CN210423600U - AGV drive wheel of big moment of big velocity ratio - Google Patents
AGV drive wheel of big moment of big velocity ratio Download PDFInfo
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- CN210423600U CN210423600U CN201921268479.1U CN201921268479U CN210423600U CN 210423600 U CN210423600 U CN 210423600U CN 201921268479 U CN201921268479 U CN 201921268479U CN 210423600 U CN210423600 U CN 210423600U
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Abstract
The utility model discloses an AGV driving wheel with large speed ratio and large torque, which comprises a driving wheel body and a planetary reduction transmission mechanism, wherein the driving wheel body realizes speed reduction and rotation through the planetary reduction transmission mechanism; the planetary reduction transmission mechanism comprises a primary planetary gear assembly, a secondary planetary gear assembly, a tertiary planetary gear assembly and a transmission gear shaft, wherein the primary planetary gear assembly, the secondary planetary gear assembly and the tertiary planetary gear assembly are sequentially arranged side by side; the transmission gear shaft sequentially penetrates through the central axis of the first-stage planetary gear assembly, the second-stage planetary gear assembly and the third-stage planetary gear assembly so that the first-stage planetary gear assembly, the second-stage planetary gear assembly and the third-stage planetary gear assembly can rotate coaxially. The multi-stage planetary gear reducer is compact and simple in structure, the transverse area of the driving wheel is reduced, and the driving wheel becomes ultrathin.
Description
Technical Field
The utility model relates to a AGV drive wheel technical field, concretely relates to is a big moment's of big velocity ratio AGV drive wheel.
Background
The AGV trolley is a transport vehicle which can run along a specified guide path and has the functions of safety protection and various transfer functions, and has the characteristics of high automation degree, safety, flexibility and the like, so the AGV trolley is widely applied to automatic production and storage systems such as automobile manufacturing, machining and the like, and is one of key equipment of modern logistics storage systems such as a flexible manufacturing production line, an automatic stereoscopic warehouse and the like.
The AGV trolley adopts a differential steering driving device to realize steering driving, realizes steering function by utilizing the differential ratio of two motors, but has poor steering effect and steering stability of the differential steering driving device, is easy to break down, and causes complex maintenance and high cost. Therefore, the AGV usually adopts an AGV steering wheel driving device, which is an integrated mechanical structure integrating a driving motor, a steering motor, a speed reducer and the like, and can realize efficient straight-moving and steering movement of the AGV.
The AGV steering wheel driving device generally adopts a driving motor provided with a speed reducer to realize the straight driving of a driving wheel, but the speed reducer externally arranged on the driving wheel increases the occupied space and the overall size of the steering wheel driving device and limits the application range of the AGV driving device. Therefore, a primary planetary gear reducer is arranged inside the driving wheel, the occupied space of the reducer can be greatly reduced, and the AGV driving rudder wheel device is more widely used.
However, the transmission ratio of the first-stage planetary gear reducer is low, when a large reduction ratio is needed, the driving force of the driving motor needs to be increased, but the heat generated in the driving motor is increased, internal components of the motor are easily burnt due to high-temperature overload, and the service life of the motor is greatly reduced. Therefore, the conventional AGV driving wheel needs to be modified and upgraded so as to meet the requirements of large reduction ratio and large torque of the driving wheel in the AGV rudder wheel driving device.
SUMMERY OF THE UTILITY MODEL
In order to overcome the technical defect, the utility model provides a big moment's of big velocity ratio AGV drive wheel, the inside multistage planetary gear reducer that adopts of drive wheel is in order to realize the purpose of big reduction ratio and big moment, and this multistage planetary gear reducer's compact structure is simple, reduces the horizontal area of drive wheel, further makes the drive wheel become more ultra-thin.
In order to solve the above problem, the utility model discloses realize according to following technical scheme:
the utility model relates to a big moment AGV drive wheel of velocity ratio, including drive wheel body and planet speed reduction drive mechanism, the drive wheel body realizes the speed reduction rotation through planet speed reduction drive mechanism;
the planetary reduction transmission mechanism comprises a primary planetary gear assembly, a secondary planetary gear assembly, a tertiary planetary gear assembly and a transmission gear shaft, wherein the primary planetary gear assembly, the secondary planetary gear assembly and the tertiary planetary gear assembly are sequentially arranged side by side;
the transmission gear shaft sequentially penetrates through the central axis of the first-stage planetary gear assembly, the second-stage planetary gear assembly and the third-stage planetary gear assembly so that the first-stage planetary gear assembly, the second-stage planetary gear assembly and the third-stage planetary gear assembly can rotate coaxially.
Furthermore, the primary planetary gear assembly comprises a primary sun gear, a plurality of primary planet pinions and a primary planet carrier, and the teeth number of the primary sun gear is smaller than that of the primary planet pinions;
the primary sun gear is fixedly connected with the transmission gear shaft, and the primary sun gear and the transmission gear shaft are integrally arranged;
primary planet gear shafts which are pivoted with the primary planet pinions are uniformly distributed on the circumference of the primary planet carrier, and the primary planet gear shafts correspond to the primary planet pinions one by one;
the first-stage sun gear is arranged in the middle of the first-stage planet carrier and meshed with the first-stage planet pinions.
Further, the secondary planetary gear assembly comprises a secondary sun gear, a plurality of secondary planet pinions and a secondary planet carrier, and the teeth number of the secondary sun gear is smaller than that of the secondary planet pinions;
the secondary sun gear is sleeved on the transmission gear shaft and is coaxially matched with the primary planet carrier in a transmission manner through a flat key;
secondary planet gear shafts which are pivoted with the secondary planet pinions are uniformly distributed on the secondary planet carrier along the circumference, and the secondary planet gear shafts correspond to the secondary planet pinions one by one;
the second-stage sun gear is arranged in the middle of the second-stage planet carrier and is meshed with the second-stage planet pinions.
Further, the three-stage planetary gear assembly comprises a three-stage sun gear and a plurality of three-stage planetary pinions, and the teeth number of the three-stage sun gear is smaller than that of the three-stage planetary pinions;
the third-stage sun gear is sleeved on the transmission gear shaft and is in coaxial transmission fit with the second-stage planet carrier through a flat key;
each of the three-stage planet pinions surrounds the three-stage sun gear and is meshed with the three-stage sun gear.
Further, the planetary reduction transmission mechanism further comprises a first inner gear ring and a rotating main shaft;
the first inner gear ring is sleeved on the peripheries of the primary planetary gear assembly and the secondary planetary gear assembly, and the inner teeth of the first inner gear ring are meshed with the primary planetary pinions and the secondary planetary pinions;
the rotating main shaft is hollow, one end of the rotating main shaft is fixedly connected with a first inner gear ring, and the rotating main shaft is sleeved on the periphery of the three-stage planetary gear assembly.
Furthermore, a plurality of slotted holes are formed in the curved surface of the rotating main shaft, and the slotted holes correspond to the three-stage planet pinions one by one;
the three-stage planet pinion is rotatably embedded in the groove hole, and part of gear teeth of the three-stage planet pinion are exposed out of the outer surface of the rotating main shaft.
Furthermore, the planetary reduction transmission mechanism also comprises a second inner gear ring which is sleeved at one end of the rotating main shaft, which is far away from the first inner gear ring;
the inner teeth of the second inner gear ring are meshed with the three-stage planet pinions, and the driving wheel body is sleeved on the outer surface of the second inner gear ring.
Furthermore, a plurality of deep groove ball bearings are arranged between the rotating main shaft and the second inner gear ring.
Furthermore, one end of the transmission gear shaft, which is close to the primary planetary gear assembly, is matched with a brake assembly in a transmission way through a flat key, and the brake assembly comprises a brake and a speed measuring encoder;
the transmission gear shaft penetrates through the inside of the brake, and the tail end of the transmission gear shaft is in driving connection with a rotating shaft of the speed measuring encoder.
Furthermore, an end cover is arranged between the brake and the primary planetary gear assembly, and a through hole matched with the transmission gear shaft to extend out is formed in the center of the end cover.
Compared with the prior art, the beneficial effects of the utility model are that: the drive wheel realizes the drive operation of big reduction ratio and big moment through multistage planetary reduction drive mechanism, it is poor to have overcome traditional AGV dolly and has adopted the differential to turn to the device and realize turning to exist in going to turn to the effect, it is poor to turn to poor stability, change speed process is loaded down with trivial details, break down easily etc. defect, compare the drive wheel that adopts one-level planetary gear reducer now simultaneously, it is fast that it has obvious speed reduction efficiency, but the advantage of the bigger moment of torsion of transmission, compact structure is slim and graceful, applicable straight going or turning to of AGV dolly is realized in various environment, can be in the wide application of modernized thing flow storage system.
Drawings
The following detailed description of embodiments of the invention is provided with reference to the accompanying drawings, in which:
FIG. 1 is a schematic perspective view of an AGV driving wheel according to the present invention;
FIG. 2 is a schematic cross-sectional view taken in half section of FIG. 1;
FIG. 3 is a schematic view of FIG. 1, taken apart;
fig. 4 is an assembly view of the present invention after half-cutting the first ring gear, the rotating main shaft, and the second ring gear;
FIG. 5 is an assembly view of the primary, secondary and tertiary planetary gear assemblies of the present invention;
fig. 6 is an assembly view of the first-stage planetary gear assembly and the second-stage planetary gear assembly after the first ring gear is half-cut;
FIG. 7 is an assembly view of the first-stage planetary gear assembly and the second-stage planetary gear assembly after the first-stage planetary carrier is half-cut;
in the figure: 1-driving wheel body;
2-a primary planetary gear assembly; 21-primary sun gear; 22-primary planet pinion; 23-a primary planet carrier; 231-wheel carrier housing; 2311-a front end wall; 2312-rear end wall;
3-a two-stage planetary gear assembly; 31-a secondary sun gear; 32-secondary planet pinions; 33-a secondary planet carrier;
4-a three-stage planetary gear assembly; 41-three-stage sun gear; 42-three-stage planetary pinion;
5-a transmission gear shaft;
6-a first ring gear;
7-rotating the main shaft; 71-slotted holes;
8-a second ring gear;
9-a brake assembly; 91-a brake; 92-a speed measuring encoder;
10-end cap.
Detailed Description
The preferred embodiments of the present invention will be described in conjunction with the accompanying drawings, and it will be understood that they are presented herein only to illustrate and explain the present invention, and not to limit the present invention.
As shown in fig. 1 to 7, it is a preferred structure of the AGV driving wheel with a large speed ratio and a large torque according to the present invention.
Wherein, the AGV drive wheel includes drive wheel body 1 and planet speed reduction drive mechanism, drive wheel body 1 can realize the big moment of big reduction ratio's speed reduction rotation through planet speed reduction drive mechanism.
Specifically, the planetary reduction transmission mechanism comprises a primary planetary gear assembly 2, a secondary planetary gear assembly 3 and a tertiary planetary gear assembly 4 which are arranged side by side, and the planetary reduction transmission mechanism further comprises a transmission gear shaft 5, wherein the transmission gear shaft 5 sequentially penetrates through the central axes of the primary planetary gear assembly 2, the secondary planetary gear assembly 3 and the tertiary planetary gear assembly 4, so that the primary planetary gear assembly 2, the secondary planetary gear assembly 3 and the tertiary planetary gear assembly 4 rotate coaxially.
The first-stage planetary gear assembly 2 comprises a first-stage sun gear 21, a plurality of first-stage planet pinions 22 and a first-stage planet carrier 23, wherein the number of teeth of the first-stage sun gear 21 is less than that of the first-stage planet pinions 22. The secondary planetary gear assembly 3 includes a secondary sun gear 31, a plurality of secondary planet pinions 32, and a secondary planet carrier 33, the number of teeth of the secondary sun gear 31 is smaller than the number of teeth 32 of the secondary planet pinions. The three-stage planetary gear assembly 4 includes a three-stage sun gear 41 and a plurality of three-stage planetary pinions 42, and the number of teeth of the three-stage sun gear 41 is smaller than that of the three-stage planetary pinions 42. In addition, according to a general structure of a conventional planetary gear reducer, the sun gear and the planetary pinion are both spur gears of an external gear type, and the engagement between the sun gear and the planetary pinion is both external gear type engagement transmission. Preferably, the number of the primary planet pinions 22, the secondary planet pinions 32 and the tertiary planet pinions 42 is 3, the number of the planet pinions is the most stable in rotation around the sun gear, the transmitted torque is more uniform, and the rotation of each planet pinion is not easy to interfere under the condition that the AGV driving wheel is small in size.
Since the transmission structure of the primary planetary gear assembly 2 and the secondary planetary gear assembly 3 is similar to the transmission structure of the secondary planetary gear assembly 3 and the tertiary planetary gear assembly 4, the transmission structure of the primary planetary gear assembly 2 and the secondary planetary gear assembly 3 will be described as an example.
As shown in fig. 6 to 7, the primary planet carrier 23 is composed of a hollow wheel carrier shell 231 and three primary planet gear shafts fixed to the wheel carrier shell and uniformly distributed along the circumference, the wheel carrier shell 231 includes a circular cylindrical peripheral wall, and a front end wall 2311 and a rear end wall 2312 fixedly connected to the front and rear end surfaces of the peripheral wall, the front end wall 2311 is provided with a central hole for inserting and matching a transmission input shaft, the rear end wall 2312 is provided with a central hole, and an inner flat key sleeve in transmission fit with the secondary sun gear 31 through a flat key is arranged in the central hole. The secondary sun gear 31 is provided with an outer flat key sleeve connected with the primary planet carrier 23 through a flat key. The front end and the rear end of the primary planet gear shaft are respectively inserted into and matched with correspondingly arranged mounting holes on the front end wall 2311 and the rear end wall 2312 of the wheel carrier shell 231 and fixed through snap springs, and each primary planet pinion 22 is pivoted with the corresponding primary planet gear shaft, so that each primary planet pinion 22 rotates on the primary planet carrier 23.
The primary sun gear 21 is fixedly connected with the transmission gear shaft 5, and the primary sun gear 21 and the transmission gear shaft 5 form an integrated component through a machining process. The primary sun gear 21 is disposed in the middle of the primary planet carrier 23, and the primary sun gear 21 is engaged with each of the primary planet pinions 22. When the planetary gear mechanism works, the driving motor is in driving connection with the transmission gear shaft 5 through the coupler to drive the first-stage sun gear 21 to rotate, the first-stage sun gear 21 drives each first-stage planetary pinion 22 to revolve, the first-stage planet carrier 23 is driven to rotate around the axis of the first-stage sun gear 21, the second-stage sun gear 31 is driven to rotate, and then the second-stage planetary gear assembly 3 and the third-stage planetary gear assembly 4 are driven to rotate.
Further, the planetary reduction transmission mechanism further comprises a first inner gear ring 6 and a rotating main shaft 7; the first inner gear ring 6 is sleeved on the peripheries of the primary planetary gear assembly 2 and the secondary planetary gear assembly 3, continuous straight teeth are arranged inside the first inner gear ring 6, and the inner teeth of the first inner gear ring 6 are meshed with the primary planetary pinions 22 and the secondary planetary pinions 32. The principle of speed reduction formed between the primary planetary gear assembly 2 and the secondary planetary gear assembly 3 is as follows: the first inner gear ring 6 is fixedly connected with an AGV steering wheel support, so that the first inner gear ring 6 does not rotate when a driving wheel works, the first-stage sun gear 21 rotates actively through the transmission gear shaft 5, the first-stage sun gear 21 with the minimum number of teeth drives the first-stage planet pinion 22 with the maximum number of teeth to rotate, the first-stage planet carrier 23 further rotates in a driven mode in a speed reducing mode, and the first-stage planet pinion 22 and the first inner gear ring 6 are meshed in an inner mode, so that a speed reducing state in the same direction is formed. So that the secondary sun gear 31, which is splined to the primary carrier 23, rotates at a reduced speed.
Because the transmission structure of the secondary planetary gear assembly 3 and the tertiary planetary gear assembly 4 is similar to the transmission structure of the primary planetary gear assembly 2 and the secondary planetary gear assembly 3, it is easy to know to those skilled in the art that the secondary sun gear 31 drives the secondary planet carrier 33 to rotate in a further decelerated driven manner, and drives the tertiary sun gear 41 to rotate in a decelerated manner, and further drives the tertiary planet pinion 42 to rotate in a decelerated manner.
Furthermore, the rotating main shaft 7 is hollow, one end of the rotating main shaft 7 is fixedly connected with the first inner gear ring 6, and the rotating main shaft 7 is sleeved on the periphery of the third-stage planetary gear assembly 4. A plurality of slotted holes 71 are formed in the curved surface of the rotating main shaft 7, and the slotted holes 71 correspond to the three-stage planet pinions 42 one by one; the third-stage planetary pinion 42 is rotatably fitted in a slot 71, and the slot 71 is used for fixing the third-stage planetary pinion 42 for only self-rotation movement. And some of the gear teeth of the tertiary planet pinions 42 are exposed to the outer surface of the rotating main shaft 7.
The planetary reduction transmission mechanism further comprises a second inner gear ring 8, and the second inner gear ring 8 is sleeved at one end, far away from the first inner gear ring 6, of the rotating main shaft 7; the internal teeth of the second ring gear 8 are engaged with the three-stage planetary pinions 42, and the three-stage planetary pinions 42 drive the second ring gear 8 to rotate in a driven manner in a speed reduction manner. The rotating main shaft 7 is used for fixedly supporting the second inner gear ring 8 to be unchanged in position of the planetary reduction transmission mechanism.
The driving wheel body 1 is sleeved on the outer surface of the second inner gear ring 8, preferably, a plurality of deep groove ball bearings are arranged between the rotating main shaft 7 and the second inner gear ring 8, and the rolling friction of the bearings is utilized to reduce the heat generated by friction.
Further, the AGV driving wheel also comprises a brake assembly 9, which comprises a brake 91 and a speed measuring encoder 92. The inside of stopper 91 is through the one end that flat key transmission cooperation is close to one-level planetary gear assembly 2 at drive gear axle 5, the end of drive gear axle 5 passes through the shaft coupling with the rotation axis of speed measuring encoder 92 and comes the drive connection. The brake 91 and the speed measuring encoder 92 are electrically connected with a controller of the AGV, and when the brake 91 receives a braking and stopping signal, an internal friction plate is controlled to tightly hold the transmission gear shaft 5 for braking; the speed measuring encoder 92 is used for counting the rotating speed of the transmission gear shaft 5 to calculate the running speed of the AGV driving wheel, and feeding back the speed to the controller of the AGV trolley to monitor the speed so as to send a braking signal.
Preferably, an end cover 10 is arranged between the brake 91 and the primary planetary gear assembly 2, a through hole for matching with the transmission gear shaft 5 to extend is arranged in the center of the end cover 10, and the transmission gear shaft 5 passes through the through hole to be matched with the brake 91 in a flat key transmission manner. The end cover 10 is used to prevent dust from entering the planetary reduction transmission mechanism when the AGV driving wheel is running.
Big moment's of big velocity ratio AGV drive wheel's theory of operation be: the driving motor is in driving connection with the transmission gear shaft through the coupler, so that a primary sun gear fixedly connected with the transmission gear shaft rotates actively, the first inner gear ring is fixedly connected with the AGV steering wheel support and does not move, and the primary sun gear with the minimum number of teeth drives a primary planet pinion with the maximum number of teeth to rotate, so that the primary planet carrier rotates in a driven mode in a speed reduction mode; the primary planet carrier is in coaxial transmission fit with the secondary sun gear through a flat key, so that the secondary sun gear also performs deceleration rotation, and the secondary sun gear with the minimum number of teeth drives the secondary planet pinion with the maximum number of teeth to rotate, so that the secondary planet carrier further performs deceleration driven rotation; the second-stage planet gear carrier is in coaxial transmission fit with the third-stage sun gear through a flat key, so that the third-stage sun gear also performs speed reduction rotation, the third-stage planet pinion is driven to perform further speed reduction rotation in the second inner gear ring, and the second inner gear ring is driven to perform speed reduction rotation. Through the one-level speed reduction of one-level planetary gear assembly and second grade planetary gear assembly, the second grade speed reduction of second grade planetary gear assembly and third grade planetary gear assembly, the tertiary speed reduction of tertiary planetary gear assembly output, carry out multistage speed reduction to the AGV drive wheel to realize the big reduction ratio of AGV drive wheel and the drive operation of big moment.
Other configurations of the high ratio, high torque AGV drive wheel described in this embodiment are found in the prior art.
The above description is only a preferred embodiment of the present invention, and is not intended to limit the present invention in any way, so that any modification, equivalent change and modification made by the technical spirit of the present invention to the above embodiments do not depart from the technical solution of the present invention, and still fall within the scope of the technical solution of the present invention.
Claims (10)
1. The utility model provides a big moment's of big velocity ratio AGV drive wheel which characterized in that: the speed-reducing self-rotating driving wheel comprises a driving wheel body (1) and a planetary speed-reducing transmission mechanism, wherein the driving wheel body (1) realizes speed-reducing self-rotation through the planetary speed-reducing transmission mechanism;
the planetary reduction transmission mechanism comprises a primary planetary gear assembly (2), a secondary planetary gear assembly (3), a tertiary planetary gear assembly (4) and a transmission gear shaft (5), wherein the primary planetary gear assembly (2), the secondary planetary gear assembly (3) and the tertiary planetary gear assembly (4) are sequentially arranged side by side;
the transmission gear shaft (5) sequentially penetrates through the central axis of the first-stage planetary gear assembly (2), the second-stage planetary gear assembly (3) and the third-stage planetary gear assembly (4) so as to enable the first-stage planetary gear assembly (2), the second-stage planetary gear assembly (3) and the third-stage planetary gear assembly (4) to rotate coaxially.
2. The high ratio high torque AGV drive wheel of claim 1 further comprising: the primary planetary gear assembly (2) comprises a primary sun gear (21), a plurality of primary planet pinions (22) and a primary planet carrier (23), and the number of teeth of the primary sun gear (21) is less than that of the primary planet pinions (22);
the primary sun gear (21) is fixedly connected with the transmission gear shaft (5), and the primary sun gear (21) and the transmission gear shaft (5) are integrally arranged;
primary planet gear shafts which are pivoted with the primary planet pinions (22) are uniformly distributed on the primary planet carrier (23) along the circumference, and the primary planet gear shafts correspond to the primary planet pinions (22) one by one;
the primary sun gear (21) is arranged in the middle of the primary planet carrier (23), and the primary sun gear (21) is meshed with each primary planet pinion (22).
3. The high ratio high torque AGV drive wheel of claim 2 further comprising: the secondary planetary gear assembly (3) comprises a secondary sun gear (31), a plurality of secondary planet pinions (32) and a secondary planet carrier (33), and the number of teeth of the secondary sun gear (31) is less than that of the secondary planet pinions (32);
the secondary sun gear (31) is sleeved on the transmission gear shaft (5), and the secondary sun gear (31) is in coaxial transmission fit with the primary planet carrier (23) through a flat key;
secondary planet gear shafts which are pivoted with the secondary planet pinions (32) are uniformly distributed on the secondary planet carrier (33) along the circumference, and the secondary planet gear shafts correspond to the secondary planet pinions (32) one by one;
the secondary sun gear (31) is arranged in the middle of the secondary planet carrier (33), and the secondary sun gear (31) is meshed with each secondary planet pinion (32).
4. The high ratio high torque AGV drive wheel of claim 3 further comprising: the three-stage planetary gear assembly (4) comprises a three-stage sun gear (41) and a plurality of three-stage planetary pinions (42), and the number of teeth of the three-stage sun gear (41) is less than that of the three-stage planetary pinions (42);
the three-stage sun gear (41) is sleeved on the transmission gear shaft (5), and the three-stage sun gear (41) is in coaxial transmission fit with the second-stage planet carrier (33) through a flat key;
each of the three-stage planetary pinions (42) surrounds the three-stage sun gear (41) and meshes with the three-stage sun gear (41).
5. The high ratio high torque AGV drive wheel of claim 4 further comprising: the planetary reduction transmission mechanism also comprises a first inner gear ring (6) and a rotating main shaft (7);
the first inner gear ring (6) is sleeved on the peripheries of the primary planetary gear assembly (2) and the secondary planetary gear assembly (3), and the inner teeth of the first inner gear ring (6) are meshed with the primary planetary pinions (22) and the secondary planetary pinions (32);
the rotating main shaft (7) is hollow, one end of the rotating main shaft (7) is fixedly connected with the first inner gear ring (6), and the rotating main shaft (7) is sleeved on the periphery of the three-stage planetary gear assembly (4).
6. The high ratio high torque AGV drive wheel of claim 5 further comprising: a plurality of slotted holes (71) are formed in the curved surface of the rotating main shaft (7), and the slotted holes (71) correspond to the three-stage planet pinions (42) one by one;
the three-stage planet pinion (42) is rotatably embedded in the groove hole (71), and part of gear teeth of the three-stage planet pinion (42) are exposed out of the outer surface of the rotating main shaft (7).
7. The high ratio high torque AGV drive wheel of claim 6 further comprising: the planetary reduction transmission mechanism further comprises a second inner gear ring (8), and the second inner gear ring (8) is sleeved at one end, far away from the first inner gear ring (6), of the rotating main shaft (7);
the inner teeth of the second inner gear ring (8) are meshed with the three-stage planet pinions (42), and the driving wheel body (1) is sleeved on the outer surface of the second inner gear ring (8).
8. The high ratio high torque AGV drive wheel of claim 7 further comprising: and a plurality of deep groove ball bearings are arranged between the rotating main shaft (7) and the second inner gear ring (8).
9. A high-speed-ratio and high-torque AGV driving wheel according to any one of claims 1 to 8, wherein: one end of the transmission gear shaft (5) close to the primary planetary gear assembly (2) is matched with a brake assembly (9) in a transmission way through a flat key, and the brake assembly (9) comprises a brake (91) and a speed measuring encoder (92);
the transmission gear shaft (5) penetrates through the inside of the brake (91), and the tail end of the transmission gear shaft (5) is in driving connection with a rotating shaft of the speed measuring encoder (92).
10. The higher ratio higher torque AGV drive wheel of claim 9 further comprising: an end cover (10) is arranged between the brake (91) and the primary planetary gear assembly (2), and a through hole which is matched with the transmission gear shaft (5) to extend out is formed in the center of the end cover (10).
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| Application Number | Priority Date | Filing Date | Title |
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| CN201921268479.1U CN210423600U (en) | 2019-08-07 | 2019-08-07 | AGV drive wheel of big moment of big velocity ratio |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201921268479.1U CN210423600U (en) | 2019-08-07 | 2019-08-07 | AGV drive wheel of big moment of big velocity ratio |
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| CN210423600U true CN210423600U (en) | 2020-04-28 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110332285A (en) * | 2019-08-07 | 2019-10-15 | 广州市中立智能装备科技有限公司 | A kind of AGV driving wheel of large speed ratio high-torque |
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2019
- 2019-08-07 CN CN201921268479.1U patent/CN210423600U/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110332285A (en) * | 2019-08-07 | 2019-10-15 | 广州市中立智能装备科技有限公司 | A kind of AGV driving wheel of large speed ratio high-torque |
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