High-stability gear reducer with good heat dissipation effect

Abstract

The utility model relates to harmonic reducer technical field proposes a high stability gear reducer with good heat dissipation effect, including input shaft, the output shaft, the cycloidal gear one, the cycloidal gear two and the gear ring that are sequentially arranged in the input shaft axis direction, the inner wall of gear ring is provided with the internal gear, the cycloidal gear one with the cycloidal gear two all are engaged with internal gear, gear adopts short tooth high, the involute gear of big pressure angle, through the setting of eccentric wheel one and eccentric wheel two structure, through the setting of input shaft and reversely opposed eccentric wheel one, eccentric wheel two, realize power synchronous reverse input, combine transmission bearing two and transmission bearing three and convert into the reciprocating motion of cycloidal gear with rotary motion, utilize the engagement of few tooth difference internal gear and cycloidal gear and realize high -efficient speed reduction transmission, single -stage transmission ratio is big and the structure flattening, through above technical scheme, solved the low speed reduction transmission efficiency and stability problem of lack in the prior art.

Description

Technical Field

[0001] This utility model relates to the field of harmonic reducer technology, specifically to a high-stability gear reducer with good heat dissipation. Background Technology

[0002] Currently, harmonic reducers are transmission devices that achieve high-precision speed reduction based on the principle of elastic deformation.

[0003] In existing harmonic reducer technology, the traditional structure achieves transmission through the elastic deformation of the flexspline. While it offers advantages in high precision and small size, it also has inherent limitations: First, the flexspline is prone to fatigue failure under high-frequency or heavy-load conditions due to continuous alternating stress, thus limiting its reliability in high-torque applications. Second, the single-stage transmission ratio is limited by the deformation capacity of the flexspline. In scenarios pursuing a flat design, the traditional structure struggles to overcome the dual constraints of transmission efficiency and space size, making it difficult to meet the dual requirements of high precision and compactness. Third, the heat dissipation path is limited by the sealed structure, and frictional heat accumulates in the meshing area, easily leading to lubrication failure and tooth surface wear. Over long-term operation, the accumulation of thermal deformation will gradually reduce transmission accuracy and system stability. Utility Model Content

[0004] This invention proposes a highly stable gear reducer with good heat dissipation, which solves the problems of low speed reduction and transmission efficiency and insufficient stability in related technologies.

[0005] The technical solution of this utility model is as follows: A high-stability gear reducer with good heat dissipation includes an input shaft, an output shaft, a cycloidal wheel one, a cycloidal wheel two, and a gear ring arranged sequentially along the axis of the input shaft. An internal gear is provided on the inner wall of the gear ring. The cycloidal wheel one and the cycloidal wheel two mesh with the internal gear. The gears are involute gears with short tooth height and large pressure angle. The number of teeth of the cycloidal wheel one and the cycloidal wheel two is at least two fewer than the number of teeth of the internal gear. Through the structure of axially arranged sequentially, efficient power transmission is achieved, while the short tooth height involute gear reduces the risk of thermal deformation.

[0006] As a preferred embodiment of this utility model, an eccentric wheel one and an eccentric wheel two are fixedly sleeved on the outer circumferential surface of the input shaft. The eccentric wheel one and the eccentric wheel two are arranged in opposite directions. The 180° eccentric arrangement in opposite directions can dynamically balance the centrifugal force of rotation, reduce the vibration amplitude, and improve the operational stability.

[0007] In a preferred embodiment of this utility model, a second transmission bearing and a third transmission bearing are respectively sleeved on the outer peripheral surfaces of the first eccentric wheel and the second eccentric wheel, and the first cycloidal wheel and the second cycloidal wheel are respectively sleeved on the outer peripheral surfaces of the second transmission bearing and the third transmission bearing.

[0008] As a preferred embodiment of this utility model, a planetary carrier is provided on the inner wall of the gear ring, and at least three circumferentially distributed limiting shafts are provided on the top of the planetary carrier. The limiting shafts pass through the interior of the first eccentric wheel and the second eccentric wheel respectively. The planetary carrier realizes the axial positioning of the eccentric wheel and the second eccentric wheel through the limiting shafts, ensuring the accuracy of the torque transmission path and improving the transmission precision.

[0009] As a preferred embodiment of this utility model, a first transmission bearing and a fourth transmission bearing are also sleeved on the outer circumferential surface of the input shaft. The first transmission bearing is disposed inside the planetary carrier, and the fourth transmission bearing is disposed inside the output shaft.

[0010] As a preferred embodiment of this utility model, at least three circumferentially distributed pins are provided inside the first eccentric wheel and the second eccentric wheel. Wear-resistant sleeves are fitted on the outer circumferential surface of the pins. The two ends of the pins are respectively located inside the planetary carrier and the output shaft. The wear-resistant sleeves reduce friction loss and extend service life, ensuring reliability under long-term high load.

[0011] As a preferred embodiment of this utility model, a first shim and a second shim are sequentially arranged at one end of the axial direction of the first transmission bearing, and a third shim is arranged at one end of the axial direction of the second transmission bearing. An elastic retaining ring is arranged on the outer circumferential surface of the output shaft. The combination of the first shim, the second shim, the third shim and the elastic retaining ring makes the axial positioning more accurate, and can absorb assembly gaps, reduce mechanical vibration and impact, and improve system stability.

[0012] As a preferred embodiment of this utility model, a first rolling bearing is sleeved on the outer circumferential surface of the planetary carrier, and a second rolling bearing is provided on the outer circumferential surface of the output shaft. The first rolling bearing and the second rolling bearing are respectively disposed inside the two ends of the gear ring.

[0013] The working principle and beneficial effects of this utility model are as follows: 1. This utility model achieves synchronous reverse power input by setting up eccentric wheel one and eccentric wheel two structures, and by setting up the input shaft and the oppositely opposed eccentric wheel one and eccentric wheel two. Combined with transmission bearing two and transmission bearing three, the rotational motion is converted into the reciprocating motion of the cycloidal wheel. The meshing of the internal gear with a small tooth difference and the cycloidal wheel is used to achieve efficient speed reduction transmission. The single-stage transmission ratio is large and the structure is flat.

[0014] 2. This utility model, through the setting of structures such as pin shafts and wear-resistant sleeves, and the support structure of rolling bearing one and rolling bearing two in conjunction with the pin shaft and wear-resistant sleeves, reduces mechanical loss when subjected to large torque impacts. High-strength materials and flat heat dissipation design ensure that thermal deformation is reduced, thus meeting the requirements for high stability. Attached Figure Description

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

[0016] Figure 1 This is a schematic diagram of the overall structure of this utility model; Figure 2 This is the front view of the present utility model; Figure 3 This utility model Figure 2 Sectional view at point AA; Figure 4 This is an exploded view of the overall structure of this utility model; Figure 5 This is an exploded bottom view of the overall structure of this utility model; Figure 6 This is a schematic diagram of the overall structure of the input shaft of this utility model; Figure 7 This is a schematic diagram of the overall structure of the transmission bearing of this utility model.

[0017] In the diagram: 1. Gear ring; 11. Internal gear; 2. Planetary carrier; 21. Limiting shaft; 3. Shim 1; 4. Shim 2; 5. Rolling bearing 1; 6. Transmission bearing 1; 7. Transmission bearing 2; 8. Cycloidal wheel 1; 9. Input shaft; 91. Eccentric wheel 1; 92. Eccentric wheel 2; 10. Cycloidal wheel 2; 11. Transmission bearing 3; 12. Transmission bearing 4; 13. Shim 3; 14. Output shaft; 15. Rolling bearing 2; 16. Elastic retaining ring; 17. Pin; 18. Wear-resistant sleeve. Detailed Implementation

[0018] The technical solutions of this utility model will be clearly and completely described below with reference to the embodiments of this utility model. Obviously, the described embodiments are only some embodiments of this utility model, and not all embodiments. Based on the embodiments of this utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of this utility model.

[0019] Example 1

[0020] like Figures 1-7 As shown, a high-stability gear reducer with good heat dissipation includes an input shaft 9, an output shaft 14, a cycloidal wheel 8, a cycloidal wheel 10, and a gear ring 1 arranged sequentially along the axis of the input shaft 9. An internal gear 101 is provided on the inner wall of the gear ring 1. The cycloidal wheel 8 and the cycloidal wheel 10 both mesh with the internal gear 101. The gears are involute gears with short tooth height and large pressure angle. The number of teeth of the cycloidal wheel 8 and the cycloidal wheel 10 is at least two fewer than the number of teeth of the internal gear 101. Through the structure of being arranged sequentially along the axis, efficient power transmission is achieved, while the short tooth height involute gear reduces the risk of thermal deformation.

[0021] Eccentric wheel 91 and eccentric wheel 92 are fixedly sleeved on the outer circumferential surface of the input shaft 9. The eccentric wheel 91 and eccentric wheel 92 are arranged in opposite directions. The 180° eccentric arrangement in opposite directions can dynamically balance the centrifugal force of rotation, reduce the vibration amplitude, and improve the operational stability.

[0022] The outer circumferential surfaces of the first eccentric wheel 91 and the second eccentric wheel 92 are respectively fitted with a second transmission bearing 7 and a third transmission bearing 11, and the first cycloidal wheel 8 and the second cycloidal wheel 10 are respectively fitted with the outer circumferential surfaces of the second transmission bearing 7 and the third transmission bearing 11.

[0023] A planetary carrier 2 is provided on the inner wall of the gear ring 1. At least three circumferentially distributed limiting shafts 21 are provided on the top of the planetary carrier 2. The limiting shafts 21 pass through the interior of the first eccentric wheel 91 and the second eccentric wheel 92 respectively. The planetary carrier 2 realizes the axial positioning of the second eccentric wheel 91 and the second eccentric wheel 91 through the limiting shafts, ensuring the accuracy of the torque transmission path and improving the transmission precision.

[0024] The outer circumferential surface of the input shaft 9 is also fitted with a transmission bearing 6 and a transmission bearing 12. The transmission bearing 6 is located inside the planetary carrier 2, and the transmission bearing 12 is located inside the output shaft 14.

[0025] The eccentric wheel 11 and the eccentric wheel 2 are provided with at least three circumferentially distributed pins 17. Wear-resistant sleeves 18 are fitted on the outer circumferential surface of the pins 17. The two ends of the pins 17 are respectively located inside the planetary carrier 2 and the output shaft 14. The wear-resistant sleeves 18 reduce friction loss and extend service life, ensuring reliability under long-term high load.

[0026] A shim 3 and a shim 4 are sequentially arranged at one end along the axial direction of the transmission bearing 6, and a shim 13 is arranged at one end along the axial direction of the transmission bearing 7. An elastic retaining ring 16 is arranged on the outer circumferential surface of the output shaft 14. The combination of shims 3, 4, 13 and the elastic retaining ring 16 makes the axial positioning more accurate, absorbs assembly gaps, reduces mechanical vibration and impact, and improves system stability.

[0027] A rolling bearing 5 is fitted on the outer circumferential surface of the planetary carrier 2, and a rolling bearing 15 is provided on the outer circumferential surface of the output shaft 14. The rolling bearing 5 and the rolling bearing 15 are respectively located inside the two ends of the gear ring 1.

[0028] In this embodiment, after the external power is input through the input shaft, it drives the opposing eccentric wheels one and two to rotate synchronously; the eccentric wheels convert the rotational power into the reciprocating motion of the cycloidal wheels one and two through the transmission bearings two and three. Further, the cycloidal wheel meshes with the gear inside the gear ring with a small tooth difference. The gear is an involute gear with a short tooth height and a large pressure angle. The first stage of speed reduction is achieved by utilizing the difference in the number of teeth. During this process, the planetary carrier receives the torque transmitted by the cycloidal wheel through the limit shafts evenly distributed on the top, and transmits the power to the output shaft through the pin and wear-resistant sleeve, forming a stable force transmission path. Furthermore, transmission bearing one and transmission bearing four support the input shaft and output shaft respectively, ensuring the stability of the rotation axis; rolling bearing one and rolling bearing two support the planetary carrier and output shaft respectively, reducing friction loss and improving transmission efficiency; shims one, two, three and elastic retaining rings achieve axial positioning and shock absorption, reducing mechanical vibration; Heat dissipation and high stability design: The equipment adopts involute gears with short teeth and high pressure angle, and optimizes the heat dissipation path with a flat structure design; high-strength materials reduce thermal deformation, and wear-resistant sleeves reduce friction loss. The overall structure can maintain high stability when subjected to high torque impact, which is especially suitable for high-requirement scenarios such as robot joint motors, and achieves long-term efficient heat dissipation and stable operation. The formula for calculating the reduction ratio i of a cycloidal pinwheel reducer is: i = - Zn / (Zn - Zy) in: i: Reduction ratio (a negative result usually indicates that the output direction is opposite to the input direction) Zn: Number of teeth on the internal gear Zc: Number of teeth on the external gear Key relationship: The number of teeth Zy on a cycloidal gear is usually two fewer than the number of needle teeth Zn, i.e., Zn - Zy = 2. This is the most standard and common design to achieve a large reduction ratio.

[0029] The above are merely preferred embodiments of the present utility model and are not intended to limit the present utility model. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present utility model shall be included within the protection scope of the present utility model.

Claims

1. A highly stable gear reducer with good heat dissipation, characterized in that, The device includes an input shaft (9), an output shaft (14), a cycloidal wheel one (8), a cycloidal wheel two (10), and a gear ring (1) arranged sequentially along the axis of the input shaft (9). An internal gear (101) is provided on the inner wall of the gear ring (1). The cycloidal wheel one (8) and the cycloidal wheel two (10) mesh with the internal gear (101). The number of teeth of the cycloidal wheel one (8) and the cycloidal wheel two (10) is at least two fewer than the number of teeth of the internal gear (101).

2. The high-stability gear reducer with good heat dissipation effect according to claim 1, characterized in that, Eccentric wheel one (91) and eccentric wheel two (92) are fixedly sleeved on the outer circumferential surface of the input shaft (9), and the eccentric wheel one (91) and the eccentric wheel two (92) are arranged in opposite directions.

3. The high-stability gear reducer with good heat dissipation effect according to claim 2, characterized in that, Eccentric wheel one (91) and eccentric wheel two (92) are respectively fitted with transmission bearing two (7) and transmission bearing three (11) on their outer peripheral surfaces. Cycloidal wheel one (8) and cycloidal wheel two (10) are respectively fitted on the outer peripheral surfaces of transmission bearing two (7) and transmission bearing three (11).

4. The high-stability gear reducer with good heat dissipation effect according to claim 3, characterized in that, The inner wall of the gear ring (1) is provided with a planet carrier (2), and the top of the planet carrier (2) is provided with at least three circumferentially distributed limiting shafts (21), which pass through the interior of the first eccentric wheel (91) and the second eccentric wheel (92) respectively.

5. A high-stability gear reducer with good heat dissipation effect according to claim 4, characterized in that, The input shaft (9) is also fitted with a first transmission bearing (6) and a fourth transmission bearing (12) on its outer circumferential surface. The first transmission bearing (6) is located inside the planetary carrier (2), and the fourth transmission bearing (12) is located inside the output shaft (14).

6. A high-stability gear reducer with good heat dissipation effect according to claim 5, characterized in that, The eccentric wheel one (91) and the eccentric wheel two (92) are provided with at least three circumferentially distributed pins (17). Wear-resistant sleeves (18) are fitted on the outer circumferential surface of the pins (17). The two ends of the pins (17) are respectively located inside the planet carrier (2) and the output shaft (14).

7. A high-stability gear reducer with good heat dissipation effect according to claim 6, characterized in that, A gasket 1 (3) and a gasket 2 (4) are sequentially provided at one end of the axial direction of the transmission bearing 1 (6), a gasket 3 (13) is provided at one end of the axial direction of the transmission bearing 2 (7), and an elastic retaining ring (16) is provided on the outer circumferential surface of the output shaft (14).

8. A high-stability gear reducer with good heat dissipation effect according to claim 7, characterized in that, Rolling bearing 1 (5) is fitted on the outer circumferential surface of the planetary carrier (2), and rolling bearing 2 (15) is provided on the outer circumferential surface of the output shaft (14). Rolling bearing 1 (5) and rolling bearing 2 (15) are respectively located inside the two ends of the gear ring (1).

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