A controllable tooth clutch with high tooth success rate

Abstract

The present application relates to the field of tooth clutch, in particular to a controllable tooth clutch with high tooth matching success rate, comprising an output assembly, a sliding assembly and an input assembly; an inner driving tooth is integrally formed on the inner circumferential surface of the output assembly, and an inner driving tooth end taper is integrally formed on the end of the inner driving tooth towards the sliding assembly; an outer driving tooth is integrally formed on the outer circumferential surface of the sliding assembly, an inner sliding tooth is integrally formed on the inner circumferential surface of the sliding assembly, a spring plug, a spring and a top rod are installed inside the sliding assembly, and an outer driving tooth end taper is integrally formed on the end of the outer driving tooth towards the output assembly. The present application sets the guiding tapers on the ends of the inner and outer driving teeth to match each other, which can convert the axial thrust into the circumferential rotation torque when the clutch is engaged, drive the sliding assembly to rotate automatically to complete the tooth matching, and transfer the interval shaving structure from the driving tooth to the sliding tooth, thereby avoiding the problem of the transmission torque capacity greatly decreasing due to the interval shaving of the driving tooth in the traditional technology.

Description

Technical Field

[0001] This invention relates to the field of toothed clutches, and more specifically to a controllable toothed clutch with a high success rate in tooth engagement. Background Technology

[0002] As a commonly used mechanical transmission component, the gear clutch is widely used in power transmission systems in vehicles, construction machinery, ships, aerospace, and other fields. It has advantages such as simple and compact structure, strong torque transmission capacity, no relative slippage after engagement, and high transmission efficiency. Among them, the controllable gear clutch controls the axial movement of the slip component through an external operating mechanism to realize the engagement and disengagement of power, and is a key core component for power switching in the transmission system.

[0003] However, existing controllable gear clutches suffer from significant technical contradictions and drawbacks in practical applications. On one hand, the success rate of tooth alignment is low. Clutch engagement requires precise angular alignment between the drive teeth and their corresponding tooth grooves, a probability extremely low under natural conditions. To improve the success rate, existing technologies typically employ thinning the tooth thickness to increase tooth clearance or intermittently shaving the drive teeth. However, even with these improvements, the success rate still falls short of the requirements for rapid engagement, necessitating repeated clutch engagement operations and severely reducing the transmission system's response speed and ease of use. On the other hand, existing methods for improving tooth alignment significantly reduce the clutch's torque transmission capacity and power density. Intermittent shaving of the drive teeth drastically reduces the number of meshing drive teeth with the same pitch circle diameter, resulting in a significant decrease in the overall torque transmission capacity of the clutch. To maintain torque transmission capacity, the clutch's radial dimension must be increased, leading to wasted space and materials and severely hindering the development of controllable gear clutches towards higher power density and miniaturization. Summary of the Invention

[0004] This invention addresses the technical problems existing in the prior art by providing a controllable gear clutch with a high gear-matching success rate.

[0005] The technical solution of the present invention to solve the above-mentioned technical problems is as follows: a controllable toothed clutch with high tooth alignment success rate, comprising an output component, a sliding component and an input component; The output component has an inner drive tooth on its inner circumferential surface, and the inner drive tooth has an inner drive tooth end cone surface facing the end of the sliding component. The outer circumferential surface of the sliding component is provided with an external driving tooth, the inner circumferential surface of the sliding component is provided with an internal sliding tooth, the sliding component is equipped with a spring plug, a spring and a push rod, and the end of the external driving tooth facing the output component is provided with an external driving tooth end cone surface. The input component has an outer sliding tooth on its outer circumferential surface facing the sliding component. The sliding component and the input component are engaged by an inner sliding tooth and an outer sliding tooth. Both the inner and outer sliding teeth are spaced-out shaving structures, and a tooth flank clearance of one tooth pitch is reserved between the inner and outer sliding teeth.

[0006] In a preferred embodiment, the spring plug, spring, and push rod are symmetrically distributed along the center line of the inner sliding tooth groove. The spring presses against the two sides of the outer sliding tooth through the push rod. The spring keeps the outer sliding tooth in the center position relative to the inner sliding tooth when the clutch is disengaged. The outer sliding tooth rotates from its central position to both sides, and the limiting angle of the outer sliding tooth is β. The rotation angle of the position where the center line of the outer driving tooth coincides with the center line of the inner driving tooth relative to the position where the center line of the outer driving tooth coincides with the center line of the inner driving tooth groove is α, where β > α. The spring plug, spring, and push rod mentioned above are symmetrically arranged along the center line of the inner sliding tooth groove, as shown in the attached figure. This is to ensure that the spring forces on both sides are equal in magnitude and opposite in direction, so that the outer sliding tooth always remains in the central position when disengaged. The rotation angle of the position where the center line of the outer driving tooth coincides with the center line of the inner driving tooth relative to the position where the center line of the outer driving tooth coincides with the center line of the inner driving tooth groove is α. As shown in the figures, the limiting angle of the outer sliding tooth rotating from its central position to both sides is β, and β > α, thereby ensuring that the conical surface plays a guiding role throughout the entire tooth-setting process, preventing tooth-setting failure due to premature locking of the sliding tooth.

[0007] In a preferred embodiment, the inner drive tooth end cone is a conical structure protruding axially outward from the end face of the inner drive tooth, with the tip of the cone pointing towards the sliding assembly. The outer drive tooth end cone is also a conical structure protruding axially outward from the end face of the outer drive tooth, with the tip pointing towards the output assembly. This decomposes the axial thrust into an axial component and a circumferential component, with the circumferential component driving the sliding assembly to rotate. When the outer drive tooth contacts the inner drive tooth, the inner and outer drive tooth end cones interact, generating a component force that rotates the sliding assembly. This guides the outer drive tooth into the tooth groove of the inner drive tooth, allowing the axial movement and rotation of the sliding assembly to occur simultaneously. The cone angle of the guide cone determines the ratio of the axial force to the rotational torque.

[0008] In a preferred embodiment, the number of teeth, module, and pressure angle of the inner and outer drive teeth are matched. The inner and outer drive teeth are used for complete meshing and disengagement through axial relative movement, ensuring good tooth surface contact and uniform load distribution when the drive teeth are meshing, avoiding uneven loading, impact, and noise. Furthermore, the inner and outer drive teeth can achieve complete meshing and disengagement through axial relative movement. When the sliding component moves to the left axial direction to its limit position, the drive teeth are fully meshed and power transmission is connected; when the sliding component moves to the right axial direction to its limit position, the drive teeth are completely disengaged and power transmission is interrupted.

[0009] In a preferred embodiment, the sliding assembly has two sets of symmetrically distributed axial blind holes inside. The axial blind holes are symmetrically arranged along the center line of the tooth groove of the inner sliding tooth. The axis of the axial blind holes is parallel to the rotation axis of the clutch to ensure that the spring force is transmitted axially and to avoid generating additional bending moment that could cause the push rod to jam. The mounting hole provides installation space for the spring plug, the spring, and the push rod. The depth of the mounting hole determines the maximum compression of the spring, which in turn determines the maximum rotation angle β of the outer sliding tooth. Therefore, in some other specific embodiments, the depth of the mounting hole needs to match the free length and pre-compression of the spring.

[0010] In a preferred embodiment, to facilitate adjustment of the spring's pre-compression and thus the pre-installation force, a spring plug, a spring, and a push rod are sequentially installed in the axial blind hole from the outside to the inside. The spring plug is fixed to the outer end of the mounting hole by its external thread engaging with the internal thread of the axial mounting hole. One end of the spring abuts against the inner end face of the spring plug, and the other end of the spring abuts against the rear end plane of the push rod. When the outer sliding tooth rotates, the push rod moves axially within the mounting hole, compressing the spring. The spring's reaction force acts on the outer sliding tooth through the push rod, providing it with a reset force.

[0011] In a preferred embodiment, the front end of the push rod is hemispherical, and the axis of the push rod is nearly perpendicular to the tooth surface of the outer sliding tooth. The hemispherical front end of the push rod contacts the working tooth surfaces on both sides of the outer sliding tooth, and the hemispherical end can form point contact with the tooth surface of the outer sliding tooth, ensuring the stability of the contact position even if the outer sliding tooth rotates. When the outer sliding tooth rotates relative to the inner sliding tooth, the hemispherical end of the push rod will roll on the tooth surface. The linkage is that the contact mode of the hemispherical end can adapt to the change of tooth surface angle when the outer sliding tooth rotates, ensuring that the push rod maintains good contact with the tooth surface throughout the rotation process, avoiding the generation of lateral force that could cause the push rod to jam.

[0012] In a preferred embodiment, the springs exert equal and opposite normal forces on the two sides of the outer sliding tooth via the push rod. This force balance ensures that the outer sliding tooth remains in the middle position of the inner sliding tooth when no external force is applied, guaranteeing equal angular space when the sliding assembly rotates in both directions. When the guide cone drives the sliding assembly to rotate in any direction, the outer sliding tooth has sufficient rotation space. The linkage is such that if the spring forces on both sides are unequal, the outer sliding tooth will deviate to one side, reducing the rotation space on that side. When the tooth needs to rotate to that side, insufficient space may cause the tooth alignment to fail.

[0013] In a preferred embodiment, the axial overlap length of the inner sliding tooth and the outer sliding tooth is greater than the axial overlap length of the outer drive tooth and the inner drive tooth. Since the axial overlap length of the drive tooth is shorter and the axial overlap length of the sliding tooth is longer, the intermittent shaving treatment of the sliding tooth will not reduce the overall torque transmission capacity of the clutch. This solves the problem of reduced torque transmission capacity caused by intermittent shaving of the drive tooth in the traditional structure. The overall torque transmission capacity of the clutch is determined by the meshing length of the outer drive tooth and the inner drive tooth, and the axial overlap length ensures that even if the sliding tooth is intermittently shaving, the number of remaining meshing teeth can still meet the torque transmission requirements.

[0014] In a preferred embodiment, the following configuration is further included: when the clutch is engaged, the outer drive tooth and the inner drive tooth are axially aligned and meshed, and the torque is transmitted from the input component to the output component sequentially through the outer sliding tooth, the inner sliding tooth, the sliding component, the outer drive tooth, and the inner drive tooth; when the clutch is disengaged, the outer drive tooth and the inner drive tooth are completely axially separated, and the spring pushes the tooth surface of the outer sliding tooth through the push rod, rotating the outer sliding tooth relative to the inner sliding tooth and automatically returning it to the centered position, in preparation for the next engagement of the teeth.

[0015] The beneficial effects of this invention are as follows: by setting mutually cooperating guide cone surface structures at the ends of the inner and outer drive teeth, the axial thrust during clutch engagement can be converted into circumferential rotational torque, driving the sliding component to automatically rotate and complete the tooth alignment. Guide failure only occurs under extreme apex interference conditions. The interval shaving structure is transferred from the drive teeth to the sliding teeth. Utilizing the structural characteristic that the axial overlap length of the sliding teeth is greater than that of the drive teeth, the number of meshing teeth of the remaining sliding teeth after interval shaving can still meet the torque transmission requirements. At the same time, the drive teeth maintain an intact structure, giving full play to their torque transmission capacity. Furthermore, through the spring-push rod mechanism symmetrically arranged along the center line of the tooth groove, the sliding teeth can be automatically pushed back to the central position after the clutch disengages, reserving uniform clockwise and counterclockwise angular rotation space for the next engagement and tooth alignment. Attached Figure Description

[0016] Figure 1 This is a cross-sectional view of the current controllable gear clutch structure; Figure 2 This is a cross-sectional view of the drive teeth of a current controllable gear clutch. Figure 3 This is a schematic diagram illustrating how current controllable gear clutches improve the success rate of gear engagement by thinning the drive teeth. Figure 4 This is a schematic diagram illustrating how current controllable gear clutches improve the success rate of gear engagement by thinning the drive teeth and shaving the teeth at intervals. Figure 5 This is a cross-sectional view of the controllable gear clutch structure of the present invention; Figure 6 This is a cross-sectional view of the controllable toothed clutch drive tooth structure of the present invention. Figure 7 This is a cross-sectional view of the sliding tooth structure of the controllable toothed clutch of the present invention; Figure 8 This is a schematic diagram of the engagement process of the controllable toothed clutch of the present invention; Figure 9 This is a schematic diagram of the guiding process of the end cone structure during tooth preparation according to the present invention; Figure 10 This is a schematic diagram illustrating another guiding process of the end cone structure during tooth alignment in this invention; Figure 11 This is a schematic diagram of the controllable gear clutch of the present invention in the fully engaged state. Figure 12 This is a schematic diagram of the sliding component of the present invention rotating during the guide process of the tapered surface at the end of the drive tooth; Figure 13 This is another rotational schematic diagram of the controllable toothed clutch sliding assembly of the present invention during the guide process of the cone surface at the end of the drive tooth; Figure 14 This is a schematic diagram of the sliding tooth compensation sliding assembly rotation of the present invention; Figure 15 This is another schematic diagram of the sliding tooth compensation sliding assembly rotation of the present invention; Figure 16 This is a schematic diagram illustrating the calculation of the successful tooth alignment probability of the controllable toothed clutch of the present invention.

[0017] In the diagram: 100, output component; 200, sliding component; 300, input component; 110, inner drive tooth; 111, inner drive tooth end cone surface; 210, outer drive tooth; 211, outer drive tooth end cone surface; 220, inner sliding tooth; 310, outer sliding tooth; 221, spring plug; 222, spring; 223, push rod. Detailed Implementation

[0018] The present invention will now be further described with reference to the accompanying drawings.

[0019] This embodiment provides a controllable gear clutch with a high success rate in gear engagement, including an output component 100, a sliding component 200, and an input component 300; like Figure 1 As shown, a known controllable gear clutch consists of an output assembly 100, a sliding assembly 200, and an input assembly 300. The sliding assembly 200 and the input assembly 300 are connected by sliding teeth. The sliding assembly 200 has an outer drive tooth 210, and the output assembly 100 has an inner drive tooth 110. According to the working principle of the controllable gear clutch, the sliding assembly 200 moves axially to the left under the action of a hydraulic or manual shift fork. When the tooth groove of the outer drive tooth 210 is exactly angularly aligned with the tooth profile of the inner drive tooth 110, the sliding assembly 200 can move to its leftmost limit position, causing the outer drive tooth 210 and the inner drive tooth 110 to axially coincide, thus completing the engagement action of the controllable gear clutch. However, the tooth groove of the outer drive tooth 210 and the tooth profile of the inner drive tooth 110 are exactly angularly aligned, achieving... Figure 2 The probability of the state shown is very small.

[0020] To improve the success rate of gear engagement in a controllable gear clutch, a common method is to thin the teeth and increase the backlash between the outer drive tooth 210 and the inner drive tooth 110. Figure 3 As shown, taking the external drive tooth 210 and internal drive tooth 110 with a tooth count Z=20 and a module m=5 as an example, the success rate of tooth alignment is calculated as follows: Tooth pitch L=π×m=15.7mm, assuming the total tooth clearance H=2mm, the success rate of tooth alignment is 2 / 15.7≈12.7%. To further improve the success rate of tooth alignment, the external drive tooth 210 and internal drive tooth 110 can be subjected to intermittent tooth shaving, such as... Figure 4 As shown, taking the external drive tooth 210, internal drive tooth 110 with 20 teeth Z and a module m=5 as an example, the success rate of tooth alignment is calculated as follows: After intermittent tooth shaving, the tooth pitch L=2×π×m=31.4mm, and the gap formed by tooth thickness reduction plus the total gap formed by tooth shaving is H=2+π×m=17.7mm. The success rate of tooth alignment is 17.7 / 31.4≈56.4%. It can be seen that even with the method of tooth thickness reduction combined with intermittent tooth shaving, the success rate of tooth alignment is less than 60%. After tooth alignment failure, the sliding component 200 needs to be operated to return to the disengaged position, and then the rotors at both ends of the clutch need to be rotated slightly to re-align the teeth. This process is repeated until tooth alignment is successful. The low success rate of tooth alignment means that the engagement operation of the controllable tooth clutch needs to be repeated, which reduces the convenience and speed of this type of clutch. Furthermore, for drive teeth with the same pitch circle diameter, the torque transmission capacity will be reduced by 50% after intermittent tooth shaving, wasting space and materials and seriously reducing the power density of the controllable tooth clutch.

[0021] Therefore, this application provides: The inner circumferential surface of the output component 100 is provided with an inner drive tooth 110, and the end of the inner drive tooth 110 facing the sliding component 200 is provided with an inner drive tooth end cone surface 111. The outer circumferential surface of the sliding component 200 is provided with an external drive tooth 210, the inner circumferential surface of the sliding component 200 is provided with an internal sliding tooth 220, the sliding component 200 is equipped with a spring plug 221, a spring 222 and a push rod 223, and the end of the external drive tooth 210 facing the output component 100 is provided with an external drive tooth end cone surface 211. An outer sliding tooth 310 is provided on the outer circumferential surface of the input component 300 facing the sliding component 200; The sliding component 200 and the input component 300 are engaged by the inner sliding tooth 220 and the outer sliding tooth 310. Both the inner sliding tooth 220 and the outer sliding tooth 310 have an intermittent shaving structure, and a tooth flank clearance of one tooth pitch is reserved between the inner sliding tooth 220 and the outer sliding tooth 310.

[0022] like Figure 5 As shown, the sliding component 200 is located between the output component 100 and the input component 300, ensuring that the rotation centers of all components are aligned during power transmission and avoiding additional vibrations and loads. Please refer to the attached diagram. Figure 5 , 6 When the sliding assembly 200 moves axially, the two guide cone surfaces first come into contact, converting the axial thrust into rotational torque, driving the sliding assembly 200 to rotate and engage the teeth.

[0023] Please refer to the appendix. Figure 7 Both the inner sliding tooth 220 and the outer sliding tooth 310 are spaced-out shaving structures, with a tooth flank clearance of one tooth pitch between them. This provides the necessary space for the angular rotation of the sliding component 200 relative to the input component 300, avoiding the problem of guide cone surface failure caused by sliding tooth locking in traditional structures.

[0024] Spring plug 221, spring 222 and push rod 223 are symmetrically distributed along the center line of the tooth groove of inner sliding tooth 220. Spring 222 presses against the two sides of tooth surface of outer sliding tooth 310 through push rod 223. Spring 222 keeps outer sliding tooth 310 in the center position relative to inner sliding tooth 220 when clutch is disengaged. The outer sliding tooth 310 rotates from the central position to both sides, and the limit angle of the outer sliding tooth 310 is β. The rotation angle between the position where the tooth profile center line of the outer driving tooth 210 coincides with the position where the tooth profile center line of the outer driving tooth 210 coincides with the position where the tooth groove center line of the inner driving tooth 110 coincides with the position where the tooth profile center line of the outer driving tooth 210 coincides with the position where the tooth groove center line of the inner driving tooth 110 coincides with the position where the tooth groove center line of the inner driving tooth 110 coincides with the position where the tooth groove center line of the outer driving tooth 2 ...

[0025] The spring plug 221, spring 222, and push rod 223 mentioned above are arranged symmetrically along the center line of the tooth groove of the inner sliding tooth 220, as shown in the attached figure. Figure 7 As shown, this is to ensure that the spring forces on both sides are equal in magnitude and opposite in direction, so that the outer sliding tooth 310 always remains in the center position when disengaged.

[0026] Figure 7 In the middle, the spring 222 presses against the two sides of the outer sliding tooth 310 through the push rod 223. Under the elastic force of the spring 222 with the same pre-installed force on both sides, the outer sliding tooth 310 is in the middle position relative to the inner sliding tooth 220 when the clutch is disengaged. When the outer sliding tooth 310 is rotated by external force, it will compress the spring 222 on one side. The reaction force of the spring 222 will provide the reset power for the outer sliding tooth 310.

[0027] Furthermore, please refer to the appendix. Figure 12 , 13 The position where the center line of the outer drive tooth 210 coincides with the center line of the inner drive tooth 110, and the rotation angle relative to the position where the center line of the outer drive tooth 210 coincides with the center line of the inner drive tooth 110 groove is α. For example... Figure 14 , Figure 15 As shown, the limit angle for the external sliding tooth 310 to rotate from the center position to both sides is β, and β > α, thereby ensuring that the conical surface can play a guiding role throughout the tooth setting process and will not cause tooth setting failure due to premature locking of the sliding tooth.

[0028] like Figure 6 As shown, the inner drive tooth end cone 111 is a conical structure that protrudes outward along the axial direction from the end face of the inner drive tooth 110. The tip of the inner drive tooth end cone 111 points in the direction of the sliding component 200. The outer drive tooth end cone 211 is a conical structure that protrudes outward along the axial direction from the end face of the outer drive tooth 210. The tip of the outer drive tooth end cone 211 points in the direction of the output component 100. The axial thrust is decomposed into an axial component and a circumferential component, wherein the circumferential component drives the sliding component 200 to rotate.

[0029] Furthermore, such as Figure 9 , Figure 10 As shown, when the outer drive tooth 210 contacts the inner drive tooth 110, the cone surface 111 at the end of the inner drive tooth interacts with the cone surface 211 at the end of the outer drive tooth, generating a component force that rotates the sliding assembly 200, guiding the outer drive tooth 210 into the tooth groove of the inner drive tooth 110, so that the axial movement and rotation of the sliding assembly 200 are carried out simultaneously. The cone angle of the guide cone surface determines the ratio of the axial force to the rotational torque.

[0030] like Figure 11As shown, the number of teeth, module, and pressure angle of the inner drive tooth 110 and the outer drive tooth 210 are matched. The inner drive tooth 110 and the outer drive tooth 210 are used for complete meshing and disengagement of the tooth profile through axial relative movement, ensuring good tooth surface contact and uniform load distribution when the drive teeth are meshing, avoiding off-center loading, impact, and noise. Furthermore, the inner drive tooth 110 and the outer drive tooth 210 can achieve complete meshing and disengagement of the tooth profile through axial relative movement. When the sliding component 200 moves to the left axial direction to the limit position, the drive teeth are fully meshed and the power transmission is connected; when the sliding component 200 moves to the right axial direction to the limit position, the drive teeth are completely disengaged and the power transmission is interrupted.

[0031] like Figure 7 As shown, the sliding assembly 200 has two sets of symmetrically distributed axial blind holes inside. The axial blind holes are symmetrically arranged along the center line of the tooth groove of the inner sliding tooth 220. The axis of the axial blind holes is parallel to the rotation axis of the clutch to ensure that the spring force is transmitted axially and to avoid the generation of additional bending moment that causes the push rod 223 to jam. The mounting hole provides installation space for the spring plug 221, the spring 222 and the push rod 223. The depth of the mounting hole determines the maximum compression of the spring 222, and thus determines the maximum rotation angle β of the outer sliding tooth 310. Therefore, in some other specific embodiments, the depth of the mounting hole needs to match the free length and pre-compression of the spring 222.

[0032] To facilitate adjustment of the pre-compression of spring 222 and thus the pre-installation force of spring 222, spring plug 221, spring 222, and push rod 223 are installed sequentially from the outside to the inside of the axial blind hole. Spring plug 221 is fixed to the outer end of the mounting hole by external thread engaging with the internal thread of the axial mounting hole. One end of spring 222 abuts against the inner end face of spring plug 221, and the other end of spring 222 abuts against the rear end plane of push rod 223. When the outer sliding tooth 310 rotates, push rod 223 moves axially within the mounting hole, compressing spring 222. The reaction force of spring 222 acts on the outer sliding tooth 310 through push rod 223, providing it with reset power.

[0033] The front end of the push rod 223 is a hemispherical end. The axis of the push rod 223 is nearly perpendicular to the tooth surface of the outer sliding tooth 310. The hemispherical front end of the push rod 223 contacts the working tooth surfaces on both sides of the outer sliding tooth 310. The hemispherical end can form point contact with the tooth surface of the outer sliding tooth 310. Even if the outer sliding tooth 310 rotates, the stability of the contact position can be guaranteed.

[0034] Furthermore, such as Figure 14 , Figure 15As shown, when the outer sliding tooth 310 rotates relative to the inner sliding tooth 220, the hemispherical end of the push rod 223 will roll on the tooth surface. The linkage relationship is that the contact mode of the hemispherical end can adapt to the change of tooth surface angle when the outer sliding tooth 310 rotates, ensuring that the push rod 223 can maintain good contact with the tooth surface throughout the entire rotation process, avoiding the generation of lateral force that would cause the push rod 223 to jam.

[0035] The spring 222, through the push rod 223, exerts equal and opposite normal forces on both sides of the outer sliding tooth 310. This force balance ensures that the outer sliding tooth 310 remains in the middle position of the inner sliding tooth 220 when no external force is applied, guaranteeing that the sliding assembly 200 has equal angular space when rotating in both directions. Figure 9 , Figure 10 As shown, when the guide cone surface drives the sliding assembly 200 to rotate in any direction, the outer sliding tooth 310 has sufficient rotation space. The linkage relationship is that if the spring forces on both sides are not equal, the outer sliding tooth 310 will be biased to one side, resulting in a reduction in the rotation space on one side. When the tooth needs to rotate to that side, the tooth alignment may fail due to insufficient space.

[0036] Please refer to the appendix. Figure 11 The axial overlap length of the inner sliding tooth 220 and the outer sliding tooth 310 is greater than the axial overlap length of the outer drive tooth 210 and the inner drive tooth 110. Since the axial overlap length of the drive tooth is shorter and the axial overlap length of the sliding tooth is longer, the intermittent shaving of the sliding tooth will not reduce the overall torque transmission capacity of the clutch. This solves the problem of reduced torque transmission capacity caused by intermittent shaving of the drive tooth in the traditional structure. The overall torque transmission capacity of the clutch is determined by the meshing length of the outer drive tooth 210 and the inner drive tooth 110, and the axial overlap length ensures that even if the sliding tooth is intermittently shaving, the remaining number of meshing teeth can still meet the torque transmission requirements.

[0037] The following settings are also included: When the clutch is engaged, the outer drive tooth 210 and the inner drive tooth 110 are axially overlapped and meshed, and the torque is transmitted from the input component 300 to the output component 100 in sequence through the outer sliding tooth 310, the inner sliding tooth 220, the sliding component 200, the outer drive tooth 210, and the inner drive tooth 110. When the clutch is disengaged, the outer drive tooth 210 and the inner drive tooth 110 are completely axially separated. The spring 222 pushes the tooth surface of the outer sliding tooth 310 through the push rod 223, causing the outer sliding tooth 310 to rotate relative to the inner sliding tooth 220 and automatically return to the center position, preparing for the next engagement of the teeth.

[0038] For ease of understanding, such as Figure 8As shown, when the clutch engages and aligns the teeth, the sliding assembly 200 moves to the left axial direction under the push of the shift fork. The inner drive tooth end cone surface 111 contacts and interacts with the outer drive tooth end cone surface 211, causing the sliding assembly 200 to rotate relative to the input assembly 300. Finally, the outer drive tooth 210 slides into the tooth groove of the inner drive tooth 110, realizing automatic tooth alignment and improving the success rate of tooth alignment.

[0039] like Figure 11 As shown, when the clutch is engaged, the outer drive tooth 210 and the inner drive tooth 110 are axially fully overlapped and meshed. Torque is transmitted from the input assembly 300 to the output assembly 100 sequentially through the outer sliding tooth 310, the inner sliding tooth 220, the sliding assembly 200, the outer drive tooth 210, and the inner drive tooth 110. The function of this power transmission path is to ensure that power can be smoothly and efficiently transmitted from the input side to the output side.

[0040] like Figure 7 As shown, when the clutch is disengaged, the outer drive tooth 210 and the inner drive tooth 110 are completely axially separated. The spring 222 pushes the tooth surface of the outer sliding tooth 310 through the push rod 223, causing the outer sliding tooth 310 to rotate relative to the inner sliding tooth 220 and automatically return to the center position, preparing for the next engagement. This automatic reset function ensures that the clutch automatically returns to its initial state after each disengagement without manual intervention, improving the ease of use of the clutch.

[0041] The complete working cycle of this application is divided into four stages: initial disengagement state, engagement and tooth pairing process, power transmission process, and disengagement and reset process, specifically: Initial disengagement state - such as Figure 5 , Figure 7 As shown, at this time, the sliding component 200 is located at the right limit position, the outer drive tooth 210 and the inner drive tooth 110 are completely axially separated, and the power transmission path is interrupted.

[0042] like Figure 7 As shown, the two sets of symmetrically installed springs 222 have equal pre-installation forces. Through the push rod 223, the normal forces acting on the working tooth surfaces on both sides of the outer sliding tooth 310 are equal in magnitude and opposite in direction, causing the outer sliding tooth 310 to automatically maintain its centered position relative to the inner sliding tooth 220. At this time, the tooth flank clearance of one tooth pitch between the outer sliding tooth 310 and the inner sliding tooth 220 is evenly distributed on both sides, reserving equal angular space for the subsequent rotation of the sliding assembly 200 in both clockwise and counterclockwise directions.

[0043] Engagement process – such as Figure 8As shown, when the clutch needs to be engaged, the hydraulic or manual shift fork pushes the sliding assembly 200 to move axially to the left along the rotation axis. Before the outer drive tooth 210 contacts the inner drive tooth 110, the outer sliding tooth 310 always maintains a centered position relative to the inner sliding tooth 220 under the balancing action of the springs 222 on both sides.

[0044] like Figure 9 , Figure 10 As shown, when the sliding assembly 200 continues to move to the left, the outer drive tooth end cone surface 211 contacts the inner drive tooth end cone surface 111. At this time, regardless of the initial angular position of the two drive teeth, except for the extreme case of interference at the apex radius, the two cone-shaped contact surfaces will decompose the axial thrust into an axial component and a circumferential component, wherein the circumferential component drives the sliding assembly 200 to rotate relative to the input assembly 300 and the output assembly 100.

[0045] like Figure 14 , Figure 15 As shown, while the sliding assembly 200 rotates, the inner sliding tooth 220 rotates with the sliding assembly 200, while the outer sliding tooth 310 remains relatively stationary with the input assembly 300. Therefore, the inner sliding tooth 220 will rotate relative to the outer sliding tooth 310, compressing the spring 222 on one side, causing the push rod 223 on that side to move axially into the mounting hole.

[0046] like Figure 12 , Figure 13 As shown, since the maximum rotation angle β of the outer sliding tooth 310 is greater than the maximum rotation angle α required for the drive tooth to be aligned, the inner sliding tooth 220 and the outer sliding tooth 310 will not interfere with each other during the entire tooth alignment process. The guide cone surface can continuously play a guiding role, guiding the tooth shape of the outer drive tooth 210 to accurately slide into the tooth groove of the inner drive tooth 110.

[0047] like Figure 16 As shown, interference will only occur and cause guide failure and tooth alignment failure when the apex radius of the outer drive tooth end cone 211 and the inner drive tooth end cone 111 are exactly aligned. Since the apex radius is usually only 0.3-1.0mm, the probability of this situation occurring is extremely low, and the tooth alignment success rate of the present invention can reach more than 93.6%.

[0048] Power transmission process - such as Figure 11 As shown, when the outer drive tooth 210 is fully slid into the tooth groove of the inner drive tooth 110, the sliding assembly 200 reaches the left limit position, the clutch completes the engagement action, and enters the power transmission state.

[0049] At this time, the torque input by the input component 300 is transmitted sequentially through the following path: input component 300, outer sliding gear 310, inner sliding gear 220, sliding component 200, outer drive gear 210, inner drive gear 110, output component 100, and finally the output component 100 outputs the power.

[0050] like Figure 11 As shown, since the axial overlap length between the outer drive tooth 210 and the inner drive tooth 110 is short, while the axial overlap length between the inner sliding tooth 220 and the outer sliding tooth 310 is long, the overall torque transmission capacity of the clutch is determined by the weaker drive tooth. Intermittent shaving of the sliding teeth only reduces the number of meshing teeth, but the remaining number of meshing teeth is still sufficient to meet the torque transmission requirements. Therefore, it does not reduce the overall torque transmission capacity of the clutch, solving the problem of reduced torque transmission capacity caused by intermittent shaving of drive teeth in traditional structures.

[0051] Disengagement and Reset Process – When it is necessary to disengage the clutch, the hydraulic or manual shift fork pulls the sliding assembly 200 to move axially to the right along the rotation axis. After the outer drive tooth 210 and the inner drive tooth 110 are completely axially separated, the force between the guide cone surfaces disappears.

[0052] like Figure 7 As shown, the spring 222, which was compressed during the engagement of the teeth, releases its elastic potential energy and pushes the tooth surface of the outer sliding tooth 310 through the push rod 223, causing the inner sliding tooth 220 to rotate in the opposite direction relative to the outer sliding tooth 310 until the outer sliding tooth 310 returns to the center position relative to the inner sliding tooth 220.

[0053] Finally, as Figure 16 As shown, the success rate of tooth alignment using the method of the present invention is calculated. Taking the external drive tooth 210, internal drive tooth 110 with a tooth count Z=20 and a module m=5 as an example, the single tooth pitch L=π×m=15.7mm. Assuming that the apex angles of the conical surfaces 211 and 111 at the ends of the external drive tooth and internal drive tooth are rounded by R0.5mm, then only when interference occurs at the rounded corners at the apex angles will the guide cones fail to provide guidance, and tooth alignment will not be possible. The interference width is 2×0.5=1mm, and the success rate of tooth alignment is 1-1 / 15.7≈93.6%, which shows that the success rate of tooth alignment is significantly improved.

[0054] At this point, the clutch has completed a full working cycle and returned to its initial disengaged state, ready for the next engagement. The entire disengagement and reset process is automatic and requires no manual intervention, significantly improving the convenience and speed of clutch operation.

Claims

1. A controllable gear clutch with high gear-fitting success rate, characterized in that, It includes an output component (100), a sliding component (200), and an input component (300); The output component (100) has an inner drive tooth (110) on its inner circumferential surface, and the end of the inner drive tooth (110) facing the sliding component (200) has an inner drive tooth end cone surface (111). The outer circumferential surface of the sliding component (200) is provided with an external drive tooth (210), the inner circumferential surface of the sliding component (200) is provided with an internal sliding tooth (220), the sliding component (200) is provided with a spring plug (221), a spring (222) and a push rod (223) installed inside the sliding component (200), and the end of the external drive tooth (210) facing the output component (100) is provided with an external drive tooth end cone surface (211). The input component (300) has an outer sliding tooth (310) on its outer circumferential surface facing the sliding component (200). The sliding component (200) and the input component (300) are engaged by an inner sliding tooth (220) and an outer sliding tooth (310). Both the inner sliding tooth (220) and the outer sliding tooth (310) are spaced-out shaving structures. A tooth flank gap of one tooth pitch is reserved between the inner sliding tooth (220) and the outer sliding tooth (310).

2. The controllable gear clutch with high gear-matching success rate according to claim 1, characterized in that, The spring plug (221), spring (222) and push rod (223) are symmetrically distributed along the center line of the tooth groove of the inner sliding tooth (220). The spring (222) presses against the two sides of the tooth surface of the outer sliding tooth (310) through the push rod (223). The spring (222) keeps the outer sliding tooth (310) in the center position relative to the inner sliding tooth (220) when the clutch is disengaged. The outer sliding tooth (310) rotates from the central position to both sides, and the limit angle of the outer sliding tooth (310) is β. The rotation angle of the position where the tooth profile center line of the outer driving tooth (210) coincides with the tooth profile center line of the inner driving tooth (110) relative to the position where the tooth profile center line of the outer driving tooth (210) coincides with the tooth groove center line of the inner driving tooth (110) is α, where β > α.

3. A controllable gear clutch with high gear-matching success rate according to claim 1, characterized in that, The inner drive tooth end cone surface (111) is a cone-shaped structure that protrudes outward along the axial direction from the end face of the inner drive tooth (110). The tip of the inner drive tooth end cone surface (111) points in the direction of the sliding component (200). The outer drive tooth end cone surface (211) is a cone-shaped structure that protrudes outward along the axial direction from the end face of the outer drive tooth (210). The tip of the outer drive tooth end cone surface (211) points in the direction of the output component (100).

4. A controllable gear clutch with high gear-matching success rate according to claim 1, characterized in that, The number of teeth, module and pressure angle of the inner drive tooth (110) and the outer drive tooth (210) are matched. The inner drive tooth (110) and the outer drive tooth (210) are used for complete meshing and separation of the tooth profiles by axial relative movement.

5. A controllable gear clutch with high gear-fitting success rate according to claim 2, characterized in that, The sliding assembly (200) has two sets of symmetrically distributed axial blind holes inside. The axial blind holes are arranged symmetrically along the center line of the tooth groove of the inner sliding tooth (220), and the axis of the axial blind holes is parallel to the rotation axis of the clutch.

6. A controllable gear clutch with high gear-matching success rate according to claim 5, characterized in that, The axial blind hole is installed with a spring plug (221), a spring (222) and a push rod (223) in sequence from the outside to the inside. The spring plug (221) is fixed to the outer end of the mounting hole by the external thread engaging with the internal thread of the axial mounting hole. One end of the spring (222) abuts against the inner end face of the spring plug (221), and the other end of the spring (222) abuts against the rear end plane of the push rod (223).

7. A controllable gear clutch with high gear-matching success rate according to claim 1, characterized in that, The front end of the push rod (223) is a hemispherical end. The axis of the push rod (223) is nearly perpendicular to the tooth surface of the outer sliding tooth (310). The hemispherical front end of the push rod (223) contacts the working tooth surfaces on both sides of the outer sliding tooth (310).

8. A controllable gear clutch with high gear-matching success rate according to claim 1, characterized in that, The spring (222) acts through the push rod (223) on the tooth surfaces on both sides of the outer sliding tooth (310) with equal magnitude and opposite direction of normal force.

9. A controllable gear clutch with high gear-matching success rate according to claim 1, characterized in that, The axial overlap length of the inner sliding tooth (220) and the outer sliding tooth (310) is greater than the axial overlap length of the outer driving tooth (210) and the inner driving tooth (110).

10. A controllable gear clutch with high gear-matching success rate according to claim 1, characterized in that, The following settings are also included: When the clutch is engaged, the outer drive tooth (210) and the inner drive tooth (110) are axially aligned and meshed, and the torque is transmitted from the input component (300) to the output component (100) in sequence through the outer sliding tooth (310), the inner sliding tooth (220), the sliding component (200), the outer drive tooth (210), and the inner drive tooth (110). When the clutch is disengaged, the outer drive tooth (210) and the inner drive tooth (110) are completely axially separated. The spring (222) pushes the tooth surface of the outer sliding tooth (310) through the push rod (223), causing the outer sliding tooth (310) to rotate relative to the inner sliding tooth (220) and automatically return to the center position.

Images