One-way clutch star wheel of the gearbox

Abstract

A sprag gear of a transmission one-way clutch proposed by the present invention includes a sprag gear body. The sprag gear body is in an annular shape. A number of transmission teeth are machined on the outer ring surface of the sprag gear body. At least two of the number of transmission teeth are arranged at intervals to form a group, and multiple groups of tooth areas are formed. The groups of tooth areas are arranged at intervals in the circumferential direction of the sprag gear body. Among them, the tooth widths of the transmission teeth in at least one group of tooth areas are different. The cross-section of the transmission tooth is rectangular. The present invention has the following beneficial effects: smooth transmission, preventing the occurrence of gear jumping, avoiding the problem of excessive power during the transmission process of the one-way clutch, improving utilization, and having a long service life.

Description

Technical Field

[0001] The present invention relates to the technical field of automotive clutches, and particularly to the star wheel of a transmission one-way clutch. Background Art

[0002] As a basic transmission component in the automotive transmission system, the transmission one-way clutch is a device with a self-clutching function by utilizing the speed change or rotation direction change of the main and driven parts. As the main load-bearing component, the one-way clutch star wheel generally has a plurality of transmission teeth evenly distributed in the circumferential direction of the star wheel body. Each transmission tooth is arranged adjacent to each other in sequence, and the circular angle between two adjacent transmission teeth is arranged at about 15°. The number of its transmission teeth is relatively large. The one-way clutch formed by such a star wheel will cause excessive strength of the combined structure of the one-way clutch and the transmission in the non-working state. The traditional one-way clutch structure cannot meet the usage requirements of the transmission in an automatic transmission (AT). Issues such as assembly, transmission, processing technology, and manufacturing convenience need to be considered. Therefore, a transmission and a one-way clutch that require relatively complex processing technology design and production and manufacturing make the structural design of the star wheel a difficult point. Summary of the Invention

[0003] Aiming at the deficiencies in the prior art, the present invention provides a star wheel of a transmission one-way clutch, which solves the problem of excessive strength of the combined structure of the one-way clutch and the transmission in the prior art.

[0004] A star wheel of a transmission one-way clutch proposed by the present invention includes a star wheel body. The star wheel body is in an annular shape. A plurality of transmission teeth are machined on the outer ring surface of the star wheel body. At least two of the plurality of transmission teeth are arranged at intervals as a group to form multiple tooth regions. Each group of tooth regions is arranged at intervals in the circumferential direction of the star wheel body. Among them, the tooth widths of the transmission teeth in at least one group of tooth regions are different, and the cross-section of the transmission tooth is rectangular.

[0005] The transmission teeth of the present invention can be processed by gear shaping equipment. In at least one group of tooth regions, there are transmission teeth with larger tooth widths and those with smaller tooth widths. This design can make the connection of the transmission structure of the transmission more convenient, facilitate the torque transmission between the star wheel and the transmission. The transmission teeth are arranged at intervals, so that the individual transmission teeth are not evenly distributed on the star wheel body, but are designed with corresponding intervals according to the needs of transmission, making the transmission stable, preventing gear jumping, and avoiding the problem of excessive power during the transmission process of the one-way clutch. The design of this structure is also convenient for processing and manufacturing. Each transmission tooth can be processed by a gear shaper, and the intervals between the teeth can be achieved through the PLC control of existing equipment, making the assembly of the one-way clutch and the transmission more convenient.

[0006] Compared with the prior art, the present invention has the following beneficial effects: the transmission is stable, preventing gear jumping, avoiding the problem of excessive power during the transmission process of the one-way clutch, improving utilization, and having a long service life.

[0007] Furthermore, the tooth region is formed by arranging two transmission teeth to form four groups of two-tooth regions and arranging three transmission teeth to form two groups of three-tooth regions; among the four groups of two-tooth regions, the interval between the two transmission teeth in one group of two-tooth regions is greater than the interval between the two transmission teeth in the other three groups; among the two groups of three-tooth regions, the interval between the three transmission teeth in one group is greater than the interval between the three transmission teeth in the other group. Through the arrangement of the two-tooth region and the three-tooth region, the transmission efficiency of the power is stronger and the performance is more excellent. BRIEF DESCRIPTION OF THE DRAWINGS

[0008] Figure 1 It is a schematic structural diagram of the present invention.

[0009] Figure 2 is Figure 1 the left view (section view) of.

[0010] Figure 3 This is for Figure 1 the partial enlarged view of the present invention. DETAILED DESCRIPTION OF THE INVENTION

[0011] The technical solutions in the present invention will be further described below with reference to the accompanying drawings and embodiments.

[0012] As Figures 1-3 shown, a one-way clutch star wheel of a gearbox proposed by the present invention includes a star wheel body 1. The star wheel body 1 is in a circular ring shape. A plurality of transmission teeth 2 are processed on the outer ring surface of the star wheel body 1. At least two of the plurality of transmission teeth 2 are arranged at intervals to form a plurality of groups of tooth regions. Each group of tooth regions is arranged at intervals in the circumferential direction of the star wheel body 1. Among them, the tooth widths of the transmission teeth 2 in at least one group of tooth regions are different, and the cross-section of the transmission tooth 2 is rectangular.

[0013] The transmission teeth 2 of the present invention can be processed by a gear shaping machine. In at least one group of tooth regions, some of the transmission teeth 2 have a larger tooth width and some have a smaller tooth width. This design can make it more convenient for the connection of the transmission structure of the gearbox, facilitate the torque transmission between the star wheel and the gearbox. The transmission teeth 2 are arranged at intervals, so that the transmission teeth 2 are not evenly distributed on the star wheel body 1, but are designed with corresponding intervals according to the needs of transmission, making the transmission stable, preventing the occurrence of gear jumping, and avoiding the problem of excessive power during the transmission of the one-way clutch. The design of this structure is also convenient for processing and manufacturing. Each transmission tooth 2 can be processed by a gear shaping machine, and the interval between the teeth can be realized by the PLC control of the existing equipment, making the assembly of the one-way clutch and the gearbox more convenient.

[0014] The tooth region is formed by arranging two transmission teeth 2 to form four groups of two-tooth regions and arranging three transmission teeth 2 to form two groups of three-tooth regions; among the four groups of two-tooth regions, the interval between the two transmission teeth 2 in one group of two-tooth regions is greater than the interval between the two transmission teeth 2 in the other three groups; among the two groups of three-tooth regions, the interval between the three transmission teeth 2 in one group is greater than the interval between the three transmission teeth 2 in the other group. The root chamfer R of each transmission tooth 2 is 0.5 mm. Through the arrangement of the two-tooth region and the three-tooth region, the power transmission efficiency is stronger, the performance is more excellent, it is suitable for the assembly of the gearbox in an automatic transmission (AT), the interval region is larger, and it avoids the excessive strength of the one-way clutch engagement structure.

[0015] As Figure 1 As shown, the four groups of two-tooth regions include the first tooth region 21, the second tooth region 22, the third tooth region 23, and the fourth tooth region 24 arranged in sequence. The arc length between the first tooth region 21 and the second tooth region 22 is b, the arc length between the second tooth region 22 and the third tooth region 23 is c, and the arc length between the third tooth region 23 and the fourth tooth region 24 is d, where b < d < c; the first tooth region 21 and the fourth tooth region 24 are respectively located on both sides of the two groups of three-tooth regions.

[0016] After the four groups of two-tooth regions are processed, the arc length between the first tooth region 21 and the second tooth region 22 can be 28.6 mm, the arc length between the second tooth region 22 and the third tooth region 23 can be 40.6 mm, and the arc length between the third tooth region 23 and the fourth tooth region 24 is 33.9 mm. This makes the intervals formed by the four groups of two-tooth regions arranged as "small - large - medium", fully considering the power utilization rate during the one-way clutch transmission process, making the power transmission smoother. The depth of the transmission tooth 2 is within the tolerance range of 3.4 mm, which is between +0.05 and -0.01, and the front power output ratio meets the requirements.

[0017] The tooth widths of the transmission teeth 2 in the first tooth region 21, the second tooth region 22, the third tooth region 23, and the fourth tooth region 24 are all D, and the tooth width D is 13.3 mm. The central angle between the two transmission teeth 2 in the first tooth region 21, the second tooth region 22, and the third tooth region 23 is a, and the central angle between the two transmission teeth 2 in the fourth tooth region 24 is 2a. The central angle a is 15°.

[0018] Through the above reasonable interval arrangement, considering the utilization rate of the one-way clutch, the transmission teeth 2 in the four groups of two-tooth regions all adopt a tooth width of 13.3 mm. The central angle distribution between the two transmission teeth 2 in the first tooth region 21, the second tooth region 22, and the third tooth region 23 is 15°, and the central angle distribution between the two transmission teeth 2 in the fourth tooth region 24 is 30°. The central angle is the included angle formed by the extension line from the midpoint of the two transmission teeth 2 to the center of the circle, making the smoothness of the transmitted power stronger and reducing the impact during the speed change process.

[0019] AsFigure 1 As shown, the two sets of three-tooth regions include a fifth tooth region 25 and a sixth tooth region 26 arranged in sequence; the fifth tooth region 25 is close to the first tooth region 21. The tooth widths of the two transmission teeth 2 in the fifth tooth region 25 are the same, and the tooth width of the other transmission tooth 2 is greater than that of the two transmission teeth 2 with the same tooth width. The transmission tooth 2 with a large tooth width is close to the sixth tooth region 26; the sixth tooth region 26 includes a transmission tooth 2 with a large tooth width, a transmission tooth 2 with a medium tooth width, and a transmission tooth 2 with a small tooth width. The transmission tooth 2 with a small tooth width is located between the transmission tooth 2 with a large tooth width and the transmission tooth 2 with a medium tooth width. The transmission tooth 2 with a large tooth width is close to the fifth tooth region 25, and the interval between the transmission tooth 2 with a medium tooth width and the transmission tooth 2 with a small tooth width is greater than the interval between the transmission tooth 2 with a small tooth width and the transmission tooth 2 with a large tooth width. The arc length of the interval between the fifth tooth region 25 and the sixth tooth region 26 can be 24.3 mm.

[0020] The tooth width of the transmission tooth 2 with a large tooth width in the fifth tooth region 25 is 19.2 mm, and the tooth widths of the other two transmission teeth 2 are 13.3 mm. The tooth width of the transmission tooth 2 with a large tooth width in the sixth tooth region 26 is 16.1 mm, the tooth width of the transmission tooth 2 with a medium tooth width is 13.3 mm, and the tooth width of the transmission tooth 2 with a small tooth width is 10.1 mm.

[0021] Through the reasonable interval arrangement of the above first to fourth tooth regions of the present invention, combined with the interval arrangement of the fifth tooth region 25 and the sixth tooth region 26 and the corresponding parameters of the transmission teeth 2, the utilization rate of the one-way clutch reaches the best state, and the manufacturing difficulty is relatively low, which is suitable for installation in the gearbox of an automatic transmission (AT).

[0022] In order to facilitate the installation of the roller and the serpentine spring on the inner ring surface of the star wheel body, five positioning grooves 3 evenly distributed in the circumferential direction of the star wheel body 1 are machined on the inner ring surface of the star wheel body 1, and four installation concave surfaces 4 are arranged between adjacent two positioning grooves 3. The installation concave surface 4 forms an obtuse triangle with the tangent of the inner ring surface of the star wheel body 1. Refer to Figure 3 , the dotted line I in the figure represents the tangent of the inner ring surface. The C region formed by the tangent of the inner ring surface and the installation concave surface 4 is an approximately obtuse triangle. The positioning groove 3 can facilitate the positioning of the cage. The roller and the serpentine spring are installed in the cage, and then the cage is positioned in the positioning groove 3, which is convenient for the installation of the cage. The installation concave surface 4 forms an obtuse triangle with the tangent of the inner ring surface of the star wheel body 1 so that the roller can move therein to achieve self-clutching.

[0023] The star wheel of the present invention can be processed through the following process: The annular blank is quenched and tempered to a core hardness of HRC25-30, the two ends of the blank are turned, the holes are bored and chamfered, and the outer diameter is turned to process the star wheel body 1 with an outer contour of φ180mm. The internal teeth are broached, and then high-frequency quenching and tempering are carried out to make the surface hardness HRC59-63; the hardened layer is 1.0-2.0mm. The star wheel is positioned on the fixture and the external teeth are cut by a gear shaper. The tooth depth is 3.4mm and the tolerance range is between +0.05 and -0.01. Deburring and shot peening treatments are carried out to obtain the star wheel.

[0024] Specifically, the present invention includes fourteen transmission teeth 2, and the transmission teeth 2 are all processed by a gear shaper. The depth of each transmission is 3.4mm and the tolerance range is between +0.05 and -0.01. Among them, the tooth widths of eleven transmission teeth 2 are the same, all being 13.3mm. Therefore, the tooth widths of the transmission teeth 2 in the four two-tooth areas are all 13.3mm. In the fifth tooth area 25, the tooth widths of the two transmission teeth 2 are 13.3mm and are close to the first tooth area 21. Among them, the transmission tooth 2 with a tooth width of 19.2mm is close to the transmission tooth 2 with a tooth width of 16.1mm in the sixth tooth area 26. The interval arc length between the fifth tooth area 25 and the sixth tooth area 26 can be 24.3mm, and the interval arc length between the sixth tooth area 26 and the fourth tooth area 24 is 57.3mm.

Claims

1. A one-way clutch star wheel for a transmission, comprising a star wheel body. The star wheel body is in an annular shape, and a plurality of transmission teeth are machined on the outer ring surface of the star wheel body. It is characterized in that at least two of the plurality of transmission teeth are arranged at intervals to form a group, and multiple groups of tooth areas are formed. The tooth areas are arranged at intervals in the circumferential direction of the star wheel body. Among them, the tooth widths of the transmission teeth in at least one group of tooth areas are different, and the cross-section of the transmission tooth is rectangular. The tooth areas are formed by arranging two transmission teeth to form four groups of two-tooth areas and arranging three transmission teeth to form two groups of three-tooth areas. Among the four groups of two-tooth areas, the interval between the two transmission teeth in one group of two-tooth areas is greater than the interval between the two transmission teeth in the other three groups. Among the two groups of three-tooth areas, the interval of the three transmission teeth in one group is greater than the interval of the three transmission teeth in the other group.

2. A one-way clutch star wheel for a transmission according to claim 1, It is characterized in that the four groups of two-tooth areas include a first tooth area, a second tooth area, a third tooth area, and a fourth tooth area arranged in sequence. The arc length between the first tooth area and the second tooth area is b, the arc length between the second tooth area and the third tooth area is c, and the arc length between the third tooth area and the fourth tooth area is d, where b < d < c; the first tooth area and the fourth tooth area are respectively located on both sides of the two groups of three-tooth areas.

3. A one-way clutch star wheel for a transmission according to claim 2, It is characterized in that the tooth widths of the transmission teeth in the first tooth area, the second tooth area, the third tooth area, and the fourth tooth area are all D.

4. A one-way clutch star wheel for a transmission according to claim 3, It is characterized in that the central angle between the two transmission teeth in the first tooth area, the second tooth area, and the third tooth area is a, and the central angle between the two transmission teeth in the fourth tooth area is 2a.

5. A one-way clutch star wheel for a transmission according to claim 2, It is characterized in that the two groups of three-tooth areas include a fifth tooth area and a sixth tooth area arranged in sequence; the fifth tooth area is close to the first tooth area. The tooth widths of the two transmission teeth in the fifth tooth area are the same, and the tooth width of the other transmission tooth is greater than that of the two transmission teeth with the same tooth width. The transmission tooth with the large tooth width is close to the sixth tooth area; the sixth tooth area includes a transmission tooth with a large tooth width, a transmission tooth with a medium tooth width, and a transmission tooth with a small tooth width. The transmission tooth with a small tooth width is located between the transmission tooth with a large tooth width and the transmission tooth with a medium tooth width. The transmission tooth with a large tooth width is close to the fifth tooth area, and the interval between the transmission tooth with a medium tooth width and the transmission tooth with a small tooth width is greater than the interval between the transmission tooth with a small tooth width and the transmission tooth with a large tooth width.

6. A one-way clutch star wheel for a transmission according to claim 5, It is characterized in that the tooth width of the transmission tooth with a large tooth width in the fifth tooth area is 19.2 mm, and the tooth widths of the other two transmission teeth are 13.3 mm.

7. A one-way clutch star wheel for a transmission according to claim 5, It is characterized in that the tooth width of the transmission tooth with a large tooth width in the sixth tooth area is 16.1 mm, the tooth width of the transmission tooth with a medium tooth width is 13.3 mm, and the tooth width of the transmission tooth with a small tooth width is 10.1 mm.

8. A one-way clutch star wheel for a transmission according to claim 1, It is characterized in that Five positioning grooves are machined on the inner ring surface of the sprag body, and are evenly distributed in the circumferential direction of the sprag body. Four mounting concave surfaces are arranged between every two adjacent positioning grooves.

9. A sprag of a gearbox one-way clutch as claimed in claim 8, wherein, an obtuse triangle is formed by the tangent line of the mounting concave surface and the inner ring surface of the sprag body.

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