Steering device and vehicle

Abstract

The application discloses a steering device and a vehicle, and belongs to the technical field of steering systems. The steering device comprises an input assembly, a planetary assembly and an output assembly. The input assembly comprises an input shaft, a first input gear, a second input gear and a transmission shaft, the first input gear is connected with the input shaft and is in mesh with the second input gear; the planetary assembly comprises a sun gear, a planet gear and a planet carrier, the second input gear is connected with the sun gear through the transmission shaft, and the planet gear is arranged on the planet carrier and is in mesh with the sun gear; and the output assembly comprises an output gear and a rack, the output gear is connected with the planet carrier and is in mesh with the rack. The steering device can improve the transmission ratio of the steering device.

Description

Technical Field

[0001] This application relates to the field of steering system technology, and more particularly to a steering device and a vehicle. Background Technology

[0002] Electric power steering (EPS) is a key component of a vehicle, and its performance directly affects the vehicle's handling, comfort, and safety. In an EPS system, the steering mechanism is the core component that converts steering wheel rotation into wheel steering action. Among them, rack-mounted electric power steering (R-EPS) is widely used in vehicles due to its compact structure and direct assistance.

[0003] In related technologies, the R-EPS system employs a single-stage gear transmission method using helical gears and racks. The torque applied by the driver to the steering wheel is transmitted through the input shaft to a single-stage helical gear, which then drives the rack to perform linear motion, thereby achieving wheel steering. However, single-stage gear transmissions have limited torque amplification capabilities, making it difficult to balance the requirements of small size and high output torque. Increasing the gear ratio to make steering easier would require a significant increase in the diameter of the driven gear, which would enlarge the entire steering system and infringe on vehicle space. Utility Model Content

[0004] This application provides a steering device and a vehicle that can improve the transmission ratio of the steering device.

[0005] To achieve the above objectives, according to a first aspect of this application, a steering device is provided, comprising: An input component, comprising an input shaft, a first input gear, a second input gear, and a transmission shaft, wherein the first input gear is connected to the input shaft and meshes with the second input gear; A planetary assembly, comprising a sun gear, planet gears, and a planet carrier, wherein a second input gear is connected to the sun gear via the drive shaft, and the planet gears are disposed on the planet carrier and mesh with the sun gear; An output assembly, comprising an output gear and a rack, wherein the output gear is connected to the planetary carrier and meshes with the rack.

[0006] Optionally, the input component further includes an adjustment mechanism for applying a thrust to the input shaft and / or the drive shaft to bring the first input gear and the second input gear closer together.

[0007] Optionally, the number of adjustment mechanisms is one or two. Each adjustment mechanism includes a first magnetic element, a second magnetic element, and a protrusion. The protrusion is disposed on the side of the second magnetic element facing away from the first magnetic element. The first magnetic element and the second magnetic element are arranged with their magnetic poles facing each other and generating a repulsive force. Wherein, when the number of the adjustment mechanism is one, the side of the protrusion facing away from the second magnetic element abuts against the drive shaft; or, the side of the protrusion facing away from the second magnetic element abuts against the input shaft; When there are two adjustment mechanisms, the protrusion of one adjustment mechanism abuts against the drive shaft on the side facing away from the second magnetic element, and the protrusion of the other adjustment mechanism abuts against the input shaft on the side facing away from the second magnetic element.

[0008] Optionally, the number of planetary gears is multiple, and the multiple planetary gears are evenly distributed around the sun gear in a circumferential direction; The planetary assembly also includes a gear ring, which is fitted over the outside of the plurality of planetary gears and meshes with the planetary gears.

[0009] Optionally, the rotation axis of the first input gear is parallel to the rotation axis of the second input gear; and / or, The rotation axis of the drive shaft is coaxial with the rotation axis of the sun gear; and / or, The rotation axis of the planetary carrier is coaxial with the rotation axis of the output gear.

[0010] Optionally, the first input gear and the second input gear have the same module and the same pressure angle, and the number of teeth of the first input gear is less than the number of teeth of the second input gear. Both the first input gear and the second input gear are one of spur gears, helical gears, and herringbone gears. The sun gear and the planet gears have the same module and the same pressure angle, and the number of teeth on the sun gear is less than the number of teeth on the planet gears. The sun gear and the planet gears are all one of the following: spur gears, helical gears, and herringbone gears. The output gear is a helical gear or a herringbone gear.

[0011] Optionally, the output gear is not arranged perpendicularly to the rack, and when the output gear meshes with the rack, at the meshing point, the center axis of the output gear teeth coincides with the center axis of the rack tooth grooves. A bearing is provided at the end of the output gear away from the planetary carrier. The bearing is a deep groove ball bearing or an angular contact ball bearing.

[0012] Optionally, there may be multiple planetary components, and in two adjacent planetary components, the planet carrier of one planetary component is connected to the sun gear of the other planetary component.

[0013] Optionally, the number of planetary components is two, and the two planetary components include a first planetary component and a second planetary component; The first planetary assembly includes a first sun gear, a first planet gear, and a first planet carrier. The second input gear is connected to the first sun gear via the drive shaft. The first planet gear is disposed on the first planet carrier and meshes with the first sun gear. The second planetary assembly includes a second sun gear, a second planet gear, and a second planet carrier. The second sun gear is connected to the first planet carrier, the second planet gear is disposed on the second planet carrier and meshes with the second sun gear, and the second planet carrier is connected to the output gear.

[0014] According to a second aspect of this application, a vehicle is provided, including a steering device as described in any of the above.

[0015] In the steering device and vehicle of this application embodiment, compared with the single-stage gear transmission method of helical gears and racks, this application sets up an input component, a planetary component, and an output component. The torque applied by the driver to the steering wheel is sequentially transmitted through the input component and the planetary component to the output gear of the output component, and then the output gear drives the rack to perform linear motion, thereby realizing wheel steering. This achieves two-stage or multi-stage deceleration and torque increase, thereby improving the transmission ratio of the steering device. Although the number of transmission stages increases, the size of each stage gear is reduced, making the steering device structure compact. At the same time, the transmission ratio of the steering device can be changed by flexibly adjusting the number of teeth of the input component, planetary component, and output component, thereby improving the steering force characteristics and better matching different vehicle models. In addition, multi-stage gear transmission distributes manufacturing and assembly errors across multiple pairs of gears, achieving an "error averaging" effect. Moreover, multi-stage transmission itself has a "filtering" attenuation effect on vibration and impact, which can reduce the impact of the road surface, thereby reducing the vibration and noise transmitted to the steering wheel and providing a smooth and quiet steering feel. Furthermore, the multi-stage gear transmission forms a high-rigidity system, which reduces elastic deformation and thus improves steering accuracy.

[0016] Other features and advantages of this application will be described in detail in the following detailed description section. Attached Figure Description

[0017] To more clearly illustrate the technical solutions in the embodiments of this application, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0018] To gain a more complete understanding of this application and its beneficial effects, the following description will be provided in conjunction with the accompanying drawings, wherein the same reference numerals in the following description denote the same parts.

[0019] Figure 1 This is a three-dimensional structural schematic diagram of the steering device provided in an exemplary embodiment of this disclosure; Figure 2 yes Figure 1 The diagram shows the exploded structure of the steering device. Figure 3 This is a schematic diagram of the structure of the input component provided in an exemplary embodiment of this disclosure; Figure 4 This is a schematic diagram of the structure of the planetary assembly provided in an exemplary embodiment of this disclosure; Figure 5 This is a schematic diagram of the planar structure of the steering device provided in an exemplary embodiment of this disclosure; Figure 6 It is along Figure 5 Schematic diagram of the cross section of line AA in the middle; Figure 7 yes Figure 6 A magnified schematic diagram of the structure at point A in the middle.

[0020] Explanation of reference numerals in the attached figures: 1. Input component; 11. Input shaft; 12. First input gear; 13. Second input gear; 14. Drive shaft; 15. Adjustment mechanism; 151. First magnetic component; 152. Second magnetic component; 153. Protrusion; 154. Bearing component; 2. Planetary assembly; 21. Sun gear; 22. Planet gears; 23. Planet carrier; 231. Connecting shaft; 232. Connector; 233. Planet shaft; 24. Gear ring; 25. First planetary assembly; 251. First sun gear; 252. 253. First planetary gear; 2531. First connecting shaft; 2532. First connecting member; 2533. First planetary shaft; 254. First gear ring; 26. Second planetary assembly; 261. Second sun gear; 262. Second planetary gear; 263. Second planetary carrier; 2631. Second connecting shaft; 2632. Second connecting member; 2633. Second planetary shaft; 264. Second gear ring; 3. Output assembly; 31. Output gear; 32. Rack; 33. Bearing. Detailed Implementation

[0021] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application. In addition, it should be understood that the specific embodiments described herein are only for illustration and explanation of this application and are not intended to limit this application. In this application, unless otherwise stated, directional terms such as "up," "down," "left," and "right" generally refer to up, down, left, and right in the actual use or working state of the device, specifically the drawing directions in the accompanying drawings.

[0022] In this application, unless otherwise expressly specified and limited, the terms "connected," "linked," "stacked," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two elements or the interaction between two elements. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances.

[0023] This application provides a steering device and a vehicle, which will be described in detail below. It should be noted that the order of description of the following embodiments is not intended to limit the preferred order of the embodiments of this application. Furthermore, in the following embodiments, the descriptions of each embodiment have their own emphasis; parts not described in detail in a certain embodiment can be referred to in the relevant descriptions of other embodiments.

[0024] According to the first aspect of this application, referring to Figure 1 and Figure 2 One embodiment of this application provides a steering device, including an input component 1, a planetary component 2, and an output component 3. The planetary component 2 is disposed between the input component 1 and the output component 3. The end of the input component 1 away from the planetary component 2 can be connected to a steering wheel, and the end of the output component 3 away from the planetary component 2 can be connected to a wheel. The steering device may further include a housing (not shown), and portions of the input component 1, the planetary component 2, and the output component 3 may be disposed within the housing.

[0025] Specifically, refer to Figure 1 and Figure 3The input component 1 may include an input shaft 11, a first input gear 12, a second input gear 13, and a drive shaft 14. The first input gear 12 is connected to the input shaft 11 and meshes with the second input gear 13. The rotation axis of the first input gear 12 and the rotation axis of the second input gear 13 may be parallel to each other to improve transmission stability. One end of the input shaft 11 may be connected to a vehicle steering wheel (not shown), and the other end of the input shaft 11 may be fixedly connected to the first input gear 12. The second input gear 13 may be fixedly connected to the drive shaft 14. When the driver turns the steering wheel, the input shaft 11 drives the first input gear 12 to rotate synchronously, and the first input gear 12 drives the second input gear 13 to rotate.

[0026] In some embodiments, the first input gear 12 and the second input gear 13 have the same module and the same pressure angle, and the number of teeth of the first input gear 12 is less than the number of teeth of the second input gear 13. Both the first input gear 12 and the second input gear 13 can be one of a spur gear, a helical gear, or a herringbone gear. As an example, both the first input gear 12 and the second input gear 13 are helical gears. Compared with spur gears, helical gears have a larger overlap ratio, smoother transmission, and lower noise, thereby improving the transmission smoothness of the first input gear 12 and the second input gear 13 and reducing noise. The first input gear 12 and the second input gear 13 both have a module of 2.5mm, a pressure angle of 20°, and a helix angle of 15° with opposite directions of rotation, ensuring that the axial forces cancel each other out during meshing. The first input gear 12 and the second input gear 13 constitute a first-stage reduction structure, achieving a reduction and torque increase effect. The first input gear 12 has 13 teeth, and the second input gear 13 has 39 teeth. The number of teeth of the first input gear 12 and the second input gear 13 can be adjusted according to the required transmission ratio.

[0027] Reference Figure 2 and Figure 4 The planetary assembly 2 may include a sun gear 21, planet gears 22, and a planet carrier 23. The end of the drive shaft 14 furthest from the second input gear 13 may be connected to the sun gear 21. The second input gear 13 can be connected to the sun gear 21 via the drive shaft 14 to transmit power to the sun gear 21. The rotation axis of the drive shaft 14 and the rotation axis of the sun gear 21 may be coaxial to reduce additional torque. The planet gears 22 may be mounted on the planet carrier 23 and mesh with the sun gear 21. When the driver turns the steering wheel, the input shaft 11 drives the first input gear 12 to rotate synchronously. The first input gear 12 drives the second input gear 13 to rotate. The second input gear 13 drives the sun gear 21 to rotate via the drive shaft 14, and the sun gear 21 drives the planet gears 22 to rotate.

[0028] Reference Figure 4The planetary carrier 23 may include a connecting shaft 231, a connecting member 232, and a planetary shaft 233. The connecting member 232 may be disposed at one end of the connecting shaft 231 and extend radially along the connecting shaft 231. The planetary shaft 233 may be disposed at the end of the connecting member 232 away from the connecting shaft 231 and extend axially along the connecting shaft 231, and the axial direction of the connecting shaft 231 and the axial direction of the planetary shaft 233 may be parallel to each other. The number of connecting members 232 is equal to the number of planetary shafts 233 and they are arranged in a one-to-one correspondence. The planetary shaft 233 is used to mount the planetary gears 22.

[0029] Reference Figure 4 The planetary assembly 2 has multiple planetary gears 22, which are evenly distributed circumferentially around the sun gear 21. The planetary assembly 2 may also include a ring gear 24, which can be fixed to the housing. The ring gear 24 is fitted around the outside of the multiple planetary gears 22 and meshes with them, forming a planetary gear transmission mechanism with higher rigidity and load-bearing capacity. As an example, there are three planetary gears 22, which are evenly distributed axially around the planet carrier 23. The included angle between the axes of adjacent planetary gears 22 is 120°, and all three mesh with the sun gear 21. The ring gear 24 is an internal gear, which can be fixed to the housing and meshes with the planetary gears 22 to form a closed transmission.

[0030] In some embodiments, the sun gear 21 and planet gear 22 have the same module and pressure angle, and the number of teeth on the sun gear 21 is less than the number of teeth on the planet gear 22. Both the sun gear 21 and planet gear 22 can be spur gears, helical gears, or herringbone gears. As an example, both the sun gear 21 and planet gear 22 are helical gears. Compared to spur gears, helical gears have a larger overlap ratio, smoother transmission, and lower noise, thereby improving the transmission smoothness of the sun gear 21 and planet gear 22 and reducing noise. The sun gear 21 and planet gear 22 both have a module of 3mm, a pressure angle of 20°, and a helix angle of 15° with opposite directions of rotation, ensuring that the axial forces cancel each other out during meshing. The sun gear 21, planet gear 22, and ring gear 24 constitute a second-stage reduction structure, achieving a reduction and torque increase effect. The sun gear 21 has 11 teeth, the planet gear 22 has 14 teeth, and the ring gear 24 has 39 teeth. The number of teeth on the sun gear 21, planet gear 22, and ring gear 24 can be adjusted according to the transmission ratio requirements.

[0031] Reference Figure 1 and Figure 2The output assembly 3 may include an output gear 31 and a rack 32. The output gear 31 can be connected to the planetary carrier 23 and mesh with the rack 32. That is, the output gear 31 can be connected to the connecting shaft 231 to receive torque from the planetary assembly 2. When the output gear 31 rotates, it drives the rack 32 to move axially. The two ends of the rack 32 can be connected to the steering knuckle arm (not shown) via tie rods (not shown), ultimately achieving wheel steering. The rotation axis of the planetary carrier 23 is coaxial with the rotation axis of the output gear 31, that is, the rotation axis of the connecting shaft 231 is coaxial with the rotation axis of the output gear 31, thus reducing additional torque. The output gear 31 can be a helical gear or a herringbone gear. As an example, the output gear 31 is a herringbone gear, which is equivalent to a combination of two helical gears with opposite helix angles. During transmission, the axial forces generated by the two opposite helix angles can cancel each other out, thereby further reducing the axial force burden on the bearing 33, improving the smoothness and accuracy of the transmission between the output gear 31 and the rack 32.

[0032] In some embodiments, refer to Figures 5 to 7 The output gear 31 and rack 32 are not arranged perpendicularly, forming an axial angle between them, for example, 85°, to adapt to the spatial layout of the vehicle's front chassis, avoid interference between the output gear 31 and other components, and ensure that the axial travel of the rack 32 meets the wheel steering angle requirements. Furthermore, when the output gear 31 and rack 32 mesh, at the meshing point, the center axis of the teeth of the output gear 31 coincides with the center axis of the tooth grooves of the rack 32 (e.g., ...). Figure 7 (As shown by the dotted line in the diagram), this ensures that when the steering wheel is in the center position, the wheels are also in the center position for straight-line driving, improving the sense of center when steering.

[0033] Reference Figure 5 A bearing 33 can be provided at the end of the output gear 31 away from the rack 32 and planetary carrier 23. The end of the output gear 31 away from the planetary carrier 23 can be supported on the housing by the bearing 33. The bearing 33 is a deep groove ball bearing or an angular contact ball bearing. As an example, the bearing 33 uses a pair of angular contact ball bearings. The two angular contact ball bearings can be installed back-to-back or face-to-face to bear the axial and radial forces generated by the transmission of the output gear 31, so as to improve the axial load capacity of the output gear 31 to offset and constrain the generated axial force, prevent the output gear 31 from axially moving, and thus improve the transmission accuracy and rigidity of the steering device.

[0034] In this application, compared to the single-stage gear transmission method using helical gears and rack 32, this application, by setting up an input component 1, a planetary component 2, and an output component 3, allows the torque applied to the steering wheel by the driver to be transmitted sequentially through the input component 1 and planetary component 2 to the output gear 31 of the output component 3. The output gear 31 then drives the rack 32 to perform linear motion, thereby achieving wheel steering. This achieves two-stage or multi-stage reduction and torque increase, thus improving the transmission ratio of the steering device. Although the number of transmission stages increases, the size of each gear is reduced, resulting in a compact steering device structure. Furthermore, the number of teeth in the input component 1, planetary component 2, and output component 3 can be flexibly adjusted to change the transmission ratio of the steering device, thereby improving steering force characteristics and better matching different vehicle models. In addition, multi-stage gear transmission distributes manufacturing and assembly errors across multiple pairs of gears, achieving an "error averaging" effect. Moreover, multi-stage transmission itself has a "filtering" and attenuation effect on vibration and impact, reducing the impact of the road surface and thus reducing vibration and noise transmitted to the steering wheel, providing a smooth and quiet steering feel. Furthermore, the multi-stage gear transmission forms a high-rigidity system, which reduces elastic deformation and thus improves steering accuracy.

[0035] In some embodiments, the input component 1 may further include an adjustment mechanism 15, which is used to apply a thrust to the input shaft 11 and / or the drive shaft 14 to bring the first input gear 12 and the second input gear 13 closer to each other, thereby eliminating or reducing the meshing clearance between the first input gear 12 and the second input gear 13, which can reduce the transmission backlash and thus improve steering precision and driving comfort.

[0036] Specifically, refer to Figure 3The adjustment mechanism 15 may include a first magnetic element 151, a second magnetic element 152, and a protrusion 153. The protrusion 153 may be disposed on the side of the second magnetic element 152 facing away from the first magnetic element 151 and connected to the second magnetic element 152. The first magnetic element 151 and the second magnetic element 152 may both be magnets, for example. The same magnetic poles of the first magnetic element 151 and the second magnetic element 152 are arranged facing each other and generate a repulsive force. Under the action of the magnetic repulsive force, the first input gear 12 and the second input gear 13 are pushed closer to each other, eliminating the meshing gap between them. The adjustment mechanism 15 may also include a support member 154, which may be connected to the housing. The first magnetic element 151 may be fixedly connected to the support member 154 to fix the position of the first magnetic element 151. The second magnetic element 152 is movably mounted on the support member 154. The second magnetic element 152 and the first magnetic element 151, with their same magnetic poles facing each other, generate a repulsive force. This causes the protrusion 153 to apply a pushing force to the input shaft 11 or the transmission shaft 14, bringing the first input gear 12 and the second input gear 13 closer together, thereby eliminating or reducing the meshing clearance between the first input gear 12 and the second input gear 13. In this application, an adjustment mechanism 15 driven by the repulsive force of magnetic elements continuously applies a pushing force to the input shaft 11 and / or the transmission shaft 14 through the repulsive action of the same poles of the first magnetic element 151 and the second magnetic element 152, thereby pushing the first input gear 12 and / or the second input gear 13 closer together, dynamically eliminating the meshing clearance between the first input gear 12 and the second input gear 13. Compared to traditional spring compensation structures, magnetic repulsion has the advantages of high stability and no risk of fatigue failure, ensuring that steering accuracy is not affected during long-term use.

[0037] The adjustment mechanism 15 can be one or two. When there is only one adjustment mechanism 15, the side of the protrusion 153 facing away from the second magnetic element 152 can abut against the drive shaft 14, so that the second input gear 13 moves closer to the first input gear 12, thereby eliminating or reducing the meshing clearance between the first input gear 12 and the second input gear 13. Alternatively, the side of the protrusion 153 facing away from the second magnetic element 152 can abut against the input shaft 11, so that the first input gear 12 moves closer to the second input gear 13, thereby eliminating or reducing the meshing clearance between the first input gear 12 and the second input gear 13.

[0038] When there are two adjustment mechanisms 15, the side of the protrusion 153 of one adjustment mechanism 15 facing away from the second magnetic element 152 can abut against the drive shaft 14, and the side of the protrusion 153 of the other adjustment mechanism 15 facing away from the second magnetic element 152 can abut against the input shaft 11, so that the first input gear 12 and the second input gear 13 are brought closer to each other, thereby eliminating or reducing the meshing gap between the first input gear 12 and the second input gear 13.

[0039] In some embodiments, the number of planetary components 2 can be one or more. (Refer to...) Figure 1 and Figure 2 When there are multiple planetary assemblies 2, in two adjacent planetary assemblies 2, the planet carrier 23 of one planetary assembly 2 can be connected to the sun gear 21 of the other planetary assembly 2, that is, the connecting shaft 231 of the planet carrier 23 of one planetary assembly 2 can be connected to the sun gear 21 of the other planetary assembly 2. Multiple planetary assemblies 2 connected in series can further improve the overall transmission ratio of the steering system, making it particularly suitable for commercial vehicles or high-performance vehicles that require extremely light steering or require a large output of assist torque.

[0040] As an example, the number of planetary components 2 is two, and the two planetary components 2 may include a first planetary component 25 and a second planetary component 26. The first planetary component 25 and the second planetary component 26 have the same or similar structures.

[0041] Reference Figure 1 and Figure 2 The first planetary assembly 25 may include a first sun gear 251, first planet gears 252, and a first planet carrier 253. The second input gear 13 can be connected to the first sun gear 251 via a drive shaft 14. The first planet gears 252 can be disposed on the first planet carrier 253 and mesh with the first sun gear 251. The first planet carrier 253 may include a first connecting shaft 2531, a first connecting member 2532, and a first planetary shaft 2533. The first connecting member 2532 can be disposed at one end of the first connecting shaft 2531 and extend radially along the first connecting shaft 2531. The first planetary shaft 2533 can be disposed at the end of the first connecting member 2532 away from the first connecting shaft 2531 and extend axially along the first connecting shaft 2531. The axial direction of the first connecting shaft 2531 and the axial direction of the first planetary shaft 2533 can be parallel to each other. The number of first connecting members 2532 is equal to the number of first planetary shafts 2533 and they are arranged in a one-to-one correspondence. The first planetary shaft 2533 is used to mount the first planet gears 252. The first planetary assembly 25 may further include a first gear ring 254, which is sleeved on the outside of the plurality of first planetary gears 252 and meshes with the first planetary gears 252.

[0042] Reference Figure 1 and Figure 2The second planetary assembly 26 may include a second sun gear 261, a second planet gear 262, and a second planet carrier 263. The second sun gear 261 may be connected to the first planet carrier 253, the second planet gear 262 may be disposed on the second planet carrier 263 and mesh with the second sun gear 261, and the second planet carrier 263 may be connected to the output gear 31. The second planet carrier 263 may include a second connecting shaft 2631, a second connecting member 2632, and a second planetary shaft 2633. The second connecting member 2632 may be disposed at one end of the second connecting shaft 2631 and extend radially along the second connecting shaft 2631, and the second planetary shaft 2633 may be disposed at the end of the second connecting member 2632 away from the second connecting shaft 2631 and extend axially along the second connecting shaft 2631, and the axial direction of the second connecting shaft 2631 and the axial direction of the second planetary shaft 2633 may be parallel to each other. The number of second connectors 2632 is equal to the number of second planetary shafts 2633 and they are arranged in a one-to-one correspondence. The second planetary shafts 2633 are used to mount the second planetary gears 262. The second planetary assembly 26 may also include a second gear ring 264, which is sleeved on the outside of the plurality of second planetary gears 262 and meshes with the second planetary gears 262.

[0043] As an example, the steering mechanism operates as follows: the driver turns the steering wheel, and torque is transmitted to the input shaft 11, which sequentially drives the first input gear 12 and the second input gear 13 to rotate; the second input gear 13 drives the first sun gear 251 of the first planetary assembly 25 to rotate through the transmission shaft 14, and the first sun gear 251 drives the first planet gear 252 to rotate on its own axis and revolve around the first sun gear 251, which in turn drives the first planet carrier 253 to rotate; the first planet carrier 253 drives the second sun gear 261 of the second planetary assembly 26 to rotate, and the second sun gear 261 drives the second planet gear 262 to rotate on its own axis and revolve around the second sun gear 261, which in turn drives the second planet carrier 263 to rotate; finally, the second planet carrier 263 drives the output gear 31 to rotate, which in turn drives the rack 32 to move linearly, thus completing the steering action.

[0044] According to a second aspect of this application, a vehicle is provided, including a steering device as described in any of the above.

[0045] In the description of this application, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include one or more features. In the description of this application, "multiple" means two or more, unless otherwise explicitly specified.

[0046] In the above embodiments, the descriptions of each embodiment have different focuses. For parts not described in detail in a certain embodiment, please refer to the relevant descriptions in other embodiments.

[0047] The embodiments, implementation methods, and related technical features of this application can be combined and substituted for each other without conflict.

[0048] The above are merely preferred embodiments of this application and are not intended to limit this application in any way. Any simple modifications, equivalent changes, and alterations made to the above embodiments based on the technical essence of this application without departing from the scope of the technical solution of this application shall still fall within the scope of the technical solution of this application.

Claims

1. A steering device characterized by comprising: include: An input component, comprising an input shaft, a first input gear, a second input gear, and a transmission shaft, wherein the first input gear is connected to the input shaft and meshes with the second input gear; A planetary assembly, comprising a sun gear, planet gears, and a planet carrier, wherein a second input gear is connected to the sun gear via the drive shaft, and the planet gears are disposed on the planet carrier and mesh with the sun gear; An output assembly, comprising an output gear and a rack, wherein the output gear is connected to the planetary carrier and meshes with the rack.

2. The steering device according to claim 1, characterized by The input component further includes an adjustment mechanism for applying a thrust to the input shaft and / or the drive shaft to bring the first input gear and the second input gear closer together.

3. The steering device of claim 2, wherein The number of adjustment mechanisms is one or two. Each adjustment mechanism includes a first magnetic element, a second magnetic element, and a protrusion. The protrusion is disposed on the side of the second magnetic element that faces away from the first magnetic element. The first magnetic element and the second magnetic element are arranged with their magnetic poles facing each other and generating a repulsive force. Wherein, when the number of the adjustment mechanism is one, the side of the protrusion facing away from the second magnetic element abuts against the drive shaft; or, the side of the protrusion facing away from the second magnetic element abuts against the input shaft; When there are two adjustment mechanisms, the protrusion of one adjustment mechanism abuts against the drive shaft on the side facing away from the second magnetic element, and the protrusion of the other adjustment mechanism abuts against the input shaft on the side facing away from the second magnetic element.

4. The steering device of claim 1, wherein The number of planetary gears is multiple, and the multiple planetary gears are evenly distributed around the sun gear in a circumferential direction. The planetary assembly also includes a gear ring, which is fitted over the outside of the plurality of planetary gears and meshes with the planetary gears.

5. The steering device of claim 1, wherein The rotation axis of the first input gear is parallel to the rotation axis of the second input gear; and / or, The rotation axis of the drive shaft is coaxial with the rotation axis of the sun gear; and / or, The rotation axis of the planetary carrier is coaxial with the rotation axis of the output gear.

6. The steering device of claim 1, wherein The first input gear and the second input gear have the same module and the same pressure angle, and the number of teeth of the first input gear is less than the number of teeth of the second input gear. Both the first input gear and the second input gear are one of the following: spur gear, helical gear, and herringbone gear. The sun gear and the planet gears have the same module and the same pressure angle, and the number of teeth on the sun gear is less than the number of teeth on the planet gears. The sun gear and the planet gears are all one of the following: spur gears, helical gears, and herringbone gears. The output gear is a helical gear or a herringbone gear.

7. The steering device of claim 1, wherein The output gear is not perpendicular to the rack, and when the output gear meshes with the rack, at the meshing point, the center axis of the output gear teeth coincides with the center axis of the rack tooth grooves. A bearing is provided at the end of the output gear away from the planetary carrier. The bearing is a deep groove ball bearing or an angular contact ball bearing.

8. The steering device of claim 1, wherein The number of the planetary assemblies is multiple, and the planet carrier of one of the adjacent two planetary assemblies is connected with the sun gear of the other planetary assembly.

9. The steering device of claim 8, wherein The number of the planetary assemblies is two, and the two planetary assemblies comprise a first planetary assembly and a second planetary assembly. The first planetary assembly comprises a first sun gear, a first planetary gear and a first planet carrier, the second input gear is connected with the first sun gear through the transmission shaft, and the first planetary gear is arranged on the first planet carrier and is in mesh with the first sun gear. The second planetary assembly comprises a second sun gear, a second planetary gear and a second planet carrier, the second sun gear is connected with the first planet carrier, the second planetary gear is arranged on the second planet carrier and is in mesh with the second sun gear, and the second planet carrier is connected with the output gear.

10. A vehicle characterized by comprising: The steering device comprises the steering device according to any one of claims 1 to 9.

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