Overload protection mechanism and reduction motor having the same

Abstract

The present application discloses an overload protection mechanism and a reduction motor having the same, wherein the overload protection mechanism includes a transmission component, a flat gasket, a disc gasket and a rotating shaft; the transmission component is provided with a first through hole, which is a circular through hole; the flat gasket is provided with a second through hole, which is non-circular; the disc gasket is provided with a third through hole, which is a circular through hole; the rotating shaft includes an expanding portion, a clamping portion and a transmission component, and the transmission component is provided with a pressing portion; the flat gasket is sleeved on the clamping portion, the clamping portion and the transmission component are sleeved on the transmission component, and the shape of the transmission component matches the first through hole and the third through hole, the flat gasket is squeezed and installed between the expanding portion and the transmission component, the peripheral portion of the disc gasket abuts against the side of the transmission component away from the flat gasket, and the middle portion of the disc gasket abuts and is pressed against the pressing portion. The present application can reduce noise during operation while achieving overload protection, and can also improve the yield rate of products equipped with the overload protection mechanism.

Description

Technical Field

[0001] The present application relates to the technical field of mechanical overload protection, and in particular to an overload protection mechanism utilizing friction and a reduction motor having the same. Background Art

[0002] In the related art, there is an overload protection mechanism, which includes a rotating shaft, a gear and two clamping washers, wherein the rotating shaft is used to output power, the two clamping washers and the gear are arranged on the rotating shaft, and the two clamping washers are respectively located on both sides of the axial direction of the gear, wherein the rotating shaft is provided with an enlarged diameter portion abutting against the first clamping washers, and a deforming portion abutting against the second clamping washers and deforming it, so as to press the gear to a position between the two clamping washers, and in order to make the two clamping washers rotate with the rotating shaft, the centers of the two clamping washers are provided with non-circular engaging holes, such as double D-shaped holes whose edges are composed of two oppositely arranged arcs and two oppositely arranged line segments. etc., the part of the rotating shaft passing through the two clamping washers and the gear is set to a locking shape with a cross-section matching the locking hole, a circular hole is set in the center of the gear, and the part of the rotating shaft passing through the two clamping washers and the gear has a cylindrical surface matching and fitting the inner wall of the circular hole, so that the gear can rotate freely relative to the rotating shaft; in this overload protection mechanism, the output torque of the rotating shaft is provided by the friction torque applied by the gear to the clamping washers. When the load borne by the rotating shaft is too large and exceeds the maximum friction torque that the gear can apply to the clamping washers, the gear will be able to rotate relative to the rotating shaft to achieve overload protection, thereby avoiding gear tooth breakage or burning of the coil part of the motor due to excessive load. Although this overload protection mechanism can achieve overload protection, since the gear is matched with the non-circular cross-section part of the rotating shaft through the circular hole, there will be a cavity between the inner side of the gear and the rotating shaft, and the rotating shaft may be subjected to lateral forces perpendicular to the axial direction during operation. As the rotating shaft rotates, the position of the cavity also changes periodically, which will cause the contact force between the rotating shaft and the gear to change periodically, thereby causing the rotating shaft and the gear to generate higher vibration noise during the rotation process; and since the part where the rotating shaft is connected to the compression gasket is a snap-fit shape that matches the snap-fit hole, and the deformed part is in this part and is obtained by extrusion deformation, the deformed part will only The arc-shaped cylindrical surfaces that can be formed on both sides of this part cannot abut and fix the second clamping gasket on the entire circle of the locking hole, and the middle part of the second clamping gasket will produce a large deformation at the position where it is squeezed by the deformation part, and the deformation at other positions in the middle is relatively small, that is, the second clamping gasket is unevenly deformed in its circumferential position, and the maximum driving torque of the entire overload protection mechanism is highly correlated with the deformation amount of the second clamping gasket. The uneven deformation of the second clamping gasket will cause fluctuations in the actual maximum driving torque and a large deviation from the designed maximum driving torque, which will lead to a high defective rate of products such as motors with this overload protection mechanism. Summary of the Invention

[0003] The present application aims to solve one of the technical problems existing in the prior art. To this end, the first embodiment of the present application proposes an overload protection mechanism, which can reduce noise during operation while achieving overload protection and also improve the yield rate of products equipped with the overload protection mechanism.

[0004] The second embodiment of the application provides a reduction motor having the overload protection mechanism of the embodiment of the first aspect.

[0005] According to the overload protection mechanism of the first aspect embodiment of the present application, it includes a transmission component, a flat gasket, a disc gasket and a rotating shaft; a first through hole is provided in the middle of the transmission component, and the first through hole is a circular through hole; a second through hole is provided in the middle of the flat gasket, and the second through hole is a non-circular anti-rotation hole; a third through hole is provided in the middle of the disc gasket, and the third through hole is a circular through hole; the rotating shaft includes an expanding part, a clamping part and a transmission part that are interconnected, and an annular clamping part is provided on the transmission part; wherein the flat gasket is sleeved on the clamping part through the second through hole, and the clamping part matches the shape of the second through hole, the transmission component is sleeved on the transmission part through the first through hole, and the disc gasket is sleeved on the transmission part through the third through hole, and the shape of the transmission part matches the first through hole and the third through hole, the flat gasket is squeezed and installed between the expanding part and the transmission component, the peripheral part of the disc gasket abuts against the side of the transmission component away from the flat gasket, and the middle part of the disc gasket abuts and is pressed on the clamping part.

[0006] The overload protection mechanism according to the embodiment of the first aspect of the present application has at least the following technical effects:

[0007] Since the pressing part is pressed against the disc gasket, and the disc gasket is pressed against the transmission component, and the transmission component presses the flat gasket against the expanded diameter part, with the help of the friction between the transmission component, the flat gasket and the disc gasket, when the load torque on the rotating shaft is small, the transmission component will be able to drive the rotating shaft to rotate together, and when the load torque is greater than the maximum friction torque that can be generated between the transmission component, the flat gasket and the disc gasket, the transmission component will produce relative rotation with the rotating shaft, thereby achieving overload protection; and since the rotating shaft is matched with the transmission component through a transmission part that matches the shape of the first through hole, there will be no cavity between the transmission component and the rotating shaft, and thus the contact force brought about by the rotation of the rotating shaft will not change periodically due to the cavity, thereby improving the noise problem during the normal rotation of the rotating shaft. Problem; moreover, since the side surface of the transmission part is a cylindrical surface that is adapted to the shape of the first through hole and the third through hole, the contact area between the transmission part and the transmission component is also larger, it is easier to ensure the coaxiality between the transmission component and the rotating shaft, and the output torque will also be smoother, and thus the product with the overload protection mechanism will also run more smoothly, which can further reduce noise; at the same time, the clamping part is a ring that surrounds the transmission part, so the circumference of the middle part of the disc gasket can abut against the clamping part, so that the deformation degree of the disc gasket in the circumferential direction is more uniform, so that the maximum driving torque that the transmission component can transmit to the rotating shaft is easier to control, and the maximum driving torque that can be achieved by the overload protection mechanism has a smaller fluctuation range and is closer to the design value, thereby improving the yield rate of products with the overload protection mechanism.

[0008] According to the overload protection mechanism of some embodiments of the first aspect of the present application, a first gasket mounting groove is provided on the side of the transmission component facing the flat gasket, and the flat gasket is located in the first gasket mounting groove and fits with the bottom of the first gasket mounting groove.

[0009] According to the overload protection mechanism of some embodiments of the first aspect of the present application, a plurality of protrusions are provided on the side of the flat gasket close to the transmission component, and a plurality of concave points are provided on the bottom of the first gasket mounting groove. The sizes of the protrusions and the concave points match each other, and when the transmission component and the rotating shaft rotate together, the protrusions are embedded in the concave points.

[0010] According to the overload protection mechanism of some embodiments of the first aspect of the present application, a plurality of protrusions are evenly arranged on the side of the flat gasket close to the transmission component, and a plurality of concave points are evenly arranged on the bottom of the first gasket mounting groove.

[0011] According to the overload protection mechanism of some embodiments of the first aspect of the present application, the number of concave points is greater than the number of convex points.

[0012] According to the overload protection mechanism of some embodiments of the first aspect of the present application, a second gasket mounting groove is provided on the side of the transmission component facing the disc gasket, and the disc gasket is provided in the second gasket mounting groove.

[0013] According to the overload protection mechanism of some embodiments of the first aspect of the present application, a circle of protrusions is provided along the outer edge of the first through hole of the second gasket mounting groove.

[0014] According to the overload protection mechanism of some embodiments of the first aspect of the present application, an output portion is formed at one end of the expanded diameter portion away from the flat gasket, and a threaded hole is provided at the end of the output portion.

[0015] According to the overload protection mechanism of some embodiments of the first aspect of the present application, gaps are provided on both sides of the output portion.

[0016] The reduction motor according to the second embodiment of the present application includes the overload protection mechanism of the first embodiment described above.

[0017] According to the overload protection mechanism of the first aspect embodiment of the present application, there are at least the following technical effects: since the reduction motor of this embodiment adopts the overload protection structure of the above-mentioned first aspect embodiment, its noise during operation is lower, and the overload torque consistency of the reduction motor produced is better, thereby improving the yield rate.

[0018] Additional aspects and advantages of the present application will be given in part in the following description and in part will become obvious from the following description or will be learned through practice of the present application. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] The above and / or additional aspects and advantages of the present application will become apparent and easily understood from the description of the embodiments in conjunction with the following drawings, in which:

[0020] Figure 1 is a structural diagram of an overload protection mechanism according to an embodiment of the present application;

[0021] Figure 2 is a cross-sectional view of a first overload protection mechanism according to an embodiment of the present application;

[0022] Figure 3 is a schematic diagram of the exploded structure of the first overload protection mechanism according to an embodiment of the present application;

[0023] Figure 4 is a cross-sectional view of a second overload protection mechanism according to an embodiment of the present application;

[0024] Figure 5 is a schematic diagram of the exploded structure of a second overload protection mechanism according to an embodiment of the present application;

[0025] Figure 61 is a schematic structural diagram of a flat gasket in a second overload protection mechanism according to an embodiment of the present application;

[0026] Figure 7 It is a structural schematic diagram of the transmission component in the second overload protection mechanism according to an embodiment of the present application.

[0027] Reference numerals:

[0028] Transmission component 100, first gasket mounting groove 110, concave point 111, second gasket mounting groove 120, protrusion 121, first through hole 130, flat gasket 200, second through hole 210, convex point 220, disc gasket 300, third through hole 310, rotating shaft 400, locking portion 411, transmission portion 412, expanded diameter portion 420, threaded hole 421, notch 422, and clamping portion 430. DETAILED DESCRIPTION

[0029] The following describes embodiments of the present application in detail. Examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are intended only to explain the present application and are not to be construed as limiting the present application.

[0030] In the description of this application, it should be understood that descriptions involving orientations, such as up, down, front, back, left, right, etc., indicating orientations or positional relationships, are based on the orientations or positional relationships shown in the accompanying drawings. They are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation. Therefore, they cannot be understood as limitations on this application.

[0031] In the description of this application, if there is a description of first or second, it is only for the purpose of distinguishing technical features, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features or implicitly indicating the order of the indicated technical features.

[0032] In the description of this application, unless otherwise clearly defined, terms such as setting, installing, and connecting should be understood in a broad sense, and technicians in the relevant technical field can reasonably determine the specific meanings of the above terms in this application based on the specific content of the technical solution.

[0033] Reference below Figures 1 to 7 The overload protection mechanism of the first embodiment of the present application is described.

[0034] like Figures 1 to 7 As shown, the overload protection mechanism according to the embodiment of the first aspect of the present application includes a transmission component 100, a flat gasket 200, a disc gasket 300 and a rotating shaft 400.

[0035] The transmission component 100 is provided with a first through hole 130 in the middle, and the first through hole 130 is a circular through hole; the flat gasket 200 is provided with a second through hole 210 in the middle, and the second through hole 210 is a non-circular anti-rotation hole; the disc gasket 300 is provided with a third through hole 310 in the middle, and the third through hole 310 is a circular through hole; the rotating shaft 400 includes an enlarged diameter portion 420, a clamping portion 411 and a transmission portion 412 that are connected to each other, and an annular pressing portion 430 is provided on the transmission portion 412; wherein, the flat gasket 200 is sleeved on the clamping portion 411 through the second through hole 210 , and the locking portion 411 matches the shape of the second through hole 210, the transmission component 100 is respectively sleeved on the transmission portion 412 through the first through hole 130, and the disc gasket 300 is respectively sleeved on the transmission portion 412 through the third through hole 310, and the shape of the transmission portion 412 matches the first through hole 130 and the third through hole 310, the flat gasket 200 is squeezed and installed between the expanded diameter portion 420 and the transmission component 100, the peripheral portion of the disc gasket 300 abuts against the side of the transmission component 100 away from the flat gasket 200, and the middle portion of the disc gasket 300 abuts and is pressed on the pressing portion 430.

[0036] It can be understood that, since the pressing portion 430 is pressed against the disc gasket 300, and the disc gasket 300 is pressed against the transmission component 100, and the transmission component 100 presses the flat gasket 200 against the enlarged diameter portion 420, by virtue of the friction between the transmission component 100 and the flat gasket 200 and the disc gasket 300, when the load torque on the rotating shaft 400 is small, the transmission component 100 will be able to drive the rotating shaft 400 to rotate together, and when the load torque is greater than the transmission component 100, the transmission component 100 will be able to drive the rotating shaft 400 to rotate together. When the maximum friction torque that can be generated between the flat washer 200 and the disc washer 300 is reached, the transmission component 100 will rotate relative to the rotating shaft 400, thereby achieving overload protection. Moreover, since the rotating shaft 400 is matched with the transmission component 100 via the transmission portion 412 whose shape matches that of the first through hole 130, there will be no cavity between the transmission component 100 and the rotating shaft 400, and thus the contact force caused by the rotation of the rotating shaft 400 will not change periodically due to the cavity. Thus, the noise problem during the normal rotation of the rotating shaft 400 is improved; moreover, since the side surface of the transmission part 412 is a cylindrical surface that is adapted to the shape of the first through hole 130 and the third through hole 310, the contact area between the transmission part 412 and the transmission component 100 is also larger, it is easier to ensure the coaxiality between the transmission component 100 and the rotating shaft 400, and the output torque will also be smoother, so that the product with the overload protection mechanism will also run more smoothly, which can further reduce noise; at the same time, the clamping part 430 is a ring surrounding the transmission part 412, so the circumference of the middle part of the disc gasket 300 can abut against the clamping part 430, so that the deformation degree of the disc gasket 300 in the circumferential direction is more uniform, so that the maximum driving torque that the transmission component 100 can transmit to the rotating shaft 400 is easier to control, and the maximum driving torque that can be achieved by the overload protection mechanism has a smaller fluctuation range and is closer to the design value, thereby improving the yield rate of products with the overload protection mechanism.

[0037] Reference Figure 3 It will be appreciated that in some embodiments, the second through hole 210 is configured as a double-D-shaped hole whose edge is formed by connecting two oppositely disposed arcs and two oppositely disposed line segments. The cross-sectional shape of the engaging portion 411 matches the shape of the second through hole 210. The line segments on the edge of the second through hole 210 enable the engaging portion 411 to engage with the second through hole 210 to limit the relative rotation between the flat gasket 200 and the rotating shaft 400. It will be appreciated that in other embodiments, the second through hole 210 can also be configured as other non-circular shapes, such as square, triangle, star, or spline groove shapes, and the cross-sectional shape of the engaging portion 411 can be configured accordingly.

[0038] Reference Figure 2 and Figure 3It is understood that the portion of the transmission portion 412 exposed from the third through hole 310 is pressed toward the side of the disc-shaped gasket 300, thereby plastically deforming to form a pressing portion 430 that presses the arched portion of the disc-shaped gasket 300. During the plastic deformation process, the pressing portion 430 partially enters the third through hole 310, thereby creating an interference fit between the transmission portion 412 and the third through hole 310, thereby enabling the disc gasket 300 to rotate along with the rotating shaft 400. It is understood that in addition to forming the pressing portion 430 by extrusion, the pressing portion 430 can also be formed by adding material to the transmission portion 412, for example, the pressing portion 430 can also be formed by welding to compress the disc-shaped gasket 300.

[0039] Reference Figure 2 and Figure 3 , it can be understood that a first gasket mounting groove 110 is provided on the side of the transmission component 100 facing the flat gasket 200, and the flat gasket 200 is located in the first gasket mounting groove 110; by opening the first gasket mounting groove 110 on the transmission component 100 and arranging the flat gasket 200 in the first gasket mounting groove 110, the axial size of the entire overload protection mechanism in the rotating shaft 400 can be reduced, making the structure more compact; and it can be understood that the flat gasket 200 is in contact with the bottom of the first gasket mounting groove 110. By contacting the flat gasket 200 with the bottom of the groove, the contact surface between the flat gasket 200 and the transmission component 100 can be a whole plane, so that the contact area between the flat gasket 200 and the transmission component 100 is more stable, and thus the friction torque generated between the flat gasket 200 and the transmission component 100 is also more stable, so as to further alleviate the problem of maximum driving torque fluctuation caused by differences in the manufacturing processes of different products, thereby reducing the defective rate. It is understandable that, since the contact surface between the flat washer 200 and the transmission component 100 is flat and its area is substantially equal to the area of the flat washer 200 , the maximum driving torque can be adjusted by changing the outer diameter of the flat washer 200 .

[0040] Reference Figures 4 to 7 It is understood that in some embodiments, the flat gasket 200 is provided with a plurality of protrusions 220 on the side close to the transmission component 100, and the bottom of the first gasket mounting groove 110 is provided with a plurality of recesses 111. The sizes of the protrusions 220 and the recesses 111 match each other. When the transmission component 100 rotates together with the rotating shaft 400, the protrusions 220 are embedded in the recesses 111. For example, Figures 4 to 7As shown, the bottom of the flat gasket 200 is provided with a protrusion 220, and the bottom of the first gasket mounting groove 110 is provided with a concave point 111 of a size that matches the protrusion 220. When the transmission component 100 drives the rotating shaft 400 to rotate together, the protrusion 220 is embedded in the concave point 111. When the load is too large, the transmission component 100 will rotate relative to the rotating shaft 400, and the bottom of the first gasket mounting groove 110 will continuously rub against the protrusion 220, making an abnormal noise. When the concave point 111 moves to the position of the protrusion 220, a "click" sound is emitted. This arrangement can further increase the maximum transmission torque of the rotating shaft 400 and the transmission component 100, and the user can also judge whether the load is too large by whether there is an abnormal noise. It is understandable that the convex point 220 is configured to be truncated cone-shaped or hemispherical, and the concave point 111 is configured to be a shape matching the convex point 220 , so that when the load is too large, the convex point 220 can be smoothly removed from the concave point 111 .

[0041] It is understandable that the plurality of protrusions 220 are evenly arranged on the side of the flat gasket 200 close to the transmission component 100, and the plurality of concave points 111 are evenly arranged on the bottom of the first gasket mounting groove 110. For example, Figures 5 to 7 As shown, the flat gasket 200 is evenly circumferentially provided with protrusions 220 on one side near the first gasket mounting groove 110. The bottom of the first gasket mounting groove 110 is evenly circumferentially provided with recesses 111. When the transmission component 100 drives the rotating shaft 400 to rotate together, the protrusions 220 respectively engage with the recesses 111 corresponding to their respective positions. When the load is too heavy, the transmission component 100 rotates relative to the rotating shaft 400, and the surface of the first gasket mounting groove 110 continuously rubs against the protrusions 220, producing an unusual noise. When the recesses 111 move to the position of the protrusions 220, a "clicking" sound is emitted. Because the protrusions 220 are evenly distributed on the bottom surface of the flat gasket 200 and the recesses 111 are evenly distributed on the first gasket mounting groove 110, the "clicking" sound is more frequent when the load is too heavy, which can more intuitively remind the user of the excessive load.

[0042] It is understood that the number of the concave points 111 is greater than the number of the convex points 220. Figure 6 and Figure 7As shown, the bottom of the flat gasket 200 is evenly distributed along the circumference with four protrusions 220 spaced 90 degrees apart. The first gasket mounting groove 110 is evenly distributed along the circumference with eight recesses 111 spaced 45 degrees apart. When the transmission component 100 drives the rotating shaft 400 to rotate together, the protrusions 220 embed into the corresponding recesses 111. When the load is too large, the rotating shaft 400 and the transmission component 100 rotate relative to each other, and the surface of the first gasket mounting groove 110 will continuously rub against the protrusions 220, producing an abnormal sound. When the recesses 111 move to the position of the protrusions 220, a "click" sound is emitted. The protrusions 220 are constantly worn away by friction with the surface of the first gasket mounting groove 110, producing unusual noises. By providing a greater number of recesses 111 than protrusions 220 at the bottom of the first gasket mounting groove 110, the travel of friction between the protrusions 220 and the bottom of the first gasket mounting groove 110 can be reduced, thereby extending the service life of the flat gasket 200 and, consequently, the overall service life of the gear overload protection system. Furthermore, the protrusions 220 will more frequently engage with the recesses 111, producing a "clicking" sound that provides a better user reminder.

[0043] Reference Figure 3 and Figure 4 It will be appreciated that in some embodiments of the present application, a second gasket mounting groove 120 is provided on the side of the transmission component 100 facing the disc-shaped gasket 300, and the disc-shaped gasket 300 is disposed in the second gasket mounting groove 120. Providing the second gasket mounting groove 120 on the transmission component 100 and disposing the flat gasket 200 in the second gasket mounting groove 120 can reduce the axial dimension of the entire overload protection mechanism in the rotating shaft 400, making the structure more compact.

[0044] Reference Figure 2 It is understood that in some further embodiments of the present application, a ring of protrusions 121 is provided at the bottom of the second gasket mounting groove 120 along the outer edge of the first through hole 130. This arrangement can increase the contact area between the rotating shaft 400 and the transmission component 100, further ensuring the coaxiality of the rotating shaft 400 and the transmission component 100, and improving the stability of the overload protection mechanism during operation.

[0045] Reference Figure 2 and Figure 3 It is understood that in some embodiments of the present application, the end of the expanded diameter portion 420 away from the flat gasket 200 forms an output portion, and a threaded hole 421 is provided at the end of the output portion. By providing the threaded hole 421 in the output portion, the user can connect the output portion to an external load through the threaded hole 421, thereby improving the convenience of using the overload protection mechanism.

[0046] It is understood that in some embodiments of the present application, notches 422 are provided on both sides of the output portion. By providing notches 422 on both sides of the output portion, the user can install protrusions at corresponding positions of the external load component, and the protrusions and notches 422 cooperate to connect the output portion and the external load component together, thereby improving the convenience of using the overload protection mechanism.

[0047] Reference Figure 2 and Figure 3 It is understood that in some embodiments of the present application, the transmission component 100 is a gear, the first through hole 130 is provided at the center of the gear, and the first gasket mounting groove 110 and the second gasket mounting groove 120 are provided on both axial sides of the gear. It is understood that in other embodiments of the present application, the transmission component 100 may be other transmission components 100 besides a gear, such as a pulley or sprocket.

[0048] The following describes a reduction motor according to a second embodiment of the present application, which includes the overload protection mechanism of the first embodiment described above.

[0049] The reduction motor further includes a stator and a rotor, wherein the rotor is connected to another transmission component 100 for transmission connection with the transmission component 100. For example, when the transmission component 100 is a driven gear, a driving gear is provided on the rotor, and the driving gear can be directly meshed with the driven gear, or be transmission-connected to the driven gear through an intermediate gear assembly.

[0050] Since the reduction motor of this embodiment adopts the overload protection structure of the first embodiment described above, it makes less noise during operation, and the overload torque of the reduction motor produced is more consistent, thereby improving the yield rate.

[0051] Throughout this specification, reference to terms such as "one embodiment," "some embodiments," "illustrative embodiments," "examples," "specific examples," or "some examples" means that the specific features, structures, materials, or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present application. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

[0052] Although the embodiments of the present application have been shown and described, those skilled in the art will appreciate that various changes, modifications, substitutions, and variations may be made to the embodiments without departing from the principles and purpose of the present application, and that the scope of the present application is defined by the claims and their equivalents.

Claims

1. An overload protection mechanism, characterized in that: include: A transmission component, wherein a first through hole is provided in the middle of the transmission component, and the first through hole is a circular through hole; A flat gasket, wherein a second through hole is provided in the middle of the flat gasket, and the second through hole is a non-circular anti-rotation hole; A disc-shaped gasket, wherein a third through hole is provided in the middle of the disc-shaped gasket, and the third through hole is a circular through hole; The rotating shaft includes an expanding portion, a clamping portion, and a transmission portion connected to each other, the transmission portion is provided with an annular pressing portion, the transmission component is provided with a second gasket mounting groove on the side facing the disc gasket, the disc gasket is arranged in the second gasket mounting groove, and the bottom of the second gasket mounting groove is provided with a circle of protrusions along the outer edge of the first through hole; wherein, The flat gasket is sleeved on the clamping portion through the second through hole, and the clamping portion matches the shape of the second through hole. The transmission component is sleeved on the transmission component through the first through hole, and the disc-shaped gasket is sleeved on the transmission component through the third through hole. The shape of the transmission component matches the first through hole and the third through hole. The flat gasket is squeezed and installed between the expanded diameter portion and the transmission component. The peripheral portion of the disc-shaped gasket abuts against the side of the transmission component away from the flat gasket, and the middle portion of the disc gasket abuts and is pressed against the pressing portion.

2. The overload protection mechanism according to claim 1, characterized in that: A first gasket installation groove is provided on a side of the transmission component facing the flat gasket. The flat gasket is located in the first gasket installation groove and fits with the bottom of the first gasket installation groove.

3. The overload protection mechanism according to claim 2, characterized in that: The flat gasket is provided with a plurality of protrusions on one side close to the transmission component, and a plurality of concave points are provided on the bottom of the first gasket mounting groove. The sizes of the protrusions match those of the concave points. When the transmission component rotates together with the rotating shaft, the protrusions are embedded in the concave points.

4. The overload protection mechanism according to claim 3, characterized in that: A plurality of the convex points are evenly arranged on a side of the flat gasket close to the transmission component, and a plurality of the concave points are evenly arranged on the bottom of the first gasket installation groove.

5. The overload protection mechanism according to claim 4, characterized in that: The number of the concave points is greater than the number of the convex points.

6. The overload protection mechanism according to any one of claims 1 to 5, characterized in that: An end of the expanded diameter portion away from the flat washer forms an output portion, and a threaded hole is provided at the end of the output portion.

7. The overload protection mechanism according to claim 6, characterized in that: Notches are provided on both sides of the output portion.

8. A reduction motor, characterized in that: The invention comprises the overload protection mechanism according to any one of claims 1 to 7.

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