A high speed ratio and high torque travel reducer

Abstract

This utility model discloses a high-ratio, high-torque travel reducer, relating to the field of mechanical transmission technology. It includes an input end cover and input shaft, an output shaft disc, and a three-stage reduction mechanism. The three-stage reduction mechanism comprises a three-stage sun gear, a three-stage planetary gear, a three-stage planetary carrier, a three-stage gear ring, and a two-stage sun gear. The advantages of this utility model are: the reducer has a three-stage reduction mechanism, resulting in a larger reduction ratio, higher output torque, shorter axial dimension, and stronger load-bearing capacity compared to traditional two-stage hub reducers. During operation, the reducer's output component is a sleeve-structured first-stage gear ring, allowing the AGV cart wheels to directly utilize the reducer's internal support. This simplifies the AGV cart structure, enhances its load-bearing capacity, and reduces the space occupied by the reducer, thus meeting assembly requirements even when AGV cart space is limited.

Description

Technical Field

[0001] This utility model relates to the field of mechanical transmission technology, specifically to a high speed ratio and high torque travel reducer. Background Technology

[0002] The main function of AGVs in industrial applications is to realize unmanned and automated handling of logistics transfers, so as to reduce production costs and improve industrial economic efficiency, and to automate the entire process of loading, unloading and handling of goods and materials.

[0003] With the continuous development of industry, AGVs are now required to be smaller in size while meeting the requirements of load-bearing capacity, and the size of the reducer is also required to be shorter.

[0004] Traditional AGV reducers use concentric planetary reducers, where the motor, reducer, and wheel hub are all on the same axis, and the wheel hub requires a separate support structure, resulting in a relatively long axial dimension. In addition, AGVs use a dual-drive structure, so the width of the AGV must be at least greater than the width of two motors, two reducers, and two wheels, making it difficult to keep the width short. Utility Model Content

[0005] In view of this, the main purpose of this utility model is to propose a high speed ratio and high torque travel reducer, which is used to reduce and improve the axial dimension of the reducer, improve its reduction ratio, output torque and load-bearing capacity, so as to meet the small size and high load-bearing requirements of AGV trolleys.

[0006] To achieve the above objectives, this utility model proposes a high speed ratio and high torque travel reducer, comprising: an input end cover and an input shaft, an output shaft disc, and a three-stage reduction mechanism;

[0007] The three-stage reduction mechanism includes a three-stage sun gear, a three-stage planet gear, a three-stage planet carrier, a three-stage gear ring, a two-stage sun gear, a two-stage planet gear, a two-stage planet carrier, a two-stage gear ring, a one-stage sun gear, a one-stage planet gear, and a one-stage gear ring;

[0008] The input end cover, output shaft disk, secondary gear ring, and tertiary gear ring are fixedly connected in sequence;

[0009] The input shaft is rotatably mounted inside the input end cover. The input shaft is coaxially connected to the third-stage sun gear so that the two rotate synchronously. The third-stage sun gear is located inside the third-stage gear ring. The third-stage planet gears mesh with both the third-stage sun gear and the third-stage gear ring. The third-stage planet gears are connected to the third-stage planet carrier via a third-stage pin.

[0010] The third-stage planetary carrier is fixedly connected to the second-stage sun gear; the second-stage sun gear is located inside the second-stage gear ring, and the second-stage planetary gear meshes with both the second-stage sun gear and the second-stage gear ring. The second-stage planetary gear is connected to the second-stage planetary carrier through the second-stage pin.

[0011] The secondary planetary carrier is fixedly connected to the primary sun gear, which is located inside the primary gear ring. The input end cover is rotatably inserted into the end of the primary gear ring on the side near the primary gear ring. The primary planetary gear meshes with both the primary sun gear and the primary gear ring. The primary planetary gear is rotatably connected to the output shaft disk via a primary pin.

[0012] Furthermore, it also includes an output end cap, which is fixedly connected to the end of the third gear ring by a second internal hexagon head screw.

[0013] Furthermore, it also includes a first bearing mounting hole on the input end cover, wherein the input shaft is mounted in the first bearing mounting hole by a first single-row deep groove ball bearing.

[0014] Furthermore, the output end cover is provided with a second bearing mounting hole, the input shaft is provided with an axial mounting inner hole, the third-stage sun gear is provided with a third-stage sun gear shaft, one end of the third-stage sun gear shaft is press-fitted into the mounting inner hole of the input shaft, so that the two rotate synchronously, and the other end of the third-stage sun gear shaft is rotatably mounted in the second bearing mounting hole through a second single-row deep groove ball bearing.

[0015] Furthermore, both the third-stage and second-stage planetary carriers are provided with mounting bores. The second-stage sun gear is press-fitted into the bore of the third-stage planetary carrier, and the second-stage sun gear is coaxially arranged with the third-stage planetary carrier. The first-stage sun gear is press-fitted into the bore of the second-stage planetary carrier, and the first-stage sun gear is coaxially arranged with the second-stage planetary carrier.

[0016] Furthermore, the width of the third-order planetary gear is smaller than the width of the second-order planetary gear, the width of the third-order sun gear is smaller than the width of the second-order sun gear, the width of the second-order planetary gear is smaller than the width of the first-order planetary gear, and the width of the second-order sun gear is smaller than the width of the first-order sun gear.

[0017] Furthermore, the output shaft disc is provided with three primary pin holes, each containing a primary pin shaft. The primary pin shaft and the primary pin hole are interference-fitted, and the primary planetary gear is rotated on the primary pin shaft.

[0018] Furthermore, the third-stage gear ring and the outer wall of the input end cover are respectively provided with seventh and eighth single-row deep groove ball bearings, and the outer rings of the seventh and eighth single-row deep groove ball bearings are both provided on the inner wall of the first-stage gear ring.

[0019] Furthermore, the input end cover and the output shaft disc are connected by a third internal hexagon head screw.

[0020] Furthermore, the third-stage gear ring, the second-stage gear ring, and the output shaft disc are locked and fixed by the first internal hexagonal head screw.

[0021] The advantages of this high-ratio, high-torque travel reducer are:

[0022] (1) The reducer has a three-stage reduction mechanism, which has a larger reduction ratio, greater output torque, shorter axial dimension, and stronger load-bearing capacity than the traditional two-stage hub reducer;

[0023] (2) When the reducer is working, its reduction output component is a first-stage gear ring with a sleeve structure. The AGV trolley wheels can be directly fitted onto the first-stage gear ring. This allows the AGV trolley wheels to directly utilize the internal support of the reducer, which simplifies the AGV trolley structure, enhances the AGV trolley's load-bearing capacity, and reduces the space occupied by the reducer. Even when the AGV trolley space is limited, it can still meet the assembly requirements.

[0024] (3) When the reducer is installed on the AGV trolley, it can ensure that the motor, reducer and hub center are on the same axis. It has a simple structure, short axial dimension, few types of parts, convenient assembly and low production cost. Attached Figure Description

[0025] 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.

[0026] Figure 1 A cross-sectional view of a high-ratio, high-torque travel reducer provided by this utility model;

[0027] Among them, 1-elastic retaining ring for the hole, 2-first single-row deep groove ball bearing, 3-elastic retaining ring for the shaft, 4-eighth single-row deep groove ball bearing, 5-first planetary gear washer, 6-first-stage needle roller bearing, 7-first-stage pin, 8-first-stage planetary gear, 9-first hexagon socket head cap screw, 10-second planetary gear washer, 11-second-stage needle roller bearing, 12-second-stage planetary gear, 13-second-stage pin, 14-third planetary gear washer, 15-third-stage needle roller bearing, 16-third-stage pin, 17-third-stage planetary gear, 18-third single-row deep groove ball bearing, 19-third-stage... 20-Second single-row deep groove ball bearing, 21-Output end cover, 22-Second internal hex socket head cap screw, 23-Third-stage planetary carrier, 24-Seventh single-row deep groove ball bearing, 25-Third-stage gear ring, 26-Fifth single-row deep groove ball bearing, 27-Fourth single-row deep groove ball bearing, 28-Second-stage planetary carrier, 29-Second-stage gear ring, 30-Second-stage sun gear, 31-Output shaft disc, 32-Sixth single-row deep groove ball bearing, 33-First-stage sun gear, 34-First-stage gear ring, 35-Input shaft, 36-Third internal hex socket head cap screw, 37-Input end cover. 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] Please see Figure 1A high-speed-ratio, high-torque travel reducer includes: an input end cover 37 and an input shaft 35, an output shaft disc 31, and a three-stage reduction mechanism.

[0032] The three-stage reduction mechanism includes a third-stage sun gear 19, a third-stage planetary gear 17, a third-stage planetary carrier 23, a third-stage ring gear 25, a second-stage sun gear 30, a second-stage planetary gear 12, a second-stage planetary carrier 28, a second-stage ring gear 29, a first-stage sun gear 33, a first-stage planetary gear 8, and a first-stage ring gear 34; the input end cover 37, the output shaft disk 31, the second-stage ring gear 29, and the third-stage ring gear 25 are sequentially and fixedly connected; the input shaft 35 is rotatably disposed within the input end cover 37, and the input shaft 35 is coaxially connected to the third-stage sun gear 19 so that the two rotate synchronously; the third-stage sun gear 19 is located within the third-stage ring gear 25, and the third-stage... The planetary gear 17 meshes with the third-stage sun gear 19 and the third-stage ring gear 25 simultaneously; the third-stage planetary gear 17 is connected to the third-stage planetary carrier 23 via a third-stage pin 16; specifically, the opening portion of the third-stage planetary carrier 23 is provided with three third-stage pin holes perpendicular to the left end face of the planetary carrier along the circumferential direction, and the third-stage pin 16 is installed in these pin holes. The third-stage pin 16 and the third-stage pin holes are interference fit. The third-stage needle roller bearing 15 and the third-stage planetary gear 17 are sequentially mounted on the third-stage pin 16. The third-stage planetary gear 17 and the third-stage sun gear 19 are external meshing gear drives, and the third-stage planetary gear 17 and the third-stage ring gear 25 are internal meshing gear drives.

[0033] The third-stage planetary carrier 23 is fixedly connected to the second-stage sun gear 30. The second-stage sun gear 30 is located inside the second-stage gear ring 29. The second-stage planetary gear 12 meshes with both the second-stage sun gear 30 and the second-stage gear ring 29. The second-stage planetary gear 12 is connected to the second-stage planetary carrier 28 via a second-stage pin 13. Specifically, the opening portion of the second-stage planetary carrier 28 has three second-stage pin holes perpendicular to the left end face of the planetary carrier along the circumferential direction. The second-stage pin 13 is installed in these pin holes. The second-stage pin 13 and the second-stage pin holes are interference-fitted. The second-stage needle roller bearing 11 and the second-stage planetary gear 12 are sequentially mounted on the second-stage pin 13. The second-stage planetary gear 12 and the second-stage sun gear 30 are externally meshing gears, and the second-stage planetary gear 12 and the second-stage gear ring 29 are internally meshing gears.

[0034] The secondary planetary carrier 28 is fixedly connected to the primary sun gear 33, which is located inside the primary gear ring 34. The input end cover 37 is rotatably inserted into the end of the primary gear ring 34 near its side. The primary planetary gear 8 meshes with both the primary sun gear 33 and the primary gear ring 34. The primary planetary gear 8 is rotatably connected to the output shaft disk 31 via a primary pin 7. Specifically, the output shaft disk 31 has three primary pin holes, each housing a primary pin 7. The primary pin 7 and the primary pin hole are interference-fitted, and the primary planetary gear 8 is rotatably mounted on the primary pin 7. That is, the open portion of the output shaft disk 31 has three primary pin holes perpendicular to the right end face of the disk along the circumferential direction. The primary pin 7 is installed in each primary pin hole, and a primary needle roller bearing 6 and a primary planetary gear 8 are sequentially mounted on the primary pin 7. The primary planetary gear 8 and the primary sun gear 33 are externally meshed gears, and the primary planetary gear 8 and the primary gear ring 34 are internally meshed gears.

[0035] In a preferred embodiment, an output end cap 21 is further included, which is fixedly connected to the end of the third-stage gear ring 25 by a second hexagon socket head cap screw 22. A third single-row deep groove ball bearing 18 is also provided between the third-stage planetary carrier 23 and the output end cap 21. A fourth single-row deep groove ball bearing 27 and a fifth single-row deep groove ball bearing 26 are respectively provided on the inner and outer rings on the left side of the second-stage planetary carrier 28, which are used to rotatably support the second-stage planetary carrier 28. A sixth single-row deep groove ball bearing 32 is provided on the outer ring on the right side of the second-stage planetary carrier 28, which rotatably supports the second-stage planetary carrier 28 and the output shaft disk 31.

[0036] In a preferred embodiment, the first bearing mounting hole on the input end cover 37 is also included. The input shaft 35 is installed in the first bearing mounting hole through the first single-row deep groove ball bearing 2. The first single-row deep groove ball bearing 2 is provided with a hole elastic retaining ring 1 and a shaft elastic retaining ring 3 on both sides, and the hole elastic retaining ring 1 and the shaft elastic retaining ring 3 limit the first single-row deep groove ball bearing 2.

[0037] The first-stage planetary gear 8, the second-stage planetary gear 12, and the third-stage planetary gear 17 are respectively provided with a first planetary gear washer 5, a second planetary gear washer 10, and a third planetary gear washer 14 at both ends.

[0038] In a preferred embodiment, the output end cover 21 is provided with a second bearing mounting hole, the input shaft 35 is provided with an axial mounting inner hole, the third-stage sun gear 19 is provided with a third-stage sun gear shaft, one end of the third-stage sun gear shaft is press-fitted into the mounting inner hole of the input shaft 35 so that the two rotate synchronously, and the other end of the third-stage sun gear shaft is rotatably mounted in the second bearing mounting hole through a second single-row deep groove ball bearing 20.

[0039] In a preferred embodiment, both the third-stage planetary carrier 23 and the second-stage planetary carrier 28 are provided with mounting inner holes. The second-stage sun gear 30 is press-fitted into the inner hole of the third-stage planetary carrier 23, and the second-stage sun gear 30 is coaxially arranged with the third-stage planetary carrier 23. The first-stage sun gear 33 is press-fitted into the inner hole of the second-stage planetary carrier 28, and the first-stage sun gear 33 is coaxially arranged with the second-stage planetary carrier 28.

[0040] In a preferred embodiment, the width of the third-stage planetary gear 17 is less than the width of the second-stage planetary gear 12, the width of the third-stage sun gear 19 is less than the width of the second-stage sun gear 30, the width of the second-stage planetary gear 12 is less than the width of the first-stage planetary gear 8, and the width of the second-stage sun gear 30 is less than the width of the first-stage sun gear 33.

[0041] In a preferred embodiment, a seventh single-row deep groove ball bearing 24 and an eighth single-row deep groove ball bearing 4 are respectively provided on the outer walls of the third-stage gear ring 25 and the input end cover 37. The outer rings of the seventh single-row deep groove ball bearing 24 and the eighth single-row deep groove ball bearing 4 are both provided on the inner wall of the first-stage gear ring 34. This not only improves the load-bearing capacity of the reducer, but also shortens the axial dimension of the reducer.

[0042] In a preferred embodiment, the input end cover 37 and the output shaft disk 31 are connected by a third hexagon socket head cap screw 36. That is, the input end cover 37, the output shaft disk 31, the secondary gear ring, the tertiary gear ring, and the output end cover are combined into a whole, and this whole part is fixed when the reducer is working.

[0043] In a preferred embodiment, the third-stage gear ring 25, the second-stage gear ring 29, and the output shaft disc 31 are locked and fixed by the first internal hexagonal head screw 9.

[0044] Working principle: During operation, the motor drives the input shaft 35 to rotate. The rotation of the input shaft 35 drives the third-stage sun gear 19 to rotate. The third-stage sun gear 19 drives the third-stage planetary gear 17 to rotate on the third-stage pin 16 through external meshing. The third-stage pin 16 drives the third-stage planetary carrier 23 to rotate. The rotation of the third-stage planetary carrier 23 drives the second-stage sun gear 30 to rotate. The second-stage sun gear 30 drives the second-stage planetary gear 12 to rotate on the second-stage pin 13 through external meshing. The second-stage pin 13 drives the second-stage planetary carrier 28 to rotate. The rotation of the second-stage planetary carrier 28 drives the first-stage sun gear 33 to rotate. The first-stage sun gear 33 drives the first-stage planetary gear 8 to rotate on the first-stage pin 7 through external meshing. Since the output shaft disk 31 is fixed, the first-stage planetary gear 8 rotates around its axis. At the same time, the first-stage planetary gear 8 and the first-stage ring gear 34 rotate through internal meshing. That is, the input shaft 35 is the input, and the first-stage ring gear 34 is the output.

[0045] Understandably, when using this high-ratio, high-torque travel reducer, the wheels of the AGV can be directly fitted and fixed to the outer wall of the first-stage gear ring 34. This allows the AGV wheels to directly utilize the internal support of the reducer, simplifying the AGV structure, enhancing its load-bearing capacity, and reducing the space occupied by the reducer. Even with limited space in the AGV, assembly requirements can still be met. When installed on the AGV, the motor shaft is connected to the reducer's input shaft 35, ensuring that the motor, reducer, and wheel hub centers are on the same axis. This results in a simple structure, short axial dimension, fewer parts, convenient assembly, and low production cost.

[0046] 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. A large speed ratio large torque walking reduction machine, characterized by, include: Input end cover (37) and input shaft (35), output shaft disk (31) and three-stage reduction mechanism; The three-stage reduction mechanism includes a three-stage sun gear (19), a three-stage planetary gear (17), a three-stage planetary carrier (23), a three-stage ring gear (25), a two-stage sun gear (30), a two-stage planetary gear (12), a two-stage planetary carrier (28), a two-stage ring gear (29), a one-stage sun gear (33), a one-stage planetary gear (8), and a one-stage ring gear (34); the input end cover (37), the output shaft disc (31), the two-stage ring gear (29), and the three-stage ring gear (25) are sequentially fixedly connected; The input shaft (35) is rotatably mounted inside the input end cover (37). The input shaft (35) is coaxially connected to the third-stage sun gear (19) so that the two rotate synchronously. The third-stage sun gear (19) is located inside the third-stage gear ring (25). The third-stage planet gear (17) meshes with both the third-stage sun gear (19) and the third-stage gear ring (25). The third-stage planet gear (17) is connected to the third-stage planet carrier (23) through the third-stage pin (16). The third-stage planetary carrier (23) is fixedly connected to the second-stage sun gear (30); the second-stage sun gear (30) is located inside the second-stage gear ring (29), and the second-stage planetary gear (12) meshes with both the second-stage sun gear (30) and the second-stage gear ring (29); The secondary planetary gear (12) is connected to the secondary planetary carrier (28) via the secondary pin (13); the secondary planetary carrier (28) is fixedly connected to the primary sun gear (33), the primary sun gear (33) is located inside the primary gear ring (34), the input end cover (37) is rotatably inserted into the end of the primary gear ring (34) on the side close to the primary gear ring (34), and the primary planetary gear (8) meshes with both the primary sun gear (33) and the primary gear ring (34); The first-stage planetary gear (8) is rotatably connected to the output shaft disk (31) via a first-stage pin (7).

2. The large speed ratio large torque walking reduction machine according to claim 1, wherein It also includes an output end cap (21), which is fixedly connected to the end of the third gear ring (25) by a second internal hexagonal head screw (22).

3. The large speed ratio, large torque walking reduction machine of claim 1, wherein It also includes a first bearing mounting hole on the input end cover (37), wherein the input shaft (35) is mounted in the first bearing mounting hole by a first single-row deep groove ball bearing (2).

4. A high-ratio, high-torque travel reducer according to claim 2, characterized in that, The output end cover (21) is provided with a second bearing mounting hole, the input shaft (35) is provided with an axial mounting inner hole, the third-stage sun gear (19) is provided with a third-stage sun gear shaft, one end of the third-stage sun gear shaft is pressed into the mounting inner hole of the input shaft (35) so that the two rotate synchronously, and the other end of the third-stage sun gear shaft is rotatably mounted in the second bearing mounting hole through a second single-row deep groove ball bearing (20).

5. The large speed ratio, large torque walking reduction machine of claim 1, wherein Both the third-stage planetary carrier (23) and the second-stage planetary carrier (28) are provided with mounting inner holes. The second-stage sun gear (30) is press-fitted into the inner hole of the third-stage planetary carrier (23), and the second-stage sun gear (30) is coaxially arranged with the third-stage planetary carrier (23). The first-stage sun gear (33) is press-fitted into the inner hole of the second-stage planetary carrier (28), and the first-stage sun gear (33) is coaxially arranged with the second-stage planetary carrier (28).

6. The large speed ratio, large torque walking reduction machine of claim 1, wherein, The width of the third-level planetary gear (17) is less than the width of the second-level planetary gear (12), the width of the third-level sun gear (19) is less than the width of the second-level sun gear (30), the width of the second-level planetary gear (12) is less than the width of the first-level planetary gear (8), and the width of the second-level sun gear (30) is less than the width of the first-level sun gear (33).

7. The large speed ratio, large torque walking reduction unit of claim 1, wherein, The output shaft disk (31) is provided with three primary pin holes, and a primary pin (7) is installed in each primary pin hole. The primary pin (7) and the primary pin hole are interference fit. The primary planetary gear (8) is rotatably mounted on the primary pin (7).

8. The large speed ratio, large torque walking reduction machine of claim 1, wherein, The outer walls of the third-stage gear ring (25) and the input end cover (37) are respectively provided with a seventh single-row deep groove ball bearing (24) and an eighth single-row deep groove ball bearing (4). The outer rings of the seventh single-row deep groove ball bearing (24) and the eighth single-row deep groove ball bearing (4) are both provided on the inner wall of the first-stage gear ring (34).

9. The large speed ratio, large torque walking reduction unit of claim 1, wherein, The input end cover (37) and the output shaft disk (31) are connected by a third internal hexagonal head screw (36).

10. The large speed ratio, large torque walking reduction unit of claim 1, wherein, The third gear ring (25), the second gear ring (29), and the output shaft disc (31) are locked and fixed by the first internal hexagonal head screw (9).

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