Reducer integrated into disc motor

Abstract

This utility model discloses a speed reducer integrated into a disc motor. The speed reducer is located on the outside of the disc motor and includes a primary planetary gear mechanism and a secondary planetary gear mechanism. The primary planetary gear mechanism has a first drive shaft for driving connection with the output shaft of the disc motor. The secondary planetary gear mechanism has a second drive shaft for driving connection with the primary planetary gear mechanism. The second drive shaft, the first drive shaft, and the output shaft are arranged with a common central axis. The speed ratio of the secondary planetary gear mechanism is the same as that of the primary planetary gear mechanism. The speed reducer also includes a wire passage that extends along the axial direction of the disc motor and sequentially passes through the first drive shaft and the second drive shaft.

Description

Technical Field

[0001] This utility model relates to the field of electric drive system technology, and in particular to a reducer integrated into a disc motor. Background Technology

[0002] A planetary reducer is a reducer with three planetary gears rotating around a sun gear. With the rapid development of the planetary reducer industry, more and more industries and companies are using planetary reducers. Existing robot joint modules typically use a two-stage reducer. Because robot joint modules generally have low power and torque densities, to meet the miniaturization requirements of the powertrain, the first-stage planetary gear structure of the reducer is designed to be small and housed inside a disc motor. As a result, the reducer has low transmission efficiency and a low overall speed ratio, failing to meet high torque requirements. Furthermore, the compact arrangement of the disc motor and reducer leaves no space for powertrain wiring; the powertrain wiring can only be routed along the outside of the disc motor, resulting in a cluttered overall powertrain structure. Utility Model Content

[0003] The main purpose of this utility model is to propose a reducer integrated into a disc motor, which aims to solve the problems that existing reducers integrated into disc motors cannot meet high torque requirements and cannot provide space for wiring.

[0004] To achieve the above objectives, this utility model proposes a speed reducer integrated into a disc motor, wherein the speed reducer is disposed on the outside of the disc motor, and the speed reducer includes:

[0005] A primary planetary gear mechanism, having a first drive shaft for drive connection with the output shaft of the disc motor; and,

[0006] The second-stage planetary gear mechanism has a second drive shaft for transmission connection with the first-stage planetary gear mechanism. The second drive shaft is arranged with the first drive shaft and the output shaft sharing a common central axis.

[0007] The speed ratio of the second-stage planetary gear mechanism is the same as that of the first-stage planetary gear mechanism.

[0008] The reducer also includes a wire passage that extends along the axial direction of the disc motor and passes through the first drive shaft and the second drive shaft in sequence.

[0009] Optionally, the reducer further includes a reducer housing, which is arranged around the outer periphery of the first-stage planetary gear mechanism and the second-stage planetary gear mechanism;

[0010] The primary planetary gear mechanism further includes a first sun gear, a plurality of first planet gears, a first planet carrier, and a first internal gear ring. The first internal gear ring is fixedly disposed on the inner wall of the reducer housing. The first sun gear is sleeved on the first transmission shaft and rotates coaxially with the first transmission shaft. The plurality of first planet gears are evenly distributed along the circumference of the first transmission shaft. The first planet gears mesh with the first sun gear and the first internal gear ring so that when the first sun gear rotates with the first transmission shaft, the first planet gears can rotate along their own axis and around the central axis of the first sun gear. The first planet carrier is connected to the plurality of first planet gears and is used to rotate along the central axis of the first sun gear.

[0011] The second drive shaft is connected to the first planetary carrier via a drive mechanism.

[0012] Optionally, the first planetary carrier is located at the end of the first drive shaft away from the disc motor, and the first planetary carrier has a first side facing away from the first drive shaft;

[0013] The second drive shaft protrudes from the first side.

[0014] Optionally, the first drive shaft and the second drive shaft rotate at different speeds, and a gap is formed between the first drive shaft and the first planetary carrier in the axial direction of the reducer.

[0015] Optionally, the reducer further includes a reducer housing, which is arranged around the outer periphery of the first-stage planetary gear mechanism and the second-stage planetary gear mechanism;

[0016] The secondary planetary gear mechanism further includes a second sun gear, multiple second planet gears, a second planet carrier, and a second internal gear ring. The second internal gear ring is fixed to the inner wall of the reducer housing. The second sun gear is sleeved on the second transmission shaft and rotates coaxially with the second transmission shaft. Multiple second planet gears are evenly distributed along the circumference of the second transmission shaft. The second planet gears mesh with the second sun gear and the second internal gear ring so that when the second sun gear rotates with the second transmission shaft, the second planet gears can rotate along their own axis and around the central axis of the second sun gear. The second planet carrier is connected to multiple second planet gears and is used to rotate around the central axis of the second sun gear.

[0017] The second planetary carrier is connected to an external load drive.

[0018] Optionally, the first internal gear ring of the primary planetary gear mechanism is the same as and integrally formed with the second internal gear ring of the secondary planetary gear mechanism to form an integrally formed gear ring, and a hollow structure is provided in a local position of the gear ring.

[0019] Optionally, a groove is provided around the inner side of the gear ring, the groove extends circumferentially along the gear ring, and in the axial direction of the reducer, the groove is located between the first planetary gear of the first-stage planetary gear mechanism and the second planetary gear of the second-stage planetary gear mechanism;

[0020] The hollow structure includes the groove.

[0021] Optionally, in the axial direction of the reducer, the thickness of the first-stage planetary gear mechanism is less than the thickness of the second-stage planetary gear mechanism.

[0022] Optionally, the wire passage includes a first wire passage hole located in the first drive shaft and a second wire passage hole located in the second drive shaft, wherein the diameter of the first wire passage hole is equal to the diameter of the second wire passage hole.

[0023] Optionally, the wire passage is arranged with the first drive shaft and the second drive shaft sharing a common central axis.

[0024] The technical solution provided by this utility model has at least the following advantages:

[0025] This utility model provides a reducer integrated into a disc motor, comprising a primary planetary gear mechanism and a secondary planetary gear mechanism. The first drive shaft of the primary planetary gear mechanism is connected to the output shaft of the disc motor. The second drive shaft of the secondary planetary gear mechanism is connected to the primary planetary gear mechanism. By aligning the second drive shaft, the first drive shaft, and the output shaft with a common central axis, eccentric losses due to axis misalignment are avoided during power transmission from the motor output shaft to the primary and secondary planetary gear mechanisms, reducing vibration and noise, and further improving transmission stability and efficiency. The speed ratio of the secondary planetary gear mechanism is the same as that of the primary planetary gear mechanism, increasing the overall efficiency of the reducer and meeting the requirements of high-load conditions. Since the reducer is located outside the disc motor, the size of the primary planetary gear mechanism can be designed to be larger. This allows for a through-path for wiring within the first and second drive shafts, providing independent internal space for the wiring without occupying external space, resulting in more rational powertrain wiring and a more orderly overall structure and cleaner, more aesthetically pleasing appearance. Attached Figure Description

[0026] 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.

[0027] Figure 1 A schematic diagram of a powertrain embodiment provided by this utility model;

[0028] Figure 2 for Figure 1 Top view of the powertrain with respect to the reducer;

[0029] Figure 3 for Figure 2 The reducer is shown in a cross-sectional view along AA.

[0030] Figure 4 for Figure 1 Side view of the powertrain with respect to the reducer;

[0031] Figure 5 for Figure 4 A cross-sectional view of the reducer along BB;

[0032] Figure 6 for Figure 4 A cross-sectional view of the reducer along CC;

[0033] Figure 7 for Figure 1 The powertrain is shown in a cross-sectional view along DD.

[0034] Explanation of icon numbers:

[0035] 1000 Powertrain; 100 Reducer; 1 First-stage planetary gear mechanism; 11 First drive shaft; 12 First sun gear; 13 First planet gear; 14 First planet carrier; 15 First internal gear ring; 2 Second-stage planetary gear mechanism; 21 Second drive shaft; 22 Second sun gear; 23 Second planet gear; 24 Second planet carrier; 25 Second internal gear ring; 3 Wire passage; 31 First wire hole; 32 Second wire hole; 4 Reducer housing; 5 Slot; 200 Disc motor; F1 Axial axis.

[0036] The realization of the purpose, functional features and advantages of this utility model will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0037] 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.

[0038] 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.

[0039] 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 technical features indicated. Therefore, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the meaning of "and / or" throughout the text includes three parallel solutions; for example, "A and / or B" includes solution A, solution B, or a solution where both A and B are satisfied simultaneously. Furthermore, 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. When 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.

[0040] A planetary reducer is a reducer consisting of three planetary gears rotating around a sun gear. With the rapid development of the planetary reducer industry, more and more industries and companies are using planetary reducers. Existing robot joint modules typically use a two-stage reducer.

[0041] In order to provide wiring space while meeting the high torque requirements, this utility model improves the structure of the reducer 100 integrated into the disc motor 200. The reducer 100 will be described in detail below with reference to the accompanying drawings.

[0042] Please see Figure 1 and Figure 2The reducer 100 includes a primary planetary gear mechanism 1 and a secondary planetary gear mechanism 2. The primary planetary gear mechanism 1 has a first drive shaft 11 for driving connection with the output shaft of the disc motor 200. The secondary planetary gear mechanism 2 has a second drive shaft 21 for driving connection with the primary planetary gear mechanism 1, and the second drive shaft 21 is arranged with the first drive shaft 11 and the output shaft as a common central axis.

[0043] The first drive shaft 11 of the first-stage planetary gear mechanism 1, the second drive shaft 21 of the second-stage planetary gear mechanism 2, and the output shaft of the disc motor 200 are arranged with the same central axis, that is, the three are coaxial. This design can ensure that during the transmission of power from the motor output shaft to the first-stage and second-stage planetary gear mechanisms 2, eccentric losses caused by shaft misalignment are avoided, vibration and noise are reduced, and transmission stability and efficiency are further improved.

[0044] Furthermore, since the reducer 100 is located outside the disc motor 200, the size design of the first-stage planetary gear mechanism 1 is unrestricted. In this case, the size of the first-stage planetary gear mechanism 1 can be designed to be larger, and the size of its first transmission shaft 11 can also be larger, and the strength of the first transmission shaft 11 can also be greater.

[0045] By setting up a wiring channel 3, which extends along the axial direction F1 of the disc motor 200 and sequentially passes through the output shaft, the first drive shaft 11, and the second drive shaft 21, a dedicated wiring path is formed inside the core transmission components of the powertrain 1000. This design directly provides independent internal space for the wiring, without occupying external space, making the wiring of the powertrain 1000 more reasonable, thus making the overall structure of the powertrain 1000 more orderly and its appearance cleaner and more aesthetically pleasing.

[0046] Meanwhile, the speed ratio of the second-stage planetary gear mechanism 2 is the same as that of the first-stage planetary gear mechanism 1. Continuing from the above, the powertrain 1000 is equipped with a wiring channel 3, which extends along the axial direction F1 of the disc motor 200 and sequentially passes through the output shaft, the first drive shaft 11, and the second drive shaft 21. To meet the wiring requirements, the speed ratio of the first-stage planetary gear mechanism 1 is set to be the same as that of the second-stage planetary gear mechanism 2, making it easier to implement the structural design of the first-stage planetary gear mechanism 1 and the second-stage planetary gear mechanism 2.

[0047] Understandably, the formula for calculating the single-stage speed ratio of a planetary gear reducer (taking "fixed ring gear, planetary carrier output" as an example) is: i = 1 + Za / Zs (Za is the number of teeth on the ring gear, and Zs is the number of teeth on the sun gear). A larger speed ratio means a stronger reduction effect (a greater reduction in input speed and a greater amplification of output torque). The total speed ratio of the two-stage reducer is the product of the two-stage speed ratios, itotal = i1 × i2. Continuing from the above, in related technologies, the speed ratio of the first-stage planetary gear mechanism 1 of the reducer 100 is set to be less than the speed ratio of the second-stage planetary gear mechanism 2.

[0048] The higher speed ratio of the second-stage planetary gear mechanism 2 means a higher relative sliding rate during gear meshing (especially in the contact area between the planetary gears and the ring gear), resulting in more significant frictional losses and thus slightly lower efficiency. Conversely, the lower speed ratio of the first-stage planetary gear mechanism 1 leads to a lower relative sliding rate during gear meshing, resulting in higher efficiency. Therefore, the overall efficiency of the reducer 100 is negatively impacted by the second-stage planetary gear mechanism 2, resulting in a lower overall efficiency.

[0049] Setting the speed ratios of the first-stage planetary gear mechanism 1 and the second-stage planetary gear mechanism 2 to be the same ensures a balance between the two speed ratios. This results in a smaller difference in their sliding rates and a more uniform distribution of frictional losses, thereby improving the overall efficiency of the reducer 100. Especially under high-speed conditions, the balanced speed ratios can reduce efficiency degradation caused by excessive load on a single stage.

[0050] Furthermore, the radial dimension of planetary gears (especially the diameter of the gear ring) is positively correlated with the speed ratio. The speed ratio of the second-stage planetary gear mechanism 2 is larger, therefore the diameter of the gear ring of the second-stage planetary gear mechanism 2 is larger than that of the first-stage planetary gear mechanism 1. This results in a significant difference in the radial dimensions between the first-stage planetary gear mechanism 1 and the second-stage planetary gear mechanism 2, but the uneven radial dimensions may increase the overall assembly difficulty.

[0051] The first-stage planetary gear mechanism 1 and the second-stage planetary gear mechanism 2 have the same speed ratio, and their inner ring diameters are similar, resulting in a more symmetrical structure. Components such as the housing and planetary carrier can be designed using a standardized approach, reducing manufacturing complexity. This leads to a more balanced overall radial dimension, making it suitable for scenarios with high requirements for spatial symmetry.

[0052] Furthermore, gear noise is related to the meshing frequency; frequencies that are too high or too low can exacerbate the noise, and a significant difference in vibration frequencies between the two stages increases the risk of resonance. The first-stage planetary gear mechanism 1 has a higher output speed, while the second-stage planetary gear mechanism 2 has an even higher meshing frequency, generating high-frequency noise. Moreover, a significant difference in vibration frequencies between the first-stage and second-stage planetary gear mechanisms increases the risk of resonance, further amplifying the noise.

[0053] Setting the speed ratio of the first-stage planetary gear mechanism 1 and the second-stage planetary gear mechanism 2 to be the same results in a balanced rotational speed distribution, similar meshing frequencies, more consistent vibration characteristics, and lower noise. Furthermore, the almost identical vibration frequencies of the first-stage and second-stage planetary gear mechanisms reduce the risk of resonance, further minimizing noise risk.

[0054] In one embodiment, the wire passage 3 includes a first wire passage hole 31 located in the first drive shaft 11 and a second wire passage hole 32 located in the second drive shaft 21. That is, the first drive shaft 11 and the second drive shaft 21 are respectively provided with the first wire passage hole 31 and the second wire passage hole 32, thereby forming the wire passage 3.

[0055] Furthermore, the diameter of the first wire-passing hole 31 is equal to the diameter of the second wire-passing hole 32. Continuing from the above, the speed ratios of the first-stage planetary gear mechanism 1 and the second-stage planetary gear mechanism 2 are set to be the same, and their structural differences are smaller. Therefore, the first transmission shaft 11 and the second transmission shaft 21 can be set to have the same radial dimension. Simultaneously, the diameter of the first wire-passing hole 31 is set to be equal to the diameter of the second wire-passing hole 32.

[0056] The first wire guide hole 31 and the second wire guide hole 32 have the same diameter, which means that when the wire enters the second drive shaft 21 from the first drive shaft 11, the cross-sectional dimensions of the wire guide channel 3 remain consistent, and there is no "step" or "narrow opening" caused by abrupt changes in diameter. This "equal diameter transition" design can prevent the wire from getting stuck, squeezed, or rubbing at the junction of the two drive shafts due to sudden changes in space, reduce the risk of wire wear, and ensure the smoothness of the wiring process.

[0057] Meanwhile, the first drive shaft 11 and the second drive shaft 21 are both core components of the reducer 100, and they must maintain a coaxial axis to ensure transmission stability. If the diameters of the first wire guide hole 31 and the second wire guide hole 32 are different, different hole machining parameters need to be designed for the two drive shafts, which will increase the machining complexity and precision control difficulty of the parts. However, if the diameters of the first wire guide hole 31 and the second wire guide hole 32 are the same, the first wire guide hole 31 and the second wire guide hole 32 can adopt a unified machining standard, reduce the manufacturing process difficulty, reduce machining errors caused by parameter differences, and facilitate standardized management during mass production, thereby improving production efficiency.

[0058] In one embodiment, the wire passage 3 is arranged with the first drive shaft 11 and the second drive shaft 21 sharing the same central axis.

[0059] As mentioned above, the first driveshaft 11 and the second driveshaft 21, as core transmission components of the powertrain 1000, have their central axes serving as the baseline for the entire power transmission and representing the areas where structural strength is most easily guaranteed. The wiring channel 3 shares a central axis with both drives, meaning it directly utilizes the central hollow area of ​​the transmission components, eliminating the need for additional wiring paths on the outer periphery or non-core areas of the components. This integration of transmission and wiring functions on the same central axis achieves efficient space reuse, without occupying external space of the powertrain 1000 or affecting the external structure of the transmission components.

[0060] Meanwhile, the coaxiality of the first drive shaft 11 and the second drive shaft 21 is fundamental to ensuring efficient power transmission. The coaxiality of the cable passage 3 means that the location of the passage (the central area of ​​the transmission component) has minimal impact on the structural strength of the transmission component (the central area is far from the outer periphery where torque is applied), reducing the weakening of the transmission component's strength due to openings and ensuring the stability of power transmission.

[0061] Furthermore, relying on the coaxial transmission components, the routing of the wiring channel 3 is completely consistent with the overall layout of the powertrain 1000. The extension path of the wiring inside the reducer 100 is synchronized with the power transmission direction, avoiding spatial interference between the wiring and other components, and further ensuring the safety of the wiring.

[0062] In one embodiment, the reducer 100 further includes a reducer housing 4, which is arranged around the outer periphery of the primary planetary gear mechanism 1 and the secondary planetary gear mechanism 2.

[0063] The first-stage planetary gear mechanism 1 also includes a first sun gear 12, multiple first planet gears 13, a first planet carrier 14, and a first internal gear ring 15. The first internal gear ring 15 is fixedly disposed on the inner wall of the reducer housing 4. The first sun gear 12 is sleeved on the first transmission shaft 11 and rotates coaxially with the first transmission shaft 11. The multiple first planet gears 13 are evenly distributed along the circumference of the first transmission shaft 11.

[0064] The first planetary gear 13 meshes with the first sun gear 12 and the first internal gear ring 15, so that when the first sun gear 12 rotates with the first drive shaft 11, the first planetary gear 13 can rotate along its own axis and around the central axis of the first sun gear 12. The first planet carrier 14 is connected to a plurality of first planetary gears 13 for rotating along the central axis of the first sun gear 12. The second drive shaft 21 is drive-connected to the first planet carrier 14.

[0065] Specifically, the first planetary carrier 14 is located at the end of the first drive shaft 11 away from the disc motor 200, and the first planetary carrier 14 has a first side facing away from the first drive shaft 11. The second drive shaft 21 protrudes from the first side.

[0066] The secondary planetary gear mechanism 2 also includes a second sun gear 22, multiple second planet gears 23, a second planet carrier 24, and a second internal gear ring 25. The second internal gear ring 25 is fixedly disposed on the inner wall of the reducer housing 4. The second sun gear 22 is sleeved on the second transmission shaft 21 and rotates coaxially with the second transmission shaft 21. The multiple second planet gears 23 are evenly distributed along the circumference of the second transmission shaft 21.

[0067] The second planetary gear 23 meshes with the second sun gear 22 and the second internal gear ring 25, so that when the second sun gear 22 rotates with the second drive shaft 21, the second planetary gear 23 can rotate along its own axis and around the central axis of the second sun gear 22. The second planetary carrier 24 is connected to multiple second planetary gears 23 for rotating along the central axis of the second sun gear 22. The second planetary carrier 24 is connected to an external load drive.

[0068] In this embodiment, the output shaft drives the first transmission shaft 11 to rotate, and the first sun gear 12 rotates coaxially with the first transmission shaft 11. Since the first internal gear ring 15 is fixed to the inner wall of the reducer housing 4, the first planetary gear 13, which meshes with the first internal gear ring 15 and the first sun gear 12, can rotate not only along its own axis but also around the central axis of the first transmission shaft 11. At this time, the multiple first planetary gears 13 can drive the first planet carrier 14 to rotate along the central axis of the first transmission shaft 11.

[0069] Simultaneously, the first planetary carrier 14 drives the second drive shaft 21 to rotate, and the second sun gear 22 rotates coaxially with the first drive shaft 11. Since the second internal gear ring 25 is fixed to the inner wall of the reducer housing 4, the second planetary gears 23, meshing with the second internal gear ring 25 and the second sun gear 22, can rotate not only along their own axis but also around the central axis of the second drive shaft 21. At this time, the multiple second planetary gears 23 can drive the second planetary carrier 24 to rotate along the central axis of the second drive shaft 21. The second planetary carrier 24 can provide power to the external load.

[0070] Therefore, it can be seen that the first drive shaft 11 and the output shaft have the same rotational speed. The rotational speed of the second drive shaft 21 is less than that of the first drive shaft 11. That is to say, the rotational speeds of the first drive shaft 11 and the second drive shaft 21 are different. This difference in rotational speed ensures that the two-stage planetary gear mechanism independently completes its respective speed ratio transmission function, avoiding power superposition conflicts or transmission interference caused by speed synchronization, ensuring a stable output of the total speed ratio (first-stage speed ratio × second-stage speed ratio), and thus ensuring the reliable realization of high torque requirements.

[0071] Meanwhile, the different rotational speeds mean that the motion states of the two-stage mechanisms are separated, which can reduce resonance or additional frictional losses caused by motion synchronization and improve overall transmission efficiency. Furthermore, by reserving an axial clearance F1 to alleviate structural interference, the structural reliability, adaptability, and service life of the reducer 100 are further improved while ensuring transmission efficiency and high torque output.

[0072] In one embodiment, the first internal gear ring 15 of the first-stage planetary gear mechanism 1 is the same as and integrally formed with the second internal gear ring 25 of the second-stage planetary gear mechanism 2 to form an integrally formed gear ring, and a hollow structure is provided in a local position of the gear ring.

[0073] As mentioned above, the reducer 100 has a two-stage structure. If the first internal gear ring 15 and the second internal gear ring 25 are separate components, an assembly gap or connecting structure needs to be reserved between them, which would increase the axial F1 or radial dimensions of the reducer 100. However, by integrating the first internal gear ring 15 and the second internal gear ring 25 into a single component, the gap and additional connecting space of the separate structure are directly eliminated, significantly reducing the overall volume of the reducer 100.

[0074] Meanwhile, the integrated design ensures that the axes of the first internal gear ring 15 and the second internal gear ring 25 are perfectly aligned, resulting in precise meshing and reducing impact and wear during gear meshing. This also strengthens the overall structure, allowing for more even load distribution, improving the gear ring's resistance to deformation, and ensuring the stability and reliability of power transmission in the reducer 100.

[0075] Furthermore, the first internal gear ring 15 is identical to the second internal gear ring 25, meaning that their parameters are unified. This further simplifies the overall gear ring structure design and avoids space waste caused by parameter differences. This design makes the internal structure of the reducer 100 more compact, perfectly meeting the core requirement of miniaturization of the powertrain 1000.

[0076] Without compromising its core load-bearing capacity, the design of a partially hollowed-out structure on the gear ring reduces the amount of material used. This not only lowers the overall weight of the reducer 100, improving the energy utilization efficiency of the powertrain 1000, but also reduces manufacturing costs while maintaining structural strength. Simultaneously, the hollowed-out structure increases the contact area between the gear ring and the air, promoting heat dissipation from the reducer 100 through air convection and preventing overheating from affecting gear life or transmission efficiency.

[0077] Specifically, a groove 5 is provided on the inner side of the gear ring. The groove 5 extends along the circumference of the gear ring and is located on the axial direction F1 of the reducer 100 between the first planetary gear 13 of the first-stage planetary gear mechanism 1 and the second planetary gear 23 of the second-stage planetary gear mechanism 2.

[0078] The groove 5 is designed to eliminate redundant material between the first planetary gear 13 and the second planetary gear 23 without affecting the overall strength of the gear ring, further reducing the weight of the gear ring. This lightweight design reduces the rotational inertia of the gear ring, decreases inertial losses during power output, and improves the dynamic response speed of the reducer 100.

[0079] Furthermore, the groove 5 increases the surface area of ​​the inner side of the gear ring, and the annular structure can form an air convection channel, which helps to conduct the heat generated by the first planetary gear 13 and the second planetary gear 23 meshing with it to the outside through the gear ring, or cooperate with the overall heat dissipation system of the reducer 100 to accelerate heat dissipation.

[0080] Meanwhile, the groove 5 extends circumferentially along the gear ring, forming an annular oil storage space, which facilitates the circulation of lubricating oil inside the gear ring. When the reducer 100 is running, the meshing of the gear ring and the planetary gears will drive the lubricating oil into the groove 5, and then the lubricating oil will be evenly distributed to the meshing surfaces of the first planetary gear 13 and the second planetary gear 23 with the gear ring through centrifugal force or gravity, ensuring sufficient lubrication of key transmission parts.

[0081] By placing the groove 5 between the first planetary gear 13 and the second planetary gear 23, a physical separation is formed in the axial direction F1. This effectively prevents the two planetary gears from contacting and rubbing due to assembly errors, axial movement in the F1 direction, or vibration during high-speed operation, thus completely eliminating the risk of transmission interference. For a first-stage planetary gear mechanism 1 and a second-stage planetary gear mechanism 2 with the same speed ratio, the motion states of the two planetary gears may differ. The separation effect of the groove 5 ensures that they operate independently, reducing power loss or component wear caused by mutual interference.

[0082] In one embodiment, the thickness of the first-stage planetary gear mechanism 1 is less than the thickness of the second-stage planetary gear mechanism 2 along the axial direction F1 of the reducer 100.

[0083] During power transmission, torque is amplified step by step along the transmission path. For example, the initial torque output from the disc motor 200 is received by the first-stage planetary gear mechanism 1. After the first-stage transmission, the torque increases and is then transmitted to the second-stage planetary gear mechanism 2. In other words, the second-stage planetary gear mechanism 2 needs to withstand a greater torque than the first-stage planetary gear mechanism 1. This can be achieved by making the thickness of the second-stage planetary gear mechanism 2 greater than that of the first-stage planetary gear mechanism 1, thereby enhancing its load-bearing capacity. For example, the axial F1 dimension of components such as the planet carrier and bearings can be increased to improve the rigidity of the support structure, preventing deformation or vibration under high torque conditions and ensuring transmission stability.

[0084] Meanwhile, the primary planetary gear mechanism 1 has a smaller thickness, which reduces the space it occupies in the axial direction F1, and avoids the overall length of the reducer 100 from being excessively increased due to its location on the outside of the motor, thus ensuring a compact layout of the powertrain 1000.

[0085] 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 concept of the present utility model and using the contents of the present utility model specification and drawings, or direct / indirect applications in other related technical fields, are included in the patent protection scope of the present utility model.

Claims

1. A reducer integrated in a disc motor, characterized by, The speed reducer is located on the outside of the disc motor, and the speed reducer includes: A primary planetary gear mechanism, having a first drive shaft for drive connection with the output shaft of the disc motor; and, The second-stage planetary gear mechanism has a second drive shaft for transmission connection with the first-stage planetary gear mechanism. The second drive shaft is arranged with the first drive shaft and the output shaft sharing a common central axis. The speed ratio of the second-stage planetary gear mechanism is the same as that of the first-stage planetary gear mechanism. The reducer also includes a wire passage that extends along the axial direction of the disc motor and passes through the first drive shaft and the second drive shaft in sequence.

2. The integrated disc motor reducer of claim 1, wherein, The reducer also includes a reducer housing, which is arranged around the outer periphery of the first-stage planetary gear mechanism and the second-stage planetary gear mechanism; The primary planetary gear mechanism further includes a first sun gear, a plurality of first planet gears, a first planet carrier, and a first internal gear ring. The first internal gear ring is fixedly disposed on the inner wall of the reducer housing. The first sun gear is sleeved on the first transmission shaft and rotates coaxially with the first transmission shaft. The plurality of first planet gears are evenly distributed along the circumference of the first transmission shaft. The first planet gears mesh with the first sun gear and the first internal gear ring so that when the first sun gear rotates with the first transmission shaft, the first planet gears can rotate along their own axis and around the central axis of the first sun gear. The first planet carrier is connected to the plurality of first planet gears and is used to rotate along the central axis of the first sun gear. The second drive shaft is connected to the first planetary carrier via a drive mechanism.

3. The integrated disc motor reducer of claim 2, wherein, The first planetary carrier is located at the end of the first drive shaft away from the disc motor, and the first planetary carrier has a first side facing away from the first drive shaft. The second drive shaft protrudes from the first side.

4. The integrated disc motor reducer of claim 3, wherein, The first drive shaft and the second drive shaft rotate at different speeds, and a gap is formed between the first drive shaft and the first planetary carrier in the axial direction of the reducer.

5. The integrated disc motor reducer of claim 1, wherein, The reducer also includes a reducer housing, which is arranged around the outer periphery of the first-stage planetary gear mechanism and the second-stage planetary gear mechanism; The secondary planetary gear mechanism further includes a second sun gear, multiple second planet gears, a second planet carrier, and a second internal gear ring. The second internal gear ring is fixed to the inner wall of the reducer housing. The second sun gear is sleeved on the second transmission shaft and rotates coaxially with the second transmission shaft. Multiple second planet gears are evenly distributed along the circumference of the second transmission shaft. The second planet gears mesh with the second sun gear and the second internal gear ring so that when the second sun gear rotates with the second transmission shaft, the second planet gears can rotate along their own axis and around the central axis of the second sun gear. The second planet carrier is connected to multiple second planet gears and is used to rotate around the central axis of the second sun gear. The second planetary carrier is connected to an external load drive.

6. The reduction gear integrated in the disc-type motor according to claim 2 or 5, characterized in that, The first internal gear ring of the primary planetary gear mechanism is the same as the second internal gear ring of the secondary planetary gear mechanism and is integrally formed to create a gear ring that is integrally set. The gear ring has a hollow structure in some parts.

7. The integrated disc motor reducer of claim 6, wherein, A groove is provided around the inner side of the gear ring, the groove extends circumferentially along the gear ring, and is located in the axial direction of the reducer between the first planetary gear of the first-stage planetary gear mechanism and the second planetary gear of the second-stage planetary gear mechanism; The hollow structure includes the groove.

8. The integrated disc motor reducer of claim 1, wherein, In the axial direction of the reducer, the thickness of the first-stage planetary gear mechanism is less than the thickness of the second-stage planetary gear mechanism.

9. The integrated disc motor reducer of claim 1, wherein, The wire passage includes a first wire passage hole located inside the first drive shaft and a second wire passage hole located inside the second drive shaft, wherein the diameter of the first wire passage hole is equal to the diameter of the second wire passage hole.

10. The integrated disc motor reducer of claim 1, wherein, The cable passage is arranged with the first drive shaft and the second drive shaft sharing the same central axis.

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