A sprocket

Abstract

The utility model provides a kind of sprocket, including circular sprocket matrix and twenty-five convex teeth evenly distributed in its outer periphery. Each convex tooth side is provided with meshing tooth surface, for meshing with chain roller. When the diameter of the circular amount stick between the adjacent two convex teeth is 4.5994.601mm, the distance R1R25 from the twenty-five measuring points on the outer wall of the circular amount stick to the center of the circle is limited in a certain range. By differentiating the geometric parameters of each convex tooth, the tension fluctuation in the chain transmission process is effectively reduced, the vibration and noise are reduced, the tooth surface and chain roller wear are delayed, the service life is prolonged, and the transmission stability is improved.

Description

Technical Field

[0001] This utility model relates to the field of transmission chain wheel technology, and more specifically, to a sprocket. Background Technology

[0002] As a core connection form in the field of mechanical transmission, the chain-wheel structure is widely used in industrial production lines, agricultural machinery, logistics conveying equipment, and automotive transmission systems. It transmits power through the meshing of chains and sprockets, and its high transmission efficiency and strong load-bearing capacity make it the mainstream choice for medium- and low-speed heavy-duty transmission scenarios. However, during the periodic meshing of the sprocket and chain, vibration and noise are inevitably generated due to the rigid contact between the sprocket teeth and the chain rollers, tooth surface friction, and sudden changes in force flow. This problem is particularly prominent in continuous operation equipment, not only affecting the comfort of the operating environment but also potentially causing equipment resonance and reducing overall transmission stability.

[0003] The conventional 25-tooth sprockets on the market generally adopt a standardized tooth design, consisting of 25 teeth arranged in a circumferential array. Key dimensions such as tooth tip height, root circle radius, and tooth thickness strictly adhere to industry standards, ensuring identical geometric parameters for all teeth. While this design facilitates mass production and interchangeability, the contact process between the sprocket teeth and the chain rollers varies periodically during actual operation, resulting in significant fluctuations in chain tension on the sprocket (as shown in Figure 1, where the curve clearly indicates a maximum chain tension peak of 4500N during conventional sprocket drives). This high chain tension not only exacerbates tooth wear and roller fatigue damage, shortening the sprocket's lifespan, but also transmits vibration to the equipment frame via the shaft system, causing coordinated vibration of adjacent components, further amplifying noise, and ultimately affecting the reliability and operational accuracy of the entire transmission system. Utility Model Content

[0004] The main technical problem this application addresses is that traditional 25-tooth sprockets suffer from large chain tension fluctuations, significant vibration and noise, and rapid wear due to the consistent geometric parameters of the convex teeth. To overcome the above-mentioned defects of the prior art, this application provides a sprocket.

[0005] This application provides a sprocket, comprising: The sprocket base has a circular ring structure, and a center point O is provided at the center of the sprocket base; The sprocket has 25 teeth, which are evenly distributed around the outer periphery of the sprocket base for chain engagement. Each tooth has a meshing tooth surface on both sides of its top along the circumferential direction, which is used to engage with the rollers of the chain. Among them, when a circular measuring rod with a diameter of 4.599-4.601mm is arranged between two adjacent protrusions, the position on the outer wall of the circular measuring rod that is farthest from the center point O is the measuring point, and the twenty-five measuring points are distributed sequentially along the circumference of the sprocket base. The distances from the twenty-five measurement points to the center point O are configured as R1, R2, R3, R4, R5, R6, R7, R8, R9, R10, R11, R12, R13, R14, R15, R16, R17, R18, R19, R20, R21, R22, R23, R24, and R25. The distance of R1 is 26.457-26.562mm, the distance of R2 is 26.367-26.47mm, the distance of R3 is 26.175-26.273mm, the distance of R4 is 26.058-26.154mm, the distance of R5 is 26.132-26.229mm, the distance of R6 is 26.323-26.424mm, and the distance of R7 is 26... The distances for R8, R9, R10, R11, R12, and R13 are 26.451-26.556mm, 26.405-26.508mm, 26.223-26.323mm, 26.071-26.167mm, 26.096-26.193mm, 26.274-26.374mm, and 26.433-26.556mm respectively. The distances are as follows: R14 is 26.433-26.538mm; R15 is 26.274-26.374mm; R16 is 26.096-26.193mm; R17 is 26.071-26.167mm; R18 is 26.223-26.323mm; and R19 is 26.405-26.5mm. The distances of R20, R21, R22, R23, R24, and R25 are 26.367-26.47 mm. The distances of R20, R21, R22, R23, R24, R25, and R25 are 26.45-26.47 mm.

[0006] Compared with existing technologies, this application discloses a sprocket with the following advantages: Addressing the shortcomings of traditional 25-tooth sprockets, where all teeth have identical geometric parameters, resulting in large chain tension fluctuations, significant vibration and noise, rapid wear of the tooth surfaces and chain rollers, and short service life during chain meshing, this application achieves differentiated and precise design of the tooth geometric parameters by limiting the fit of circular measuring bars with diameters of 4.599-4.601mm between adjacent teeth and defining specific ranges of distances R1-R25 from the 25 measuring points to the center point O. The differentiated R value range corresponds to the reasonable adjustment of the contact position and contact angle when the teeth mesh with the chain rollers, significantly reducing the chain tension fluctuation amplitude during meshing, minimizing sudden changes in force flow, thereby significantly reducing transmission vibration and operating noise, improving operating comfort, reducing the risk of equipment resonance, and enhancing overall transmission stability. Reducing chain tension fluctuations directly decreases the rigid impact and frictional loss between the meshing tooth surface and the chain rollers, slowing down tooth surface wear and roller fatigue damage, effectively extending the service life of the sprocket and chain, and reducing the maintenance cost of the transmission structure. Defining the diameter range of the round gauge bar (4.599-4.601mm) provides a unified and accurate benchmark for determining measurement points, ensuring the measurement and design matching of R1-R25 values, avoiding tooth parameter design failures due to gauge bar specification deviations, and guaranteeing the transmission performance of the sprocket.

[0007] In one possible implementation, a reference groove is provided on the inner wall of the sprocket base, and the angle between the reference groove and the measuring point corresponding to R1 on the sprocket base is 129.45 degrees. Compared with the prior art, this provides a clear positioning reference for sprocket production, assembly, and inspection, can quickly identify and determine the position of the tooth corresponding to R1, ensures that the twenty-five measuring points are accurately distributed in the design order, avoids the disorder of the R value sequence caused by the deviation of the tooth position during processing, and ensures the effective implementation of differentiated meshing design.

[0008] In one possible implementation, the twenty-five measuring points are distributed clockwise along the circumference of the sprocket base, and the R1 to R25 values ​​corresponding to each measuring point are matched sequentially in the clockwise direction. Compared with the prior art, limiting the twenty-five measuring points to a clockwise distribution along the circumference and matching the R1-R25 values ​​in the clockwise direction ensures that the meshing sequence of the sprocket teeth and the chain strictly follows the designed R value variation law in the corresponding transmission scenario. This makes the chain tension fluctuation control and vibration noise reduction effect during operation more stable and reliable, and avoids sudden changes in local force caused by mismatch between the meshing sequence and the rotation direction.

[0009] In one possible implementation, the twenty-five measuring points are distributed counterclockwise along the circumference of the sprocket base, and the R1 to R25 values ​​corresponding to each measuring point are matched sequentially in the same counterclockwise direction. Compared with the prior art, limiting the twenty-five measuring points to a counterclockwise distribution along the circumference and matching the R1-R25 values ​​in the same counterclockwise direction ensures that the meshing sequence of the sprocket precisely matches the R value design rules in the corresponding transmission scenario, thereby reducing chain tension fluctuations and vibration noise, and avoiding a decrease in transmission performance due to disordered meshing sequence.

[0010] In one possible implementation, the distances of R1, R2, R3, R4, R5, R6, R7, R8, R9, R10, R11, R12, R13, R14, and R15 are 26.324 mm, 26.519 mm, 26.424 mm, 26.424 mm, 26.424 mm, 26.424 mm, 26.424 mm, and 26.424 mm respectively. The distances R16, R17, R18, R19, R20, R21, R22, R23, R24, and R25 are 26.419 mm, respectively. Compared to existing technologies, limiting the distance range of R1-R25 to specific values ​​allows for more precise locking of the tooth's geometric parameters. This avoids deviations in sprocket transmission performance caused by fluctuations in R values ​​within the range, ensuring that the meshing characteristics of each tooth fully meet optimal design expectations. This further reduces chain tension fluctuations and minimizes vibration, noise, and wear. Attached Figure Description

[0011] Figure 1 The test chain tension curve is shown for a traditional 25-tooth sprocket drive. Figure 2 This is a schematic diagram of the structure of this application; Figure 3 This is a line graph showing the values ​​of R in this application; Figure 4 This is a test chain tension curve diagram of Embodiment 1 of this application; Figure 5This is a test chain tension data table for Embodiment 1 of this application; Figure 6 This is a test chain tension curve diagram of Embodiment 2 of this application; Figure 7 This is a test chain tension data table for Embodiment 2 of this application; Figure 8 This is a test chain tension curve diagram of Embodiment 3 of this application; Figure 9 This is a test chain tension data table for Embodiment 3 of this application; Explanation of reference numerals in the attached figures: 1. Sprocket base; 11. Reference groove; 2. Convex tooth; 3. Circular gauge bar. Detailed Implementation

[0012] First, those skilled in the art should understand that these embodiments are merely used to explain the technical principles of the embodiments of this application and are not intended to limit the scope of protection of the embodiments of this application. Those skilled in the art can make adjustments as needed to adapt to specific application scenarios.

[0013] In the description of the embodiments of this application, it should be noted that, unless otherwise explicitly specified and limited, the terms "connected" and "linked" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in the embodiments of this application based on the specific circumstances.

[0014] In the embodiments of this application, unless otherwise expressly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "on top of," and "over" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0015] The present application will now be described in further detail with reference to the accompanying drawings and specific embodiments.

[0016] Example 1 See Figures 2 to 5 This application discloses a sprocket, including a sprocket base 1 and protruding teeth 2 integrally formed on the sprocket base 1.

[0017] The sprocket base 1 is made of high-strength metal and is machined into a circular structure. The inner diameter of the base is designed according to the matching shaft diameter. During the machining of the sprocket base 1, the centering tool of the CNC lathe is used for positioning, and the center point O is marked at the center of the base. This center point O serves as the reference point for the subsequent machining of the convex tooth 2 and the measurement of the distance between the measuring points, ensuring the accuracy of the machining position of each component.

[0018] Twenty-five protruding teeth 2 are machined on the outer periphery of the sprocket base 1 using milling and other machining processes. During machining, the center point O is used as a reference, and the circumferential indexing function of the CNC milling machine is used to evenly distribute the twenty-five protruding teeth 2 along the circumference of the sprocket base 1 (the central angle between adjacent protruding teeth 2 is 14.4°), ensuring that the spacing between each protruding tooth 2 is consistent and avoiding chain jamming caused by uneven distribution of protruding teeth 2 during transmission. The tooth tip width of each protruding tooth 2 is designed according to the size of the chain roller, and meshing tooth surfaces are milled on both sides of the top of each protruding tooth 2 along the circumferential direction to ensure that the contact surface is evenly stressed when in contact with the chain roller, reducing vibration and noise caused by rigid contact, and avoiding local wear between the roller and the meshing tooth surface.

[0019] On the inner wall of the sprocket base 1, a reference groove 11 is machined by milling and other processes. The cross-sectional shape of the reference groove 11 is set to be rectangular, and the groove length is consistent with the axial thickness of the sprocket base 1, so as to ensure that the reference groove 11 is completely through in the axial direction, which is convenient for positioning and inspection during assembly. The position of the reference groove 11 is based on the center point O of the sprocket base 1, and the size is precisely controlled.

[0020] Select a cylindrical measuring rod 3 with a diameter of 4.599-4.601mm (made of cemented carbide to avoid deformation of the measuring rod itself affecting the measurement accuracy), and place it one by one in the tooth groove between two adjacent convex teeth 2, ensuring that the cylindrical measuring rod 3 and the two corresponding meshing tooth surfaces of the adjacent convex teeth 2 are in contact; at this time, the position on the outer wall of the cylindrical measuring rod 3 that is farthest from the center point O of the sprocket base 1 is the measuring point. Mark twenty-five measuring points in sequence using a coordinate measuring instrument, and number them from measuring point one to measuring point twenty-five in clockwise order along the circumference of the sprocket base 1.

[0021] At the same time, an angle measurement benchmark is established, with one side being the center line of the benchmark groove 11 (the line connecting the midpoint of the groove width and the center point O), and the other side being the line connecting the measuring point 1 and the center point O. The included angle between the two lines is ensured to be 129.45 degrees by using an angle measuring instrument. This included angle is set as the positioning benchmark for machining the protruding teeth 2 on the sprocket base 1, which facilitates quick alignment of the relative positions of the sprocket and the shaft system, avoids transmission eccentricity caused by machining deviations, and further improves transmission stability.

[0022] Then, the distances from the twenty-five measuring points to the center point O were measured using a coordinate measuring instrument, and each distance was denoted as the R value. Figure 3 As shown in line segment one, the specific values ​​are as follows: Measurement point 1 corresponds to R1=26.51mm, measurement point 2 corresponds to R2=26.419mm, measurement point 3 corresponds to R3=26.224mm, measurement point 4 corresponds to R4=26.106mm, measurement point 5 corresponds to R5=26.181mm, measurement point 6 corresponds to R6=26.374mm, measurement point 7 corresponds to R7=26.504mm, measurement point 8 corresponds to R8=26.457mm, measurement point 9 corresponds to R9=26.273mm, measurement point 10 corresponds to R10=26.119mm, measurement point 11 corresponds to R11=26.145mm, measurement point 12 corresponds to R12=26.324mm, measurement point 13 corresponds to R13=26.486mm, measurement point... Point 14 corresponds to R14=26.486mm, point 15 corresponds to R15=26.324mm, point 16 corresponds to R16=26.145mm, point 17 corresponds to R17=26.119mm, point 18 corresponds to R18=26.273mm, point 19 corresponds to R19=26.457mm, point 20 corresponds to R20=26.504mm, point 21 corresponds to R21=26.374mm, point 22 corresponds to R22=26.181mm, point 23 corresponds to R23=26.106mm, point 24 corresponds to R24=26.224mm, and point 25 corresponds to R25=26.419mm.

[0023] This set of R values ​​reduces the fluctuation range of chain tension on the sprocket during transmission by optimizing the meshing position between the tooth and the chain roller. Figure 4 and Figure 5 As shown, the peak chain tension in the test was controlled at 2909N, which is significantly lower than the peak chain tension of 4500N for a traditional 25-tooth sprocket. This reduces tooth surface wear and roller fatigue damage, and reduces transmission vibration.

[0024] Example 2 The difference between this embodiment and Embodiment 1 is that, Figure 3 As shown in line segment two, the maximum value of the distance from each measuring point to the center point O is set to ensure that the sprocket can still mesh normally with the chain even under extreme size conditions. The specific values ​​of R are as follows: R1=26.562mm, R2=26.47mm, R3=26.273mm, R4=26.154mm, R5=26.229mm, R6=26.424mm, R7=26.5 56mm, R8=26.508mm, R9=26.323mm, R10=26.167mm, R11=26.193mm, R12=26.374mm, R13=26.538m m, R14=26.538mm, R15=26.374mm, R16=26.193mm, R17=26.167mm, R18=26.323mm, R19=26.508m m, R20=26.556mm, R21=26.424mm, R22=26.229mm, R23=26.154mm, R24=26.273mm, R25=26.47mm.

[0025] like Figure 6 and Figure 7 As shown, the peak chain tension corresponding to this set of R values ​​is controlled at 2584N, which is also less than the peak chain tension of a traditional 25-tooth sprocket, thus reducing transmission vibration.

[0026] Example 3 The difference between this embodiment and Embodiment 1 is that, Figure 3 As shown in line segment three, the minimum distance from each measuring point to the center point O is set to ensure that the sprocket can still mesh normally with the chain even under extreme size conditions. The specific values ​​of R are as follows: R1=26.457mm, R2=26.367mm, R3=26.175mm, R4=26.058mm, R5=26.132mm, R6=26.323mm, R7=26.4 51mm, R8=26.405mm, R9=26.223mm, R10=26.071mm, R11=26.096mm, R12=26.274mm, R13=26.433m m, R14=26.433mm, R15=26.274mm, R16=26.096mm, R17=26.071mm, R18=26.223mm, R19=26.405mm , R20=26.451mm, R21=26.323mm, R22=26.132mm, R23=26.058mm, R24=26.175mm, R25=26.367mm.

[0027] like Figure 8 and Figure 9 As shown, the peak chain tension corresponding to this set of R values ​​is controlled at 2884N, which is also less than the peak chain tension of a traditional 25-tooth sprocket, thus reducing transmission vibration.

[0028] The beneficial effects of this application include: I. To address the problems of large chain tension fluctuations (peak value 4500N), significant vibration and noise, and rapid wear caused by the uniform parameters of the convex teeth in traditional 25-tooth sprockets, a differentiated convex tooth design is achieved by limiting the distance R1-R25 from the center point O of the 25 preset measuring points between adjacent convex teeth. This reduces the peak chain tension, significantly reduces tension fluctuations, lowers vibration and noise and the risk of resonance, and improves transmission stability.

[0029] Second, reduced tension fluctuations decrease the rigid impact and friction between the teeth and the chain rollers, delaying wear and fatigue damage, extending the service life of the sprockets and chains, and reducing maintenance costs.

[0030] Third, the sprocket base is equipped with a reference groove to provide a positioning reference for machining, assembly and inspection, and to avoid deviation in the position of the protruding teeth; a unified round gauge bar reference is used to ensure accurate measurement of the R value and to avoid design failure due to specification deviation.

[0031] In the description of the embodiments of this application, it should be noted that the terms "inner" and "outer" and other terms indicating direction or positional relationship are based on the direction or positional relationship shown in the drawings. This is only for the convenience of description and does not indicate or imply that the device or component must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, it should not be construed as a limitation of this application.

[0032] In the description of this application, the references to terms such as "an embodiment," "some embodiments," "in this embodiment," "specific example," or "some examples," etc., refer to specific features, structures, materials, or characteristics described in connection with that embodiment or example, which are included in at least one embodiment or example of this application. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in a suitable manner in any one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0033] The above description is merely a specific embodiment of this application, but the scope of protection of this application is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the technical scope disclosed in this application should be included within the scope of protection of this application. Therefore, the scope of protection of this application should be determined by the scope of the claims.

Claims

1. A sprocket, characterized in that, include: The sprocket base has a circular ring structure, and a center point O is provided at the center of the sprocket base; The sprocket has 25 teeth, which are evenly distributed around the outer periphery of the sprocket base for chain engagement. Each tooth has a meshing tooth surface on both sides of its top along the circumferential direction, which is used to engage with the rollers of the chain. Among them, when a circular measuring rod with a diameter of 4.599-4.601mm is arranged between two adjacent protrusions, the position on the outer wall of the circular measuring rod that is farthest from the center point O is the measuring point, and the twenty-five measuring points are distributed sequentially along the circumference of the sprocket base. The distances from the twenty-five measurement points to the center point O are configured as R1, R2, R3, R4, R5, R6, R7, R8, R9, R10, R11, R12, R13, R14, R15, R16, R17, R18, R19, R20, R21, R22, R23, R24, and R25. The distance of R1 is 26.457-26.562mm, the distance of R2 is 26.367-26.47mm, the distance of R3 is 26.175-26.273mm, the distance of R4 is 26.058-26.154mm, the distance of R5 is 26.132-26.229mm, the distance of R6 is 26.323-26.424mm, and the distance of R7 is 26... The distances for R8, R9, R10, R11, R12, and R13 are 26.451-26.556mm, 26.405-26.508mm, 26.223-26.323mm, 26.071-26.167mm, 26.096-26.193mm, 26.274-26.374mm, and 26.433-26.556mm respectively. The distances are as follows: R14 is 26.433-26.538mm; R15 is 26.274-26.374mm; R16 is 26.096-26.193mm; R17 is 26.071-26.167mm; R18 is 26.223-26.323mm; and R19 is 26.405-26.5mm. The distances of R20, R21, R22, R23, R24, and R25 are 26.367-26.47 mm. The distances of R20, R21, R22, R23, R24, R25, and R25 are 26.45-26.47 mm.

2. The sprocket according to claim 1, characterized in that, The inner wall of the sprocket base is provided with a reference groove, and the angle between the reference groove and the measuring point corresponding to R1 on the sprocket base is 129.45 degrees.

3. The sprocket according to claim 2, characterized in that, The twenty-five measuring points are distributed clockwise along the circumference of the sprocket base, and the R1 to R25 values ​​corresponding to each measuring point are matched sequentially along the clockwise direction.

4. The sprocket according to claim 2, characterized in that, The twenty-five measuring points are distributed counterclockwise along the circumference of the sprocket base, and the R1 to R25 values ​​corresponding to each measuring point are matched sequentially along this counterclockwise direction.

5. The sprocket according to claim 3 or 4, characterized in that, The distances of R1, R2, R3, R4, R5, R6, R7, R8, R9, R10, R11, R12, and R13 are 26.486 mm. The distances of R1, R2, R3, R4, R5, R6, R11, R12, R13, R14, R15, R16, R17, R12, R13, R14, R15, R16, R17, R18, R19, R10, R1 ...9, R11, R12, R13, R14, R15, R16, R19, R19, R19, R19, R19, R19, R19, R19, R19, R19, R19, R19, R19, R19, R19, R19, R19, R19, R19, R19, R19 The distances for R14, R15, R16, R17, R18, R19, R20, R21, R22, R23, R24, and R25 are 26.419 mm.

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