Involute low-tooth-difference reduction motor

Abstract

This utility model relates to an involute geared motor with a small tooth difference, comprising a fixed base, a stator, a rotor, a transmission gear, an eccentric shaft, and an output shaft. An internal gear ring is mounted on the fixed base. The transmission gear is fitted onto the eccentric portion of the eccentric shaft and meshes with the internal gear ring. The stator is fixedly connected to the fixed base, and the rotor is driven by the eccentric shaft. The stator drives the rotor to rotate, causing the rotor to drive the eccentric shaft to rotate. The eccentric shaft, when rotating, drives the transmission gear to rotate via its eccentric portion. The transmission gear, when rotating, drives the output shaft to rotate via a limiting pin. Both the transmission gear and the internal gear ring have involute tooth profiles, and both have a tooth addendum coefficient of 0.4-0.6. The number of teeth on the internal gear ring is greater than the number of teeth on the transmission gear. Compared to the machining of cycloidal profiles, the involute tooth profile of this utility model has a lower machining cost, thereby reducing the machining cost of the gear.

Description

Technical Field

[0001] This utility model relates to the field of geared motor technology, and in particular to an involute geared motor with a small tooth difference. Background Technology

[0002] A cycloidal pinwheel reducer motor in the prior art includes a needle roller holder, a stator, a rotor, a cycloidal gear, an eccentric shaft, and an output shaft. The inner wall of the needle roller holder is provided with a circumferentially arranged needle roller structure; the cycloidal gear is sleeved on the eccentric portion of the eccentric shaft and meshes with the needle roller structure on the inner wall of the needle roller holder; the stator is fixedly connected to the holder and drives the rotor to rotate, causing the rotor to drive the eccentric shaft to rotate. When the eccentric shaft rotates, it drives the cycloidal gear to rotate through the eccentric portion, causing the cycloidal gear to drive the output shaft to rotate through a limiting pin.

[0003] The aforementioned cycloidal gear meshes with the needle roller structure on the inner wall of the needle roller holder to form a speed reduction structure. However, the machining cost of the cycloidal profile of both the cycloidal gear and the needle roller structure is relatively high, so this problem needs to be solved. Utility Model Content

[0004] In view of this, the present invention provides an involute geared motor with a small tooth difference, and the main technical problem to be solved is: how to reduce the processing cost of gears.

[0005] To achieve the above objectives, this utility model mainly provides the following technical solutions:

[0006] This utility model provides an involute geared motor with a small tooth difference, comprising a fixed base, a stator, a rotor, a transmission gear, an eccentric shaft, and an output shaft. The fixed base is provided with an internal gear ring; the transmission gear is sleeved on the eccentric portion of the eccentric shaft and meshes with the internal gear ring; the stator is fixedly connected to the fixed base, and the rotor is drively connected to the eccentric shaft; the stator drives the rotor to rotate, causing the rotor to drive the eccentric shaft to rotate; the eccentric shaft, when rotating, drives the transmission gear to rotate through the eccentric portion.

[0007] The transmission gear has two or more connecting holes, and the output shaft has limiting pins. The number of limiting pins is equal to the number of connecting holes and they correspond one-to-one. Each limiting pin is inserted into the corresponding connecting hole. The axis of the output shaft coincides with the axis of the eccentric shaft. When the transmission gear is used to rotate, it drives the output shaft to rotate through each of the limiting pins.

[0008] Both the transmission gear and the internal gear ring have involute tooth profiles, and both have a tooth tip height coefficient of 0.4-0.6. The number of teeth on the internal gear ring is greater than the number of teeth on the transmission gear.

[0009] In some embodiments, the tooth tip surface of the internal gear ring is a plane, and the tooth side surfaces on both sides of the tooth tip surface are transitioned by arcs.

[0010] In some embodiments, the number of teeth on the internal gear ring differs from the number of teeth on the transmission gear by 1-4.

[0011] In some embodiments, the internal gear ring is integrally formed on the mounting base.

[0012] In some embodiments, the rotor is sleeved on the outside of the stator, and the rotor is fixedly connected to the eccentric shaft via an end cover; the end cover and the output shaft are located at both axial ends of the involute low-tooth-difference geared motor.

[0013] The eccentric shaft has a wiring hole inside, and the end cap has a connecting through hole; one end of the eccentric shaft is inserted into the connecting through hole to be fixedly connected to the end cap.

[0014] The output shaft is provided with a through hole opposite to the end of the wiring hole that is away from the end cap, and a removable sealing block is provided in the through hole.

[0015] In some embodiments, the end of the through hole opposite to the eccentric shaft is flared, and the sealing block is used to be embedded in the flared opening and to fit with the flared opening with a clearance.

[0016] By employing the above technical solution, the involute geared motor with low tooth difference of this utility model has at least the following beneficial effects:

[0017] 1. This utility model designs both the transmission gear and the internal gear ring with involute tooth profiles, which is beneficial for processing. Compared with the processing form of cycloidal profile, the processing cost of involute tooth profile is lower, thereby reducing the processing cost of gears.

[0018] 2. This utility model designs the addendum coefficient of both the transmission gear and the internal gear ring to be 0.4-0.6, which helps to improve the stability of the meshing transmission between the transmission gear and the internal gear ring when the transmission gear rotates under the drive of the eccentric shaft.

[0019] 3. This utility model achieves the speed reduction function of the motor by making the number of teeth of the internal gear ring greater than the number of teeth of the transmission gear, so that the meshing of the transmission gear and the internal gear ring can form a speed reduction structure.

[0020] The above description is only an overview of the technical solution of this utility model. 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 preferred embodiments of this utility model are described in detail below with reference to the accompanying drawings. Attached Figure Description

[0021] To more clearly illustrate the technical solutions in the embodiments of this utility model or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0022] Figure 1 This is a schematic diagram of the structure of an involute geared motor with a small tooth difference, provided in one embodiment of the present invention;

[0023] Figure 2 This is a cross-sectional view of the involute low-tooth-difference geared motor of this utility model;

[0024] Figure 3 It is a schematic diagram illustrating the meshing of the transmission gear and the internal gear ring;

[0025] Figure 4 yes Figure 3 Enlarged view of point A in the middle;

[0026] Figure 5 This is a structural diagram of the fixed base.

[0027] Reference numerals in the attached diagram: 1. Stator; 2. Rotor; 3. End cover; 4. Eccentric shaft; 5. Transmission gear; 6. Fixed base; 7. Limiting pin; 8. Output shaft; 9. Sealing block; 10. Output end cover; 11. Bearing support ring; 12. Bearing; 31. Connecting through hole; 41. Wiring hole; 51. Connecting hole; 61. Internal gear ring; 81. Through hole; 611. Tooth top surface; 612. Tooth side surface; 613. Arc. Detailed Implementation

[0028] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the protection scope of the present utility model.

[0029] It should be noted that if the embodiments of this utility model involve directional indicators (such as up, down, left, right, front, back, etc.), the directional indicators are only used to explain the relative positional relationship and movement of the components in a certain specific posture (as shown in the figure). If the specific posture changes, the directional indicators will also change accordingly.

[0030] Furthermore, if the embodiments of this utility model involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of indicated technical features. Therefore, features defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. If the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed by this utility model.

[0031] like Figure 1-5 As shown in the figure, an embodiment of the present invention discloses an involute geared motor with a small tooth difference, which includes a fixed base 6, a stator 1, a rotor 2, a transmission gear 5, an eccentric shaft 4, and an output shaft 8. The fixed base 6 is provided with an internal gear ring 61; the transmission gear 5 is fitted onto the eccentric portion of the eccentric shaft 4 and meshes with the internal gear ring 61. The stator 1 is fixedly connected to the fixed base 6, and the rotor 2 is drivenly connected to the eccentric shaft 4. The stator 1 drives the rotor 2 to rotate, causing the rotor 2 to drive the eccentric shaft 4 to rotate. The eccentric shaft 4, when rotating, drives the transmission gear 5 to rotate through its eccentric portion. The transmission gear 5 is provided with two or more connecting holes 51, and the output shaft 8 is provided with limiting pins 7. The number of limiting pins 7 is equal to the number of connecting holes 51 and corresponds one-to-one. Each limiting pin 7 is inserted into the corresponding connecting hole 51. The axis of the output shaft 8 coincides with the axis of the eccentric shaft 4, and the transmission gear 5, when rotating, drives the output shaft 8 to rotate through the limiting pins 7. Both the transmission gear 5 and the internal gear ring 61 have involute tooth profiles, and both have a tooth addendum coefficient of 0.4-0.6. Furthermore, the number of teeth on the internal gear ring 61 is greater than the number of teeth on the transmission gear 5.

[0032] In the example above, by designing the tooth profiles of both the transmission gear 5 and the internal gear ring 61 as involute tooth profiles, it is easier to process. Compared with the machining form of cycloidal profile, the machining cost of involute tooth profile is lower, thereby reducing the machining cost of gears.

[0033] By designing the addendum coefficients of both the transmission gear 5 and the internal gear ring 61 to be 0.4-0.6, the stability of the meshing transmission between the transmission gear 5 and the internal gear ring 61 when the transmission gear 5 rotates under the drive of the eccentric shaft 4 is improved.

[0034] In addition, by making the number of teeth of the internal gear ring 61 greater than the number of teeth of the transmission gear 5, the meshing of the transmission gear 5 and the internal gear ring 61 can form a speed reduction structure, thus realizing the speed reduction function of the motor of this utility model.

[0035] It should be noted that the specific implementation method of the aforementioned transmission gear 5 driving the output shaft 8 to rotate through the limit pin 7 when driven is the existing technology. It is the same as the working principle of the cycloidal gear driving the output shaft to rotate through the limit pin when driven, and will not be described in detail here.

[0036] In some implementations, such as Figure 4 As shown, the tooth tip surface 611 of the aforementioned internal gear ring 61 can be a plane, and the tooth side surfaces 612 on both sides of the tooth tip surface 611 are transitioned by arcs 613. This can improve the meshing effect between the internal gear ring 61 and the transmission gear 5 and reduce the transmission noise between them.

[0037] In some embodiments, the number of teeth on the aforementioned internal gear ring 61 differs from the number of teeth on the transmission gear 5 by 1-4, thus forming a "small tooth difference transmission." This allows high-speed rotation to be converted into low-speed, high-torque output through the difference in the number of teeth. This novel involute small tooth difference geared motor can improve efficiency, reduce power loss, achieve high precision and strong stability, while also reducing noise and enabling a larger reduction ratio.

[0038] In some implementations, such as Figure 5 As shown, the aforementioned internal gear ring 61 can be integrally formed on the fixed base 6, which can improve the stability of the connection between the internal gear ring 61 and the fixed base 6.

[0039] In some implementations, such as Figure 2 As shown, the aforementioned rotor 2 is sleeved on the outside of the stator 1, forming an external rotor. The rotor 2 is fixedly connected to the eccentric shaft 4 via the end cover 3. The end cover 3 and the aforementioned output shaft 8 are located at both axial ends of the involute low-tooth-difference geared motor. The eccentric shaft 4 has a wiring hole 41 inside, and the end cover 3 has a connecting through hole 31. One end of the eccentric shaft 4 is inserted into the connecting through hole 31 to be fixedly connected to the end cover 3. The output shaft 8 has a through hole 81 opposite to the end of the wiring hole 41 that is away from the end cover 3, and a removable sealing block 9 is provided in the through hole 81.

[0040] In the example above, the internal cables of the motor can be routed through the interior of the eccentric shaft 4 and then exit through the connecting through-hole 31 on the end cover 3. Additionally, by designing a removable sealing block 9 within the through-hole 81 on the output shaft 8, it is possible to decide whether to install the sealing block 9 based on actual needs, thereby determining whether the cables should be routed through the through-hole or not.

[0041] To achieve the detachable function of the aforementioned sealing block 9, in some embodiments, the end of the aforementioned through hole 81 opposite to the eccentric shaft 4 can be a flared opening, in which the aforementioned sealing block 9 is fitted with a clearance fit. When it is necessary to remove the sealing block 9, a tool can be inserted from the other end of the eccentric shaft 4 to push the sealing block 9 out of the flared opening.

[0042] It should be noted that the aforementioned transmission gear 5 may also be referred to as a planetary gear in some contexts.

[0043] For ease of understanding, the overall structure of this utility model will be described below, and its working principle will be explained.

[0044] This utility model discloses an involute geared motor with a small tooth difference. Its core principle is to achieve speed reduction and torque increase through the difference in the number of teeth between the transmission gear 5 and the internal gear ring 61. This technology belongs to a type of planetary gear transmission. The transmission gear 5 and the internal gear ring 61 form an internal meshing gear pair, both using involute tooth profiles, and the difference in their tooth count is very small (usually 1-4 teeth), hence the name "small tooth difference transmission." This tooth difference converts high-speed rotational motion into low-speed, high-torque output. This novel involute geared motor with a small tooth difference improves efficiency, reduces power loss, offers high precision and strong stability, while also reducing noise and enabling a larger reduction ratio.

[0045] The aforementioned end cap 3 is interference-fitted with the eccentric shaft 4 through the connecting through hole 31.

[0046] The aforementioned involute geared motor with a small tooth difference also includes an output end cover 10, which is fixedly connected to the aforementioned mounting base 6. Specifically, the output end cover 10 is locked and fixed to the mounting base 6 by screws.

[0047] The aforementioned fixed base 6 may also be provided with a bearing support ring 11, which provides support for the eccentric shaft 4 through the bearing 12 installed on the inner side.

[0048] The aforementioned transmission gears 5 can be two, and the aforementioned eccentric parts on the eccentric shaft 4 can also be two, with the two arranged diagonally at 180 degrees. The two transmission gears 5 are fitted onto their respective eccentric parts in a one-to-one correspondence. The two transmission gears 5 achieve power transmission through the eccentric shaft 4, integrating a zero-tooth-difference output mechanism, optimizing spatial layout and transmission stability.

[0049] The internal cables of the involute low-tooth-difference geared motor of this utility model, such as motor wires, can pass through the inside of the eccentric shaft 4 and out through the through hole on the output end cover 10 for external power supply.

[0050] The aforementioned output end cover 10 is used for fixed connection. The stator 1 and rotor 2 cooperate to form a motor assembly to input power, and the eccentric shaft 4 is used for intermediate transmission. The involute low tooth difference geared motor of this utility model is small in size, light in weight, low in noise, high in precision, and has good running stability. It can also improve energy conversion efficiency, has a large transmission ratio, high efficiency, and strong load-bearing capacity, thereby extending the range and improving the service life.

[0051] This utility model's involute geared motor with a small tooth difference drives a transmission gear 5 to mesh with an internal gear ring 61 via an eccentric shaft 4, utilizing the small tooth difference characteristic of the involute gear to achieve a large transmission ratio. When the rotor 2 drives the eccentric shaft 4 to rotate, the eccentric shaft 4 drives the transmission gear 5 to rotate, and the low-speed, high-torque power is transmitted to the output shaft 8 through the limiting pin 7. When this utility model's involute geared motor with a small tooth difference is applied to a joint module, it can improve the flexibility and adaptability of the joint module.

[0052] The involute geared motor with low tooth difference of this invention has the following advantages:

[0053] 1. Achieve a larger reduction ratio and output greater torque within the same volume.

[0054] 2. By innovatively applying a planetary structure with low tooth difference, and using this as the core, the motor, sensing and control functions are highly integrated to ultimately create an involute low tooth difference joint module geared motor with high torque density, high rigidity, low backlash and low noise.

[0055] 3. The outer ring-shaped rotor 2 is integrated on the inner wall of the connecting cylinder and rotates synchronously with the connecting cylinder. The fixed base 6 is locked to the output end cover 10.

[0056] 4. This utility model optimizes and integrates the mature advantages of involute gears with the principle of planetary transmission with small tooth difference by setting a small tooth difference structure inside it, thereby achieving excellent performance and load-bearing capacity far exceeding that of ordinary planetary gearboxes. Ultimately, it realizes the transformation of the high speed and low torque input of the motor into low speed and high torque output at the output end.

[0057] This utility model's involute geared motor with low tooth difference significantly improves the durability and fatigue resistance of the gearbox through optimized gear pair design and structural layout; precise tooth profile design and optimized meshing performance ensure high transmission accuracy and stability, reduce vibration and noise during operation, and improve the smoothness of equipment operation; by reducing frictional losses of the gear pair, transmission efficiency is improved, failure rate is reduced, thereby extending the service life of the equipment; and it can output a large torque in an extremely compact size.

[0058] This utility model's involute low-tooth-difference geared motor, through its ingenious low-tooth-difference planetary structure, achieves a larger reduction ratio and outputs greater torque within the same volume. It also boasts advantages such as long lifespan and high reliability. The low-tooth-difference transmission technology utilizes gear meshing with a small tooth difference to achieve speed reduction, offering advantages such as small size, light weight, high precision, and strong stability.

[0059] The involute low-tooth-difference geared motor of this invention can be applied to industrial automation, stair transport vehicles, robot joints, precision equipment and other fields that require high-precision transmission, meeting the transmission needs of different scenarios and having broad application prospects.

[0060] The above description is only a preferred embodiment of the present utility model and does not limit the patent scope of the present utility model. All equivalent structural transformations made under the inventive concept of the present utility model using the contents of the present utility model specification and drawings, or direct / indirect applications in other related technical fields, are included within the patent protection scope of the present utility model.

Claims

1. An involute geared motor with a small tooth difference, characterized in that, The system includes a fixed base (6), a stator (1), a rotor (2), a transmission gear (5), an eccentric shaft (4), and an output shaft (8). The fixed base (6) is provided with an internal gear ring (61). The transmission gear (5) is sleeved on the eccentric part of the eccentric shaft (4) and meshes with the internal gear ring (61). The stator (1) is fixedly connected to the fixed base (6), and the rotor (2) is driven to the eccentric shaft (4). The stator (1) is used to drive the rotor (2) to rotate, so that the rotor (2) drives the eccentric shaft (4) to rotate. The eccentric shaft (4) is used to drive the transmission gear (5) to rotate through the eccentric part when rotating. The transmission gear (5) is provided with two or more connecting holes (51), and the output shaft (8) is provided with limiting pins (7). The number of limiting pins (7) is equal to the number of connecting holes (51) and they correspond one-to-one. Each limiting pin (7) is inserted into the corresponding connecting hole (51) one-to-one. The axis of the output shaft (8) coincides with the axis of the eccentric shaft (4). When the transmission gear (5) is used to rotate, it drives the output shaft (8) to rotate through each of the limiting pins (7). The tooth profiles of both the transmission gear (5) and the internal gear ring (61) are involute tooth profiles, and the tooth tip height coefficients of both are 0.4-0.

6. The number of teeth of the internal gear ring (61) is greater than the number of teeth of the transmission gear (5).

2. The involute low-tooth-difference geared motor as described in claim 1, characterized in that, The tooth top surface (611) of the internal gear ring is a plane, and the tooth side surfaces (612) on both sides of the tooth top surface (611) are transitioned by arcs (613).

3. The involute low-tooth-difference geared motor as described in claim 1, characterized in that, The number of teeth of the internal gear ring (61) differs from the number of teeth of the transmission gear (5) by 1-4.

4. The involute low-tooth-difference geared motor as described in claim 1, characterized in that, The internal gear ring (61) is integrally formed on the fixed base (6).

5. The involute low-tooth-difference geared motor as described in any one of claims 1-4, characterized in that, The rotor (2) is sleeved on the outside of the stator (1), and the rotor (2) is fixedly connected to the eccentric shaft (4) through the end cover (3); the end cover (3) and the output shaft (8) are located at both ends of the axial direction of the involute low tooth difference geared motor. The eccentric shaft (4) has a wiring hole (41) inside, and the end cap (3) has a connecting through hole (31); one end of the eccentric shaft (4) is inserted into the connecting through hole (31) to be fixedly connected to the end cap (3); The output shaft (8) is provided with a through hole (81) opposite to the end of the wiring hole (41) away from the end cap (3), and a removable sealing block (9) is provided in the through hole (81).

6. The involute low-tooth-difference geared motor as described in claim 5, characterized in that, The end of the through hole (81) opposite to the eccentric shaft (4) is flared, and the sealing block (9) is used to be embedded in the flared opening and to fit with the flared opening with a clearance.

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