Clutch mechanism with radial compensation

Abstract

The utility model relates to a clutch mechanism with radial compensation function, and relates to the technical field of clutches. The utility model solves the problem that the existing axial arrangement clutch is not centered at both ends during use, the axis is deflected during operation, and the bearing is easily abnormally stressed, worn or damaged. The clutch gear ring of the utility model is sleeved outside the starting shaft, the clutch gear ring is slidably connected with the starting shaft through a straight toothed spline pair, the end of the clutch gear ring and the end of the driving gear ring are respectively and uniformly provided with a plurality of double helix end face teeth in the circumferential direction, the double helix end face teeth provided on the clutch gear ring are matched with the double helix end face teeth provided on the driving gear ring, the engagement and separation of the double helix end face teeth are realized through the axial movement of the clutch gear ring along the straight toothed spline pair, and the mechanism is put into operation and separated. The utility model can be controlled to be put into operation and automatically separated, and the structural characteristics of the double helix end face teeth ensure that the mechanism can still operate under the condition of radial misalignment.

Description

Technical Field

[0001] This invention relates to the field of clutch technology, and more specifically to a clutch mechanism with radial compensation function. Background Technology

[0002] When using an axially arranged clutch, the operational risks caused by misalignment at both ends must be considered. Taking a gearbox turning gear as an example, the turning gear clutch adopts an axial arrangement, with its input end supported by a rolling bearing and its output end supported by a sliding bearing. The radial oil clearance of the two types of bearings is significantly different, which indirectly leads to misalignment. During operation, the shaft misalignment can easily cause abnormal stress on the bearings, resulting in wear or damage. Summary of the Invention

[0003] The purpose of this invention is to solve the problem that existing axially arranged clutches have misalignment at both ends during use, and the shaft is misaligned during operation, which easily causes abnormal stress on the bearings, resulting in wear or damage. Therefore, this invention provides a clutch mechanism with radial compensation function.

[0004] The technical solution of this invention is:

[0005] A clutch mechanism with radial compensation function includes a starter shaft 1, a clutch gear ring 2, and a drive gear ring 3. The starter shaft 1, clutch gear ring 2, and drive gear ring 3 are coaxially arranged from front to back. The starter shaft 1 is the input end, and the drive gear ring 3 is the output end. The clutch gear ring 2 is sleeved on the outside of the starter shaft 1 and is slidably connected to the starter shaft 1 through a spur spline pair 6. The ends of the clutch gear ring 2 and the ends of the drive gear ring 3 are each uniformly provided with a plurality of double helical end face teeth 7 along the circumferential direction. The double helical end face teeth 7 on the clutch gear ring 2 and the double helical end face teeth 7 on the drive gear ring 3 are matched with each other. By moving the clutch gear ring 2 along the axial direction of the spur spline pair 6, the engagement and disengagement of the double helical end face teeth 7 are realized, thereby completing the engagement and disengagement of the mechanism.

[0006] Furthermore, it also includes a baffle 4 and an auxiliary spring 5. The clutch gear ring 2 has an annular stepped groove along the axial direction on the end face near the drive gear ring 3. The auxiliary spring 5 is coaxially arranged in the first annular stepped groove. The end of the auxiliary spring 5 is provided with a baffle 4. The baffle 4 is a circular plate structure. The baffle 4 is fixedly connected to the end of the starter shaft 1 through a connector. The outer side of the baffle 4 is clearance-fitted with the inner side of the first annular stepped groove of the clutch gear ring 2. One end of the auxiliary spring 5 rests on the end face of the baffle 4, and the other end of the auxiliary spring 5 rests on the bottom surface of the annular stepped groove of the clutch gear ring 2.

[0007] Furthermore, each double-helix end face tooth 7 includes a forward working tooth surface 71 and a reverse working tooth surface 72, wherein the helical direction of the forward working tooth surface 71 and the reverse working tooth surface 72 is consistent.

[0008] Furthermore, within the same radial section, the fitting line between the forward working tooth surface 71 and the reverse working tooth surface 72 is a straight line, which coincides with the rotation center of the mechanism.

[0009] Furthermore, an external spline is machined on the outer side of one end of the starter shaft 1 along the axial direction, and an internal spline is machined on the inner side of the clutch gear ring 2 along the axial direction. The internal spline and the external spline cooperate to form a straight tooth spline pair 6.

[0010] Furthermore, the other end of the starter shaft 1 is provided with a first flange, and the starter shaft 1 is connected to the external power input part through the first flange. The other end of the drive gear ring 3 is provided with a second flange, and the drive gear ring 3 is connected to the external power output part through the second flange.

[0011] Furthermore, the outer side of the starter shaft 1 away from the drive gear ring 3 is provided with a second annular stepped groove and a third annular stepped groove from left to right along the axial direction. The inner side of the clutch gear ring 2 away from the drive gear ring 3 is provided with a fourth annular stepped groove and a fifth annular stepped groove from left to right along the axial direction. The starter shaft 1 can slide with the clutch gear ring 2 through the second and fourth annular stepped grooves, and the starter shaft 1 can slide with the clutch gear ring 2 through the third and fifth annular stepped grooves. A circular countersunk hole is machined at the center of the end of the starter shaft 1 away from the drive gear ring 3 along the axial direction. The circular countersunk hole is the main hydraulic oil circuit. A hydraulic oil branch circuit is machined radially on the side of the third annular stepped groove of the starter shaft 1. The hydraulic oil branch circuit is connected to the main hydraulic oil circuit.

[0012] Furthermore, the length of the second annular stepped groove of the starter shaft 1 is less than the length of the fourth annular stepped groove of the clutch gear ring 2, and the side of the second annular stepped groove is in clearance fit with the side of the fourth annular stepped groove; the length of the third annular stepped groove of the starter shaft 1 is less than the length of the fifth annular stepped groove of the clutch gear ring 2, and the third annular stepped groove is in clearance fit with the fifth annular stepped groove.

[0013] Compared with the prior art, the present invention has the following advantages:

[0014] 1. The double-helix end face tooth 7 of the present invention includes a forward working tooth surface 71 and a reverse working tooth surface 72 with the same helical direction. Within the same radial section, the fitting line of the forward working tooth surface 71 and the reverse working tooth surface 72 is a straight line, which coincides with the rotation center of the mechanism. Based on this feature, even if there is a radial deviation at both ends of the mechanism, the forward working tooth surface 71 and the reverse working tooth surface 72 still fit along the fitted straight line, ensuring that the rotation centers of the clutch gear ring 2 and the drive gear ring 3 do not change, that is, the rotation centers of the input end and the output end do not change. This feature of the present invention ensures that the operation of the mechanism is not affected by the radial deviation between the input end and the output end, greatly expanding the applicable scenarios.

[0015] 2. In this invention, a baffle 4 and an auxiliary spring 5 are provided between the starter shaft 1 and the clutch gear ring 2. When the mechanism is engaged, the baffle 4 axially limits the clutch gear ring 2, ensuring the accurate engagement position of the double helix end face teeth 7. Additionally, the baffle 4 provides auxiliary support to ensure the stability of its axial movement. When the mechanism disengages, the auxiliary spring 5 releases the axial force generated by compression, assisting the clutch gear ring 2 to quickly disengage into position.

[0016] 3. The present invention can be controlled to engage and automatically disengage. The structural feature of the double helical end face teeth ensures that the mechanism can still operate under radial misalignment conditions, which greatly expands the applicable scenarios of the present invention. Attached Figure Description

[0017] Figure 1 This is a schematic diagram of the structure of a clutch mechanism with radial compensation function according to the present invention;

[0018] Figure 2 This is an isometric view of the drive gear ring 3 of the present invention;

[0019] Figure 3 This is an isometric view of the double-helix end face teeth in the activated state of the present invention;

[0020] Figure 4 This is a schematic diagram of the function of the double helix end face teeth in the engaged state of the present invention;

[0021] Figure 5 This is an isometric view of the action of the double-helix end face teeth in the disengaged state of the present invention;

[0022] Figure 6 This is a schematic diagram of the function of the double helix end face teeth in the disengaged state of the present invention;

[0023] Figure 7 This is a schematic diagram of the cross-sectional view of the double helix end face teeth of the present invention;

[0024] Figure 8 yes Figure 7 A-direction view.

[0025] In the diagram: 1-Starting shaft; 2-Clutch gear ring; 3-Drive gear ring; 4-Baffle; 5-Auxiliary spring; 6-Straight spline pair; 7-Double helical end face teeth; 71-Forward working tooth surface; 72-Reverse working tooth surface. Detailed Implementation

[0026] Embodiments of the present invention are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and should not be construed as limiting the present invention.

[0027] Specific implementation method one: Combining Figures 1 to 8 This embodiment describes a clutch mechanism with radial compensation function, comprising a starter shaft 1, a clutch gear ring 2, and a drive gear ring 3. The starter shaft 1, clutch gear ring 2, and drive gear ring 3 are coaxially arranged from front to back, with the starter shaft 1 as the input end and the drive gear ring 3 as the output end. The clutch gear ring 2 is sleeved outside the starter shaft 1 and is slidably connected to the starter shaft 1 via a spur spline pair 6. The ends of the clutch gear ring 2 and the drive gear ring 3 are each uniformly provided with a plurality of double helical end face teeth 7 along the circumferential direction. The double helical end face teeth 7 on the clutch gear ring 2 and the double helical end face teeth 7 on the drive gear ring 3 are matched with each other. By moving the clutch gear ring 2 along the axial direction of the spur spline pair 6, the engagement and disengagement of the double helical end face teeth 7 are realized, thereby completing the engagement and disengagement of the mechanism.

[0028] In this embodiment, the starter shaft 1 is the input end and includes the external spline of the straight spline pair 6; the clutch gear ring 2 includes the internal spline of the straight spline pair 6 and the double helical end face teeth 7; the drive gear ring 3 is the output end and includes the double helical end face teeth 7.

[0029] Specific Implementation Method Two: Combining Figure 1 This embodiment also includes a baffle 4 and an auxiliary spring 5. The clutch gear ring 2 has an annular stepped groove along the axial direction on the end face near the drive gear ring 3. The auxiliary spring 5 is coaxially arranged in the first annular stepped groove. The end of the auxiliary spring 5 is provided with a baffle 4. The baffle 4 is a circular plate structure. The baffle 4 is fixedly connected to the end of the starter shaft 1 through a connector. The outer side of the baffle 4 is clearance-fitted with the inner side of the first annular stepped groove of the clutch gear ring 2. One end of the auxiliary spring 5 abuts against the end face of the baffle 4, and the other end of the auxiliary spring 5 abuts against the bottom surface of the annular stepped groove of the clutch gear ring 2. With this configuration, the baffle 4 is connected to the starting shaft 1. Its functions are: first, when the mechanism is engaged, it axially limits the clutch gear ring 2 to ensure the accurate engagement position of the double helix end face teeth 7; second, it provides auxiliary support for the clutch gear ring 2 to ensure the stability of its axial movement. The auxiliary spring 5 is connected to the clutch gear ring 2, with one end pressing against the baffle 4. When the mechanism is engaged, the auxiliary spring 5 is compressed; when the mechanism is disengaged, the auxiliary spring 5 releases the axial force generated by the compression, assisting the clutch gear ring 2 to quickly disengage into position. Other components and connections are the same as in Specific Implementation Method 1.

[0030] Specific implementation method three: Combining Figures 2 to 6This embodiment describes a double-helix end face tooth 7 comprising a forward working tooth surface 71 and a reverse working tooth surface 72, wherein the helical directions of the forward working tooth surface 71 and the reverse working tooth surface 72 are consistent. With this configuration, the forward working tooth surface 71 engages after the mechanism is engaged, and the reverse working tooth surface 72 functions when the mechanism is disengaged. Specifically, based on the axial force generated by the interaction of the helical tooth surfaces, after the mechanism is engaged, the axial force causes the clutch gear ring 2 to move towards the drive gear ring 3, thus ensuring stable engagement. When the mechanism is disengaged, the axial force forces the clutch gear ring 2 to move towards the starter shaft 1, thus ensuring smooth disengagement. Other components and connections are the same as in specific embodiments one or two.

[0031] Specific implementation method four: Combination Figure 7 and Figure 8 In this embodiment, the fitting line between the forward working tooth surface 71 and the reverse working tooth surface 72 is a straight line within the same radial cross section, and this straight line coincides with the rotation center of the mechanism. With this configuration, based on the characteristics of the double-helix end face teeth, the operation of the mechanism is not affected by radial deviation. After dissecting the double-helix end face teeth 7, it can be seen that within the same radial cross section, the fitting line between the forward working tooth surface 71 and the reverse working tooth surface 72 is a straight line, and this straight line coincides with the rotation center of the mechanism. Based on this characteristic, even if there is radial deviation at both ends of the mechanism, the forward working tooth surface 71 and the reverse working tooth surface 72 still fit along the fitted straight line, ensuring that the rotation centers of the clutch gear ring 2 and the drive gear ring 3 do not change, that is, the rotation centers of the input end and the output end do not change. This feature of the present invention ensures that the operation of the mechanism is not affected by radial deviation between the input and output ends, greatly expanding the applicable scenarios. Other components and connections are the same as in specific embodiments one, two, or three.

[0032] Specific Implementation Method Five: Combining Figure 1 In this embodiment, the outer surface of one end of the starter shaft 1 is machined with an external spline along the axial direction, and the inner surface of the clutch gear ring 2 is machined with an internal spline along the axial direction. The internal spline and the external spline cooperate to form a spur spline pair 6. With this configuration, the clutch gear ring 2 is connected to the starter shaft 1 through the spur spline pair 6 and can move axially along the spur spline pair 6. Other components and connections are the same as in specific embodiments one, two, three, or four.

[0033] Specific Implementation Method Six: Combination Figure 1 and Figure 2In this embodiment, the other end of the starter shaft 1 is provided with a first flange, through which the starter shaft 1 is connected to the external power input part. The other end of the drive gear ring 3 is provided with a second flange, through which the drive gear ring 3 is connected to the external power output part. This configuration allows the mechanism to connect to the external input and output parts via flange connections, simplifying operation and improving versatility. Other components and connections are the same as in specific embodiments one, two, three, four, or five.

[0034] Specific implementation method seven: Combination Figure 1 In this embodiment, the outer side of the starting shaft 1 away from the drive gear ring 3 is provided with a second annular stepped groove and a third annular stepped groove from left to right along the axial direction. The inner side of the clutch gear ring 2 away from the drive gear ring 3 is provided with a fourth annular stepped groove and a fifth annular stepped groove from left to right along the axial direction. The starting shaft 1 can slide with the clutch gear ring 2 through the second and fourth annular stepped grooves, and the starting shaft 1 can slide with the clutch gear ring 2 through the third and fifth annular stepped grooves. A circular countersunk hole is machined at the center of the end of the starting shaft 1 away from the drive gear ring 3 along the axial direction. The circular countersunk hole is the main hydraulic oil passage. A hydraulic oil branch passage is machined radially on the side of the third annular stepped groove of the starting shaft 1. The hydraulic oil branch passage is connected to the main hydraulic oil passage. With this configuration, when hydraulic oil is injected into the cavity formed between the starter shaft 1 and the clutch gear ring 2 through the main hydraulic oil circuit and the branch hydraulic oil circuit, the clutch gear ring 2 moves towards the drive gear ring 3 under the push of the hydraulic oil. When hydraulic oil is withdrawn from the cavity formed between the starter shaft 1 and the clutch gear ring 2 through the main hydraulic oil circuit and the branch hydraulic oil circuit, the clutch gear ring 2 moves towards the starter shaft 1 under the action of the auxiliary spring 5. Other components and connections are the same as in specific embodiments one, two, three, four, five, or six.

[0035] Specific implementation method eight: Combination Figure 1 In this embodiment, the length of the second annular stepped groove of the starter shaft 1 is less than the length of the fourth annular stepped groove of the clutch gear ring 2, and the side of the second annular stepped groove is clearance-fitted with the side of the fourth annular stepped groove; the length of the third annular stepped groove of the starter shaft 1 is less than the length of the fifth annular stepped groove of the clutch gear ring 2, and the third annular stepped groove is clearance-fitted with the fifth annular stepped groove. With this configuration, the starter shaft 1 and the clutch gear ring 2 have a clearance fit with a tolerance grade of H7-h6, ensuring that hydraulic oil does not flow out of the cavity formed between the starter shaft 1 and the clutch gear ring 2. Other components and connections are the same as in specific embodiments one, two, three, four, five, six, or seven.

[0036] As can be seen from the above features, the present invention has the functions of controlled deployment and automatic disengagement, and the controlled deployment method can be manual operation, hydraulic boosting or other methods.

[0037] It should be noted that the size of the mechanism and the number of teeth on the end face can be optimized and adjusted according to the mechanism's ability to transmit torque. Nevertheless, any changes or substitutions that can be easily conceived by those skilled in the art within the scope of the technology disclosed in this invention should be included within the protection scope of this invention. Therefore, the protection scope of this invention is defined by the claims and their equivalents.

[0038] Working principle

[0039] Combination Figures 1 to 8 The working principle of a clutch mechanism with radial compensation function according to the present invention is as follows: The clutch gear ring 2 is connected to the starting shaft 1 through the straight spline pair 6 and can move axially along the straight spline pair 6. When it moves towards the driving gear ring 3, it connects with the driving gear ring 3 through the double helical end face teeth 7 to realize the engagement of the mechanism. Conversely, when it moves towards the starting shaft 1, it separates from the double helical end face teeth 7 of the driving gear ring 3 to realize the disengagement of the mechanism.

[0040] The above embodiments are only used to illustrate the technical solutions of the present invention, and are not intended to limit it. Although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features. Such modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. A clutch mechanism with radial compensation function, characterized in that: It includes a starting shaft (1), a clutch gear ring (2) and a drive gear ring (3). The starting shaft (1), clutch gear ring (2) and drive gear ring (3) are coaxially arranged from front to back. The starting shaft (1) is the input end and the drive gear ring (3) is the output end. The clutch gear ring (2) is sleeved on the outside of the starting shaft (1). The clutch gear ring (2) is slidably connected to the starting shaft (1) through a straight spline pair (6). The ends of the clutch gear ring (2) and the ends of the drive gear ring (3) are evenly provided with several double helical end face teeth (7) along the circumferential direction. The double helical end face teeth (7) provided on the clutch gear ring (2) and the double helical end face teeth (7) provided on the drive gear ring (3) match each other. By moving the clutch gear ring (2) along the axial direction of the straight spline pair (6), the meshing and separation of the double helical end face teeth (7) are realized, thereby completing the engagement and disengagement of the mechanism. It also includes a baffle (4) and an auxiliary spring (5). The clutch gear ring (2) has a first annular stepped groove along the axial direction on one end face near the drive gear ring (3). The auxiliary spring (5) is coaxially arranged in the first annular stepped groove. The end of the auxiliary spring (5) is provided with a baffle (4). The baffle (4) is a circular plate structure. The baffle (4) is fixedly connected to the end of the starter shaft (1) through a connector. The outer side of the baffle (4) is clearance-fitted with the inner side of the first annular stepped groove of the clutch gear ring (2). One end of the auxiliary spring (5) is pressed against the end face of the baffle (4), and the other end of the auxiliary spring (5) is pressed against the bottom surface of the first annular stepped groove of the clutch gear ring (2). Each double-helix end face tooth (7) includes a forward working tooth surface (71) and a reverse working tooth surface (72), wherein the forward working tooth surface (71) and the reverse working tooth surface (72) are in the same helical direction; within the same radial section, the fitting line of the forward working tooth surface (71) and the reverse working tooth surface (72) is a straight line, which coincides with the rotation center of the mechanism.

2. The clutch mechanism with radial compensation function according to claim 1, characterized in that: The outer side of one end of the starter shaft (1) is machined with an external spline along the axial direction, and the inner side of the clutch gear ring (2) is machined with an internal spline along the axial direction. The internal spline and the external spline cooperate to form a straight tooth spline pair (6).

3. A clutch mechanism with radial compensation function according to claim 1 or 2, characterized in that: The other end of the starter shaft (1) is provided with a first flange, and the starter shaft (1) is connected to the external power input part through the first flange. The other end of the drive gear ring (3) is provided with a second flange, and the drive gear ring (3) is connected to the external power output part through the second flange.

4. A clutch mechanism with radial compensation function according to claim 3, characterized in that: The outer side of the starting shaft (1) away from the drive gear ring (3) is provided with a second annular stepped groove and a third annular stepped groove from left to right along the axial direction. The inner side of the clutch gear ring (2) away from the drive gear ring (3) is provided with a fourth annular stepped groove and a fifth annular stepped groove from left to right along the axial direction. The starting shaft (1) can slide with the clutch gear ring (2) through the second annular stepped groove and the fourth annular stepped groove. The starting shaft (1) can slide with the clutch gear ring (2) through the third annular stepped groove and the fifth annular stepped groove. A circular countersunk hole is machined at the center of the end of the starting shaft (1) away from the drive gear ring (3) along the axial direction. The circular countersunk hole is the main hydraulic oil circuit. A hydraulic oil branch circuit is machined radially on the side of the third annular stepped groove of the starting shaft (1). The hydraulic oil branch circuit is connected to the main hydraulic oil circuit.

5. A clutch mechanism with radial compensation function according to claim 4, characterized in that: The length of the second annular stepped groove of the starting shaft (1) is less than the length of the fourth annular stepped groove of the clutch gear ring (2), and the side of the second annular stepped groove is in clearance fit with the side of the fourth annular stepped groove; the length of the third annular stepped groove of the starting shaft (1) is less than the length of the fifth annular stepped groove of the clutch gear ring (2), and the third annular stepped groove is in clearance fit with the fifth annular stepped groove.

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