Transfer case actuator and vehicle

Abstract

The embodiments of the present application relate to the field of vehicle apparatuses. Provided are a transfer case actuator and a vehicle. The vehicle comprises the transfer case actuator. The transfer case actuator comprises a cycloidal reduction assembly, an output assembly and a swing arm. The cycloidal reduction assembly comprises an input shaft, a cycloidal gear, a cycloidal ring gear and an output shaft, the cycloidal gear is meshed with the cycloidal ring gear, the output shaft is configured to be in transmission connection with a driving member, the cycloidal gear is connected to the input shaft and the output shaft, and the output assembly comprises an output cam connected to the output shaft. The axis of the cycloidal ring gear is parallel to the axis of the cycloidal gear, so that the size of the overall outer contour of the actuator is reduced, thereby facilitating the fitting of an assembly. The required space is small, so that the arrangement of the whole actuator is more compact, thereby expanding the application scenarios of the transfer case actuator.

Description

Transfer case actuator and vehicle

[0001] CROSS-REFERENCE TO RELATED APPLICATIONS

[0002] This application claims priority to the Chinese patent application with application number CN202311686644.6 and title “A transfer case actuator and vehicle” filed with the Patent Office of China on December 8, 2023, the entire contents of which are incorporated by reference into this application. Technical Field

[0003] The present application relates to the field of vehicle equipment, and in particular, to a transfer case actuator and a vehicle. Background Art

[0004] Transfer cases are currently widely used in high-performance four-wheel drive vehicles as a solution for distributing torque between the front and rear axles. The wet clutch, the core of the torque distribution system, achieves variable torque transmission by varying the pressure on the working surface of the friction plate. Changing the pressure on the clutch friction plate generally involves two methods: hydraulics and a reduction mechanism with a ball cam, both of which are mature applications within the industry. Transfer cases using hydraulics offer rapid response and high controllability, but require a complete hydraulic system, which is complex and difficult to produce. The reduction mechanism with a ball cam essentially converts the rotational motion of the actuator power source into axial thrust on the ball cam, thereby varying the torque transmission pressure ultimately acting on the wet clutch friction plate.

[0005] The applicant has found through research that some existing reduction mechanisms use worm gears to achieve reduction, but the worm gear reduction mechanism is large in size and requires the shaft of the driving member to be staggered with the axis of the transfer case, which limits the applicable space.

[0006] Application Contents

[0007] The purpose of this application is to provide a transfer case actuator, which can reduce the space size occupied by the reduction mechanism and improve the applicable scenarios of the reduction mechanism.

[0008] The embodiment of the present application is implemented as follows:

[0009] In a first aspect, the present application provides a transfer case actuator, comprising:

[0010] The cycloid reduction assembly includes an input shaft, a cycloid gear, a cycloid ring gear, and an output shaft. The cycloid gear meshes with the cycloid ring gear. The input shaft is used for transmission connection with the driving member. The cycloid gear is connected to the input shaft and the output shaft.

[0011] The output assembly includes an output cam, which is connected to the output shaft. The output shaft is used to drive the output cam to rotate;

[0012] A swing arm, one end of the swing arm is connected to the output cam, and the other end of the swing arm is used to connect to the clutch.

[0013] In an optional embodiment, the cycloid gear and the cycloid ring gear are eccentrically arranged, and the cycloid ring gear and the cycloid gear differ by one tooth.

[0014] In an optional embodiment, the cycloid reduction assembly also includes an output gear, which is sleeved on the output shaft. The output assembly also includes a camshaft and a driven gear, and the output cam and the driven gear are both sleeved on the camshaft, and the driven gear is engaged with the output gear.

[0015] In an optional embodiment, the output cam has a first curved wall and a second curved wall connected in sequence along the circumferential direction, the first curved wall is concave, the second curved wall is convex, and the curvature radius of the second curved wall gradually increases in the direction away from the first curved wall. When the swing arm is in contact with the first curved wall, the clutch connected to the swing arm is in a disengaged position. When the swing arm is in contact with the second curved wall, the clutch connected to the swing arm is in a tightened state.

[0016] In an optional embodiment, the output cam also includes a third curved wall, which is connected to the second curved wall and is located on the side of the second curved wall away from the first curved wall. The third curved wall is convex and its own curvature radius remains unchanged. The curvature radius of the third curved wall is greater than or equal to the curvature radius of the end of the second curved wall away from the first curved wall.

[0017] In an optional embodiment, a ball bearing is further provided on the swing arm, and the ball bearing abuts against the cam.

[0018] In an optional embodiment, the cycloid reduction assembly further includes a first bearing, which is sleeved on the input shaft, and the outer wall of the first bearing is in contact with the inner wall of the output shaft.

[0019] In an optional embodiment, the cycloid reduction assembly further includes a transfer case housing and a second bearing. The cycloid ring gear is connected to the transfer case housing via threaded fasteners. The second bearing is sleeved on the output shaft and abuts against the inner wall of the transfer case housing.

[0020] In an optional embodiment, the transfer case actuator further includes a driving member, which is a brushless motor.

[0021] In a second aspect, the present application provides a vehicle comprising a transfer case actuator according to any one of the aforementioned embodiments.

[0022] The beneficial effects of the embodiments of the present application are as follows: the embodiments of the present application provide a transfer case actuator and a vehicle, the vehicle including a transfer case actuator, the transfer case actuator including a cycloid reduction assembly, an output assembly and a swing arm. The cycloid reduction assembly includes an input shaft, a cycloid gear, a cycloid ring gear and an output shaft, the cycloid gear meshes with the cycloid ring gear, the output shaft is used for transmission connection with the drive member, the cycloid gear is connected to the input shaft and the output shaft, the output assembly includes an output cam, and the output cam is connected to the output shaft. Since the axes of the cycloid ring gear and the cycloid gear are parallel, the overall outer contour of the mechanism can be made smaller, which is more conducive to the assembly of the assembly. The required space is smaller, making the layout of the overall mechanism more compact, and improving the applicable scenarios of the transfer case actuator.

[0023] In order to make the above-mentioned objects, features and advantages of the present application more obvious and easy to understand, preferred embodiments are given below and described in detail with reference to the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] In order to more clearly illustrate the specific implementation methods of the present application or the technical solutions in the prior art, the following is a brief introduction to the drawings required for use in the specific implementation methods or the description of the prior art. Obviously, the drawings described below are some implementation methods of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without any creative work.

[0025] FIG1 is a schematic structural diagram of a transfer case actuator provided in an embodiment of the present application from a first viewing angle;

[0026] FIG2 is a schematic structural diagram of a cycloid speed reduction assembly provided in an embodiment of the present application;

[0027] FIG3 is a schematic structural diagram of the transfer case actuator provided in an embodiment of the present application from a second perspective.

[0028] Figure markings: 1-transfer case actuator; 100-cycloid reduction assembly; 110-input shaft; 120-cycloid gear; 130-cycloid ring gear; 140-output shaft; 150-first bearing; 160-second bearing; 170-third bearing; 180-input shaft bearing; 190-output gear; 101-transfer case housing; 310-output cam; 311-first curved wall; 312-second curved wall; 313-third curved wall; 320-camshaft; 330-driven gear; 410-swing arm; 420-ball bearing; 500-driving member. DETAILED DESCRIPTION

[0029] To make the objectives, technical solutions, and advantages of the embodiments of the present application more clear, the technical solutions in the embodiments of the present application will be clearly and completely described below in conjunction with the accompanying drawings of the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, not all of the embodiments. Generally, the components of the embodiments of the present application described and shown in the drawings herein can be arranged and designed in various different configurations.

[0030] Therefore, the following detailed description of the embodiments of the present application provided in the accompanying drawings is not intended to limit the scope of the present application for protection, but merely represents selected embodiments of the present application. All other embodiments obtained by persons of ordinary skill in the art based on the embodiments in the present application without creative work are within the scope of protection of the present application.

[0031] It should be noted that similar reference numerals and letters denote similar items in the following drawings, and therefore, once an item is defined in one drawing, it does not need to be further defined or explained in subsequent drawings.

[0032] In the description of this application, it should be noted that the terms "center," "upper," "lower," "left," "right," "vertical," "horizontal," "inner," "outer," etc., indicating orientations or positional relationships, are based on the orientations or positional relationships shown in the accompanying drawings, or are the orientations or positional relationships in which the product of this application is typically placed when in use. These terms are intended only to facilitate the description of this application and simplify the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, be constructed, or operate in a specific orientation. Therefore, they should not be construed as limitations on this application. Furthermore, the terms "first," "second," "third," etc., are used only to distinguish descriptions and should not be construed as indicating or implying relative importance.

[0033] Furthermore, terms such as "horizontal" and "vertical" do not necessarily mean that a component must be absolutely horizontal or overhanging, but rather that it can be slightly tilted. For example, "horizontal" simply means that its direction is more horizontal than "vertical," and does not mean that the structure must be completely horizontal, but rather that it can be slightly tilted.

[0034] It should also be noted that, in the description of this application, unless otherwise expressly specified or limited, the terms "disposed," "installed," "connected," and "connected" should be understood in a broad sense. For example, they can refer to fixed connections, detachable connections, or integral connections; they can refer to mechanical connections or electrical connections; they can refer to direct connections or indirect connections through an intermediate medium; and they can refer to internal connections between two components. Those skilled in the art will understand the specific meanings of the above terms in this application based on the specific circumstances.

[0035] The specific structure of a transfer case actuator provided by an embodiment of the present application and the corresponding technical effects thereof are described in detail below with reference to the patent drawings.

[0036] 1 to 3 , the transfer case actuator 1 provided in the embodiment of the present application includes a cycloid reduction assembly 100 , an output assembly, and a swing arm 410 .

[0037] The cycloid reduction assembly 100 includes an input shaft 110, a cycloid gear 120, a cycloid ring gear 130 and an output shaft 140. The cycloid gear 120 is meshed with the cycloid ring gear 130. The output shaft 140 is used for transmission connection with the driving member 500. The cycloid gear 120 is connected to the input shaft 110 and the output shaft 140.

[0038] It can be understood that, through the cooperation between the cycloid ring gear 130 and the cycloid gear 120 , the rotational speed transmitted by the input shaft 110 can be reduced and transmitted to the output shaft 140 , thereby completing the deceleration.

[0039] Compared to existing worm gear reduction mechanisms, which occupy a larger space due to the staggered arrangement of the worm gear axes, they are not suitable for assembly in small spaces and have limited space applicability. In this embodiment, the cycloid ring gear 130 is parallel to the axis of the cycloid gear 120, ensuring that the axis of the output shaft 140 of the driving member 500 is parallel to the circumference of the cycloid gear 120. This can make the overall outer profile of the mechanism smaller and more convenient for assembly. The required space is smaller, making the overall mechanism layout more compact, improving the applicability of the reduction mechanism (i.e., the aforementioned cycloid reduction assembly 100) and the transfer case actuator 1.

[0040] The output assembly includes an output cam 310, which is connected to the output shaft 140. This connection can be direct or indirect via other components. The output shaft 140 drives the output cam 310 to rotate. One end of a swing arm 410 is connected to the output cam 310, and the other end of the swing arm 410 is connected to the clutch.

[0041] It will be appreciated that when the output cam 310 rotates in conjunction with the rotation of the output shaft 140, the swing arm 410, one end of which is connected to the output cam 310, will swing during the rotation of the output cam 310. Furthermore, since the other end of the swing arm 410 is connected to the clutch, the torque pressure acting on the clutch friction plate will change during the rotation of the swing arm 410.

[0042] Specifically, the end of the swing arm 410, away from the cam, includes a clutch ball-cam assembly. As the swing arm 410 swings, it drives the ball-cam to rotate. The ball-cam itself converts rotational motion into axial movement of the ball-cam, in other words, converts rotational motion into linear motion, thereby controlling the clutch's engagement and disengagement. It should be noted that the clutch ball-cam assembly described above is a conventional clutch configuration and will not be described in detail here.

[0043] Optionally, in this embodiment, the cycloid reduction assembly 100 further includes an output gear 190, which is sleeved on the output shaft 140. The output assembly further includes a camshaft 320 and a driven gear 330. The output cam 310 and the driven gear 330 are both sleeved on the camshaft 320, and the driven gear 330 meshes with the output gear 190. In other words, in this embodiment, further reduction can be achieved through the output gear 190 and the driven gear 330. Therefore, the transfer case actuator 1 in this embodiment has a two-stage reduction.

[0044] Of course, in some optional embodiments, deceleration can be achieved only by the cycloid gear 120 and the cycloid ring gear 130, without setting the output gear 190 and the driven gear 330. It can be understood that deceleration is achieved only by the cycloid gear 120 and the cycloid ring gear 130, and space for setting the camshaft 320 and the driven gear 330 can also be saved.

[0045] Optionally, in this embodiment, the cycloid ring gear 130 differs from the cycloid gear 120 by one tooth. It is understood that the tooth count relationship between the cycloid gear 120 and the cycloid ring gear 130 provides a deceleration effect. In other embodiments, the tooth count difference between the cycloid ring gear 130 and the cycloid gear 120 may be more than one tooth.

[0046] Optionally, in order to ensure that the output shaft 140 can stably drive the cycloid gear 120 to rotate, in this embodiment, the cycloid gear 120 and the cycloid ring gear 130 are eccentrically arranged, the input shaft 110 is a crankshaft, and the input shaft 110 includes a first shaft and a second shaft connected to each other. The first shaft is connected to the cycloid gear 120, and the end of the second shaft away from the first shaft is used to connect to the driving member 500. The eccentricity between the first shaft and the second shaft is equal to the eccentricity between the cycloid gear 120 and the cycloid ring gear 130.

[0047] It can be understood that since the cycloid ring gear 130 and the cycloid gear 120 only differ by one tooth, the eccentricity between the cycloid gear 120 and the cycloid ring gear 130 is small. Similarly, the eccentricity between the first shaft and the second shaft is also small, so the cycloid reduction assembly 100 does not occupy a large space.

[0048] Optionally, the cycloid reduction assembly 100 further includes a first bearing 150, which is sleeved on the input shaft 110. The outer wall of the first bearing 150 is in contact with the inner wall of the output shaft 140. In other words, the output shaft 140 has a hole for mounting the first bearing 150, and the inner wall of the hole is in contact with the outer wall of the first bearing 150. In other words, the output shaft 140 is sleeved on the first bearing 150. It is understood that the first bearing 150 can provide support for the output shaft 140.

[0049] Optionally, the cycloid reduction assembly 100 further includes a transfer case housing 101 and a second bearing 160, and the cycloid ring gear 130 is connected to the transfer case housing 101 by threaded fasteners. In detail, the end wall of the cycloid ring gear 130 is provided with a plurality of mounting holes spaced apart along its own circumferential direction. Similarly, the transfer case housing 101 is provided with a plurality of mating holes corresponding to the plurality of mounting holes, and the threaded fasteners are sequentially passed through the mounting holes and mating holes (not shown in the figure). The assembly of the cycloid ring gear 130 is completed. In some other embodiments, the cycloid ring gear 130 can also be assembled with the transfer case housing 101 by other connection methods, such as welding. The assembly method of the cycloid ring gear 130 and the transfer case housing 101 is not specifically limited here, as long as the stability of the assembly of the cycloid ring gear 130 and the transfer case housing 101 can be guaranteed.

[0050] The second bearing 160 is sleeved on the output shaft 140 and abuts against the inner wall of the transfer case housing. It can be understood that the provision of the second bearing 160 can ensure the service life of the output shaft 140.

[0051] In detail, in this embodiment, the output cam 310 has a first curved wall 311 and a second curved wall 312 connected in sequence along the circumferential direction. The first curved wall 311 is concave, and the second curved wall 312 is convex. The curvature radius of the second curved wall 312 gradually increases in the direction away from the first curved wall 311. When the swing arm 410 is in contact with the first curved wall 311, the clutch connected to the swing arm 410 is in a disengaged state. That is to say, when the output cam 310 is rotating, and at this time the first curved wall 311 is in contact with the swing arm 410, the ball cam at the other end of the swing arm 410 rotates, but at this time the clutch is in a disengaged state.

[0052] When the swing arm 410 is in contact with the second curved wall 312, the clutch connected to the swing arm 410 is in a compressed state. Specifically, when the output cam 310 rotates and the second curved wall 312 is in contact with the swing arm 410, the ball cam at the other end of the swing arm 410 rotates, converting its rotational motion into linear motion, thereby compressing the clutch. Furthermore, because the radius of curvature of the second curved wall 312 gradually increases as it moves away from the first curved wall 311, the clutch's compression force gradually increases as the output cam 310 rotates in the direction the second curved wall 312 moves away from the first curved wall 311.

[0053] Optionally, the output cam 310 also includes a third curved wall 313, which is connected to the second curved wall 312 and is located on the side of the second curved wall 312 away from the first curved wall 311. The third curved wall 313 is convex and its own curvature radius remains unchanged. The curvature radius of the third curved wall 313 is greater than or equal to the curvature radius of the end of the second curved wall 312 away from the first curved wall 311.

[0054] In this embodiment, the curvature radius of the third curved wall 313 is equal to the curvature radius of the end of the second curved wall 312 away from the first curved wall 311 , that is, the curvature radius of the third curved wall 313 is equal to the maximum curvature radius of the second curved wall 312 .

[0055] That is, when the output cam 310 rotates to the third curved wall 313 , that is, when the swing arm 410 swings under the action of the third curved wall 313 , the clutch is in a state of maximum pressing force.

[0056] In other words, the first curved wall 311 , the second curved wall 312 and the third curved wall 313 of the output cam 310 , which are sequentially connected along the circumferential direction, correspond to the clutch disengagement position, the clutch pressing force increasing stage and the clutch maximum pressing force maintaining stage.

[0057] In order to reduce the wear between the swing arm 410 and the output cam 310, in this embodiment, a ball bearing 420 is further provided on the swing arm 410, and the ball bearing 420 abuts against the cam. It can be understood that through the provision of the ball bearing 420, the sliding friction between the swing arm 410 and the output cam 310 can be converted into rolling friction, thereby reducing the wear between the swing arm 410 and the output cam 310 and improving the service life of the swing arm 410 and the output cam 310.

[0058] Optionally, in this embodiment, the transfer case actuator 1 further includes a driver 500, which is a brushless motor. It will be appreciated that the driver 500 uses a brushless motor as its power source, and control software can be used to perform open-loop control of the target position of the output terminal based on the brushless motor's own rotor position signal feedback, thereby improving the accuracy of the angular position of the output cam 310.

[0059] After testing, it was found that when the brushless motor rotor position was controlled within ±15°, the actual control accuracy of the angular position of the output cam 310 could be within ±0.5°, thereby improving the control accuracy of the clutch.

[0060] It can be understood that, through the cooperation between the output cam 310 and the driving member 500, the rotation angle of the brushless motor can be conveniently adjusted to control the rotation angle of the output cam 310, thereby controlling the clutch pressing state.

[0061] Optionally, the cycloid reduction assembly 100 further includes a third bearing 170 , wherein the third bearing 170 is sleeved on the input shaft 110 , and the cycloid gear 120 is sleeved on the third bearing 170 .

[0062] Optionally, the cycloid reduction assembly 100 further includes an input shaft bearing 180 sleeved on the input shaft 110 . It should be noted that the input shaft bearing 180 , the third bearing 170 , the first bearing 150 and the second bearing 160 are gradually away from the driving member 500 .

[0063] It should be noted that, in this embodiment, other components for transmitting power are also included between the cycloid ring gear 130 and the cycloid gear 120. Since the transmission structure of the cycloid ring gear 130 and the cycloid gear 120 is a conventional structure in the mechanical field, they will not be described in detail here. As long as the power transmitted by the input shaft 110 can be transmitted to the output shaft 140 through the cycloid ring gear 130 and the cycloid gear 120 to complete the deceleration and torque increase, it will be sufficient.

[0064] The present application also provides a vehicle comprising the aforementioned transfer case actuator 1. Since the vehicle comprises the aforementioned transfer case actuator 1, the vehicle provided by this embodiment also possesses the same technical effects as the transfer case actuator 1. Therefore, the technical effects of the vehicle will not be further elaborated upon here. It should be noted that the vehicle can be a pure electric or hybrid vehicle.

[0065] In summary, the embodiments of the present application provide a transfer case actuator 1 and a vehicle, the vehicle including the transfer case actuator 1, the transfer case actuator 1 including a cycloid reduction assembly 100, an output assembly, and a swing arm 410. The cycloid reduction assembly 100 includes an input shaft 110, a cycloid gear 120, a cycloid ring gear 130, and an output shaft 140. The cycloid gear 120 meshes with the cycloid ring gear 130. The output shaft 140 is used for transmission connection with the driving member 500. The cycloid gear 120 is connected to the input shaft 110 and the output shaft 140. The output assembly includes an output cam 310, which is connected to the output shaft 140. Because the axes of the cycloid ring gear 130 and the cycloid gear 120 are parallel, the required space is small, making the overall mechanism layout more compact and improving the applicable scenarios of the transfer case actuator 1.

[0066] The above description is merely a preferred embodiment of the present application and is not intended to limit the present application. Various modifications and variations are possible for those skilled in the art. Any modifications, equivalent substitutions, or improvements made within the spirit and principles of the present application shall be included within the scope of protection of the present application. Industrial Applicability

[0067] A cycloid reduction assembly, an output assembly, and a swing arm are provided in the vehicle's transfer case actuator. The cycloid reduction assembly includes an input shaft, a cycloid gear, a cycloid ring gear, and an output shaft. The cycloid gear meshes with the cycloid ring gear. The output shaft is used for transmission connection with the drive member. The cycloid gear is connected to the input shaft and the output shaft. The output assembly includes an output cam, which is connected to the output shaft. Because the axes of the cycloid ring gear and the cycloid gear are parallel, the overall outer dimensions of the mechanism can be made smaller, making assembly more convenient. The required space is smaller, making the overall mechanism layout more compact and improving the applicable scenarios of the transfer case actuator.

Claims

1. A transfer case actuator, characterized in that: include: A cycloid reduction assembly, the cycloid reduction assembly comprising an input shaft, a cycloid gear, a cycloid gear ring and an output shaft, the cycloid gear meshing with the cycloid gear ring, the input shaft being used for transmission connection with a driving member, the cycloid gear being connected with the input shaft and the output shaft; An output assembly, the output assembly comprising an output cam, the output cam being connected to the output shaft, and the output shaft being used to drive the output cam to rotate; A swing arm, one end of which is connected to the output cam, and the other end of which is used to be connected to a clutch.

2. The transfer case actuator according to claim 1, characterized in that: The cycloid gear and the cycloid gear ring are eccentrically arranged, and the cycloid gear ring is one tooth away from the cycloid gear.

3. The transfer case actuator according to claim 1, characterized in that: The cycloid reduction assembly also includes an output gear, which is sleeved on the output shaft. The output assembly also includes a camshaft and a driven gear, the output cam and the driven gear are both sleeved on the camshaft, and the driven gear is meshed with the output gear.

4. The transfer case actuator according to claim 1, characterized in that: The output cam has a first curved wall and a second curved wall connected in sequence along the circumferential direction, the first curved wall is concave, the second curved wall is convex, and the curvature radius of the second curved wall gradually increases in the direction away from the first curved wall. When the swing arm is in contact with the first curved wall, the clutch connected to the swing arm is in a disengaged position, and when the swing arm is in contact with the second curved wall, the clutch connected to the swing arm is in a tightened state.

5. The transfer case actuator according to claim 4, characterized in that: The output cam also includes a third curved wall, which is connected to the second curved wall and is located on the side of the second curved wall away from the first curved wall. The third curved wall is convex and its own curvature radius remains unchanged. The curvature radius of the third curved wall is greater than or equal to the curvature radius of the end of the second curved wall away from the first curved wall.

6. The transfer case actuator according to claim 1, characterized in that: A ball bearing is also provided on the swing arm, and the ball bearing abuts against the cam.

7. The transfer case actuator according to claim 1, characterized in that: The cycloid reduction assembly further includes a first bearing, which is sleeved on the input shaft, and an outer wall of the first bearing is in contact with an inner wall of the output shaft.

8. The transfer case actuator according to claim 1, characterized in that: The cycloid reduction assembly further includes a transfer case housing and a second bearing. The cycloid gear ring is connected to the transfer case housing via threaded fasteners. The second bearing is sleeved on the output shaft and abuts against the inner wall of the transfer case housing.

9. The transfer case actuator according to claim 1, characterized in that: The transfer case actuator also includes a driving member, which is a brushless motor.

10. A vehicle, characterized in that: It comprises the transfer case actuator as described in any one of claims 1 to 9.

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