CN214661798U - Two keep off variable speed ratio RV reduction gears - Google Patents
Two keep off variable speed ratio RV reduction gears Download PDFInfo
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- CN214661798U CN214661798U CN202023009689.4U CN202023009689U CN214661798U CN 214661798 U CN214661798 U CN 214661798U CN 202023009689 U CN202023009689 U CN 202023009689U CN 214661798 U CN214661798 U CN 214661798U
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- 239000003638 chemical reducing agent Substances 0.000 claims abstract description 24
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Abstract
The utility model discloses a two-gear variable-speed ratio RV reducer, which comprises an input gear shaft, a pressing disc, two cycloid gears, a plurality of crankshafts, a pin gear shell and an output disc; a plurality of needle teeth are uniformly embedded in the inner wall of the needle tooth shell to form an annular needle tooth group; the two cycloid gears are both internally meshed with the annular needle gear group; the output disc is arranged in the needle gear shell, and a boss of the output disc penetrates through connecting holes of the two cycloid gears; the pressing disc is arranged in the needle gear shell and is connected with a boss of the output disc through a screw; the two ends of the crank shaft are respectively connected with a first-gear planetary gear and a second-gear planetary gear; when the input gear moves towards the direction of the output disc, the first-gear external teeth of the input gear shaft are meshed with the first-gear planetary gear; when the input gear axially presses the disc to move in the direction, the second-gear external teeth of the input gear shaft are meshed with the second-gear planetary gear; the utility model discloses a two sets of different speed ratio planetary gear drive part's operating condition switches, reaches two and keeps off speed ratio transmission function.
Description
Technical Field
The utility model belongs to the technical field of the derailleur, concretely relates to two keep off variable speed ratio RV reduction gears.
Background
The RV reducer is widely applied to precision transmission of joints of industrial robots and precision driving of AGV wheels. The RV reducer is designed by adopting a two-stage transmission structure, the first stage adopts planetary gear transmission, and the second stage adopts cycloid transmission. The transmission ratio of the existing RV reducer is fixed, the requirement of speed ratio switching of an industrial robot and an AGV under high-speed and low-speed working conditions cannot be met, and the performance exertion of the robot and the AGV is severely restricted.
Accordingly, there is a need in the art for an RV reducer that addresses the above-mentioned problems.
SUMMERY OF THE UTILITY MODEL
The technical scheme who adopts for realizing the utility model aims at so, a two keep off variable speed ratio RV reduction gears, include input gear axle, compress tightly dish, two cycloid wheels, a plurality of crankshafts to and pin wheel shell and output dish.
A plurality of needle teeth are uniformly embedded in the inner wall of the needle tooth shell to form an annular needle tooth group.
And the two cycloidal gears are internally meshed with the annular needle gear set, and the two cycloidal gears and the annular needle gear set form a small-tooth-difference planetary gear transmission mechanism with one tooth difference. And the center of each cycloidal gear is provided with a through hole I. Each cycloid wheel is provided with a plurality of bearing holes in the circumferential direction, and each bearing hole is provided with a needle bearing. And a connecting hole is arranged between every two adjacent bearing holes.
And a plurality of bosses corresponding to the connecting holes are arranged on the output disc. The output disc is circumferentially and uniformly distributed with a plurality of crankshaft accommodating holes I in the circumferential direction.
The output disc is installed in the needle gear shell, a boss of the output disc penetrates through connecting holes of the two cycloidal gears, and a gap is reserved between the boss and the connecting holes.
The center of the pressing disc is provided with a through hole II. The pressing disc is circumferentially and uniformly distributed with a plurality of crank shaft accommodating holes II in the circumferential direction. The pressing disc is installed in the needle gear shell and connected with a boss of the output disc through a screw.
The crank shaft is provided with a first eccentric section and a second eccentric section. The first eccentric section and the second eccentric section are distributed in a 180-degree staggered mode.
A plurality of crank shafts penetrate into the pin gear shell. The first eccentric section and the second eccentric section of each crank shaft respectively and correspondingly penetrate into the needle roller bearings of the two cycloidal gears. One end of each crankshaft corresponds to one crankshaft accommodating hole I penetrating through the output disc, and the other end of each crankshaft corresponds to one crankshaft accommodating hole II penetrating through the pressing disc.
And two ends of each crank shaft are respectively connected with a first-gear planetary gear and a second-gear planetary gear. The first gear planetary gear is located on the outer side of the output disc, and the second gear planetary gear is located on the outer side of the pressing disc.
The outer wall of one end of the input gear shaft is provided with a first blocking outer tooth, and the outer wall of the other end of the input gear shaft is provided with a second blocking outer tooth. The input gear shaft penetrates into a through hole I of the cycloid wheel. When the input gear shaft moves towards the direction of the output disc, the first-gear external teeth of the input gear shaft are meshed with the first-gear planetary gear. When the input gear axially compresses the disc to move in the direction, the second gear external teeth of the input gear shaft are meshed with the second gear planetary gear.
Further, the device also comprises two angular contact ball bearings.
The two angular contact ball bearings are respectively installed on two sides of the annular pin gear group to circumferentially position the annular pin gear group and the two cycloidal gears.
Further, the output disc and the pin gear shell are sealed through a framework oil seal.
Further, the connecting hole is a sector annular hole. The boss is a sector annular boss matched with the sector annular hole.
Further, a tapered roller bearing is arranged between the crank shaft and the crank shaft accommodating hole II. A tapered roller bearing is arranged between the crank shaft and the crank shaft accommodating hole I.
Furthermore, the crankshaft accommodating hole II and the crankshaft accommodating hole I are both provided with hole elastic check rings for limiting the tapered roller bearing.
Further, the first-gear planetary gear is spline-mounted on the crank shaft. And the second-gear planetary gear is arranged on the crank shaft through a spline. The first gear planetary gear and the second gear planetary gear are axially positioned by elastic check rings for shafts.
The technical effect of the utility model is undoubtedly, the utility model discloses a RV reduction gear two keep off the transmission of gear ratio, have different drive ratios's external tooth at RV reduction gear input gear axle both ends design, the crank axle both ends are respectively in the output disc outside and compress tightly the dish outside installation and input gear epaxial external tooth engaged with planetary gear simultaneously. The planetary gear transmission groups on the two sides of the input gear shaft do not work simultaneously, when the gear teeth on one side are in meshing transmission, the gear teeth on the other side are separated from the meshing transmission, and the input gear shaft moves left and right, so that the working state switching of the planetary gear transmission parts with two different speed ratios can be realized, and the function of two-gear transmission ratio transmission is achieved.
Drawings
FIG. 1 is an exploded view of a two speed ratio RV retarder;
FIG. 2 is a first gear drive longitudinal section configuration of the two speed ratio RV reduction;
FIG. 3 is a longitudinal cross-sectional view of the second gear drive of the two speed ratio RV reduction;
FIG. 4 is a sectional view taken along the plane A-A of FIG. 2;
FIG. 5 is a side elevational view of the output disk of the two speed ratio RV reducer;
FIG. 6 is a side elevational view of a pressure plate of the two speed ratio RV reducer;
FIG. 7 is a view of a planetary gear-crankshaft assembly of the two speed ratio RV reducer;
FIG. 8 is a crankshaft detail view of the two speed ratio RV reducer;
FIG. 9 is a detail view of the input gear shaft of the two speed ratio RV reducer.
In the figure: the transmission comprises an input gear shaft 1, first-gear external teeth 101, second-gear external teeth 102, second-gear planetary gears 2, a shaft circlip 3, a pressing disc 4, a through hole II401, a crankshaft accommodating hole II402, a cycloid wheel 5, a through hole I501, a bearing hole 502, a connecting hole 503, a tapered roller bearing 6, an angular contact ball bearing 7, needle teeth 8, a needle bearing 9, a crankshaft 10, a hole circlip 11, a first-gear planetary gear 12, a framework oil seal 13, a needle tooth shell 14, an output disc 15, a boss 1501 and a crankshaft accommodating hole I1502.
Detailed Description
The present invention will be further described with reference to the following examples, but it should not be construed that the scope of the present invention is limited to the following examples. Various substitutions and modifications can be made without departing from the technical spirit of the invention and according to the common technical knowledge and conventional means in the field, and all shall be included in the scope of the invention.
Example 1:
the present embodiment discloses a two-gear transmission ratio RV reducer, which, referring to fig. 1 to 3, includes an input gear shaft 1, a pressing disc 4, two cycloidal gears 5, two angular contact ball bearings 7, three crank shafts 10, a pin gear housing 14 and an output disc 15.
A plurality of needle teeth 8 are uniformly embedded in the inner wall of the needle tooth shell 14 to form an annular needle tooth group.
Referring to fig. 4, the two cycloidal gears 5 are both internally meshed with the annular needle tooth group, and the two cycloidal gears 5 and the annular needle tooth group form a small-tooth-difference planetary gear transmission mechanism with a tooth difference. Each of the cycloid gears 5 has a through hole I501 at the center. Three bearing holes 502 are uniformly distributed on the circumference of each cycloid wheel 5 in the circumferential direction, and a needle bearing 9 is installed in each bearing hole 502. A connecting hole 503 is formed between two adjacent bearing holes 502. The connecting hole 503 is a fan-shaped annular hole.
The output disc 15 is provided with three sector-ring-shaped boss 1501 corresponding to the connecting hole 503, and three threaded holes are processed on the end face of each sector-ring-shaped boss 1501. The output disc 15 has three crank shaft receiving holes I1502 circumferentially and uniformly distributed in the circumferential direction.
The output disc 15 is installed in the needle gear shell 14, the boss 1501 of the output disc 15 penetrates through the connecting holes 503 of the two cycloidal gears 5, and a gap is reserved between the boss 1501 and the connecting holes 503. Referring to fig. 5, the output disc 15 and the needle gear housing 14 are sealed by a framework oil seal 13.
A through hole II401 is processed in the center of the pressing disc 4. The pressing disc 4 is circumferentially and uniformly distributed with three crankshaft accommodating holes II402 in the circumferential direction. The pressing plate 4 is installed in the needle gear shell 14, and the pressing plate 4 is connected with the boss 1501 of the output plate 15 through a screw.
Referring to fig. 8, the crank shaft 10 is provided with a first eccentric section and a second eccentric section. The first eccentric section and the second eccentric section are distributed in a 180-degree staggered mode.
Three of the crankshafts 10 are each inserted into the needle housing 14. Wherein, the first eccentric section and the second eccentric section of each crankshaft 10 respectively penetrate into the needle roller bearings 9 of the two cycloidal gears 5. One end of each of the crankshafts 10 corresponds to one crankshaft receiving hole I1502 penetrating the output disc 15, and the other end of each of the crankshafts 10 corresponds to one crankshaft receiving hole II402 penetrating the pressing disc 4. Referring to fig. 6, a tapered roller bearing 6 is installed between the crank shaft 10 and the crank shaft receiving hole II 402. A tapered roller bearing 6 is mounted between the crankshaft 10 and the crankshaft receiving hole I1502. A circlip 11 for a bore for restricting the tapered roller bearing 6 is attached to each of the crank shaft receiving hole II402 and the crank shaft receiving hole I1502.
Referring to fig. 7, a first gear planetary gear 12 and a second gear planetary gear 2 are respectively connected to both ends of each crank shaft 10. The first-gear planetary gear 12 is located in a containing groove in the side wall of the output disc 15, and the second-gear planetary gear 2 is located outside the pressing disc 4. The first-speed planetary gear 12 is spline-mounted on the crank shaft 10. The second gear planetary gear 2 is spline-mounted on the crank shaft 10. The first gear planetary gear 12 and the second gear planetary gear 2 are axially positioned by the elastic retainer ring 3 for the shaft, so that the first gear planetary gear 12, the second gear planetary gear 2 and the crankshaft 10 can synchronously rotate.
The two angular contact ball bearings 7 are respectively installed on two sides of the annular pin gear group to circumferentially position the annular pin gear group and the two cycloidal gears 5.
Referring to fig. 9, the outer wall of one end of the input gear shaft 1 is provided with a first-gear outer tooth 101, and the outer wall of the other end is provided with a second-gear outer tooth 102. The input gear shaft 1 penetrates into a through hole I501 of the cycloid wheel 5. When the input gear shaft 1 moves in the direction of the output disc 15, the first-stage external teeth 101 of the input gear shaft 1 mesh with the first-stage planetary gears 12. When the input gear shaft 1 moves in the direction of the pressing disk 4, the second-gear external teeth 102 of the input gear shaft 1 mesh with the second-gear planetary gear 2.
During transmission, power is input through the input gear shaft 1, the input gear shaft 1 is meshed with the second-gear planetary gear 2 or the first-gear planetary gear 12 to drive the crankshaft 10 to rotate, the first eccentric section and the second eccentric section of the crankshaft 10 drive the two cycloidal gears 5 to rotate, the two cycloidal gears 5 drive the pressing disc 4 and the output disc 15 to rotate relative to the needle gear shell 14 where the needle gears 8 are located, and the output of the power after speed reduction is completed through the output disc 15.
The two-gear variable-speed ratio RV reducer disclosed by the embodiment realizes two-gear variable-speed ratio transmission of the RV reducer, external teeth with different transmission ratios are designed at two ends of an input gear shaft 1 of the RV reducer, and meanwhile, planetary gears meshed with the external teeth on the input gear shaft 1 are respectively arranged at two ends of a crankshaft 10 outside an output disc 15 and outside a pressing disc 4. The planetary gear transmission groups on the two sides of the input gear shaft 1 do not work simultaneously, when the gear teeth on one side are in meshing transmission, the gear teeth on the other side are separated from the meshing transmission, and the input gear shaft 1 moves left and right, so that the working state switching of the planetary gear transmission parts with two different speed ratios can be realized, and the transmission function of two gears with variable speed ratios is achieved.
Example 2:
the present embodiment provides a basic implementation, a two-speed ratio RV reducer, see fig. 1-3, comprising an input gear shaft 1, a hold-down disk 4, two cycloidal gears 5, three crankshafts 10, and a pin housing 14 and an output disk 15.
A plurality of needle teeth 8 are uniformly embedded in the inner wall of the needle tooth shell 14 to form an annular needle tooth group.
Referring to fig. 4, the two cycloidal gears 5 are both internally meshed with the annular needle tooth group, and the two cycloidal gears 5 and the annular needle tooth group form a small-tooth-difference planetary gear transmission mechanism with a tooth difference. Each of the cycloid gears 5 has a through hole I501 at the center. Three bearing holes 502 are uniformly distributed on the circumference of each cycloid wheel 5 in the circumferential direction, and a needle bearing 9 is installed in each bearing hole 502. A connecting hole 503 is formed between two adjacent bearing holes 502. The output disc 15 is provided with three bosses 1501 corresponding to the connecting holes 503, and three threaded holes are processed on the end surface of each sector-shaped boss 1501. The output disc 15 has three crank shaft receiving holes I1502 circumferentially and uniformly distributed in the circumferential direction.
The output disc 15 is installed in the needle gear shell 14, the boss 1501 of the output disc 15 penetrates through the connecting holes 503 of the two cycloidal gears 5, and a gap is reserved between the boss 1501 and the connecting holes 503.
A through hole II401 is processed in the center of the pressing disc 4. The pressing disc 4 is circumferentially and uniformly distributed with three crankshaft accommodating holes II402 in the circumferential direction. The pressing plate 4 is installed in the needle gear shell 14, and the pressing plate 4 is connected with the boss 1501 of the output plate 15 through a screw.
Referring to fig. 8, the crank shaft 10 is provided with a first eccentric section and a second eccentric section. The first eccentric section and the second eccentric section are distributed in a 180-degree staggered mode.
Three of the crankshafts 10 are each inserted into the needle housing 14. Wherein, the first eccentric section and the second eccentric section of each crankshaft 10 respectively penetrate into the needle roller bearings 9 of the two cycloidal gears 5. One end of each of the crankshafts 10 corresponds to one crankshaft receiving hole I1502 penetrating the output disc 15, and the other end of each of the crankshafts 10 corresponds to one crankshaft receiving hole II402 penetrating the pressing disc 4.
Referring to fig. 7, a first gear planetary gear 12 and a second gear planetary gear 2 are respectively connected to both ends of each crank shaft 10. The first-gear planetary gear 12 is located outside the output disc 15, and the second-gear planetary gear 2 is located outside the pressing disc 4.
Referring to fig. 9, the outer wall of one end of the input gear shaft 1 is provided with a first-gear outer tooth 101, and the outer wall of the other end is provided with a second-gear outer tooth 102. The input gear shaft 1 penetrates into a through hole I501 of the cycloid wheel 5. When the input gear shaft 1 moves in the direction of the output disc 15, the first-stage external teeth 101 of the input gear shaft 1 mesh with the first-stage planetary gears 12. When the input gear shaft 1 moves in the direction of the pressing disk 4, the second-gear external teeth 102 of the input gear shaft 1 mesh with the second-gear planetary gear 2.
During transmission, power is input through the input gear shaft 1, the input gear shaft 1 is meshed with the second-gear planetary gear 2 or the first-gear planetary gear 12 to drive the crankshaft 10 to rotate, the first eccentric section and the second eccentric section of the crankshaft 10 drive the two cycloidal gears 5 to rotate, the two cycloidal gears 5 drive the pressing disc 4 and the output disc 15 to rotate relative to the needle gear shell 14 where the needle gears 8 are located, and the output of the power after speed reduction is completed through the output disc 15.
The two-gear variable-speed ratio RV reducer disclosed by the embodiment realizes two-gear variable-speed ratio transmission of the RV reducer, external teeth with different transmission ratios are designed at two ends of an input gear shaft 1 of the RV reducer, and meanwhile, planetary gears meshed with the external teeth on the input gear shaft 1 are respectively arranged at two ends of a crankshaft 10 outside an output disc 15 and outside a pressing disc 4. The planetary gear transmission groups on the two sides of the input gear shaft 1 do not work simultaneously, when the gear teeth on one side are in meshing transmission, the gear teeth on the other side are separated from the meshing transmission, and the input gear shaft 1 moves left and right, so that the working state switching of the planetary gear transmission parts with two different speed ratios can be realized, and the transmission function of two gears with variable speed ratios is achieved.
Example 3:
the main structure of this embodiment is the same as that of embodiment 2, and further, the present embodiment further includes two angular contact ball bearings 7.
The two angular contact ball bearings 7 are respectively installed on two sides of the annular pin gear group to circumferentially position the annular pin gear group and the two cycloidal gears 5.
Example 4:
the main structure of this embodiment is the same as that of embodiment 2, and further, referring to fig. 5, the output disc 15 and the pin gear housing 14 are sealed by a framework oil seal 13.
Example 5:
the main structure of this embodiment is the same as that of embodiment 2, and further, the connection hole 503 is a sector annular hole. The boss 1501 is a sector annular boss which is matched with the sector annular hole, and four corners of the sector annular hole and four corners of the sector annular boss are rounded corners so as to reduce abrasion between the boss 1501 and the cycloid wheel 5.
Example 6:
the main structure of this embodiment is the same as that of embodiment 2, and further, referring to fig. 6, a tapered roller bearing 6 is installed between the crankshaft 10 and the crankshaft receiving hole II 402. A tapered roller bearing 6 is mounted between the crankshaft 10 and the crankshaft receiving hole I1502.
The crankshaft receiving hole II402 and the crankshaft receiving hole I1502 are respectively provided with a circlip 11 for a hole for limiting the tapered roller bearing 6, so as to realize axial positioning.
Example 7:
the main structure of the present embodiment is the same as that of embodiment 2, and further, the first-gear planetary gear 12 is spline-mounted on the crank shaft 10. The second gear planetary gear 2 is spline-mounted on the crank shaft 10. The first gear planetary gear 12 and the second gear planetary gear 2 are axially positioned by the elastic retainer ring 3 for the shaft, so that the first gear planetary gear 12, the second gear planetary gear 2 and the crankshaft 10 can synchronously rotate.
Claims (7)
1. The utility model provides a two keep off speed ratio RV reduction gears which characterized in that: the device comprises an input gear shaft (1), a compaction disc (4), two cycloidal gears (5), a plurality of crankshafts (10), a pin gear shell (14) and an output disc (15);
a plurality of needle teeth (8) are uniformly embedded in the inner wall of the needle tooth shell (14) to form an annular needle tooth group;
the two cycloidal gears (5) are both internally meshed with the annular needle tooth group, and the two cycloidal gears (5) and the annular needle tooth group form a small-tooth-difference planetary gear transmission mechanism with a tooth difference; the center of each cycloid wheel (5) is provided with a through hole I (501); a plurality of bearing holes (502) are uniformly distributed on the periphery of each cycloidal gear (5) in the circumferential direction, and a needle bearing (9) is arranged in each bearing hole (502); a connecting hole (503) is arranged between two adjacent bearing holes (502);
the output disc (15) is provided with a plurality of bosses (1501) corresponding to the connecting holes (503); a plurality of crank shaft accommodating holes I (1502) are uniformly distributed on the output disc (15) in the circumferential direction in a circumferential direction;
the output disc (15) is installed in the needle gear shell (14), a boss (1501) of the output disc (15) penetrates through connecting holes (503) of the two cycloidal gears (5), and a gap is formed between the boss (1501) and the connecting holes (503);
a through hole II (401) is formed in the center of the pressing disc (4); a plurality of crank shaft accommodating holes II (402) are uniformly distributed on the circumferential direction of the pressing disc (4) in a circumferential manner; the pressing disc (4) is installed in the needle gear shell (14), and the pressing disc (4) is connected with a boss (1501) of the output disc (15) through a screw;
the crank shaft (10) is provided with a first eccentric section and a second eccentric section; the first eccentric section and the second eccentric section are distributed in a 180-degree staggered manner;
a plurality of crankshafts (10) penetrate into a pin gear shell (14); wherein, the first eccentric section and the second eccentric section of each crankshaft (10) respectively and correspondingly penetrate into the needle roller bearings (9) of the two cycloidal gears (5); one end of each crankshaft (10) corresponds to one crankshaft accommodating hole I (1502) penetrating through the output disc (15), and the other end of each crankshaft (10) corresponds to one crankshaft accommodating hole II (402) penetrating through the pressing disc (4);
two ends of each crank shaft (10) are respectively connected with a first-gear planetary gear (12) and a second-gear planetary gear (2); the first-gear planetary gear (12) is positioned on the outer side of the output disc (15), and the second-gear planetary gear (2) is positioned on the outer side of the pressing disc (4);
the outer wall of one end of the input gear shaft (1) is provided with a first-gear outer tooth (101), and the outer wall of the other end of the input gear shaft is provided with a second-gear outer tooth (102); the input gear shaft (1) penetrates into a through hole I (501) of the cycloid wheel (5); when the input gear shaft (1) moves towards the direction of the output disc (15), the first-gear external teeth (101) of the input gear shaft (1) are meshed with the first-gear planetary gear (12); when the input gear shaft (1) moves towards the direction of the pressing disc (4), the second-gear external teeth (102) of the input gear shaft (1) are meshed with the second-gear planetary gear (2).
2. A two speed ratio RV reducer according to claim 1 in which: the device also comprises two angular contact ball bearings (7);
the two angular contact ball bearings (7) are respectively installed on two sides of the annular pin gear group to circumferentially position the annular pin gear group and the two cycloidal gears (5).
3. A two speed ratio RV reducer according to claim 1 in which: the output disc (15) and the pin gear shell (14) are sealed through a framework oil seal (13).
4. A two speed ratio RV reducer according to claim 1 in which: the connecting hole (503) is a sector annular hole; the boss (1501) is a sector annular boss matched with the sector annular hole.
5. A two speed ratio RV reducer according to claim 1 in which: a tapered roller bearing (6) is arranged between the crank shaft (10) and the crank shaft accommodating hole II (402); a tapered roller bearing (6) is arranged between the crank shaft (10) and the crank shaft accommodating hole I (1502).
6. A two speed ratio RV reducer according to claim 5 in which: and the crankshaft accommodating hole II (402) and the crankshaft accommodating hole I (1502) are respectively provided with a hole elastic retainer ring (11) for limiting the tapered roller bearing (6).
7. A two speed ratio RV reducer according to claim 1 in which: the first-gear planetary gear (12) is mounted on the crank shaft (10) through a spline; the second gear planetary gear (2) is arranged on the crank shaft (10) through a spline; the first gear planetary gear (12) and the second gear planetary gear (2) are axially positioned by the elastic retainer ring (3) for the shaft.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202023009689.4U CN214661798U (en) | 2020-12-14 | 2020-12-14 | Two keep off variable speed ratio RV reduction gears |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202023009689.4U CN214661798U (en) | 2020-12-14 | 2020-12-14 | Two keep off variable speed ratio RV reduction gears |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN214661798U true CN214661798U (en) | 2021-11-09 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202023009689.4U Withdrawn - After Issue CN214661798U (en) | 2020-12-14 | 2020-12-14 | Two keep off variable speed ratio RV reduction gears |
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| Country | Link |
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| CN (1) | CN214661798U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112483609A (en) * | 2020-12-14 | 2021-03-12 | 重庆大学 | Two-gear variable speed ratio RV reducer |
-
2020
- 2020-12-14 CN CN202023009689.4U patent/CN214661798U/en not_active Withdrawn - After Issue
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112483609A (en) * | 2020-12-14 | 2021-03-12 | 重庆大学 | Two-gear variable speed ratio RV reducer |
| CN112483609B (en) * | 2020-12-14 | 2023-12-26 | 重庆大学 | RV speed reducer with two gear ratios |
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