CN112253703A - Engagement method of variable-diameter movable tooth helical teeth and continuously variable transmission - Google Patents
Engagement method of variable-diameter movable tooth helical teeth and continuously variable transmission Download PDFInfo
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- CN112253703A CN112253703A CN202011154211.2A CN202011154211A CN112253703A CN 112253703 A CN112253703 A CN 112253703A CN 202011154211 A CN202011154211 A CN 202011154211A CN 112253703 A CN112253703 A CN 112253703A
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- 238000005096 rolling process Methods 0.000 claims description 3
- 230000008901 benefit Effects 0.000 abstract description 4
- 238000004519 manufacturing process Methods 0.000 abstract description 3
- 230000004044 response Effects 0.000 abstract description 2
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- 229910000831 Steel Inorganic materials 0.000 description 3
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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
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/76—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with an orbital gear having teeth formed or arranged for obtaining multiple gear ratios, e.g. nearly infinitely variable
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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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/08—Profiling
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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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/17—Toothed wheels
- F16H55/18—Special devices for taking up backlash
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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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/08—Profiling
- F16H2055/0893—Profiling for parallel shaft arrangement of toothed members
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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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/17—Toothed wheels
- F16H2055/176—Ring gears with inner teeth
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- Transmission Devices (AREA)
Abstract
The invention relates to a meshing method of variable-diameter movable tooth helical teeth and a continuously variable transmission, and belongs to the technical field of continuously variable transmission mechanisms. The meshing method of the variable-diameter movable-tooth helical teeth is characterized in that two helical tooth blocks are connected through a group of wane structures to form wane movement, when the movable-tooth gear is meshed with the fixed gear or the transmission gear chain, when one of the helical tooth blocks generates interference top teeth, the helical tooth block is extruded, and then the wane structure is driven, so that the other related helical tooth block extends out to be meshed with the gear. The structure is simplified, the large-ratio stepless speed change is realized, the maximum torque can reach the same condition of a fixed gear, the stepless speed change response is quick, the slippage, the power loss and the pause are avoided, and the problems of a CVT gearbox are solved; meanwhile, compared with an AT transmission, the invention has the advantages of small volume, small power loss, high transmission efficiency and low manufacturing cost.
Description
Technical Field
The invention discloses a method for meshing variable-diameter movable tooth helical teeth, which is an improvement on the meshing of the existing fixed tooth gear. The stepless speed changer can change the diameter and the moving teeth within a certain range to complete the constant meshing with other fixed gears, and simultaneously, the stepless speed changer for realizing the meshing method is also provided, and belongs to the technical field of stepless speed change mechanisms.
Background
The constant-gear engagement stepless speed change can not be realized by using a common gear with a fixed gear ratio in the stepless speed change device.
The existing AT hydraulic stepless speed change appears in the United states of the three and four decades of the last century, and is a scheme for realizing stepless speed change by adding hydraulic torque into a stepped multi-gear speed changer. The common fixed gear in the AT hydraulic stepless speed changer also plays a role of step-by-step speed change, and the rest part realizes stepless speed change by hydraulic force and hydraulic pressure. The AT continuously variable transmission is mostly used in medium and high power transmission. The structure is complex, the volume is large, the mechanical efficiency is low, the manufacturing cost is high, but the transmission power is larger. Large automobiles, tanks, trains and the like.
The existing stepless speed change with movable teeth, namely a stepless speed changer with movable teeth meshed with sliding vane deformation (HN-CVT), is a stepless speed change with non-friction transmission and constant meshing, wherein a movable tooth sliding vane group is formed by overlapping steel sheets, and is driven by a reducing telescopic control sliding block to be meshed with a transmission chain for transmission. The thickness, tension and strength of the steel sheet affect the power and service life, the chain drives in a certain range, and the high power has certain limitation.
The existing CVT stepless speed changer is stepless speed change realized by friction transmission of wheels, belts, chains and the like, and has the problems of low power, easy 'slipping' power loss and the like. From the initial belt to the existing steel belt, the strength and the performance are improved to a certain extent, but the strength and the transmission mode directly influence the transmission efficiency and the maximum power is limited.
The existing pulse stepless speed changer uses a plurality of groups of connecting rods and one-way clutches to realize stepless speed change, but has the advantages of small power, large volume, complex structure and little use under the working condition of large torque.
Disclosure of Invention
The invention aims to solve the problems in the prior art and provides a variable-diameter moving tooth and helical tooth meshing method and a continuously variable transmission.
In order to achieve the technical purpose, the invention adopts the following technical scheme:
a method for meshing variable-diameter moving tooth and helical teeth comprises the steps that a moving tooth gear is composed of two helical tooth blocks which are arranged in parallel in a gear rolling mode; the two bevel gear blocks are formed by associating a group of wane structures, and each bevel gear block and the wane structure are connected by two parallel bevel shafts; when the movable-tooth gear is meshed with the gear or the toothed chain, when one of the helical tooth blocks has interference top teeth, the helical tooth block is extruded to drive the rocker structure, so that the other associated helical tooth block extends out to be meshed with the gear; when the gap appears in the meshing, the helical tooth block axially moves on the parallel shaft until the gap between the teeth is eliminated.
A kind of stepless speed change gear, including housing, power input mechanism, speed change mechanism and power take-off mechanism;
the power input mechanism comprises a power input shaft and a reducing crank connected with the power input shaft;
the speed change mechanism comprises a reducing gear ring and a helical gear engaged with the reducing gear ring in a planetary manner; the helical long gear is connected with the reducing crank to form a reducing crank mechanism; the variable-diameter gear ring is formed by axially distributing a plurality of groups of variable-diameter fluted discs, and the variable-diameter fluted discs are fixedly connected by a connecting plate; the reducing fluted disc comprises an annular ring body and a movable gear; the annular ring body is provided with circular and aligned slideways; the movable gear is arranged on the slideway and can synchronously slide on the slideway along with the helical long gear in the radial direction;
the power output mechanism comprises a first universal joint, a connecting shaft, a second universal joint and a power output shaft; one end of the first universal joint is connected with the helical gear long gear, and the other end of the first universal joint is sequentially connected with the connecting shaft, the second universal joint and the power output shaft.
The moving-tooth gear includes: the bevel gear block I, the bevel gear block II and the rocker structure;
the rocker structure includes: a tooth block base I, a tooth block base II and a base body; the base body is of a boss structure and comprises a plane I, a plane II and a boss; the tooth block base I and the tooth block base II are respectively arranged above the plane I and the plane II and are connected with the warping plate through warping plate shafts; the fulcrum of the wane is connected with the boss of the base body through a pin shaft;
two pairs of coaxial inclined holes are formed in the tooth block base I; the helical tooth block I is connected with the tooth block base I through a helical shaft I;
two pairs of coaxial inclined holes are formed in the tooth block base II; the helical tooth block II is connected with the tooth block base II through a helical shaft II;
the oblique axis I is not parallel to the oblique tooth angle of the oblique tooth block I;
the oblique axis II is not parallel to the oblique tooth angle of the oblique tooth block II.
Preferably, skewed tooth piece I and skewed tooth piece II all are equipped with the opening, avoid two skewed tooth pieces to take place to interfere when the wane moves.
Preferably, the oblique axis I and the oblique axis II are not parallel to the axis of the wane shaft, and the included angle of the projection of the oblique axis I and the oblique axis II on the horizontal plane is 0.5-67.5 degrees, so that the oblique tooth block can move axially on the oblique axis conveniently.
Preferably, a gap is formed between each of the tooth block base I and the tooth block base II and between the plane I and the plane II of the base body, so that the base body limits the motion of the rocker of the tooth block base.
Compared with the prior art, the invention has the beneficial effects that:
according to the invention, the helical tooth block I and the helical tooth block II are arranged on the rocker structure, so that when an outer gear ring of the reducing gear ring system is meshed with the moving gear, when one of the helical tooth blocks generates interference top teeth, the helical tooth block is extruded to drive the rocker structure, and the other associated helical tooth block extends out to be meshed with the gear; all set up with the axis nonparallel of wane axle through oblique axle I and oblique axle II for during the clearance that the meshing appears, skewed tooth piece axial displacement on the oblique axle eliminates the tooth clearance, and then can effectively increase the transmission moment of torsion. Meanwhile, by adopting a transmission mode that the helical-tooth long gear and the reducing gear ring which are connected by the reducing crankshaft are constantly meshed, the stepless speed change is realized, the stepless speed change has the advantages of quick response, no slip, no power loss and no pause and contusion, and the problems of the CVT are solved while the CVT is smooth; meanwhile, compared with an AT transmission, the invention has the advantages of small volume, small power loss, high transmission efficiency and low manufacturing cost.
Drawings
FIG. 1 is a schematic structural diagram of the continuously variable transmission;
FIG. 2 is a schematic structural diagram of a variable speed transmission mechanism of the continuously variable transmission;
FIG. 3 is a schematic structural view of the moving-tooth gear;
fig. 4 is a schematic view of the structure of the seesaw.
The device comprises a box body 11, a power input shaft 1, a power input shaft 2, a movable gear 3, a helical gear long gear, a first universal joint 4, a connecting shaft 5, a second universal joint 6, a power output shaft 7, an annular ring body 8, a slideway 81, a variable diameter crank 9, a connecting plate 10, a helical gear block I21, a helical gear block II22, a helical gear block I24, a helical gear shaft II25, a rocker shaft 26, a pin shaft 27, a gear block base I231, a gear block base II232, a gear block base 233-a base 234-a rocker.
Detailed Description
The preferred embodiments of the present invention will be described with reference to the accompanying drawings, which are included to provide further understanding, and are not intended to limit the scope of the invention.
The invention discloses a method for meshing variable-diameter moving tooth helical teeth, which is characterized in that a moving tooth gear 2 is composed of two helical tooth blocks arranged in parallel with teeth rolling as shown in figures 1 and 3; the two bevel gear blocks are formed by associating a group of wane structures, and each bevel gear block and the wane structure are connected by two parallel bevel shafts; when the moving-tooth gear 2 is meshed with the helical-tooth long gear 3, when one of the helical-tooth blocks has interference top teeth, the helical-tooth block is extruded to drive the wane structure, so that the other associated helical-tooth block extends out to be meshed with the gear; when the gap appears in the meshing, the helical tooth block axially moves on the parallel shaft until the gap between the teeth is eliminated.
Example 1
The embodiment discloses a continuously variable transmission applying a meshing method of variable-diameter moving teeth and helical teeth, which is shown in figure 1 and comprises a box body 11, a power input mechanism, a speed change mechanism and a power output mechanism;
referring to fig. 2, the power input mechanism comprises a power input shaft 1 and a reducing crank 9 connected with the power input shaft 1; the speed change mechanism comprises a reducing gear ring and a helical gear long gear 3 meshed with the reducing gear ring in a planetary manner; the helical long gear 3 is connected with the reducing crank 9 through a shaft to form a reducing crank mechanism; the variable-diameter gear ring is formed by axially distributing a plurality of groups of variable-diameter fluted discs, and the groups of variable-diameter fluted discs are fixedly connected by a connecting plate 10; the reducing fluted disc comprises an annular ring body 8 and a movable gear 2; a circular array of slide ways 81 are arranged on the annular ring body 8; the moving gear 2 is arranged on the slideway 81 and can radially and synchronously slide on the slideway 81 along with the helical long gear 3; the power output mechanism comprises a first universal joint 4, a connecting shaft 5, a second universal joint 6 and a power output shaft 7; one end of the first universal joint 4 is connected with the helical long gear 3, and the other end of the first universal joint is sequentially connected with the connecting shaft 5, the second universal joint 6 and the power output shaft 7.
Referring to fig. 3, the moving-tooth gear 2 includes: the bevel gear block I21, the bevel gear block II22 and the rocker structure;
referring to fig. 4, the seesaw structure includes: a tooth block base I231, a tooth block base II232 and a base 233; the base body 233 is of a boss structure and comprises a plane I, a plane II and a boss; the tooth block base I231 and the tooth block base II232 are respectively arranged above the plane I and the plane II and are connected with the warping plate 234 through the warping plate shaft 26; the pivot of the rocker 234 is connected with the boss of the base 233 through a pin 27;
two pairs of coaxial inclined holes are formed in the tooth block base I231; the helical tooth block I21 is connected with the tooth block base I231 through a helical shaft I24;
two pairs of coaxial inclined holes are formed in the tooth block base II 232; the helical tooth block II22 is connected with the tooth block base II232 through a helical shaft II 25.
The oblique axis I24 is not parallel to the oblique tooth angle of the oblique tooth block I21;
the oblique axis II25 is not parallel to the oblique tooth angle of the oblique tooth block II 22.
Preferably, the bevel gear block I21 and the bevel gear block II22 are both provided with rectangular openings to avoid interference between the two bevel gear blocks during the motion of the rocker.
Preferably, the inclined shaft I24 and the inclined shaft II25 are not parallel to the axis of the rocker shaft 26, and have a projection angle of 20 ° in the horizontal plane, so that the helical toothed block can move axially on the inclined shaft.
Preferably, a gap is formed between each of the tooth block base I231 and the tooth block base II232 and the plane I and the plane II of the base 233, so that the base 233 limits the tilting motion of the tooth block base. A gap is reserved between the plane I and the plane II of the base body 233, and the gap is 0.3mm, so that the base body 233 limits the tilting motion of the gear block base.
The working process is as follows:
the power input shaft 1 is connected with a power source device, the long helical gear 3 is driven to rotate in a planetary mode through the reducing crank 9 and is meshed with the movable gear in the reducing gear ring, the long helical gear 3 drives the power output mechanism to rotate, power output is achieved through the power output shaft 7, and finally stepless speed change is achieved through shaft diameter change of the reducing crankshaft mechanism. The reducing crankshaft mechanism is the prior art of the inventor, and is referred to as Chinese patent CN201210409635.8 'a reducing crankshaft type gear stepless speed change method and a speed changer'.
The transmission torque of the continuously variable transmission provided by the embodiment is more than 3 times of the transmission torque in the prior art, the structure is simple, and the power loss of the continuously variable transmission is extremely small.
It should be noted that, when the present invention is used, the functions of the power input shaft 1 and the power output shaft 7 can be exchanged, that is, power is input from the power output shaft 7 end and output from the power input shaft 1 end, which is a reversible speed change process.
It is noted that, herein, relational terms such as first and second, and the like may be used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions. Also, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. Without further limitation.
Although particular implementations of the present invention have been shown and described, it will be appreciated by those skilled in the art that changes, modifications, substitutions and alterations can be made in these embodiments without departing from the principles and spirit of the invention, the scope of which is defined in the appended claims and their equivalents.
Claims (5)
1. A method for meshing variable-diameter movable tooth helical teeth is characterized in that: the moving gear (2) is composed of two helical tooth blocks which are arranged in parallel with the gear rolling; the two bevel gear blocks are formed by associating a group of wane structures, and each bevel gear block (2) is connected with the wane structure through two parallel bevel shafts; when the movable-tooth gear (2) is meshed with a gear or a toothed chain, when one of the helical-tooth blocks has interference top teeth, the helical-tooth block is extruded to drive the rocker structure, so that the other associated helical-tooth block extends out to be meshed with the gear; when the gap appears in the meshing, the helical tooth block axially moves on the parallel shaft until the gap between the teeth is eliminated.
2. The utility model provides a continuously variable transmission, includes box (11), power input mechanism, speed change mechanism and power take off mechanism, its characterized in that:
the power input mechanism comprises a power input shaft (1) and a reducing crank (9) connected with the power input shaft (1);
the speed change mechanism comprises a reducing gear ring and a helical gear (3) meshed with the reducing gear ring in a planetary manner; the helical long gear (3) is connected with the reducing crank (9) to form a reducing crankshaft mechanism; the variable-diameter gear ring is formed by axially distributing a plurality of groups of variable-diameter fluted discs, and the groups of variable-diameter fluted discs are fixedly connected by a connecting plate (10); the reducing fluted disc comprises an annular ring body (8) and a movable gear (2); the annular ring body (8) is provided with circular and aligned slideways (81); the movable gear (2) is arranged on the slideway (81) and can radially and synchronously slide on the slideway (81) along with the helical long gear (3);
the power output mechanism comprises a first universal joint (4), a connecting shaft (5), a second universal joint (6) and a power output shaft (7); one end of the first universal joint (4) is connected with the helical long gear (3), and the other end of the first universal joint is sequentially connected with the connecting shaft (5), the second universal joint (6) and the power output shaft (7);
the moving-tooth gear (2) includes: a bevel gear block I (21), a bevel gear block II (22) and a wane structure;
the rocker structure includes: a tooth block base I (231), a tooth block base II (232) and a base body (233); the base body (233) is of a boss structure and comprises a plane I, a plane II and a boss; the gear block base I (231) and the gear block base II (232) are respectively arranged above the plane I and the plane II and are connected with a warping plate (234) through a warping plate shaft (26); the fulcrum of the rocker (234) is connected with the boss of the base body (233) through a pin shaft (27);
two pairs of coaxial inclined holes are formed in the tooth block base I (231); the helical tooth block I (21) is connected with the tooth block base I (231) through a helical shaft I (24);
two pairs of coaxial inclined holes are formed in the tooth block base II (232); the helical tooth block II (22) is connected with the tooth block base II (232) through a helical shaft II (25);
the oblique axis I (24) is not parallel to the oblique tooth angle of the oblique tooth block I (21);
the oblique axis II (25) is not parallel to the oblique tooth angle of the oblique tooth block II (22).
3. A continuously variable transmission as claimed in claim 2, wherein: the helical tooth block I (21) and the helical tooth block II (22) are both provided with openings.
4. A continuously variable transmission as claimed in claim 2, wherein: the inclined shaft I (24) and the inclined shaft II (25) are not parallel to the axis of the warping plate shaft (26), and the projection included angle of the inclined shafts on the horizontal plane is 0.5-67.5 degrees.
5. A continuously variable transmission as claimed in claim 2, wherein: gaps are arranged between the tooth block base I (231) and the tooth block base II (232) and the plane I and the plane II of the base body (233).
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011154211.2A CN112253703A (en) | 2020-10-26 | 2020-10-26 | Engagement method of variable-diameter movable tooth helical teeth and continuously variable transmission |
| CN202111242926.8A CN113719592B (en) | 2020-10-26 | 2021-10-25 | Meshing method of movable-tooth gear and variable-diameter continuously variable transmission applying same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011154211.2A CN112253703A (en) | 2020-10-26 | 2020-10-26 | Engagement method of variable-diameter movable tooth helical teeth and continuously variable transmission |
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| Publication Number | Publication Date |
|---|---|
| CN112253703A true CN112253703A (en) | 2021-01-22 |
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| CN202011154211.2A Pending CN112253703A (en) | 2020-10-26 | 2020-10-26 | Engagement method of variable-diameter movable tooth helical teeth and continuously variable transmission |
| CN202111242926.8A Active CN113719592B (en) | 2020-10-26 | 2021-10-25 | Meshing method of movable-tooth gear and variable-diameter continuously variable transmission applying same |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111242926.8A Active CN113719592B (en) | 2020-10-26 | 2021-10-25 | Meshing method of movable-tooth gear and variable-diameter continuously variable transmission applying same |
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| CN (2) | CN112253703A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113217587A (en) * | 2021-06-02 | 2021-08-06 | 田应雄 | Variable diameter gear stepless speed changer |
| CN113719592A (en) * | 2020-10-26 | 2021-11-30 | 杨建明 | Meshing method of moving tooth gear and variable-diameter stepless transmission applying same |
| CN114151533A (en) * | 2021-11-27 | 2022-03-08 | 江苏威玛斯精密机械有限公司 | Gear structure with reducing function and gear transmission system |
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| KR19980060750A (en) * | 1996-12-31 | 1998-10-07 | 김광호 | Double gear |
| JP2006038190A (en) * | 2004-07-30 | 2006-02-09 | Sumitomo Electric Hardmetal Corp | Rack and pinion device |
| CN102878268A (en) * | 2012-10-24 | 2013-01-16 | 杨建明 | Variable-diameter crankshaft type gear stepless speed change method and speed changer |
| CN203836136U (en) * | 2014-05-12 | 2014-09-17 | 温岭市驰诚机电有限公司 | Gear |
| CN209483888U (en) * | 2018-12-15 | 2019-10-11 | 北京摩云阁精密齿条股份有限公司 | A kind of rack gear gap-eliminating structure |
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| CN1032699A (en) * | 1987-10-23 | 1989-05-03 | 钟迎炎 | Stepless self-varying diameter chain type transmission device |
| CN103277477A (en) * | 2013-06-07 | 2013-09-04 | 田雷 | Variable-radius type toothed-chain stepless transmission with smooth output |
| CN108006177B (en) * | 2017-12-05 | 2019-12-13 | 陈学琴 | Planetary gear tracking engagement continuously variable transmission |
| CN112253703A (en) * | 2020-10-26 | 2021-01-22 | 杨建明 | Engagement method of variable-diameter movable tooth helical teeth and continuously variable transmission |
-
2020
- 2020-10-26 CN CN202011154211.2A patent/CN112253703A/en active Pending
-
2021
- 2021-10-25 CN CN202111242926.8A patent/CN113719592B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR19980060750A (en) * | 1996-12-31 | 1998-10-07 | 김광호 | Double gear |
| JP2006038190A (en) * | 2004-07-30 | 2006-02-09 | Sumitomo Electric Hardmetal Corp | Rack and pinion device |
| CN102878268A (en) * | 2012-10-24 | 2013-01-16 | 杨建明 | Variable-diameter crankshaft type gear stepless speed change method and speed changer |
| CN203836136U (en) * | 2014-05-12 | 2014-09-17 | 温岭市驰诚机电有限公司 | Gear |
| CN209483888U (en) * | 2018-12-15 | 2019-10-11 | 北京摩云阁精密齿条股份有限公司 | A kind of rack gear gap-eliminating structure |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113719592A (en) * | 2020-10-26 | 2021-11-30 | 杨建明 | Meshing method of moving tooth gear and variable-diameter stepless transmission applying same |
| CN113719592B (en) * | 2020-10-26 | 2024-01-16 | 杨建明 | Meshing method of movable-tooth gear and variable-diameter continuously variable transmission applying same |
| CN113217587A (en) * | 2021-06-02 | 2021-08-06 | 田应雄 | Variable diameter gear stepless speed changer |
| CN114151533A (en) * | 2021-11-27 | 2022-03-08 | 江苏威玛斯精密机械有限公司 | Gear structure with reducing function and gear transmission system |
Also Published As
| Publication number | Publication date |
|---|---|
| CN113719592B (en) | 2024-01-16 |
| CN113719592A (en) | 2021-11-30 |
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Application publication date: 20210122 |