CN111322355A - Mechanism for synchronizing rotation of planetary motion and rotation of fixed shaft - Google Patents
Mechanism for synchronizing rotation of planetary motion and rotation of fixed shaft Download PDFInfo
- Publication number
- CN111322355A CN111322355A CN201811566711.XA CN201811566711A CN111322355A CN 111322355 A CN111322355 A CN 111322355A CN 201811566711 A CN201811566711 A CN 201811566711A CN 111322355 A CN111322355 A CN 111322355A
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- China
- Prior art keywords
- rotation
- drive plate
- tooth
- planetary motion
- cross
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- 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.)
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- 230000005540 biological transmission Effects 0.000 description 4
- 230000007704 transition Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
- F16H2001/327—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear with orbital gear sets comprising an internally toothed ring gear
Abstract
The invention provides a mechanism for synchronizing the autorotation of planetary motion and the rotation of a fixed shaft. A mechanism that synchronizes rotation of the planetary motion and rotation of the fixed shaft is known as a shift lever mechanism. The mechanism for synchronizing the autorotation of the planetary motion and the rotation of the fixed shaft comprises an external gear drive plate and an internal gear drive plate, wherein a plurality of teeth are distributed on the periphery of the external gear drive plate, a plurality of teeth are distributed in an inner hole of the internal gear drive plate, a cross section curve of a tooth surface of the internal gear drive plate and a cross section curve of the tooth surface of the external gear drive plate are equidistant curves, and the offset distance of the equidistant curves is equal to or slightly greater than the eccentric distance of the planetary motion. The external gear driving plate is a straight-tooth external gear, the internal gear driving plate is a straight-tooth internal gear, and the cross section curve of the tooth surface of the internal gear driving plate is an equidistant curve which is offset outwards from the cross section curve of the tooth surface of the external gear driving plate. When the external gear drive plate performs planetary motion, the internal gear drive plate can drive the fixed shaft to rotate, and the fixed shaft rotation speed of the internal gear drive plate is equal to the rotation speed of the external gear drive plate.
Description
Technical Field
The present invention relates to a mechanism for synchronizing rotation of a planetary motion and rotation of a fixed shaft.
Background
The known mechanism for synchronizing the autorotation of the planetary motion and the rotation of the fixed shaft is a deflector rod mechanism, which consists of a deflector rod disc 1 and a thrust disc 2, wherein the deflector rod disc 1 is arranged on a planetary shaft 12 to perform eccentric planetary motion, and the thrust disc 2 is arranged on a transmission shaft 13 to perform fixed shaft rotation. A circle of deflector rod 3 is arranged on the deflector rod disc 1, a circle of round hole 4 is arranged on the position corresponding to the thrust disc 2, the diameter of the round hole 4 of the thrust disc is equal to or slightly larger than the sum of the diameter of the deflector rod 3 and the eccentricity of a planetary shaft which is 2 times of the diameter of the deflector rod disc, when the deflector rod disc 1 performs eccentric planetary motion, the deflector rod 3 is inserted into the round hole 4 on the thrust disc 2 to drive the thrust disc 2 to perform fixed-axis rotation, and the rotation speed of the deflector rod disc 1 is equal to the fixed-axis rotation speed of.
The driving lever mechanism has the following disadvantages: the space occupied by the poking rod disc 1 and the thrust disc 2 is large, and the structure is not compact due to more parts.
Disclosure of Invention
The technical problem to be solved by the invention is as follows: a driving plate mechanism which has a simple structure and a small volume and synchronizes the autorotation of the planetary motion and the fixed-axis rotation of the transmission shaft is designed.
The technical scheme adopted by the invention for solving the technical problems is as follows:
an external gear plate 5 is arranged on a planet shaft 12, a plurality of teeth are distributed on the periphery of the external gear plate 5, an internal gear plate 6 is arranged on a transmission shaft 13 which rotates on a fixed shaft, a plurality of teeth are also distributed on an inner hole of the internal gear plate 6, a cross section curve of the tooth surface of the internal gear plate 6 and a cross section curve of the tooth surface of the external gear plate 5 are equidistant curves, and the offset distance of the equidistant curves is equal to or slightly larger than the eccentricity of the planetary motion. The external gear dial 5 is a straight tooth external gear, the internal gear dial 6 is a straight tooth internal gear, and the cross section curve of the tooth surface of the internal gear dial 6 is an equidistant curve which is offset outwards from the cross section curve of the tooth surface of the external gear dial 5. When the external gear plate 5 makes planetary motion, the internal gear plate 6 can be driven to make fixed-axis rotation, and the rotation speed of the external gear plate is equal to the fixed-axis rotation speed of the internal gear plate.
The invention has the beneficial effects that:
the structure is simple, and only two parts are needed; the volume is small, a round hole on the thrust disc 2 does not exist, and the diameter of the external gear drive plate 6 can be designed to be small.
Drawings
Fig. 1 is a front view of a lever mechanism of a conventional type.
Fig. 2 is a sectional view a-a of fig. 1.
Fig. 3 is a front view of the dial mechanism of the present invention.
Fig. 4 is a sectional view B-B of fig. 3.
Fig. 5 is a cross-sectional curvilinear schematic of the external gear tooth flanks of the present invention.
Detailed Description
As shown in fig. 5, the cross-sectional curve of one tooth of the tooth surface of the external tooth dial 5 is composed of a large arc 7 with a diameter equal to the large diameter of the tooth surface, a small arc 8 with a diameter equal to the small diameter of the tooth surface, a radial straight line 9, an outer radius 10 of the large arc 7 and the radial straight line 9, and an inner radius 11 of the small arc 8 and the radial straight line 9, and all the curves are in smooth transition. And stretching the cross section curve of the tooth surface of the external gear plate 5 to form a straight tooth external gear. The cross section curve of the tooth surface of the external gear plate 5 is biased outwards, the offset distance is equal to or slightly larger than the eccentricity of the planetary motion, and the formed equidistant curve is the cross section curve of the tooth surface of the internal gear plate 6. And stretching the cross section curve of the tooth surface of the internal gear plate 6 to form a straight-tooth internal gear.
As shown in fig. 3, an external gear plate 5 is mounted on the planetary shaft 12, an internal gear plate 6 is mounted on the transmission shaft 13 which rotates around the fixed shaft, and when the external gear plate 5 performs planetary motion with the planetary shaft 12, at least one tooth of the external gear plate 5 and the internal gear plate 6 is engaged together to drive the internal gear plate 6 to rotate around the fixed shaft with the rotation of the external gear plate 5.
The length of a radial straight line 9 of a cross section curve of one tooth forming the tooth surface of the external tooth drive plate 5 can also be equal to 0, namely the radial straight line is composed of a large arc 7 with the diameter equal to the large diameter of the tooth surface, a small arc 8 with the diameter equal to the small diameter of the tooth surface, an outer radius 10 and an inner radius 11, wherein the large arc 7 is tangent to the outer radius 10, the small arc 8 is tangent to the inner radius 11, and the outer radius 10 is tangent to the inner radius 11 to form a curve with smooth transition.
Claims (6)
1. A mechanism for synchronizing rotation of planetary motion and rotation of a fixed shaft is characterized in that: one of the external tooth drive plate and the internal tooth drive plate performs planetary motion, the other one performs fixed shaft rotation, a plurality of teeth are distributed on the outer ring of the external tooth drive plate, a plurality of teeth are distributed on the inner hole of the internal tooth drive plate, and the cross section curve of the tooth surface of the external tooth drive plate and the cross section curve of the tooth surface of the internal tooth drive plate are equidistant curves.
2. The mechanism for synchronizing rotation of planetary motion and rotation of a stationary shaft according to claim 1, wherein: the offset distance of the equidistant curve is equal to or slightly larger than the eccentricity of the planetary motion.
3. The mechanism for synchronizing rotation of planetary motion and rotation of a stationary shaft according to claim 1, wherein: the cross-sectional curve of the tooth surface of the internal-tooth dial is an equidistant curve that is offset outward from the cross-sectional curve of the tooth surface of the external-tooth dial.
4. The mechanism for synchronizing rotation of planetary motion and rotation of a stationary shaft according to claim 1, wherein: the tooth surfaces of the internal gear drive plate and the external gear drive plate are straight tooth surfaces.
5. The mechanism for synchronizing rotation of planetary motion and rotation of a stationary shaft according to claim 1, wherein: the cross section curve of the tooth surface of the external tooth drive plate is a circle of smooth curves which are connected end to end.
6. The mechanism for synchronizing rotation of planetary motion and rotation of the stationary shaft according to claim 5, wherein: the cross section curve of the tooth surface of the outer drive plate consists of a large arc with the diameter equal to the large diameter of the tooth surface, a small arc with the diameter equal to the small diameter of the tooth surface, a radial straight line and the rounding of the large arc, the small arc and the radial straight line.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811566711.XA CN111322355A (en) | 2018-12-14 | 2018-12-14 | Mechanism for synchronizing rotation of planetary motion and rotation of fixed shaft |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811566711.XA CN111322355A (en) | 2018-12-14 | 2018-12-14 | Mechanism for synchronizing rotation of planetary motion and rotation of fixed shaft |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN111322355A true CN111322355A (en) | 2020-06-23 |
Family
ID=71166822
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201811566711.XA Pending CN111322355A (en) | 2018-12-14 | 2018-12-14 | Mechanism for synchronizing rotation of planetary motion and rotation of fixed shaft |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN111322355A (en) |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH10205458A (en) * | 1997-01-27 | 1998-08-04 | Mitsubishi Motors Corp | Inscribed gear pump |
| CN202690900U (en) * | 2012-07-31 | 2013-01-23 | 孟石如 | Novel tooth-shaped gear eccentric drive mechanism |
| CN103742609A (en) * | 2013-12-23 | 2014-04-23 | 陕西秦川机械发展股份有限公司 | Planetary reducer |
| CN106402285A (en) * | 2016-11-16 | 2017-02-15 | 李宗翰 | Eccentric swing type planetary gear speed reducer capable of increasing output torque |
| CN108286575A (en) * | 2018-03-09 | 2018-07-17 | 武汉仁先机械设备有限公司 | By the rotation of the planetary motion mechanism synchronous with the rotation of fixing axle |
-
2018
- 2018-12-14 CN CN201811566711.XA patent/CN111322355A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH10205458A (en) * | 1997-01-27 | 1998-08-04 | Mitsubishi Motors Corp | Inscribed gear pump |
| CN202690900U (en) * | 2012-07-31 | 2013-01-23 | 孟石如 | Novel tooth-shaped gear eccentric drive mechanism |
| CN103742609A (en) * | 2013-12-23 | 2014-04-23 | 陕西秦川机械发展股份有限公司 | Planetary reducer |
| CN106402285A (en) * | 2016-11-16 | 2017-02-15 | 李宗翰 | Eccentric swing type planetary gear speed reducer capable of increasing output torque |
| CN108286575A (en) * | 2018-03-09 | 2018-07-17 | 武汉仁先机械设备有限公司 | By the rotation of the planetary motion mechanism synchronous with the rotation of fixing axle |
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