Speed reducer with small tooth difference

Abstract

The utility model discloses a small-tooth-difference speed reducer, and belongs to the technical field of speed reducers. The small-tooth-difference speed reducer comprises an eccentric shaft. The at least two external gears are arranged on the eccentric shaft; the flange assembly comprises an outer flange and a supporting flange which are located on the two sides of the outer gears respectively, and the outer flange, the at least two outer gears and the supporting flange are connected through pin shafts; wherein a first gasket is arranged between every two adjacent outer gears, and second gaskets are arranged between the outer gears and the outer flange and between the outer gears and the supporting flange. Compared with the prior art, the speed reducer with the small tooth difference is good in damping performance, and the reliability and the service life of equipment can be effectively improved.

Description

Technical Field

[0001] This utility model relates to a speed reducer with a small tooth difference, belonging to the field of speed reducer technology. Background Technology

[0002] The low-tooth-difference gear reducer is a high-efficiency, compact transmission device. Its core structure includes basic components such as internal gears, external gears, and eccentric shafts. It achieves speed reduction through the difference in the number of teeth between the internal and external gears. It features small size, light weight, large transmission ratio, high efficiency, and strong load-bearing capacity, and is widely used in industrial machinery, automobiles, robots, ships, and aerospace fields.

[0003] During operation, the meshing of gears in a low-tooth-difference reducer generates impact and vibration, especially under high-speed, heavy-load conditions. Furthermore, the eccentric motion of the eccentric shaft leads to uneven gear meshing, further exacerbating vibration and impact. These vibrations and impacts not only cause resonance in the equipment, resulting in significant noise, but can also cause fatigue damage to critical components such as gears and bearings, thereby reducing the equipment's reliability and lifespan. Simultaneously, vibration can cause fasteners to loosen, and even lead to overall structural instability, posing certain safety hazards. Utility Model Content

[0004] To solve the above-mentioned technical problems, this utility model provides a low-tooth-difference reducer with good shock absorption performance.

[0005] The technical solution of this utility model is:

[0006] This utility model provides a speed reducer with a small tooth difference, including an eccentric shaft;

[0007] At least two external gears are mounted on the eccentric shaft;

[0008] A flange assembly includes an outer flange and a support flange located on both sides of the external gear, wherein the outer flange, at least two of the external gears and the support flange are connected by a pin.

[0009] A first gasket is provided between two adjacent external gears, and a second gasket is provided between the external gear and the external flange, and between the external gear and the supporting flange.

[0010] Optionally, both the outer flange and the support flange include a chassis and a connecting portion protruding outward from the chassis, and the connecting portion is provided with a clearance portion for avoiding the second gasket.

[0011] Optionally, the connecting part is provided with a plurality of connecting holes for connecting the pin, and the second gasket is provided with a clearance hole for avoiding the pin at the position corresponding to the connecting hole.

[0012] Optionally, the connecting portion is provided with a positioning protrusion for positioning and connecting the second gasket.

[0013] Optionally, the positioning protrusion is disposed in the connecting hole and positioned and connected with the clearance hole of the second gasket.

[0014] Optionally, the first gasket is an annular gasket, and the first gasket is sleeved on the outside of the pin.

[0015] Optionally, the connecting portion includes an outer side and an inner side disposed opposite to each other, a first step portion for accommodating a first bearing is provided between the chassis and the outer side, and a second step portion for accommodating a second bearing is provided between the chassis and the inner side.

[0016] Optionally, the first bearing is an angular contact ball bearing, and the second bearing is a deep groove ball bearing.

[0017] Optionally, it may also include an internal gear disposed on the outside of the external gear and directly meshing with the external gear.

[0018] Optionally, the tooth profiles of the external gear and the internal gear include connected convex and concave surfaces.

[0019] The beneficial technical effects of this utility model are:

[0020] This utility model's low-tooth-difference reducer effectively absorbs vibrations and impacts generated during gear meshing by placing a first shim between adjacent external gears and a second shim between the external gear and the external flange, and between the external gear and the supporting flange. This results in a significant vibration reduction effect, effectively suppressing resonance and improving the stability and reliability of the equipment. Furthermore, the second shim effectively disperses pressure between the external gear and the flange assembly, preventing localized stress concentration and enhancing the reliability of connections between components. Attached Figure Description

[0021] Figure 1 This is a structural schematic diagram of a low-tooth-difference reducer conforming to a preferred embodiment of the present utility model;

[0022] Figure 2 yes Figure 1 A sectional view;

[0023] Figure 3 yes Figure 1 Schematic diagram of the structure of the Chinese and foreign flanges;

[0024] Figure 4 yes Figure 1 Schematic diagram of the middle support flange;

[0025] Figure 5 yes Figure 1 A schematic diagram of the structure of the second gasket.

[0026] Explanation of reference numerals in the attached figures:

[0027] A reducer with a small tooth difference 100, an eccentric shaft 10, an input section 11, a roller bearing 12, an external gear 20, an internal gear 30, a flange assembly 40, an outer flange 41, a support flange 42, a chassis 43, a connecting section 44, a clearance section 45, a connecting hole 46, a positioning protrusion 47, a first step section 48, a second step section 49, a first bearing 51, a second bearing 52, a first gasket 61, a second gasket 62, a clearance hole 621, a pin 70, and a motor mounting flange 80. Detailed Implementation

[0028] In order to better understand the technical means of this utility model and to implement it in accordance with the contents of the specification, the specific embodiments of this utility model will be further described in detail below with reference to the accompanying drawings and examples. The following examples are used to illustrate this utility model, but are not intended to limit the scope of this utility model.

[0029] Please see Figures 1 to 5 As shown, this utility model provides a low-tooth-difference speed reducer 100, including an eccentric shaft 10, at least two external gears 20, an internal gear 30, a flange assembly 40, a pin 70, and a gasket assembly. At least two external gears 20 are mounted on the eccentric shaft 10. The flange assembly 40 includes an outer flange 41 and a support flange 42 located on both sides of the external gears 20, respectively. The outer flanges 41, the at least two external gears 20, and the support flange 42 are connected by the pin 70. The internal gear 30 is located outside the external gears 20 and directly meshes with them. There is a tooth difference between the external gears 20 and the internal gear 30. Driven by the eccentric shaft 10, the external gears 20 revolve and rotate, generating relative motion with the internal gear 30, thereby achieving the effect of reducing speed and increasing torque.

[0030] Furthermore, the eccentric shaft 10 includes an input section 11 for connection to a motor, and a plurality of eccentric sections disposed on the eccentric shaft 10. In this embodiment, the input section 11 is hollow, and the motor shaft is inserted into the input section 11, thereby driving the eccentric shaft 10 to rotate. The eccentric shaft 10 is provided with two eccentric sections, each eccentric section is fitted with a roller bearing 12, and the external gear 20 is fitted on the outside of the roller bearing 12 and disposed on the eccentric shaft 10 through the roller bearing 12. The eccentric shaft 10 is driven to rotate by the motor, causing the central axis of the external gear 20 to move eccentrically relative to the central axis of the internal gear 30, thereby driving the external gear 20 to revolve around the internal gear ring of the internal gear 30. In addition, due to the difference in the number of teeth between the external gear 20 and the internal gear 30, the external gear 20 will generate relative motion with the internal gear 30 during the revolution, thereby enabling the external gear 20 to rotate around its own central axis.

[0031] Furthermore, a first shim 61 is provided between two adjacent external gears 20. By providing the first shim 61, the vibration and impact generated by the external gears 20 during revolution and rotation can be effectively absorbed, reducing vibration and noise during equipment operation, and suppressing resonance phenomena of the equipment, thereby improving the stability of equipment operation.

[0032] The external gear 20 has several through holes for the pin 70 to pass through. A first washer 61 is disposed on the outside of the through holes, thereby avoiding the pin 70. That is, the first washer 61 is an annular washer, and the first washer 61 is sleeved on the outside of the pin 70. This arrangement can effectively protect the pin 70 through the first washer 61 while absorbing shock, reducing wear caused by vibration and impact, and extending the service life of the pin 70.

[0033] Furthermore, second gaskets 62 are provided between the external gear 20 and the external flange 41, and between the external gear 20 and the supporting flange 42. By providing the second gaskets 62, the vibration and impact generated by the external gear 20 during its revolution and rotation can be effectively absorbed, reducing the possibility of vibration transmission to the flange assembly 40 and other components, thereby reducing vibration and noise during equipment operation, suppressing resonance, and improving the stability of equipment operation. Simultaneously, the second gaskets 62 can evenly distribute the pressure between the external gear 20 and the flange assembly 40, avoiding localized stress concentration, reducing the risk of structural instability, reducing localized wear on the external gear 20, flange assembly 40, and pin 70, and extending the service life of critical components. In addition, the elastic properties of the gaskets can enhance the connection reliability between the external gear 20 and the flange assembly 40, reducing loosening or damage caused by vibration, and ensuring long-term stable operation of the equipment. By reducing noise during equipment operation, a quieter working environment is provided for operators, reducing safety hazards and improving equipment safety.

[0034] Please see Figures 3 to 5 As shown, both the outer flange 41 and the support flange 42 include a base 43 and a connecting portion 44 protruding outward from the base 43. The connecting portion 44 has a clearance portion 45 for accommodating the second gasket 62. By providing the clearance portion 45, the necessary installation space for the second gasket 62 is provided without changing the thickness of the outer flange 41, ensuring that the second gasket 62 can be accurately positioned and perform its vibration damping function. Furthermore, the design of the clearance portion 45 helps optimize the spatial layout, making the overall structure of the low-tooth-difference reducer 100 more compact.

[0035] Optionally, the connecting part 44 is provided with a plurality of connecting holes 46 for connecting the pin 70, and the second gasket 62 is provided with a clearance hole 621 for avoiding the pin 70 at the position corresponding to the connecting holes 46. By providing the clearance hole 621, interference and obstruction of the pin 70 by the second gasket 62 are avoided, ensuring that the pin 70 can pass smoothly through the connecting holes 46 and the clearance hole 621, thereby achieving a reliable connection between the flange assembly 40 and the external gear 20.

[0036] Furthermore, the connecting hole 46 on the outer flange 41 is a blind hole, which can prevent the pin 70 from being exposed and improve the service life of the low tooth difference reducer 100.

[0037] Furthermore, the connecting hole 46 on the support flange 42 is a through hole to ensure the connection strength between the pin 70 and the support flange 42.

[0038] Optionally, the connecting portion 44 is provided with a positioning protrusion 47 for positioning and connecting the second gasket 62. By providing the positioning protrusion 47, precise installation of the second gasket 62 can be achieved, ensuring accurate alignment between the clearance hole 621 on the second gasket 62 and the connecting hole 46 on the outer flange 41. This design effectively prevents displacement or deformation of the second gasket 62 during installation, thereby avoiding interference and obstruction between the gasket and the pin 70. The use of the positioning protrusion 47 not only improves installation accuracy but also simplifies the installation process, reducing rework and adjustment time caused by inaccurate alignment, and significantly improving installation efficiency. Simultaneously, because the gasket can be stably held in its designed position, its shock absorption effect is fully utilized, ensuring the stability and reliability of the equipment during operation.

[0039] Furthermore, the positioning protrusion 47 is disposed within the connecting hole 46. That is, the positioning protrusion 47 is located within the connecting hole 46, and a through hole for the pin shaft 70 to pass through is formed at the center of the positioning protrusion 47. The second gasket 62 is sleeved on the outside of the positioning protrusion 47 through the clearance hole 621. That is, the clearance hole 621 serves both as a clearance and as a positioning function, thereby enhancing the positioning accuracy of the second gasket 62. The positioning protrusion 47 provides reliable support and guidance for the second gasket 62, and ensures that the second gasket 62 remains stable during equipment operation, avoiding displacement caused by vibration and ensuring the continuity of the shock absorption effect.

[0040] Please see Figure 3 and Figure 4 As shown, in this embodiment, there are three positioning protrusions 47, which are evenly distributed on the connecting part 44 to ensure that the second gasket 62 is accurately aligned during installation and to prevent the second gasket 62 from shifting or misaligning.

[0041] Furthermore, the connecting portion 44 includes an outer side and an inner side disposed opposite to each other. A first step portion 48 for accommodating the first bearing 51 is provided between the chassis 43 and the outer side, and a second step portion 49 for accommodating the second bearing 52 is provided between the chassis 43 and the inner side. This arrangement can make reasonable use of space and ensure the installation accuracy and operational stability of the first bearing 51 and the second bearing 52.

[0042] Optionally, the first bearing 51 is an angular contact ball bearing, and the second bearing 52 is a deep groove ball bearing. By using angular contact ball bearings and deep groove ball bearings, respectively, large axial and radial loads can be borne, as well as good rotational accuracy and low friction performance, ensuring efficient operation of the equipment under high-speed and heavy-load conditions.

[0043] The motor mounting flange 80 is located on the outside of the support flange 42 to protect the support flange 42 while providing installation space for the motor.

[0044] The internal gear 30 is located outside the external gear 20 and meshes directly with the external gear 20, thereby avoiding the transmission of the oscillating needle, reducing costs, improving transmission efficiency, reducing transmission errors, and ensuring the transmission accuracy and stability of the equipment.

[0045] Optionally, the tooth profiles of the external gear 20 and the internal gear 30 include connected convex and concave surfaces. During operation, the convex surface of the external gear 20 engages with the concave surface of the internal gear 30, while the concave surface can engage with the convex surface of the external gear 20, achieving surface-to-surface contact to significantly improve the meshing performance of the external gear 20 and the internal gear 30. Furthermore, the engagement of the convex and concave surfaces reduces impact and noise during gear meshing, improving the smoothness and accuracy of the transmission.

[0046] In summary, the low-tooth-difference reducer 100 of this utility model effectively absorbs the vibration and impact generated during gear meshing by setting a first shim 61 between adjacent external gears 20 and a second shim 62 between the external gear 20 and the outer flange 41, and between the external gear 20 and the supporting flange 42. This results in a significant vibration reduction effect, effectively suppressing resonance and improving the stability and reliability of the equipment. Furthermore, the second shim 62 effectively disperses the pressure between the external gear 20 and the flange assembly 40, preventing localized stress concentration and enhancing the reliability of connections between components. Additionally, by providing clearance portions 45 on the outer flange 41 and the supporting flange 42, the vibration reduction performance is effectively improved without increasing the thickness of the low-tooth-difference reducer 100. The positioning protrusion 47 provides reliable support and guidance for the second shim 62, ensuring its stability during equipment operation, preventing displacement due to vibration, and ensuring the continuity of the vibration reduction effect.

[0047] The above description is only a preferred embodiment of the present utility model and is not intended to limit the present utility model. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present utility model, and these improvements and modifications should also be considered within the protection scope of the present utility model.

Claims

1. A reducer with a small tooth difference, characterized in that, include: Eccentric shaft; At least two external gears are mounted on the eccentric shaft; A flange assembly includes an outer flange and a support flange located on both sides of the external gear, wherein the outer flange, at least two of the external gears and the support flange are connected by a pin. A first gasket is provided between two adjacent external gears, and a second gasket is provided between the external gear and the external flange, and between the external gear and the supporting flange.

2. The low-tooth-difference reducer according to claim 1, characterized in that, Both the outer flange and the support flange include a chassis and a connecting portion protruding outward from the chassis. The connecting portion is provided with a clearance portion for avoiding the second gasket.

3. The low-tooth-difference reducer according to claim 2, characterized in that, The connecting part is provided with a plurality of connecting holes for connecting the pin, and the second gasket is provided with a clearance hole for avoiding the pin at the position corresponding to the connecting hole.

4. The low-tooth-difference reducer according to claim 3, characterized in that, The connecting part is provided with a positioning protrusion for positioning and connecting the second gasket.

5. The low-tooth-difference reducer according to claim 4, characterized in that, The positioning protrusion is disposed in the connection hole and is positioned and connected with the clearance hole of the second gasket.

6. The low-tooth-difference reducer according to claim 1, characterized in that, The first gasket is an annular gasket, and the first gasket is sleeved on the outside of the pin.

7. The low-tooth-difference reducer according to claim 2, characterized in that, The connecting part includes an outer side and an inner side that are disposed opposite to each other. A first step portion for accommodating a first bearing is provided between the chassis and the outer side, and a second step portion for accommodating a second bearing is provided between the chassis and the inner side.

8. The low-tooth-difference reducer according to claim 7, characterized in that, The first bearing is an angular contact ball bearing, and the second bearing is a deep groove ball bearing.

9. The low-tooth-difference reducer according to claim 1, characterized in that, It also includes an internal gear located outside the external gear and directly meshing with the external gear.

10. The low-tooth-difference reducer according to claim 9, characterized in that, The tooth profiles of the external gear and the internal gear include connected convex and concave surfaces.

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