CN107687500B - Envelope gear transmission device - Google Patents
Envelope gear transmission device Download PDFInfo
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- CN107687500B CN107687500B CN201710670234.0A CN201710670234A CN107687500B CN 107687500 B CN107687500 B CN 107687500B CN 201710670234 A CN201710670234 A CN 201710670234A CN 107687500 B CN107687500 B CN 107687500B
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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
- 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
- F16H2001/323—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 comprising eccentric crankshafts driving or driven by a gearing
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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
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
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Abstract
The invention relates to an envelope gear transmission device, and belongs to the technical field of mechanical transmission. The transmission device comprises a power input shaft, an eccentric motion gear, a crank (or a rotating arm), a planetary gear, an eccentric motion gear autorotation control mechanism, an equal angular speed ratio mechanism, an output shaft and a transmission device outer shell. The combination of the envelope gear and the planetary gear forms a planetary transmission scheme with small tooth number difference, the tooth number difference of the envelope gear and the planetary gear can be less than one, the transmission ratio can be greatly improved, and the planetary transmission scheme can be used for transmission of various motions and power. The transmission device of the invention comprises: simple structure, easy manufacture, convenient maintenance, large transmission ratio range, high transmission efficiency, large transmission power, reliable transmission, low use cost and the like.
Description
Technical Field
The invention belongs to the technical field of mechanical transmission, and relates to a gear transmission device, in particular to a planetary transmission device with small tooth difference.
Background
In the existing planetary transmission technology with small tooth difference, a planetary gear is generally meshed with a fixed internal gear, and when the tooth difference between the planetary gear and the fixed internal gear is one tooth, the transmission ratio is the largest. The transmission device has the advantages of large transmission ratio, simple structure, small volume, light weight, easy processing and maintenance, high efficiency and the like, but has some disadvantages due to small difference of the number of teeth of the two, such as more complex displacement calculation, increased meshing angle, larger load of a shaft and a bearing, reduced tooth form, reduced bearing capacity, limited transmission ratio by the number of teeth of the two and the like.
The invention aims to realize micro-tooth difference planetary transmission by utilizing a multi-tooth difference gear pair, in the transmission device, another actually-working internal gear is formed by utilizing an envelope curve of a pitch circle of an eccentric motion gear, so that the tooth number difference of the actually-working gear and the tooth number of the planetary gear can be far less than one, and the eccentric motion gear and the planetary gear are in multi-tooth difference, thereby eliminating some defects caused by too small tooth number difference of the gear pair and obviously increasing the transmission ratio.
Disclosure of Invention
The technical scheme of the invention is to design a transmission device, wherein a planetary gear is meshed with an eccentric motion gear, the tooth difference of the planetary gear and the eccentric motion gear can be multiple teeth, and is not limited by a transmission ratio.
In the transmission device, the inner meshing of the planetary gear and the eccentric motion gear is the inner meshing with the envelope gear, so that the small-tooth-difference planetary transmission of the envelope gear and the planetary gear is realized.
The transmission mainly comprises a power input (crank) shaft 1; fixing a gear 2; a crank and bearing 3 supporting the eccentric motion gear; the control planetary gear 4; an eccentric motion control gear 5; an eccentric motion female gear 6; an output planetary gear 7; an equal angular speed ratio mechanism and an output shaft 8; the transmission housing 9. The fixed gear 2, the control planetary gear 4 and the eccentric motion control gear 5 constitute a rotation control mechanism.
The eccentric motion female gear 6 is an inner gear ring, is a female gear forming an envelope gear in the transmission process, the number of teeth of the female gear is larger than the number of teeth of the output planetary gear, the difference between the number of teeth of the female gear and the number of teeth of the planetary gear is larger than the difference between the number of teeth of the non-meshing gear and the number of teeth of the output planetary gear, which cannot generate mutual interference, and the difference between the number of teeth of the female gear and the number of.
The eccentric motion control gear 5 may be an internal gear or an external gear, and is coaxial with and connected to the eccentric motion female gear 6.
The crank shaft is connected with the input shaft into a whole, the crank is a rotating arm of the planetary gear and the eccentric motion gear, and the planetary gear and the eccentric motion gear are driven to rotate around the axis of the input shaft.
The eccentric motion control gear 5 and the eccentric motion female gear 6 do eccentric motion along with the rotation of the crank shaft and also independently rotate around the axes of the crank shaft.
The autorotation of the eccentric motion gear refers to the rotation of the eccentric motion gear around the axis of the eccentric motion gear; is restrained by a self-rotation control mechanism, and the control mechanism is used for controlling the speed and the direction of the self-rotation of the eccentric motion gear.
The envelope line gear is a working gear formed by the circumferential teeth of the eccentric motion female gear 6 corresponding to another pitch circle formed by the envelope line of the pitch circle of the eccentric motion female gear 6 in the transmission process.
When the female gear eccentrically rotates around the driving shaft, the female gear can also rotate around the own axis, and along with the difference of the rotation speed, two special conditions can appear in the change of the node:
one is that when the rotation speed is zero, the node is unchanged, the meshed teeth are unchanged, the female gear and the planetary gear are relatively fixed and do not move, and the female gear and the planetary gear rotate around the driving shaft together;
the other is that when the rotation speed is a specific speed, the nodes are continuously changed and form another pitch circle, and the nodes have a common characteristic and are fixed relative to the driving shaft. For example: when an inner gear ring rotates around a fixed cylindrical gear with a diameter smaller than that of the inner gear ring in an inner meshing manner, the node is fixed like the cylindrical gear, the axis of the inner gear ring rotates around the axis of the fixed cylindrical gear, and the inner gear ring (namely the peripheral teeth on the inner gear ring) rotates around the axis of the inner gear ring. This example illustrates that a series of successive nodes of the ring gear which are thus momentarily stationary relative to the drive shaft are present, the other pitch circle formed by these nodes being the envelope of the pitch circle of the ring gear, the peripheral teeth of the ring gear corresponding thereto forming a said envelope gear. This envelope gear, in operation, serves the same function as a fixed annulus gear of equal diameter.
The relation between the radius of the envelope gear and the radius and the eccentricity of the female gear is as follows:
r = R – e
r: the radius of the envelope gear;
r: radius of the eccentric motion female gear;
e: the eccentricity of the eccentric motion female gear.
To form the envelope gear, the rotation speed of the eccentric motion female gear and the rotation speed of the eccentric motion gear drive shaft satisfy the following relationship:
n×R = N×e
n: the rotation speed of the eccentric motion female gear;
r: radius of the eccentric motion female gear;
n: the rotational speed of the eccentric motion gear drive shaft;
e: the eccentricity of the eccentric motion female gear.
The eccentric motion gear autorotation control mechanism controls the speed and the direction of the autorotation of the female gear according to the set requirements according to the principle, and the autorotation direction of the eccentric motion gear is equal to the direction of the eccentric motion gear.
The eccentric motion gear autorotation rotating speed control mechanism consists of a fixed gear 2, a control planetary gear 4 and an eccentric motion control gear 5; the control planetary gears 4 are respectively engaged with the fixed gear 2 and the eccentric motion control gear 5, and play a transitional role therebetween.
When the fixed gear 2 and the eccentric motion control gear 5 can be directly engaged, the rotation control mechanism does not need to control the planetary gear 4 to transit.
In the transmission device, an envelope line gear with the radius of R-e is formed by an eccentric motion female gear in the working process, the envelope line gear has the same function as a corresponding fixed inner gear ring in the transmission process, solid teeth forming the envelope line gear are peripheral teeth of the female gear which periodically changes, and the number of teeth forming the envelope line gear is unchanged.
The eccentricity e of the female gear can be arbitrarily selected within the range of 0 to R, and correspondingly, the radius or the number of teeth of the envelope gear is determined, and in the transmission device, the number of teeth of the envelope gear is fixed, but the number of teeth is not limited to be an integer.
The number of teeth of the envelope curve gear can be larger than that of the planet gear or smaller than that of the planet gear, and the difference of the numbers of teeth can be a micro-tooth difference smaller than one, so that a larger transmission ratio can be realized.
The equal angular speed ratio transmission mechanism equivalently transmits the absolute rotating speed of the output planetary gear to the output mechanism.
In the transmission device, the eccentric motion gear can be supported by an internal crank and a bearing, and can also be supported by an external crank and a bearing.
In the transmission device, a mechanism with eccentric motion exists, and all components can be arranged in a coordinated mode or a balance mechanism is added to keep rotation balance and realize stable operation.
The gear pair of the envelope gear transmission device can be an involute gear or a cycloid pin gear and the like.
Besides the internal engagement mode, the envelope curve gear transmission device can easily realize the planetary gear transmission in the external engagement mode of the planetary gear and the envelope curve gear.
The functions of the transmission, input, output and transmission housing may be switched with one another, i.e.: the fixed shell, the said input shaft and output shaft can be exchanged; the input shaft is fixed, and the shell and the output shaft can be used for mutual input and output; the output shaft is fixed, and the shell and the input shaft can be input and output mutually.
The transmission device does not have the mutual interference of the gear teeth in the non-meshing area, and avoids the problem caused by small tooth difference in the prior art.
According to the transmission device, the difference between the number of output planet gears and the number of teeth of the envelope track gear can be much less than one micro-tooth difference, so that the transmission ratio can be greatly improved under the condition that the number of teeth of the planet gears and the eccentric motion mother gear is not increased, and meanwhile, the bearing capacity is also improved.
Drawings
Fig. 1 is a drive diagram of the present invention.
In FIG. 1, 1-input (crank) shaft; 2-fixing a gear; 3-crank and bearing to support the eccentric motion gear; 4-controlling the planetary gear; 5-eccentric motion control gear; 6-eccentric motion female gear; 7-output planetary gear; 8-equiangular speed ratio mechanism (output shaft); 9-transmission housing.
Fig. 2 is a drive diagram of the first embodiment.
In FIG. 2, 1-input (crank) shaft; 2-a crank disk and a bearing for supporting the eccentric motion gear ring; 3-eccentric motion female gear ring; 4-eccentric motion control gear ring; 5-fixing the gear ring; 6-output planetary gear and shaft; 7-Transmission housing.
Fig. 3 is a drive diagram of the second embodiment.
In FIG. 3, 1-input (crank) shaft; 2-fixing the gear ring; 3-a crank and a bearing supporting the eccentric motion gear ring; 4-eccentric motion control gear ring; 5-eccentric motion female gear ring; 6-output planetary gear and shaft; 7-Transmission housing.
Detailed Description
The invention lists two specific embodiments, in the listed modes, the difference between the tooth number of the fixed gear ring and the eccentric motion control gear ring of the control mechanism and the difference between the tooth number of the output planetary gear and the tooth number of the eccentric motion mother gear ring are not more than one.
In the illustrated version, the diameter of the envelope gear differs from the diameter of the output planet gears by less than one millimeter.
The first embodiment is as follows:
as shown in fig. 2, a first embodiment of the present invention is an envelope gear planetary transmission with small teeth difference, which includes an input shaft (crankshaft) 1, a crank disk and a bearing 2 for supporting an eccentric motion gear ring, an eccentric motion female gear ring 3, an eccentric motion control gear ring 4, a fixed gear ring 5, an output planetary gear and shaft 6, and a transmission housing 7.
In the first embodiment, the input shaft 1 is connected to the crank disk 2.
In the first embodiment, the eccentric motion gear rings 3 and 4 are both inner gear rings, and are coaxial and connected together.
The eccentric motion gear rings 3 and 4 are arranged in the crank disc 2 through external bearings, are driven by the crank disc 2 to do eccentric motion, and can rotate around the axes of the gear rings.
The fixed gear ring 5 is an outer gear ring which is connected with a transmission device shell 7 and is internally engaged with the eccentric motion control gear ring 4.
The fixed gear ring 5 and the eccentric motion control gear ring 4 constitute a rotation control mechanism of the eccentric motion gear ring. The rotation speed and direction of the eccentric motion gear rings 3 and 4 in the transmission process are controlled by the engagement of the control gear ring 4 and the fixed gear ring 5. The rotation speed and the eccentricity of the rotor are adaptive to meet the corresponding relation; the rotation direction is consistent with the rotation direction of the eccentric motion gear.
Under the constraint of the autorotation control mechanism, the eccentric motion female gear ring 3 forms the envelope gear in the transmission process.
The output planetary gear is internally meshed with the eccentric motion female gear ring 3, namely, the output planetary gear is internally meshed with the envelope line gear formed by the eccentric motion female gear ring 3, so that the small tooth difference planetary transmission of the output planetary gear and the envelope line gear is realized.
In the first embodiment, the output planetary gear is directly mounted on the input shaft through the built-in bearing, and the difference between the actual center distance and the standard center distance is solved by adopting the modified gear.
The output planetary gear is directly connected with the output shaft, and an equiangular speed ratio transmission mechanism is not needed.
In the transmission device of the first embodiment, the eccentric motion gear rings 3 and 4 are installed in the crank disk 2, and the shape of the crank disk 2 is adjusted to enable the whole rotating body to achieve rotation balance and achieve stable operation.
The second embodiment is as follows:
the second embodiment is different from the first embodiment mainly in the supporting manner of the eccentric motion gear ring.
As shown in fig. 3, the second embodiment of the present invention is also an envelope gear planetary transmission with small teeth difference, and includes an input shaft (crankshaft) 1, a fixed gear ring 2, a crank and bearing 3 for supporting an eccentric motion gear ring, an eccentric motion control gear ring 4, an eccentric motion female gear ring 5, an output planetary gear and shaft 6, and a transmission housing 7.
In the second embodiment, the input shaft 1 and the crank 3 are connected together.
In the second embodiment, the eccentric motion gear rings 4 and 5 are both ring gears, and are coaxial and connected together.
The eccentric motion gear rings 4 and 5 are arranged on the crank 3 through built-in bearings, are driven by the crank 3 to do eccentric motion, and can also rotate.
The fixed gear ring 2 is an outer gear ring, is connected with the shell 7 of the transmission device and is internally engaged with the eccentric motion control gear ring 4.
The fixed gear ring 2 and the eccentric motion control gear ring 4 form a rotation control mechanism of the eccentric motion gear ring. The rotation speed and the rotation direction of the eccentric motion gear rings 4 and 5 in the transmission process are controlled by controlling the gear ring 4 to be meshed with the fixed gear ring 2. The rotation speed and the eccentricity of the rotor are adaptive to meet the corresponding relation; the rotation direction is consistent with the rotation direction of the eccentric motion gear.
Under the constraint of the autorotation control mechanism, the eccentric motion female gear ring 5 forms the envelope gear in the transmission process.
The output planetary gear meshes with the eccentric motion ring gear 5, that is, with the envelope gear formed by the eccentric motion ring gear 5. And small tooth difference planetary transmission of the output planetary gear and the envelope gear is realized.
In the second embodiment, the output planetary gear is directly mounted on the input shaft through the built-in bearing, and the difference between the actual center distance and the standard center distance is solved by adopting the modified gear.
The output planetary gear is directly connected with the output shaft, and an equiangular speed ratio transmission mechanism is not needed.
In the transmission device of the second technical mode, the eccentric motion gear rings 4 and 5 and the supporting bearings thereof eccentrically move, and the whole rotating body achieves rotation balance by adjusting the shape of the crank and adding a balance mechanism, so that stable operation is realized.
Claims (8)
1. The utility model provides an envelope gear few teeth difference planetary transmission, includes input shaft (1), supports crank disc and bearing (2) of eccentric motion ring gear, eccentric motion female ring gear (3), eccentric motion control ring gear (4), fixed ring gear (5), output planetary gear and axle (6), transmission shell (7), the input shaft is the crank axle
The method is characterized in that:
the input shaft (1) is connected with the crank disc (2); the eccentric motion female gear ring (3) and the eccentric motion control gear ring (4) are both inner gear rings, the two are coaxial and connected together, the eccentric motion female gear ring (3) and the eccentric motion control gear ring (4) are installed in the crank disc (2) through external bearings, are driven by the crank disc (2) to do eccentric motion, and can rotate around the axes of the eccentric motion female gear ring and the eccentric motion control gear ring; the fixed gear ring 5 is an outer gear ring, is connected with a shell (7) of the transmission device and is internally meshed with the eccentric motion control gear ring (4) to form an eccentric motion gear ring rotation control mechanism, the eccentric motion control gear ring (4) is controlled to be meshed with the fixed gear ring (5), the rotation speed and the rotation direction of the eccentric motion female gear ring (3) and the eccentric motion control gear ring (4) are controlled, the rotation speed and the eccentricity of the eccentric motion female gear ring are adapted, and the rotation direction is consistent with the rotation direction of the eccentric motion gear; under the constraint of the autorotation control mechanism, the eccentric motion gear ring 3 forms an envelope curve gear in the transmission process; the output planetary gear (6) is internally meshed with the eccentric motion female gear ring (3), namely internally meshed with an envelope gear formed by the eccentric motion female gear ring (3), so that the small-tooth-difference planetary transmission of the output planetary gear (6) and the envelope gear is realized; the output planetary gear (6) is directly installed on the input shaft through a built-in bearing, and the difference between the actual center distance and the standard center distance is solved by adopting a modified gear; the output planetary gear is directly connected with the output shaft, and an equiangular velocity ratio transmission mechanism is not needed; the eccentric motion female gear ring (3) and the eccentric motion control gear ring (4) are arranged in the crank disc, and the whole rotating body achieves rotation balance by adjusting the shape of the crank disc (2), so that stable operation is realized.
2. The transmission according to claim 1, wherein the transmission is a single-stage transmission,
the method is characterized in that:
the eccentric motion female gear ring (3) and the output planetary gear (6) are involute or cycloid pinwheels.
3. The transmission according to claim 1, wherein the transmission is a single-stage transmission,
the method is characterized in that:
in the transmission process, the envelope curve of the pitch circle of the eccentric motion female ring gear forms another pitch circle, the gear teeth of the corresponding female ring gear form an actual working ring gear with the envelope curve of the pitch circle as the pitch circle, and the actual transmission ratio generated between the gears meshed with the actual working ring gear is related to the curvature radius of the envelope curve of the pitch circle.
4. The transmission according to claim 1, wherein the transmission is a single-stage transmission,
the method is characterized in that:
the roles of the input, output and transmission housings may be switched for each other, i.e.: a fixed housing, the input and output being interchangeable; the input shaft is fixed, and the shell and the output shaft can be used for mutual input and output; the output shaft is fixed, and the shell and the input shaft can be input and output mutually.
5. The utility model provides an envelope gear few teeth difference planetary transmission, includes input shaft (1), fixed ring gear (2), supports crank and bearing (3) of eccentric motion ring gear, eccentric motion control ring gear (4), female ring gear of eccentric motion (5), output planetary gear and axle (6), transmission shell (7), the input shaft is crank axle (7)
The method is characterized in that:
the input shaft (1) is connected with the crank (3); the eccentric motion control gear ring (4) and the eccentric motion mother gear ring (5) are both inner gear rings, the two are coaxial and connected together, the eccentric motion control gear ring (4) and the eccentric motion mother gear ring (5) are arranged on the crank (3) through a built-in bearing, are driven by the crank (3) to do eccentric motion, and can also rotate; the fixed gear ring (2) is an outer gear ring, is connected with a shell 7 of the transmission device and is internally meshed with the eccentric motion control gear ring (4) to form an eccentric motion gear ring rotation control mechanism, the eccentric motion control gear ring (4) is controlled to be meshed with the fixed gear ring (2), the rotation speed and the rotation direction of the eccentric motion control gear ring (4) and the eccentric motion mother gear ring (5) are controlled, the rotation speed and the eccentricity of the eccentric motion mother gear ring are adapted, and the rotation direction is consistent with the rotation direction of the eccentric motion gear; under the constraint of the autorotation control mechanism, an envelope gear is formed in the eccentric motion female gear ring (5) in the transmission process; the output planetary gear (6) is internally meshed with the eccentric motion female gear ring (5), namely internally meshed with an envelope gear formed by the eccentric motion female gear ring (5), so that the small-tooth-difference planetary transmission of the output planetary gear (6) and the envelope gear is realized; the output planetary gear (6) is directly installed on the input shaft through a built-in bearing, and the difference between the actual center distance and the standard center distance is solved by adopting a modified gear; the output planetary gear is directly connected with the output shaft, and an equiangular velocity ratio transmission mechanism is not needed; the eccentric motion control gear ring (4), the eccentric motion master gear ring (5) and the supporting bearing thereof are in eccentric motion, and the whole rotating body achieves rotating balance by adjusting the shape of the crank (3) and adding a balance mechanism, so that the stable operation is realized.
6. The transmission according to claim 5, wherein the transmission is a single-stage transmission,
the method is characterized in that:
the eccentric motion master gear ring (5) is an involute or cycloid pinwheel.
7. The transmission according to claim 5, wherein the transmission is a single-stage transmission,
the method is characterized in that:
in the transmission process, the envelope curve of the pitch circle of the eccentric motion female ring gear forms another pitch circle, the gear teeth of the corresponding female ring gear form an actual working ring gear with the envelope curve of the pitch circle as the pitch circle, and the actual transmission ratio generated between the gears meshed with the actual working ring gear is related to the curvature radius of the envelope curve of the pitch circle.
8. The transmission according to claim 5, wherein the transmission is a single-stage transmission,
the method is characterized in that:
the roles of the input, output and transmission housings may be switched for each other, i.e.: a fixed housing, the input and output being interchangeable; the input shaft is fixed, and the shell and the output shaft can be used for mutual input and output; the output shaft is fixed, and the shell and the input shaft can be input and output mutually.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710670234.0A CN107687500B (en) | 2017-08-08 | 2017-08-08 | Envelope gear transmission device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710670234.0A CN107687500B (en) | 2017-08-08 | 2017-08-08 | Envelope gear transmission device |
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| Publication Number | Publication Date |
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| CN107687500A CN107687500A (en) | 2018-02-13 |
| CN107687500B true CN107687500B (en) | 2020-12-08 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710670234.0A Active CN107687500B (en) | 2017-08-08 | 2017-08-08 | Envelope gear transmission device |
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Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2118861U (en) * | 1992-02-29 | 1992-10-14 | 锦州齿轮厂 | Rolling furnace grate gear box |
| CN2183471Y (en) * | 1993-11-15 | 1994-11-23 | 梁晓煜 | Less tooth-differance epicyclic gear driving mechanism |
| CN2608763Y (en) * | 2003-01-22 | 2004-03-31 | 梁晓煜 | Triwheel biaxle less teeth planetary gear driving device |
| CN203809612U (en) * | 2014-01-13 | 2014-09-03 | 昆明理工大学 | Double-circular-arc correction cycloid gear planetary gear train |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8840512B2 (en) * | 2009-10-16 | 2014-09-23 | University of Chongqing | Gapless planetary transmission |
-
2017
- 2017-08-08 CN CN201710670234.0A patent/CN107687500B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2118861U (en) * | 1992-02-29 | 1992-10-14 | 锦州齿轮厂 | Rolling furnace grate gear box |
| CN2183471Y (en) * | 1993-11-15 | 1994-11-23 | 梁晓煜 | Less tooth-differance epicyclic gear driving mechanism |
| CN2608763Y (en) * | 2003-01-22 | 2004-03-31 | 梁晓煜 | Triwheel biaxle less teeth planetary gear driving device |
| CN203809612U (en) * | 2014-01-13 | 2014-09-03 | 昆明理工大学 | Double-circular-arc correction cycloid gear planetary gear train |
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| CN107687500A (en) | 2018-02-13 |
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