worm.

[0007] The transmission device of the present application realizes the transmission function of the transmission device of the present application by arranging the worm on the inner ring of the bearing in the inner hole of the support and connecting the worm to the worm wheel so that the worm can rotate and drive the worm wheel to rotate under the action of external driving force.

[0008] The transmission device of the present application is provided with a supporting portion that abuts against the outer ring of the bearing along the direction of the rotation axis of the worm. When the worm and the worm wheel rotate in coordination and generate a deflection torque, the supporting portion can limit the radial displacement of the worm through the abutment effect with the bearing, thereby offsetting the deflection torque of the worm, ensuring the fitting clearance between the worm wheel and the worm, and improving the transmission accuracy of the transmission device of the present application.

[0009] In one embodiment, the abutting portion includes a first abutting portion and a second abutting portion, the first abutting portion abuts against an end surface of the bearing close to the worm gear, and the second abutting portion abuts against an end surface of the bearing away from the worm gear.

[0010] In this embodiment, a first abutment is provided on the side of the bearing end face closest to the worm gear, and a second abutment is provided on the side of the bearing end face facing away from the worm gear, so that both opposing end faces of the bearing are abutted by the corresponding abutment, thereby limiting the axial displacement of the bearing. Simultaneously, based on the abutment's restriction of the worm's radial displacement, the cooperation between the first and second abutment can further limit the worm's radial displacement.

[0011] In one embodiment, in the arrangement direction of the worm wheel and the worm, the first abutting portion is closer to the rotation axis of the worm wheel relative to the rotation axis of the worm.

[0012] In one embodiment, in the arrangement direction of the worm wheel and the worm, the second abutting portion is farther away from the rotation axis of the worm wheel relative to the rotation axis of the worm.

[0013] In this embodiment, by arranging the first abutting portion on the side of the rotation axis of the worm close to the rotation axis of the worm wheel, when the axial force of the worm wheel acting on the worm causes the bearing to abut against the first abutting portion, the axial force can cooperate with the first abutting portion to form a reverse eccentric torque to offset the eccentric torque formed by the worm wheel acting on the worm, prevent the worm from flipping around the bearing, and ensure the fitting clearance between the worm and the worm wheel.

[0014] In addition, by arranging the second abutting portion on the side of the rotation axis of the worm close to the rotation axis of the worm wheel, when the axial force of the worm wheel acting on the worm causes the bearing to abut against the second abutting portion, the axial force can cooperate with the second abutting portion to form an opposite eccentric torque to offset the eccentric torque formed by the worm wheel acting on the worm, prevent the worm from flipping around the bearing, and ensure the fitting clearance between the worm and the worm wheel.

[0015] In one embodiment, along the arrangement direction of the worm wheel and the worm, the first abutting portion is located closer to the rotation axis of the worm wheel than the second abutting portion.

[0016] In this embodiment, by providing a first supporting portion and a second supporting portion along the arrangement direction of the worm wheel and the worm, the axial force exerted on the worm can form a reverse eccentric torque under the action of the first supporting portion and / or the second supporting portion. The reverse eccentric torque can offset the eccentric torque formed by the worm wheel acting on the worm, prevent the worm from flipping around the bearing, and ensure the fitting clearance between the worm and the worm wheel.

[0017] In one embodiment, there is a first distance between the first abutting portion and the rotation axis of the bearing, and there is a second distance between the second abutting portion and the rotation axis of the bearing, and the first distance is less than or equal to the second distance.

[0018] In this embodiment, since the distance between the second abutting portion and the rotation axis of the worm wheel is longer than that between the first abutting portion and the rotation axis of the worm wheel, by setting the second spacing of the second abutting portion to be greater than or equal to the first spacing of the first abutting portion, the influence of the distance between the second abutting portion and the rotation axis of the worm wheel on the effect of the second abutting portion in preventing the worm from flipping over is reduced. Therefore, the second abutting portion can prevent the worm from flipping over and ensure the fitting clearance between the worm and the worm wheel.

[0019] In one embodiment, the abutting portion is a circular ring structure, which includes an axial protrusion that extends along the rotation axis of the bearing toward the end face of the bearing and abuts against the end face of the outer ring of the bearing to limit the radial displacement generated when the worm and worm wheel are in cooperative transmission.

[0020] In this embodiment, by setting the supporting portion as a circular ring structure and providing an axial protrusion extending toward the end face of the bearing along the direction of the bearing rotation axis, the axial protrusion can be abutted against the end face of the bearing, so that the worm and the worm wheel rotate in coordination to generate an axial force. Through the abutment effect of the axial protrusion and the bearing, a reverse deflection torque is formed that can offset the deflection torque of the worm, thereby limiting the radial displacement of the bearing, ensuring the fitting clearance between the worm wheel and the worm, and improving the transmission accuracy of the transmission device of this application.

[0021] In one embodiment, there are two axial protrusions, and along the arrangement direction of the worm wheel and the worm, the two axial protrusions are located on the same side of the rotation axis of the bearing, and the distances between the two bearing protrusions and the rotation axis of the bearing are equal.

[0022] In this embodiment, by arranging the two axial projections on the same side of the bearing's rotational axis and equidistant from the bearing's rotational axis, when the worm wheel and worm rotate in conjunction and cause the bearing to undergo axial displacement, the two axial projections exert force on the bearing, ensuring relatively uniform force on the bearing. Furthermore, this ensures that the direction of the torque generated by the axial projections and the bearing is opposite to the direction of the deflection torque generated by the transmission of the worm wheel and worm.

[0023] In one embodiment, the axial protrusion is arc-shaped, located on one side of the rotation axis of the bearing, and arranged circumferentially around the rotation axis of the bearing.

[0024] In this embodiment, the axial projection is configured as an arc, located on one side of the bearing's rotational axis, and arranged circumferentially around the bearing's rotational axis. This ensures that the force on the bearing end face closest to the axial projection is relatively uniform. This also ensures that the direction of the torque generated by the axial projection and the bearing is opposite to the direction of the deflection torque generated by the transmission of the worm gear and worm.

[0025] In one embodiment, the supporting portion further includes a radial protrusion, which protrudes along the radial direction of the bearing. The support is also provided with a mounting groove, which is arranged along the radial direction of the bearing. The radial protrusion is accommodated in the mounting groove to achieve position fixation of the support relative to the supporting portion.

[0026] In this embodiment, a radial protrusion protruding along the radial direction of the bearing is provided, and a mounting groove is provided on the support so that the radial protrusion can be accommodated in the mounting groove, thereby achieving position fixation of the support and the abutting portion.

[0027] In one embodiment, the supporting portion is detachably connected to the support.

[0028] In this embodiment, the supporting portion is detachably connected to the support, so that the supporting portion can be manufactured separately during the process of manufacturing the support, thereby reducing the complexity of manufacturing the support.

[0029] In one embodiment, the transmission device further includes a buffer member, which is filled between the bearing and the support and is used to absorb vibration between the bearing and the support.

[0030] In this embodiment, a buffer is provided and is able to fill the space between the bearing and the support to absorb the vibration transmitted to the bearing and the support during the transmission process of the worm gear and the worm, thereby reducing the noise generated by the vibration of the bearing and the support during the operation of the transmission device of this application.

[0031] In a second aspect, an embodiment of the present application provides a steering mechanism, comprising a steering input device, a steering actuator device, and a transmission device, wherein the steering input device is connected to the transmission device via a worm transmission, and the steering actuator device is connected to the transmission device via a worm transmission.

[0032] In a third aspect, an embodiment of the present application provides a vehicle including a steering mechanism.

[0033] It can be understood that the vehicle provided in the third aspect of this application adopts the transmission device provided in the second aspect of this application, and the steering mechanism provided in the second aspect of this application has the beneficial effect of improving transmission accuracy, and the vehicle of this application also has higher transmission accuracy. BRIEF DESCRIPTION OF THE DRAWINGS

[0034] FIG1 is a schematic structural diagram of a transmission device provided in one embodiment of the present application;

[0035] FIG2 is a top view of a transmission device provided in one embodiment of the present application;

[0036] FIG3 is a schematic diagram of a force analysis of a transmission device provided in one embodiment of the present application;

[0037] FIG4 is another schematic diagram of force analysis of a transmission device provided in one embodiment of the present application;

[0038] FIG5 is a schematic diagram of force analysis of a transmission device in the prior art;

[0039] FIG6 is a schematic diagram of a partial cross-sectional structure of a transmission device provided in one embodiment of the present application;

[0040] FIG7 is another schematic diagram of force analysis of a transmission device provided in one embodiment of the present application;

[0041] FIG8 is another schematic diagram of force analysis of a transmission device provided in one embodiment of the present application;

[0042] FIG9 is a partial front view of a transmission device provided in one embodiment of the present application;

[0043] FIG10 is a partial exploded schematic diagram of a transmission device provided in one embodiment of the present application;

[0044] FIG11 is another partially exploded schematic diagram of a transmission device provided in one embodiment of the present application;

[0045] FIG12 is another partial cross-sectional structural diagram of a transmission device provided in one embodiment of the present application;

[0046] FIG13 is a partially enlarged schematic diagram of a transmission device provided in one embodiment of the present application;

[0047] FIG14 is another partial cross-sectional structural diagram of a transmission device provided in one embodiment of the present application;

[0048] FIG15 is a schematic structural diagram of a steering mechanism provided in one embodiment of the present application;

[0049] FIG16 is a schematic structural diagram of a vehicle provided in one embodiment of the present application.

[0050] Reference numerals: 100 - transmission device; 200 - steering mechanism; 300 - vehicle; 201 - steering input device; 202 - steering actuator; 40 - worm gear; 30 - worm; 20 - bearing; 21 - inner ring; 22 - outer ring; 10 - support; 11 - inner hole; 12 - abutment portion; 10a - mounting groove; L1 - first rotation axis; L2 - second rotation axis; L3 - third rotation axis; T1 - first eccentric moment; T2 - second eccentric moment; F1 - radial force; F2 - axis force; 121-first abutting portion; 121a-first axial protrusion; 121b-first radial protrusion; 122-second abutting portion; 122a-second axial protrusion; 122b-second radial protrusion; 231-first end face; 232-second end face; 100'-transmission device; 40'-spring; 30'-bearing; 20'-worm; 10'-worm wheel; T'-eccentric torque; F1'-radial force; F2'-elastic force; D1-first distance; D2-second distance. DETAILED DESCRIPTION

[0051] To facilitate understanding of the present application, a more comprehensive description of the present application will be provided below with reference to the accompanying drawings. The accompanying drawings illustrate preferred embodiments of the present application. However, the present application can be implemented in many different forms and is not limited to the embodiments described herein. Rather, these embodiments are provided to provide a more thorough and comprehensive understanding of the disclosure of the present application.

[0052] The following descriptions of the embodiments are with reference to the attached diagrams to illustrate specific embodiments that the present application can be used to implement. The serial numbers of the components herein, such as "first", "second", etc., are only used to distinguish the objects described and do not have any order or technical meaning. The "connection" and "coupling" mentioned in the present application include direct and indirect connections (couplings) unless otherwise specified. The directional terms mentioned in the present application, such as "up", "down", "front", "back", "left", "right", "inside", "outside", "side", etc., are only with reference to the directions of the attached drawings. Therefore, the directional terms used are for better and clearer explanation and understanding of the present application, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present application.

[0053] In the description of this application, it should be noted that, unless otherwise expressly specified or limited, the terms "mounted," "connected," and "connected" should be understood broadly. For example, they can refer to fixed connections, detachable connections, or integral connections; they can refer to mechanical connections; they can refer to direct connections, indirect connections through an intermediate medium, or internal connections between two components. A person of ordinary skill in the art will understand the specific meanings of the above terms in this application based on the specific circumstances. It should be noted that the terms "first," "second," and so on, in the specification, claims, and accompanying drawings of this application are used to distinguish between different objects, not to describe a specific order. Furthermore, the terms "include," "may include," "comprise," or "may include" as used in this application indicate the presence of the corresponding functions, operations, components, etc. disclosed, and do not limit the presence or absence of one or more additional functions, operations, components, etc. Furthermore, the terms "include" or "comprising" indicate the presence of the corresponding features, numbers, steps, operations, elements, components, or combinations thereof disclosed in the specification, and do not exclude the presence or addition of one or more other features, numbers, steps, operations, elements, components, or combinations thereof, and are intended to cover non-exclusive inclusions.

[0054] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as those commonly understood by those skilled in the art to which this application pertains. The terms used herein in the specification of this application are only for the purpose of describing specific embodiments and are not intended to limit this application.

[0055] The present application provides a steering structure comprising a steering input device, a steering actuator, and a transmission device. The transmission device comprises a worm gear and a worm in a transmission connection, the worm gear being in a transmission connection with the steering input device, and the worm gear being in a transmission connection with the steering actuator. Due to the transmission coordination between the worm gear and the worm gear, the torque output by the steering input device is amplified by the transmission device and then transmitted to the steering actuator. The steering actuator then implements the corresponding actuating function of the steering structure based on the torque.

[0056] In one embodiment, the steering input device includes a steering wheel, and the steering actuator includes a wheel. The steering wheel controls the direction of the wheel through a transmission device, thereby achieving the steering function of the vehicle. It is understood that in another embodiment, the steering input device and the steering actuator may also have other structures, and this application does not specifically limit this.

[0057] Please refer to FIG1 , which is a schematic structural diagram of a transmission device 100 provided in an embodiment of the present application.

[0058] As shown in Figure 1, the transmission device 100 of the present application includes a support 10, a bearing 20, a worm 30, and a worm wheel 40. The outer ring 22 of the bearing 20 is disposed in the inner hole 11 of the support 10, so that the bearing 20 is relatively fixed in the support 10.

[0059] One end of the worm 30 extends into the inner ring 21 of the bearing 20, allowing the support 10 to support the worm 30 while also allowing the worm 30 to rotate relative to the support 10. Furthermore, as shown in FIG1 , the third rotation axis L3 of the bearing 20 coincides with the first rotation axis L1 of the worm 30, so that the worm 30 and the bearing 20 have the same rotation axis.

[0060] The other end of the worm 30 is in driving connection with the worm wheel 40. As shown in Figure 2, the first rotation axis L1 and the second rotation axis L2 have an included angle therebetween. It is understood that in another embodiment, the first rotation axis L1 and the second rotation axis L2 are perpendicular to each other.

[0061] It is understood that the transmission connection between the worm 30 and the worm wheel 40 enables the worm 30 to rotate under the action of an external driving force and drives the worm wheel 40 to rotate, thereby realizing the transmission function of the transmission device 100 of the present application. In other embodiments, the external driving force can also directly drive the worm wheel 40 to rotate, so that the worm wheel 40 drives the worm 30 to rotate.

[0062] Specifically, please refer to Figure 3, which is a force analysis diagram of the transmission device 100 provided in an embodiment of the present application. For the sake of convenience of description, the description of the support 10 is omitted in Figure 3 and the subsequent force analysis diagrams, and the bearing 20, the worm 30, and the worm wheel 40 are simplified. At the same time, the abutting portion 12 is also simplified to facilitate the description of the positional relationship between the abutting portion 12 and the first rotation axis L1. As shown in Figures 1 and 3, the support 10 is also provided with a abutting portion 12. The abutting portion 12 extends along the direction of the first rotation axis L1 of the worm 30 to the outer ring 22 of the bearing 20, and abuts against the outer ring 22 of the bearing 20.

[0063] As shown in FIG3 , when the worm 30 and the worm wheel 40 rotate in conjunction, the force exerted by the worm wheel 40 on the worm 30 generates an eccentric torque on the worm 30. The force generated by this eccentric torque acts on the bearing 20, causing the bearing 20 to produce axial displacement. At the same time, this eccentric torque also cooperates with the bearing 20 to cause radial displacement of the worm 30.

[0064] There is a distance between the line of action of the force that drives the worm 30 to generate axial displacement and the location of the abutment 12. The abutment 12 provides a reaction force to the support bearing 20. Since the abutment 12 is not located at the central axis of the bearing 20, but is located at a distance from the central axis of the bearing 20, the support force provided by the abutment 12 to the bearing 20 is eccentric. This eccentric force balances the axial force of the support bearing 20 while also generating a clockwise torque on the bearing 20. Adjusting the position of the abutment 12 to change its distance from the centerline of the bearing 20 can change the ratio of the torque to the axial force of the worm 30, thereby changing the magnitude of the torque. Adjusting the torque to an appropriate magnitude can offset or support the downward radial force exerted on the worm 30 by the worm wheel 40, thereby ensuring that the worm is close to the worm wheel without being subjected to radial force and generating a displacement gap.

[0065] Specifically, as shown in Figures 1 and 3, when the worm 30 and the worm wheel 40 cooperate in transmission, the worm wheel 40 exerts a radial force F1 and an axial force F2 on the worm 30. Since only one side of the worm 30 extends into the support 10, and the support 10 restricts the radial displacement of the worm 30, it is understandable that under the action of the radial force F1, the worm 30 has a tendency to rotate around the support 10 in a direction away from the worm wheel 40 and produce radial displacement, thereby increasing the clearance between the worm wheel 40 and the worm 30. When the clearance between the worm wheel 40 and the worm 30 is too large, it will affect the transmission between the worm 30 and the worm wheel 40, and may even cause the worm 30 or worm wheel 40 to rotate without driving the corresponding worm wheel 40 or worm 30 to rotate. The radial force F1 can be converted into a first eccentric torque T1 that applies to the worm 30 to rotate away from the worm wheel 40.

[0066] Because the abutment 12 abuts the outer ring 22 of the bearing 20, while the worm 30 extends into the inner ring 21 of the bearing 20, it is understandable that there is a gap between the abutment 12 and the first rotation axis L1 of the worm 30. As shown in Figure 3, the axial force F2 exerted by the worm wheel 40 on the worm 30 is transmitted along the first rotation axis L1 to the abutment 12. This not only limits the axial displacement of the bearing 20, but also cooperates with the abutment 12 to generate a second eccentric torque T2 that rotates the worm 30 toward the worm wheel 40. Furthermore, the second eccentric torque T2 is greater than or equal to the first eccentric torque T1.

[0067] As shown in FIG3 , the first eccentric moment T1 and the second eccentric moment T2 are in opposite directions, so that the second eccentric moment T2 can offset the first eccentric moment T1, thereby ensuring that the change in the clearance between the worm 30 and the worm wheel 40 is relatively small during the transmission of the worm 30 and the worm wheel 40. This improves the transmission accuracy of the transmission device 100 of the present application.

[0068] FIG4 is another schematic diagram of a force analysis of a transmission device provided in an embodiment of the present application. As shown in FIG4 , in another embodiment, the abutting portion 12 can be provided on the side of the bearing 20 close to the worm wheel 40, and abuts against the corresponding end face of the bearing 20. The direction of the axial force F2 generated by the worm wheel 40 acting on the worm 30 is along the first rotation axis L1 in the direction away from the abutting portion 12, and the radial force F1 generated by the worm wheel 40 acting on the worm 30 can cause the worm 30 to have a tendency to radially displace away from the worm wheel 40. It can be understood that the axial force F2 can also cooperate with the abutting portion 12 to form a second eccentric torque T2 that causes the worm 30 to rotate in the direction close to the worm wheel 40, so as to offset the first eccentric torque T1 formed by the radial force F1 and the support 10, thereby ensuring the matching clearance between the worm 30 and the worm wheel 40.

[0069] Therefore, the transmission device 100 of the present application is provided with a supporting portion 12 that can support the outer ring 22 of the bearing 20, so that when the worm 30 and the worm wheel 40 cooperate in transmission and generate a deflection torque, the supporting portion 12 can cooperate with the bearing 20 to generate a reverse deflection torque to limit the radial displacement of the worm 30, thereby ensuring the fitting clearance between the worm 30 and the worm wheel 40, and improving the transmission accuracy of the transmission device 100 of the present application.

[0070] Please refer to FIG. 5 , which is a schematic diagram illustrating force analysis of a transmission device 100 ′ in the prior art.

[0071] As shown in Figure 5, in the prior art, a transmission device 100' includes a worm wheel 10', a worm 20', a bearing 30', and a spring 40'. One end of the worm 20' extends into the bearing 30', while the other end is in driving connection with the worm wheel 10'. The spring 40' is fixed to the housing (not shown) of the transmission device 100' and is positioned on the side of the worm 20' facing away from the worm wheel 10', where it abuts against the worm wheel 10'.

[0072] When worm wheel 10' and worm 20' are in gear, the radial force F1' exerted by worm wheel 10' on worm 20' exerts an eccentric torque T' on worm 20', causing worm 20' to tilt away from worm wheel 10'. The spring force F2' provided by spring 40' is in the opposite direction of radial force F1', counteracting radial force F1' and ensuring clearance between worm wheel 10' and worm 20'.

[0073] However, in the prior art, to adapt to different operating conditions, the torque transmitted by the worm wheel 10' or worm 20' may vary significantly. The spring 40', limited by its elastic force range, cannot provide reliable elastic force feedback under all operating conditions. This results in a mismatch between the force exerted by the worm wheel 10' on the worm 20' and the force exerted by the spring 40' on the worm 20' under certain operating conditions. This may cause the worm 20' to move away from or toward the worm wheel 10', thereby increasing or decreasing the clearance between the worm 20' and the worm wheel 10', affecting the transmission accuracy of the worm wheel 10' and the worm 20'.

[0074] Therefore, the transmission device 100 of the present application is provided with a supporting portion 12 that abuts against the outer ring 22 of the bearing 20 along the first rotation axis L1 direction of the worm 30, so that when the worm 30 and the worm wheel 40 rotate in coordination and generate a deflection torque, the supporting portion 12 can cooperate with the bearing 20 to cause the bearing 20 to generate an axial displacement force, thereby forming a reverse deflection torque that can offset the radial displacement of the worm 30, thereby limiting the fitting clearance between the worm wheel 40 and the worm 30.

[0075] Because the first eccentric torque T1 and second eccentric torque T2 acting on the worm 30 of the transmission device 100 of the present application are provided by the radial force F1 and the axial force F2, respectively, and the magnitudes of the radial force F1 and the axial force F2 are related to the rotational torque of the worm wheel 40, it is understandable that when the rotational torque transmitted by the worm wheel 40 or the worm 30 changes, the magnitudes of the radial force F1 and the axial force F2 will also change, and accordingly, the first eccentric torque T1 and the second eccentric torque T2 will also change. In addition, the second eccentric torque T2 will change synchronously with the change of the first eccentric torque T1.

[0076] It can be understood that, compared to the eccentric torque provided by the elastic force of the spring 40' in the prior art, the arrangement of the abutting portion 12 of the transmission device 100 of the present application ensures that the second eccentric torque T2 can also change with the change of the first eccentric torque T1 when the rotational torque of the worm wheel 40 changes, and both can offset the first eccentric torque T1, thereby preventing the worm 30 from flipping relative to the support 10. This ensures the matching clearance between the worm 30 and the worm wheel 40, and improves the transmission accuracy of the transmission device 100 of the present application.

[0077] Please refer to FIG. 6 , which is a schematic diagram of a partial cross-sectional structure of a transmission device 100 provided in an embodiment of the present application.

[0078] As shown in Figure 6, the abutting portion 12 includes a first abutting portion 121 and a second abutting portion 122. The bearing 20 has a first end face 231 and a second end face 232 along the third rotation axis L3 of the bearing 20, with the first end face 231 being closer to the worm gear 40 (not shown) than the second end face 232. The first abutting portion 121 abuts against the first end face 231 of the bearing 20, and the second abutting portion 122 abuts against the second end face 232 of the bearing 20, thereby restricting the bearing 20 between the first abutting portion 121 and the second abutting portion 122 in the direction of the third rotation axis L3. This effectively limits the axial displacement of the bearing 20.

[0079] 6 , along the arrangement direction of the worm wheel 40 and the worm 30 , the first abutting portion 121 is closer to the second rotation axis L2 (not shown) of the worm wheel 40 than the second abutting portion 122 .

[0080] Since both the worm 30 and the bearing 20 are rotating structures, it is understandable that when the worm wheel 40 changes position along the circumference of the worm 30, the first abutting portion 121 or the second abutting portion 122 may coincide with the first rotation axis L1 in the arrangement direction of the worm wheel 40 and the worm 30.

[0081] Therefore, in the arrangement direction of the worm wheel 40 and the worm 30, a first abutting portion 121 and a second abutting portion 122 with different distances from the second rotation axis L2 are provided, which can avoid the situation where the first abutting portion 121 and the second abutting portion 122 coincide with the first rotation axis L1 at the same time when the arrangement direction of the worm wheel 40 changes.

[0082] Because the abutting portion 121 abuts against the outer ring 22 of the bearing 20, it is understood that both the first abutting portion 121 and the second abutting portion 122 can cooperate with the axial force F2 to generate a second eccentric moment T2. Therefore, in the arrangement direction of the worm wheel 40 and the worm 30, the spacing between the first abutting portion 121 and the second abutting portion 122 ensures the generation of the second eccentric moment T2, thereby offsetting the first eccentric moment T1 generated by the radial force F1 exerted by the worm wheel 40 on the worm 30. This prevents the worm 30 from flipping around the bearing 20 and ensures a clearance between the worm 30 and the worm wheel 40.

[0083] Specifically, please refer to Figure 7, which is another schematic diagram of force analysis of the transmission device 100 provided in one embodiment of the present application, and to Figure 8, which is another schematic diagram of force analysis of the transmission device 100 provided in one embodiment of the present application, and refer to Figure 6 in conjunction. Both Figures 7 and 8 are schematic diagrams of force analysis of the transmission device 100 of the present application using the structure of the first abutting portion 121 and the second abutting portion 122 shown in Figure 6.

[0084] As shown in Figures 6-8, in the arrangement direction of the worm wheel 40 and the worm 30, the first abutting portion 121 is closer to the second rotation axis L2 (not shown in the figure) relative to the first rotation axis L1, and the second abutting portion 122 is farther away from the second rotation axis L2 relative to the first rotation axis L1.

[0085] As shown in Figure 7, the rotation direction of the worm wheel 40 and the worm 30 may change during the transmission process. It is understandable that when the rotation direction of the worm wheel 40 or the worm 30 changes, the direction of the axial force F2 exerted by the worm wheel 40 on the worm 30 will also change accordingly.

[0086] When the axial force F2 exerted by the worm wheel 40 on the worm 30 is directed away from the bearing 20, the axial force F2 causes the outer ring 22 of the bearing 20 to press against the first abutting portion 121. That is, the outer ring 22 of the bearing 20 primarily bears the reaction force from the first abutting portion 121 in the direction along the third rotation axis L3 of the bearing 20.

[0087] Because the first abutting portion 121 is relatively close to the worm wheel 40 and spaced apart from the third rotation axis L3, the axial force F2 causes the worm 30 to tilt toward the worm wheel 40. In other words, under the action of the axial force F2 and the first abutting portion 121, the worm 30 experiences a second eccentric moment T2, tilting toward the worm wheel 40.

[0088] The second eccentric torque T2 can offset the influence of the first eccentric torque T1 on the worm 30 , thereby ensuring the fitting clearance between the worm 30 and the worm wheel 40 and improving the transmission accuracy of the transmission device 100 of the present application.

[0089] On the other hand, as shown in FIG8 , when the axial force F2 exerted by the worm wheel 40 on the worm 30 is directed toward the bearing 20, the axial force F2 can cause the outer ring 22 of the bearing 20 to press against the second abutting portion 122. It will be appreciated that the outer ring 22 of the bearing 20 primarily bears the force from the second abutting portion 122 in the direction along the third rotation axis L3 of the bearing 20.

[0090] Because the second abutting portion 122 is relatively far from the worm wheel 40 and spaced apart from the third rotation axis L3, the axial force F2 causes the worm 30 to tilt toward the worm wheel 40. That is, under the action of the axial force F2 and the second abutting portion 122, the worm 30 also experiences a second eccentric moment T2, tilting toward the worm wheel 40.

[0091] The second eccentric torque T2 can offset the influence of the first eccentric torque T1 on the worm 30 , thereby ensuring the fitting clearance between the worm 30 and the worm wheel 40 and improving the transmission accuracy of the transmission device 100 of the present application.

[0092] Therefore, the transmission device 100 of the present application arranges the first abutting portion 121 and the second abutting portion 122 on opposite sides of the first rotation axis L1, which can ensure the matching clearance between the worm 30 and the worm wheel 40 even when the rotation direction of the worm wheel 40 changes. This improves the applicable working conditions of the transmission device 100 of the present application.

[0093] In another embodiment, when the rotation direction of the worm wheel 40 or the worm 30 remains unchanged, and the axial force F2 exerted by the worm wheel 40 on the worm 30 is directed away from the bearing 20, both the first abutting portion 121 and the second abutting portion 122 are closer to the second rotation axis L2 relative to the first rotation axis L1 in the arrangement direction of the worm wheel 40 and the worm 30. Accordingly, the axial force F2 exerted by the worm wheel 40 on the worm 30 can cause the first abutting portion 121 to abut against the first end face 231. The second abutting portion 122 is used to cooperate with the first abutting portion 121 to define the axial position of the bearing 20.

[0094] Meanwhile, in another embodiment, when the rotation direction of the worm wheel 40 or the worm 30 remains unchanged and the direction of the axial force F2 exerted by the worm wheel 40 on the worm 30 is toward the bearing 20, in the arrangement direction of the worm wheel 40 and the worm 30, the first abutting portion 121 and the second abutting portion 122 are both farther away from the second rotation axis L2 relative to the first rotation axis L1. This application does not impose any particular limitation on this.

[0095] As shown in Figures 7 and 8, in one embodiment, there is a first distance D1 between the first abutting portion 121 and the third rotation axis L3 of the bearing 20, and there is a second distance D2 between the second abutting portion 122 and the third rotation axis L3 of the bearing 20, and the first distance D1 is less than or equal to the second distance D2.

[0096] In the direction of the first rotation axis L1, since the distance between the second abutting portion 122 and the second rotation axis L2 is longer than the distance between the first abutting portion 121 and the second rotation axis L2, the magnitude of the torque is not only related to the magnitude of the force, but also to the vertical distance from the line of action of the force to the rotation axis.

[0097] It is understandable that, under the action of the same radial force F1, the first eccentric moment T1 generated by the worm 30 around the first abutting portion 121 is smaller than the first eccentric moment T1 generated by the worm 30 around the second abutting portion 122. Correspondingly, the second eccentric moment T2 generated by the axial force F2 in conjunction with the first abutting portion 121 should be smaller than the second eccentric moment T2 generated by the axial force F2 in conjunction with the second abutting portion 122.

[0098] Because the magnitude of the axial force F2 changes synchronously with the magnitude of the radial force F1, setting a second distance D2 that is greater than or equal to the first distance D1 ensures that the second eccentric torque T2 generated by the axial force F2 and the second abutting portion 122 offsets the corresponding first eccentric torque T1. This ensures that the second abutting portion 122 effectively limits the radial displacement of the worm 30 and maintains the clearance between the worm 30 and the worm wheel 40.

[0099] Please refer to Figure 9, which is a partial front view of the transmission device 100 provided in one embodiment of the present application, and please refer to Figure 10, which is a partial exploded schematic diagram of the transmission device 100 provided in one embodiment of the present application, and refer to Figure 6 in conjunction.

[0100] As shown in FIG6 , the first abutting portion 121 can be detachably connected to the support 10 so that the first abutting portion 121 can be manufactured separately during the manufacturing process of the support 10, thereby reducing the manufacturing complexity of the support 10. The first abutting portion 121 includes a first axial protrusion 121a and a first radial protrusion 121b. As shown in FIG9 and FIG10 , the first abutting portion 121 is a circular ring structure, and the first axial protrusion 121a extends along the third rotation axis L3 toward the first end face 231 of the bearing 20 to abut the first end face 231. The first radial protrusion 121b protrudes in the radial direction.

[0101] The support 10 is provided with a mounting groove 10a that matches the first radial protrusion 121b. By accommodating the first radial protrusion 121b in the mounting groove 10a, the position of the first abutting portion 121 is fixed.

[0102] As shown in Figure 10, in one embodiment, two first axial protrusions 121a are provided, and in the arrangement direction of the worm wheel 40 and the worm 30, the two first axial protrusions 121a are located on the same side of the third rotation axis L3, and the distance between the two first axial protrusions 121a and the third rotation axis L3 is equal.

[0103] It can be understood that, as shown in Figure 10, by providing two first axial protrusions 121a, when the worm wheel 40 and the worm 30 cooperate in transmission, the forces applied by the two first axial protrusions 121a to the first end face 231 of the bearing 20 can be relatively uniform. On the other hand, when the worm wheel 40 and the worm 30 cooperate in transmission and generate an eccentric torque, the mutual cooperation of the two first axial protrusions 121a can prevent the axial force F2 from being directed in other directions when the eccentric torque is formed by the cooperation with the single first axial protrusion 121a, thereby ensuring the limiting effect of the first abutment 121 on the radial displacement of the worm 30. For another partial exploded schematic diagram of the transmission device 100, please refer to Figure 12, which is another partial cross-sectional schematic diagram of the transmission device 100 provided in one embodiment of the present application, and refer to Figure 13, which is a partial enlarged schematic diagram of the transmission device 100 provided in one embodiment of the present application.

[0104] As shown in Figures 11-13, the first axial protrusion 121a is an arc-shaped structure. The axial protrusion is located on one side of the bearing's rotational axis and is circumferentially arranged around the third rotational axis L3 to increase the contact area with the outer ring 22 of the bearing 20, thereby ensuring the contact effect between the first contact portion 121 and the outer ring 22 of the bearing 20. As shown in Figure 13, a first distance D1 is defined between the first axial protrusion 121a and the third rotational axis L3.

[0105] It will be appreciated that, as shown in FIG14 , in other embodiments, the second abutting portion 122 may also be detachably connected to the support 10. Accordingly, the second abutting portion 122 also includes a second axial protrusion 122 a and a second radial protrusion 122 b. The second axial protrusion 122 a extends toward the bearing 20 and abuts against the bearing 20, while the second radial protrusion 122 b engages with a mounting position (not shown) on the support 10 to achieve relative fixation of the second abutting portion 122.

[0106] The second axial protrusion 122a may also be provided in a manner similar to the first axial protrusion 121a shown in FIG. 10 , FIG. 11 , and FIG. 12 , and this application does not impose any particular limitation thereto.

[0107] In one embodiment, the transmission device 100 of the present application further includes a buffer member. The buffer member is positioned between the bearing 20 and the support 10. During the transmission process, the worm 30 and the worm wheel 40 may vibrate, which may be transmitted to the bearing 20 and cause friction between the bearing 20 and the support 10, thereby generating noise.

[0108] The buffer can absorb the vibration between the bearing 20 and the support 10, thereby avoiding the mutual friction between the bearing 20 and the support 10 due to vibration, reducing the noise generated by the transmission device 100 of the present application during operation, and improving the user experience.

[0109] As shown in Figure 15, in one embodiment, the steering mechanism 200 includes a steering input device 201, a steering execution device 202, and a transmission device 100. The transmission device 100 of the present application can be applied to the steering mechanism 200 of the vehicle 300 to rely on the higher transmission efficiency of the transmission device 100 of the present application to improve the steering efficiency of the steering mechanism.

[0110] As shown in FIG. 16 , in one embodiment, the steering mechanism 200 of the present application may be applied to a vehicle 300 to improve the steering efficiency of the vehicle 300 .

[0111] It should be understood that the terms "first," "second," etc. are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of the technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of the described features. In the description of the embodiments of this application, "plurality" means two or more, unless otherwise specifically defined.

[0112] Throughout this specification, reference to terms such as "one embodiment," "some embodiments," "illustrative embodiments," "examples," "specific examples," or "some examples" means that a specific feature, structure, material, or characteristic described in conjunction with the embodiment or example is included in at least one embodiment or example of the present application. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

[0113] It should be understood that the application of this application is not limited to the above examples. Those skilled in the art can make improvements or modifications based on the above description, and all such improvements and modifications should fall within the scope of protection of the claims appended to this application. Those skilled in the art will understand that implementing all or part of the processes of the above embodiments and making equivalent changes in accordance with the claims of this invention still fall within the scope of this invention.

Claims

1. A transmission device (100), characterized in that: The invention comprises a support (10), a bearing (20), a worm (30), and a worm wheel (40), wherein the bearing (20) is arranged in an inner hole (11) of the support, the worm (30) extends into an inner ring (21) of the bearing (20), and the worm (30) is drivingly connected to the worm wheel (40); The support (10) is also provided with a supporting portion (12), and the supporting portion (12) can be supported against the outer ring (22) of the bearing (20) along the rotation axis direction of the worm (30), and the supporting portion (12) is used to limit the radial displacement generated when the worm (30) and the worm wheel (40) are matched for transmission, so as to ensure the matching clearance between the worm wheel (40) and the worm (30).

2. The transmission device (100) according to claim 1, characterized in that: The abutting portion (12) comprises a first abutting portion (121) and a second abutting portion (122), wherein the first abutting portion (121) abuts against an end surface of the bearing (20) close to the worm gear (40), and the second abutting portion (122) abuts against an end surface of the bearing (20) away from the worm gear.

3. The transmission device (100) according to claim 2, characterized in that: In the arrangement direction of the worm wheel (40) and the worm (30), the first abutting portion (121) is closer to the rotation axis of the worm wheel (40) relative to the rotation axis of the worm (30).

4. The transmission device (100) according to claim 2, characterized in that: In the arrangement direction of the worm wheel (40) and the worm (30), the second abutting portion (122) is further away from the rotation axis of the worm wheel (40) relative to the rotation axis of the worm (30).

5. The transmission device (100) according to claim 2, characterized in that: Along the arrangement direction of the worm wheel (40) and the worm (30), the first abutting portion (121) is closer to the rotation axis of the worm wheel (40) than the second abutting portion (122).

6. The transmission device (100) according to claim 5, characterized in that: A first distance (D1) is provided between the first abutting portion (121) and the rotation axis of the bearing (20), a second distance (D2) is provided between the second abutting portion (122) and the rotation axis of the bearing (20), and the first distance (D1) is less than or equal to the second distance (D2).

7. The transmission device (100) according to any one of claims 1 to 6, characterized in that: The abutting portion (12) is a circular ring structure, and includes an axial protrusion, which extends along the rotation axis of the bearing (20) toward the end face of the bearing (20) and abuts against the end face of the outer ring (22) of the bearing (20) to limit the radial displacement generated when the worm (30) and the worm wheel (40) cooperate in transmission.

8. The transmission device (100) according to claim 7, characterized in that: There are two axial protrusions, and along the arrangement direction of the worm wheel (40) and the worm (30), the two axial protrusions are located on the same side of the rotation axis of the bearing (20), and the distance between the two axial protrusions and the rotation axis of the bearing (20) is equal.

9. The transmission device (100) according to claim 7, characterized in that: The axial protrusion is arc-shaped, is located on one side of the rotation axis of the bearing (20), and is circumferentially arranged around the rotation axis of the bearing (20).

10. The transmission device (100) according to claim 7, characterized in that: The supporting portion (12) further comprises a radial protrusion, which protrudes along the radial direction of the bearing (20). The support is also provided with a mounting groove (10a), and the radial protrusion is received in the mounting groove (10a) to achieve the position fixation of the supporting portion (12) by the support (10).

11. The transmission device (100) according to any one of claims 1 to 10, characterized in that: The supporting portion (12) is detachably connected to the support (10).

12. The transmission device (100) according to any one of claims 1 to 11, characterized in that: The transmission device (100) further comprises a buffer component, which is filled between the bearing (20) and the support (10), and is used to absorb vibration between the bearing (20) and the support (10).

13. A steering mechanism (200), characterized in that: The invention comprises a steering input device (201), a steering actuator device (202) and a transmission device (100) as claimed in any one of claims 1 to 12, wherein the steering input device (201) is drivingly connected to a worm (30) of the transmission device (100), and the steering actuator device (202) is drivingly connected to a worm wheel (40) of the transmission device (100).

14. A vehicle (300), characterized in that: It comprises a steering mechanism (200) as claimed in claim 13.

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