CN215908330U - Return difference type RV speed reducer - Google Patents
Return difference type RV speed reducer Download PDFInfo
- Publication number
- CN215908330U CN215908330U CN202121788391.XU CN202121788391U CN215908330U CN 215908330 U CN215908330 U CN 215908330U CN 202121788391 U CN202121788391 U CN 202121788391U CN 215908330 U CN215908330 U CN 215908330U
- Authority
- CN
- China
- Prior art keywords
- gear
- fixed
- wheel
- input shaft
- disc
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Images
Landscapes
- Retarders (AREA)
Abstract
The utility model discloses a return difference type RV reducer, which comprises a shell and an input shaft, wherein the shell comprises an annular shell and a fixed disc fixed on one end surface of the annular shell, the input shaft rotatably penetrates through the center of the fixed disc to be superposed with the axis of the annular shell, the end part of the annular shell far away from the fixed disc is rotatably provided with an output disc, the output disc is superposed with the axis of the annular shell, one end of the input shaft is positioned outside the shell, the other end of the input shaft is rotatably arranged at the center of the output disc, a gear ring is rotatably arranged inside the annular shell, the inner circumference of the gear ring is provided with a first internal gear and a second internal gear which are arranged at intervals, the outer circumference of the input shaft positioned inside the annular shell is provided with a first sun gear and a second sun gear which are arranged at intervals, a fixed planet gear is meshed and driven between the first sun gear and the first internal gear, the fixed disc is rotatably matched with the wheel shaft of the fixed planet gear, and a movable planet gear is meshed and driven between the second sun gear and the second internal gear, the output disc is in running fit with the wheel shaft of the movable planet wheel.
Description
Technical Field
The utility model relates to a return difference type RV speed reducer, and belongs to the technical field of speed reducers.
Background
The reducer is a mechanical device with wide application, such as an NGW planetary reducer, an RV reducer, a cycloid reducer, a column gear reducer and the like. The common NGW planetary reducer has small reduction ratio, large volume and poor transmission precision, but has mature technology, low manufacturing cost and long service life; the cycloidal RV reducer is large in reduction ratio, small in size, high in transmission precision, high in machining precision requirement, high in manufacturing cost and short in service life; other various reducers have the defects of small reduction ratio, large volume, poor transmission precision, high noise and the like.
The prior technical schemes such as those disclosed in patent numbers ZL201520573620.4, ZL202011522567.7, ZL201420424503.7, ZL202011611999.5, ZL202011522567.7, ZL202010861088.1, ZL202010520825.1 and the like all have the problems.
Disclosure of Invention
The utility model aims to provide a novel return difference type planetary speed reducing mechanism with large speed reducing ratio, small volume, high transmission precision, long service life, low noise and low cost.
The utility model adopts the following technical scheme: the utility model provides a return difference type RV reduction gear, it includes shell and input shaft, and the shell includes annular housing and fixes the fixed disk on an end face of annular housing, the input shaft rotates the center and the coincidence of annular housing axis that pass the fixed disk, the tip that the fixed disk was kept away from to annular housing rotates installs the output dish, output dish and the coincidence of annular housing axis, the one end of input shaft is located the shell outside, the center at the output dish is installed in the other end rotation, the inside ring gear that is equipped with of annular housing, the ring gear outside and the inboard normal running fit of annular outer lane, be equipped with the first internal gear and the second internal gear that the interval set up on the ring gear is interior, the input shaft is located the periphery in the annular housing and is equipped with first sun gear and the second sun gear that the interval set up, first internal gear and first sun gear just are close to the fixed disk on the radial coplanar of input shaft, meshing transmission has the fixed planet wheel between first sun gear and the first internal gear, the fixed disc is provided with a first shaft hole for the fixed planet gear to rotate and install in, the second inner gear and the second sun gear are arranged on the same radial plane of the input shaft and close to the output disc, the second sun gear and the second inner gear are in meshing transmission with the movable planet gear, and the output disc is provided with a second shaft hole for the movable planet gear to rotate and install in.
The number of the fixed planet wheels is more than two, and each fixed planet wheel is uniformly distributed in an annular space between the first sun gear and the first inner gear; the number of the movable planet wheels is more than two, and the movable planet wheels are uniformly distributed in an annular space between the second sun gear and the second inner gear.
The number of the fixed planet wheels is equal to that of the movable planet wheels.
The first internal gear and the second internal gear are both helical gears.
The spiral angle directions of the first internal gear and the second internal gear are the same.
The annular shell is internally provided with a fixed frame, wheel shafts are arranged on two sides of the fixed planet wheel, one wheel shaft of the fixed planet wheel is rotatably arranged in a first shaft hole of the fixed disc through a bearing, and the other wheel shaft of the fixed planet wheel is arranged in the fixed frame through a bearing.
And a wheel shaft is arranged on one side of the movable planet wheel, two bearings are arranged between the wheel shaft of the movable planet wheel and the second shaft hole of the output disc, and the two bearings are arranged on the wheel shaft of the movable planet wheel at intervals.
The output disc is rotatably arranged on the inner side of the end part of the annular shell, and the periphery of the output disc is rotatably matched with the inner side of the annular shell.
And bearings are arranged between the input shaft and the fixed disc and between the input shaft and the output disc.
And a bearing is arranged between the gear ring and the annular shell, and a bearing is arranged between the output disc and the annular shell.
The utility model has the beneficial effects that: the working process and principle of the utility model are as follows: the output end of the external driving mechanism is connected with the input shaft to drive the first sun gear coaxial with the input shaft to rotate, the first sun gear is meshed with all the fixed planet gears to rotate simultaneously, all the fixed planet gears are meshed with the first inner gear on the gear ring to rotate simultaneously, the second inner gear on the gear ring is meshed with all the movable planet gears to rotate simultaneously, all the movable planet gears are meshed with the second sun gear to rotate simultaneously, and the integral synchronous revolution motion of all the movable planet gears is driven by the output disc to rotate to output power.
According to the utility model, when the movable planet wheel revolves around the second sun gear, a rotation with a fixed speed ratio opposite to the revolving direction of the movable planet wheel is applied to the gear ring, and the revolving speed of the movable planet wheel is partially counteracted by the reverse rotation of the gear ring to be slowed down, so that the reduction ratio of the output rotating speed of the output disc to the input rotating speed of the input shaft is greatly increased, and the reduction ratio is larger as the counteraction is larger. The reverse rotation of the gear ring is driven by the second sun gear, and transmission is realized by the engagement of the fixed planet gear without revolution and the first sun gear.
The utility model has the excellent characteristics of simple and compact structure, high output precision, large reduction ratio, high impact resistance and high durability. The revolution speed difference of the dynamic planet wheel and the static planet wheel is utilized to obtain a larger reduction ratio range, the output reduction ratio value of the reduction ratio range is determined by subtracting the difference of the rotation speed of the fixed planet wheel driving the gear ring from the rotation speed of the movable planet wheel relative to the gear, the reduction ratio is larger when the difference is smaller, the difference is negative, and the rotation direction of the output disc is opposite to that of the input shaft. This feature can be directly adapted to a particular situation requiring the input/output rotation direction to be reversed without adding an additional reverse mechanism.
Meanwhile, due to the compact structure and the adoption of the integrated bevel gear, the utility model can realize high transmission precision output. And has larger output torque and shock resistance capability due to multi-gear meshing. The large reduction ratio and the small volume are realized through the innovative return difference type planet wheel combination, and a larger reduction ratio range can be obtained under the same volume; the integrated gear is adopted, so that the accumulated error of machining and assembling is reduced; the helical gear is adopted, so that the running stability is improved, and the noise is reduced; and meanwhile, higher transmission precision and efficiency are obtained due to a more compact structure, smaller accumulated error and the adoption of the bevel gear.
Drawings
FIG. 1 is a schematic diagram of the overall structure of a return-difference RV reducer according to one embodiment of the utility model;
FIG. 2 is an exploded view of FIG. 1;
FIG. 3 is a cross-sectional view of FIG. 1;
fig. 4 is a schematic diagram of fig. 1.
In the figure: 1-shell, 11-annular shell, 12-fixed disc, 13-first shaft hole, 14-fixed frame, 2-input shaft, 21-first sun gear, 22-second sun gear, 3-fixed planet gear, 4-gear ring, 41-first internal gear, 42-second internal gear, 5-movable planet gear, 6-output disc, 61-second shaft hole.
Detailed Description
The utility model is described in detail below with reference to the figures and specific embodiments.
The structure of the return difference type RV reducer of an embodiment of the present invention is shown in fig. 1 to fig. 3, the return difference type RV reducer of this embodiment includes a housing 1 and an input shaft 2, the housing 1 includes an annular housing 11 and a fixed disk 12 fixed on one end surface of the annular housing 11, the input shaft 2 rotates to pass through the center of the fixed disk 12 and coincide with the axis of the annular housing 11, an output disk 6 is rotatably mounted on an end portion of the annular housing 11 away from the fixed disk 12, the output disk 6 coincides with the axis of the annular housing 11, one end of the input shaft 2 is located outside the housing 1, the other end is rotatably mounted in the center of the output disk 6, one end of the input shaft 2 located outside the housing 1 is used for connecting with an output end of a driving mechanism, a gear ring 4 is disposed inside the annular housing 11, the outside of the gear ring 4 is rotatably matched with the inside of the annular outer ring 11, a first internal gear 41 and a second internal gear 42 are disposed at intervals on the inner circumference of the gear ring 4, the input shaft 2 is provided with a first sun gear 21 and a second sun gear 22 which are arranged at intervals on the periphery in the annular shell 11, the first inner gear 41 and the first sun gear 21 are arranged on the same radial plane of the input shaft 2 and close to the fixed disc 12, the fixed planet gears 3 are meshed and driven between the first sun gear 21 and the first inner gear 41, the fixed disc 12 is provided with a first shaft hole 13 for the wheel shaft of the fixed planet gears 3 to be rotatably arranged inside, the second inner gear 42 and the second sun gear 22 are arranged on the same radial plane of the input shaft 2 and close to the output disc 6, the movable planet gears 5 are meshed and driven between the second sun gear 22 and the second inner gear 42, and the output disc 6 is provided with a second shaft hole 61 for the wheel shaft of the movable planet gears 5 to be rotatably arranged inside.
The number of the fixed planet wheels 3 is more than two, and each fixed planet wheel 3 is uniformly distributed in an annular space between the first sun gear 21 and the first inner gear 41; the number of the movable planet wheels 5 is more than two, and each movable planet wheel 5 is uniformly distributed in the annular space between the second sun gear 22 and the second inner gear 42. The number of the fixed planet wheels 3 is equal to that of the movable planet wheels 5. In this embodiment, the number of the fixed planet wheels 3 and the number of the movable planet wheels 5 are four.
The first internal gear 41 and the second internal gear 42 are both helical gears, and the helical angles of the first internal gear 41 and the second internal gear 42 are the same.
A fixed frame 14 (not shown in fig. 2) is arranged in the annular housing 11, wheel shafts are arranged on two sides of the fixed planet wheel 3, one wheel shaft of the fixed planet wheel 3 is rotatably mounted in a first shaft hole of the fixed disc 12 through a bearing, and the other wheel shaft of the fixed planet wheel 3 is mounted in the fixed frame 14 through a bearing. And a wheel shaft is arranged on one side of the movable planet wheel 5, two bearings are arranged between the wheel shaft of the movable planet wheel 5 and the second shaft hole 61 of the output disc 6, and the two bearings are arranged on the wheel shaft of the movable planet wheel 5 at intervals.
The principle of the return difference type RV reducer of the embodiment is shown in FIG. 4, and the working process and the principle are as follows: the output end of the external driving mechanism is connected with the input shaft to drive the first sun gear coaxial with the input shaft to rotate, the first sun gear is meshed with all the fixed planet gears to rotate simultaneously, all the fixed planet gears are meshed with the first inner gear on the gear ring to rotate simultaneously, the second inner gear on the gear ring is meshed with all the movable planet gears to rotate simultaneously, all the movable planet gears are meshed with the second sun gear to rotate simultaneously, and the integral synchronous revolution motion of all the movable planet gears is driven by the output disc to rotate to output power.
According to the utility model, when the movable planet wheel revolves around the second sun gear, a rotation with a fixed speed ratio opposite to the revolving direction of the movable planet wheel is applied to the gear ring, and the revolving speed of the movable planet wheel is partially counteracted by the reverse rotation of the gear ring to be slowed down, so that the reduction ratio of the output rotating speed of the output disc to the input rotating speed of the input shaft is greatly increased, and the reduction ratio is larger as the counteraction is larger. The reverse rotation of the gear ring is driven by the second sun gear, and transmission is realized by the engagement of the fixed planet gear without revolution and the first sun gear.
The return difference type RV reducer of the embodiment realizes large reduction ratio and small volume through innovative return difference type planet wheel combination, and can obtain larger reduction ratio range under the same volume; the integrated gear is adopted, so that the accumulated error of machining and assembling is reduced; the helical gear is adopted, so that the running stability is improved, and the noise is reduced; and meanwhile, higher transmission precision and efficiency are obtained due to a more compact structure, smaller accumulated error and the adoption of the bevel gear.
Claims (10)
1. The utility model provides a return difference type RV reduction gear, its includes shell and input shaft, and the shell includes annular housing and fixes the fixed disk on an end face of annular housing, the input shaft rotates the center and the coincidence of annular housing axis that pass the fixed disk, its characterized in that: an output disc is rotatably arranged at the end part of the annular shell far away from the fixed disc, the axis of the output disc is overlapped with the axis of the annular shell, one end of the input shaft is positioned outside the shell, the other end of the input shaft is rotatably arranged at the center of the output disc, a gear ring is arranged inside the annular shell, the outer side of the gear ring is in rotating fit with the inner side of the annular outer ring, a first internal gear and a second internal gear which are arranged at intervals are arranged on the inner circumference of the gear ring, a first sun gear and a second sun gear which are arranged at intervals are arranged on the outer circumference of the input shaft in the annular shell, the first internal gear and the first sun gear are arranged on the same radial plane of the input shaft and close to the fixed disc, a fixed planet wheel is meshed and driven between the first sun gear and the first internal gear, a first shaft hole for the axle of the fixed planet wheel to rotate and arranged in is arranged on the fixed disc, and the second internal gear and the second sun gear are arranged on the same radial plane of the input shaft and close to the output disc, a movable planet wheel is in meshing transmission between the second sun gear and the second inner gear, and a second shaft hole for rotatably mounting a wheel shaft of the movable planet wheel is formed in the output disc.
2. The heterodyne RV reducer of claim 1, wherein: the number of the fixed planet wheels is more than two, and each fixed planet wheel is uniformly distributed in an annular space between the first sun gear and the first inner gear; the number of the movable planet wheels is more than two, and the movable planet wheels are uniformly distributed in an annular space between the second sun gear and the second inner gear.
3. The heterodyne RV reducer of claim 2, wherein: the number of the fixed planet wheels is equal to that of the movable planet wheels.
4. The heterodyne RV reducer of claim 1, wherein: the first internal gear and the second internal gear are both helical gears.
5. The heterodyne RV reducer of claim 4, wherein: the spiral angle directions of the first internal gear and the second internal gear are the same.
6. The heterodyne RV reducer of claim 1, wherein: the annular shell is internally provided with a fixed frame, wheel shafts are arranged on two sides of the fixed planet wheel, one wheel shaft of the fixed planet wheel is rotatably arranged in a first shaft hole of the fixed disc through a bearing, and the other wheel shaft of the fixed planet wheel is arranged in the fixed frame through a bearing.
7. The heterodyne RV reducer of claim 1, wherein: and a wheel shaft is arranged on one side of the movable planet wheel, two bearings are arranged between the wheel shaft of the movable planet wheel and the second shaft hole of the output disc, and the two bearings are arranged on the wheel shaft of the movable planet wheel at intervals.
8. The heterodyne RV reducer of claim 1, wherein: the output disc is rotatably arranged on the inner side of the end part of the annular shell, and the periphery of the output disc is rotatably matched with the inner side of the annular shell.
9. The heterodyne RV reducer of claim 1, wherein: and bearings are arranged between the input shaft and the fixed disc and between the input shaft and the output disc.
10. The heterodyne RV reducer of claim 1, wherein: and a bearing is arranged between the gear ring and the annular shell, and a bearing is arranged between the output disc and the annular shell.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202121788391.XU CN215908330U (en) | 2021-08-03 | 2021-08-03 | Return difference type RV speed reducer |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202121788391.XU CN215908330U (en) | 2021-08-03 | 2021-08-03 | Return difference type RV speed reducer |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN215908330U true CN215908330U (en) | 2022-02-25 |
Family
ID=80290455
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202121788391.XU Expired - Fee Related CN215908330U (en) | 2021-08-03 | 2021-08-03 | Return difference type RV speed reducer |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN215908330U (en) |
-
2021
- 2021-08-03 CN CN202121788391.XU patent/CN215908330U/en not_active Expired - Fee Related
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN110185748B (en) | Integrated robot joint structure | |
| CN110802422B (en) | Non-return difference machine tool rotary table | |
| CN215908330U (en) | Return difference type RV speed reducer | |
| CN112128319A (en) | High-speed silent type sealing speed reducing mechanism | |
| CN113565937A (en) | Return difference type RV speed reducer | |
| CN112072849A (en) | Coaxial speed reducing motor | |
| CN109139815A (en) | A kind of closed cycloid speed reducer of industrial robot high-precision | |
| CN210318407U (en) | Integrated robot joint structure | |
| JPS58203250A (en) | Rotation converting mechanism | |
| CN209212899U (en) | The cascade retarder of balance wheel gear unit | |
| CN209925523U (en) | Planetary cycloidal speed reducer for light robot | |
| CN209516825U (en) | Decelerating motor in a kind of electric car wheel | |
| CN112228516A (en) | Precision speed reducer for industrial robot | |
| CN110510052B (en) | Brushless motor of gasoline-electric hybrid motorcycle | |
| CN109281996B (en) | Cascade speed reducer of balance wheel transmission unit | |
| CN109139812A (en) | A kind of New-type cycloidal planetary reducer | |
| CN112046276A (en) | Motor-driven coaxial axle | |
| CN216131346U (en) | Sealed oscillating tooth reduction gear of engineering vehicle shaft section | |
| CN100472091C (en) | Crank pingear transmission | |
| CN216895581U (en) | Speed reducer of low-noise large-torque ultra-flat structure | |
| CN214788852U (en) | RV speed reducer | |
| CN216045246U (en) | Sealed cycloidal speed reducer for light robot | |
| CN113404823B (en) | Miniature high-precision small-tooth-difference cycloidal speed reducer | |
| CN216478713U (en) | Eccentric shaft planetary reducer | |
| CN216078162U (en) | Off-axis simple two-gear speed change mechanism |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20220225 |