CN102094945A - High-power stepless transmission - Google Patents
High-power stepless transmission Download PDFInfo
- Publication number
- CN102094945A CN102094945A CN200910229141XA CN200910229141A CN102094945A CN 102094945 A CN102094945 A CN 102094945A CN 200910229141X A CN200910229141X A CN 200910229141XA CN 200910229141 A CN200910229141 A CN 200910229141A CN 102094945 A CN102094945 A CN 102094945A
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- China
- Prior art keywords
- self
- locking
- speed
- toothed chain
- planetary pinion
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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
- F16H9/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members
- F16H9/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion
- F16H9/04—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes
- F16H9/10—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley provided with radially-actuatable elements carrying the belt
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transmission Devices (AREA)
- Friction Gearing (AREA)
Abstract
The invention relates to a tooth chain type stepless transmission for an automobile. A tooth chain is arranged around a plurality of planetary gears which can unidirectionally rotate; all the planetary gears can move in a corresponding radial chute on a drive wheel; and stepless transmission is realized by changing the revolution diameter of the planetary gears. An unlocking key is arranged in a one-way clutch of each planetary gear; and when the tooth chain and the planetary gears are meshed and separated, the unlocking key can be driven so that the clutch is maintained in a one-way locking state or unlocking state. The invention breaks through the traditional theory that the stepless transmission is only friction power transmission, solves the problem of carrying out stepless transmission by utilizing a gear, can effectively improve the transfer power of the stepless transmission and has the advantages of large force transmission, high rotating speed, stable running, reliable work, and the like.
Description
Technical field
The invention belongs to the mechanical transmission field, be specially a kind of high-powered automobiles stepless speed variator.
Background technique
Electrodeless variable-speed is the ultimate aim of automotive transmission development.The principle of existing stepless speed variator all is a friction transferring power mode, and the power that is transmitted is all smaller.The fundamental way that realizes big power variable speed unit should be gear transmission, and this problem is never effectively solved.As a kind of slide plate teeth belt type stepless speed variator, the slide plate on the cingulum can embed and play the tooth transmission in the radial groove on the driving wheel, and slide plate can move with change driving radius in chute and realize electrodeless variable-speed.This structure since slide plate and chute in engagement when breaking away from, the moving direction of the two is inharmonious, one be circumferencial direction, another be the tangent direction of circumference, causes the two mutual interference of moving, and can not adapt to high rotating speed and powerful needs.Another kind of rotating disk roller sliding vane stepless speed variator, many profile of tooth pits are arranged on the rotating disk, roller circumferentially be evenly equipped with many slide plates, slide plate can embed and play the tooth transmission in the profile of tooth pit during work, by changing the contact radius realization electrodeless variable-speed of roller and rotating disk.This structure is when high speed rotating, and slide plate can do random jump under the effect of inertial force on turntable surface, it can not in time maybe can not be embedded in the profile of tooth pit and skids, and can not adapt to high rotating speed and powerful needs.The third is the toothed-chain type buncher that is used for bicycle, toothed chain be centered around a plurality of can the planetary pinion of one-way rotation on, each planetary pinion can move in the corresponding radial groove on driving wheel, realizes electrodeless variable-speed by changing planetary revolution diameter.The deficiency of this structure is: the one, and, the locking slide block of planetary pinion overrunning clutch slides easily, can not transmit bigger power; The 2nd,, because the electrodeless variation of planetary pinion revolution diameter, can change planetary pinion and toothed chain under non-engagement state, corresponding position between tooth and the teeth groove, cause the two interference that in engagement process, bumps, even adopted the yielding of spring return gap is arranged, can not eliminate this interference and collision, also can make a concession the gap and cause running vibration owing to this; The 3rd,, the plane of rotation that a plurality of planetary pinion surrounded is not circle but polygonal, causes when work toothed chain fixing with the point of contact of plane of rotation, makes the point of contact produce circular runout, causes the toothed chain vibrations and causes the elasticity generation cyclically-varying of toothed chain.These all can not satisfy the needs of high-speed high-power transferring power.At present, auto continuously variable transmission can only be used for the compact car of medium and small discharge capacity.
In sum, the transmission of power that solves high-power electrodeless variable-speed is a global difficult problem always.
Summary of the invention
Purpose of the present invention is exactly in order to solve an above-mentioned difficult problem, and a kind of high-speed high-power buncher of energy transmitting large torque is provided.
Basic embodiment of the present invention is: driving wheel and speed disk all are housed on the driving and driven transmission shaft, driving wheel is provided with a plurality of equally distributed radial grooves, speed disk is provided with the oblique slotted eye of involute shape with radial groove equivalent, in each radial groove and the oblique slotted eye planetary pinion is housed all, planet pin is positioned at radial groove and oblique slotted eye simultaneously and can moves therein, but can not rotate in radial groove; Be provided with single clutch between planetary pinion and its axle; Toothed chain is centered around on each planetary pinion and connects driving and driven transmission shaft; Speed disk is connected with the speed governing driving mechanism and can rotates with respect to driving wheel, when speed disk rotates oblique slotted eye stir planet pin and planetary pinion radially chute move, thereby change planetary revolution diameter, the realization stepless time adjustment.Planetary pinion is unidirectional when not rotating, and just plays the power transmission effect of fixed gear; When reducing moved, planetary pinion was a counter-rotation, just the toothed chain length between each planetary pinion of can regulate.Constant for the elasticity that keeps toothed chain, the reducing direction of driving and driven transmission shaft should be reversed simultaneously.One of feature of the present invention is: the locking slide block of overrunning clutch is a self-locking pendulum pin, self-locking pendulum pin can be that swing in the center of circle with its strong point, the length of self-locking pendulum pin has an angle greater than the radial distance between its strong point and the planet pin surface between its length direction and the planetary radial direction.Produce the self-locking effect between energy and the rotating component when self-locking pendulum lock ends,, increase transferring power to prevent cltuch slipping; Two of feature is: be provided with the key of unblanking in the overrunning clutch, and an end of the key of unblanking and self-locking pendulum pin contacts, the other end can contact with toothed chain; Toothed chain with planetary pinion engagement when separating, can drive the key of unblanking makes it stir self-locking pendulum pin to remain on the unidirectional locking position or break away from this position, be that planet gear and toothed chain are under engagement, clutch has the unidirectional locking function, clutch does not have latch functions under non-engagement state, and planetary pinion is the two-way free state that can both rotate; Planetary pinion under the free state is meshing in the contact process with toothed chain, and the angle that can two-wayly freely swing can the servo-actuated adjustment be aimed at the position of tooth and perforation, thereby be realized smooth and easy engagement, eliminates interference and collision; Three of feature is: planetary both sides are equipped with conical surface driving wheel and speed disk, form " V " shape annular groove in the middle of the conical surface of both sides folds, and toothed chain is positioned at " V " shape annular groove, and the both sides of toothed chain are provided with the inclined-plane that adapts with " V " shape annular groove; " V " shape annular groove is shaped as circular segmental arc with the polygonal segmental arc of toothed chain, can improve the smoothness of running.During speed change, speed regulation control mechanism drives the speed disk rotation and driving wheel moves axially, to change the width of planetary revolution diameter and " V " shape groove.
Second scheme of the present invention be based on the first string, is provided with damping spring between planetary pinion and its axle, under free state, flies change phenomenon because of what centrifugal force caused with restrictions planetary gear, helps weakening the collision when meshing with toothed chain.
The 3rd scheme of the present invention is based on first or second scheme, and self-locking pendulum pin is provided with the tooth line with the surface of friction pair of planet pin, to increase the locking effect.Tooth line direction on two friction surfaces or identical, or different.
The 4th scheme of the present invention is based on first or second or the 3rd scheme, and speed disk is by screw rod and transmission shaft socket, and speed disk also rotates simultaneously axially movable.
The invention has the advantages that: the first, power transmission is big, rotating speed is high.The present invention has broken through the traditional theory that electrodeless variable-speed can only be the friction power transmission, has solved to utilize gear to carry out the difficult problem of electrodeless variable-speed, can effectively improve the transmitted power of buncher.The second, gear ratio is big, and application area is wide.For automobile for metal band type stepless speed variator, if when wanting by increase driving wheel diameter desire raising velocity ratio, the width of cause " V " shape groove also can increase thereupon, to cause wide, the reduction in strength of metal tape, cause transmission of power limited, produce skidding, thereby restricted the increase of gear ratio.There is not the problem of skidding in the present invention when toothed chain broadening, thereby, bigger gear ratio can be arranged.The 3rd, reliable operation is non-slip.The present invention helps reducing manufacture cost and improves functional reliability automatically controlled not high with required precision hydraulic control.
Description of drawings
Fig. 1 fundamental diagram
1. oblique slotted eye 2. toothed chains 3. planetary pinions 4. speed disks 5. initiative drive shafts 6. driven transmission shafts
Fig. 2 driving wheel
7. slotted eye 8. driving wheels radially
Fig. 3 overrunning clutch
9. clutch chamber 10. release springs 11. self-lockings pendulum is sold 12. holddown springs, 13. voussoirs
Fig. 4 key of unblanking
The key 13. voussoir 14. flanges 15. are unblanked
Fig. 5 sprocket wheel erection drawing
2. toothed chain 3. planetary pinions 4. speed disks 7. radially push away limit 18. setting sleeves, 19. conical surfaces, 20. return springs, 21. planet pins, 22. ball bearings in slotted eye 8. driving wheels 15. key 16. inclined-planes 17. of unblanking
Fig. 6 toothed chain
2. toothed chain 16. inclined-planes
Fig. 7 planetary pinion shaft end
23. cylindrical section 24. slide block sections
Fig. 8 Hydraulic Adjustable Speed schematic representation
2. toothed chain 5. initiative drive shafts 6. driven transmission shaft 4a. speed disk standing part 4b. speed disk moving element 8a. driving wheel standing part 8b. driving wheel moving element 25. oil hydraulic cylinders 26. screw rods
Embodiment
The present invention will be further described below in conjunction with drawings and Examples.
See Fig. 1 and Fig. 2, speed disk (4) and driving wheel (8) all are housed on initiative drive shaft (5) and the driven transmission shaft (6), driving wheel is positioned at the back side of speed disk, the axle of planetary pinion (3) passes the radial groove (7) that oblique slotted eye (1) on the speed disk is positioned at driving wheel, and toothed chain (2) is centered around on the planetary pinion and by speed disk and is connected driving and driven transmission shaft with driving wheel.See Fig. 3, be provided with clutch chamber (9) in the planetary axis hole, the indoor self-locking pendulum pin (11) that is provided with, self-locking pendulum pin positions installation by holddown spring (12) and release spring (10) and can be that swing in the center of circle with its strong point.The length of self-locking pendulum pin has an angle greater than the radial distance between its strong point and the planet pin surface between its length direction and the planetary radial direction.As shown in Figure 3, when planetary pinion clockwise rotated, self-locking pendulum pin promptly produced the self-locking effect to the direction swing that angle reduces, thus the rotation of restrictions planetary gear; When planetary pinion rotated counterclockwise, locking phenomenon did not promptly take place in the backswing of self-locking pendulum pin, and planetary pinion is just free to rotate.Self-locking pendulum pin is provided with the tooth line with the surface of friction pair of planet pin.
The key (15) of unblanking is provided with voussoir (13) and flange (14), sees Fig. 4, and the key of unblanking is installed in planet pin (21) by setting sleeve (18) and goes up and can axially move, and sees Fig. 5.Toothed chain (2) is provided with and pushes away limit (17), when toothed chain and planetary pinion engagement, pushing away the limit contacts with flange voussoir (13) propelling clutch chamber, voussoir is pressed on the planet pin surface by pushing holddown spring (12) with self-locking pendulum pin, see Fig. 3, at this moment, planetary pinion has just had the unidirectional locking function; When toothed chain and planetary pinion disengaging engagement, self-locking pendulum pin is return under the effect of return spring (20) just, see Fig. 5, voussoir is promptly removed the spacing of pin is put in self-locking, under the effect of release spring (10), see Fig. 3, the disengaging of self-locking pendulum pin contacts with the planet pin surface, and planetary pinion just is in the two-way free state that can both rotate.Return spring (20) contacts the effect of the damping spring of having held concurrently with the planet pin surface.
The end of planet pin is provided with cylindrical section (23) and slide block section (24), sees Fig. 7, lays respectively in the radial groove of the oblique slotted eye of speed disk and driving wheel.Can be provided with ball bearing (22) between speed disk and the driving wheel.Setting sleeve (18) is used for planetary pinion and the axially locating of the key of unblanking, and sees Fig. 5.
The working surface of driving wheel and speed disk is the conical surface (19), " V " shape groove of the middle relatively formation of the conical surface of both sides, and toothed chain and planetary pinion are positioned at this " V " shape groove, see Fig. 5 and Fig. 8.The both sides of toothed chain are provided with the inclined-plane (16) that matches with " V " shape groove, see Fig. 5 and Fig. 6.
Driving wheel and speed disk constitute by standing part and moving element, see Fig. 8.Driving wheel moving element (8b) is connected with oil hydraulic cylinder (25), when reducing is regulated, axially moves under the driving of hydraulic oil.Speed disk moving element (4b) also rotates axially movable simultaneously by screw rod (26) and transmission shaft socket.During reducing, do not have relative movement between driving wheel standing part (8a) and the transmission shaft, speed disk standing part (4a) only rotatablely moves.Driving wheel on the driving and driven transmission shaft is identical with the structure of speed disk, and position and moving direction are opposite, see Fig. 8.
Claims (4)
1. big power variable speed unit, driving wheel and speed disk all are housed on the driving and driven transmission shaft, driving wheel is provided with a plurality of equally distributed radial grooves, speed disk is provided with the oblique slotted eye of involute shape with radial groove equivalent, in each radial groove and the oblique slotted eye planetary pinion is housed all, planet pin is positioned at radial groove and oblique slotted eye simultaneously and can moves therein, but can not rotate in radial groove; Be provided with single clutch between planetary pinion and its axle; Toothed chain is centered around on each planetary pinion and connects driving and driven transmission shaft; Speed disk is connected with the speed governing driving mechanism and can rotates with respect to driving wheel, one of its feature is: the locking slide block of overrunning clutch is a self-locking pendulum pin, self-locking pendulum pin can be that swing in the center of circle with its strong point, the length of self-locking pendulum pin has an angle greater than the radial distance between its strong point and the planet pin surface between its length direction and the planetary radial direction; Two of feature is: be provided with the key of unblanking in the overrunning clutch, end of key and the self-locking pendulum pin contacts of unblanking, the other end can contact with toothed chain, toothed chain with planetary pinion engagement when separating, can drive the key of unblanking and make it stir self-locking to put to sell and remain on the unidirectional locking position or break away from this position; Three of feature is: planetary both sides are equipped with conical surface driving wheel and speed disk, form " V " shape annular groove in the middle of the conical surface of both sides folds, and toothed chain is positioned at " V " shape annular groove, and the both sides of toothed chain are provided with the inclined-plane that adapts with " V " shape annular groove.
2. big power variable speed unit as claimed in claim 1 is characterized in that being provided with damping spring between planetary pinion and its axle.
3. big power variable speed unit as claimed in claim 1 or 2 is characterized in that the self-locking pendulum pin and the surface of friction pair of planet pin are provided with the tooth line.
4. as claim 1 or 2 or 3 described big power variable speed units, it is characterized in that speed disk by screw rod and transmission shaft socket, speed disk also rotates simultaneously axially movable.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910229141XA CN102094945A (en) | 2009-12-11 | 2009-12-11 | High-power stepless transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910229141XA CN102094945A (en) | 2009-12-11 | 2009-12-11 | High-power stepless transmission |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN102094945A true CN102094945A (en) | 2011-06-15 |
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ID=44128153
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200910229141XA Pending CN102094945A (en) | 2009-12-11 | 2009-12-11 | High-power stepless transmission |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN102094945A (en) |
Cited By (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103910022A (en) * | 2013-01-08 | 2014-07-09 | 任孝忠 | Bicycle gear speed-change device |
| CN104196969A (en) * | 2014-08-14 | 2014-12-10 | 中科动力（福建）新能源汽车有限公司 | Continuously variable transmission for electric vehicle |
| CN104806658A (en) * | 2014-01-28 | 2015-07-29 | 本田技研工业株式会社 | One-way clutch and crank-type continuously-variable transmission |
| CN105546093A (en) * | 2016-02-23 | 2016-05-04 | 陈志雄 | Continuously variable transmission |
| CN106208617A (en) * | 2015-02-09 | 2016-12-07 | 徐夫子 | Dynamic magnetoelectric amplifying device |
| CN106402303A (en) * | 2015-07-30 | 2017-02-15 | 郑云兵 | Transmission |
| CN107830151A (en) * | 2017-11-30 | 2018-03-23 | 西安石油大学 | A kind of hydraulic column array multi-stage reducing belt wheel |
| CN107858758A (en) * | 2017-12-07 | 2018-03-30 | 中国热带农业科学院农业机械研究所 | A kind of sprocket transmission device that numb machine regulation draw ratio is managed for sisal hemp |
| CN108843755A (en) * | 2018-06-15 | 2018-11-20 | 李存伟 | A kind of stepless automatic transmission |
| WO2019119531A1 (en) * | 2017-12-20 | 2019-06-27 | 谭波 | Chain-type stepless speed reducer |
| CN110566642A (en) * | 2019-09-20 | 2019-12-13 | 付鹰波 | Stepless speed variator for motor vehicle |
| CN110630710A (en) * | 2019-09-29 | 2019-12-31 | 梁恩 | Anti-skid continuously variable transmission |
| CN112354833A (en) * | 2020-10-09 | 2021-02-12 | 重庆工程职业技术学院 | Cleaning mechanism and kitchen waste sorting assembly line thereof |
| CN112354835A (en) * | 2020-10-09 | 2021-02-12 | 重庆工程职业技术学院 | Drum screen and kitchen waste sorting production line thereof |
| CN112354834A (en) * | 2020-10-09 | 2021-02-12 | 重庆工程职业技术学院 | Drum screen and kitchen waste sorting assembly line |
| US20230228319A1 (en) * | 2022-01-14 | 2023-07-20 | Keith Nicholas Jourden | Reduced Vibration, Shift Compensating, Continuously Variable Transmission |
-
2009
- 2009-12-11 CN CN200910229141XA patent/CN102094945A/en active Pending
Cited By (21)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103910022A (en) * | 2013-01-08 | 2014-07-09 | 任孝忠 | Bicycle gear speed-change device |
| CN104806658A (en) * | 2014-01-28 | 2015-07-29 | 本田技研工业株式会社 | One-way clutch and crank-type continuously-variable transmission |
| CN104196969A (en) * | 2014-08-14 | 2014-12-10 | 中科动力（福建）新能源汽车有限公司 | Continuously variable transmission for electric vehicle |
| CN106208617A (en) * | 2015-02-09 | 2016-12-07 | 徐夫子 | Dynamic magnetoelectric amplifying device |
| CN106402303A (en) * | 2015-07-30 | 2017-02-15 | 郑云兵 | Transmission |
| CN106402303B (en) * | 2015-07-30 | 2019-07-09 | 郑云兵 | A kind of speed changer |
| CN105546093A (en) * | 2016-02-23 | 2016-05-04 | 陈志雄 | Continuously variable transmission |
| CN105546093B (en) * | 2016-02-23 | 2018-11-16 | 陈志雄 | Stepless transmission |
| CN107830151A (en) * | 2017-11-30 | 2018-03-23 | 西安石油大学 | A kind of hydraulic column array multi-stage reducing belt wheel |
| CN107858758A (en) * | 2017-12-07 | 2018-03-30 | 中国热带农业科学院农业机械研究所 | A kind of sprocket transmission device that numb machine regulation draw ratio is managed for sisal hemp |
| WO2019119531A1 (en) * | 2017-12-20 | 2019-06-27 | 谭波 | Chain-type stepless speed reducer |
| US11566689B2 (en) | 2017-12-20 | 2023-01-31 | Bo Tan | Chain type stepless transmission |
| CN108843755A (en) * | 2018-06-15 | 2018-11-20 | 李存伟 | A kind of stepless automatic transmission |
| CN110566642A (en) * | 2019-09-20 | 2019-12-13 | 付鹰波 | Stepless speed variator for motor vehicle |
| CN110566642B (en) * | 2019-09-20 | 2023-02-03 | 付鹰波 | Stepless speed variator for motor vehicle |
| CN110630710A (en) * | 2019-09-29 | 2019-12-31 | 梁恩 | Anti-skid continuously variable transmission |
| CN112354833A (en) * | 2020-10-09 | 2021-02-12 | 重庆工程职业技术学院 | Cleaning mechanism and kitchen waste sorting assembly line thereof |
| CN112354835A (en) * | 2020-10-09 | 2021-02-12 | 重庆工程职业技术学院 | Drum screen and kitchen waste sorting production line thereof |
| CN112354834A (en) * | 2020-10-09 | 2021-02-12 | 重庆工程职业技术学院 | Drum screen and kitchen waste sorting assembly line |
| US20230228319A1 (en) * | 2022-01-14 | 2023-07-20 | Keith Nicholas Jourden | Reduced Vibration, Shift Compensating, Continuously Variable Transmission |
| US11739817B2 (en) * | 2022-01-14 | 2023-08-29 | Keith Nicholas Jourden | Reduced vibration, shift compensating, continuously variable transmission |
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Application publication date: 20110615 |