CN101699101B - Gear transmission automatic continuously variable transmission - Google Patents
Gear transmission automatic continuously variable transmission Download PDFInfo
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- CN101699101B CN101699101B CN2009101882840A CN200910188284A CN101699101B CN 101699101 B CN101699101 B CN 101699101B CN 2009101882840 A CN2009101882840 A CN 2009101882840A CN 200910188284 A CN200910188284 A CN 200910188284A CN 101699101 B CN101699101 B CN 101699101B
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Abstract
The invention provides a gear transmission automatic continuously variable transmission, which is characterized in that: a dual input gear is rotationally connected to an output shaft; a central non-circular gear is rotationally connected to the output shaft; the central non-circular gear is fixedly connected with the dual input gear; a non-circular planetary gear is connected to the output shaft via a planet carrier; the non-circular planetary gear is engaged with the central non-circular gear; a spiral shaft is connected in the non-circular planetary gear; a rotatable dual planetary gear is sleeved outside the non-circular planetary gear; an internal thread of the non-circular planetary gear is connected with a torque setting gear; a cam is assembled between a partition board and the torque setting gear; a polyurethane spring is assembled in an inner hole of the cam; the polyurethane spring is arranged between the partition board and the spiral shaft; a power dividing gear is rotationally connected to the output shaft; and an inverter is assembled between the power dividing gear and a case wall. The invention has the advantage that the gear transmission automatic continuously variable transmission keeps a balanced power property, achieves sensitive variation and response and improves working efficiency and operation capacity within ranges of a pre-set input revolution and a minimum use revolution during automatic stepless variation of rotational speed. The gear transmission automatic continuously variable transmission can prevent an entire equipment system from being damaged and can ensure safe use and efficient operation in a speed changing process, in which the revolution of the output shaft falls to zero revolution from the minimum revolution.
Description
Technical field
The invention belongs to a kind of speed change gear, particularly a kind of gear transmission automatic continuously variable transmission.
Background technique
Existing stepless change has many forms; Like square position rub wheeled, steel band cone disk type, mechanical pulse formula, friction and gear train is box-like, conical ring formula, viscous liquid formula, electricity (magnetic) rheological body formula, frequency control of motor speed formula, automatically controlled soft start etc.; These technology belong to automatic stepless speed change seldom, but are control continuously variable transmission mostly, and need the external force pressurization device; Do not have zero rotating speed output, have different separately deficiency and shortcomings such as constant output characteristic difference.
Summary of the invention
The purpose of this invention is to provide a kind of gear transmission automatic continuously variable transmission, 1, can adapt to the load frequent changes, the peak power in changing is high and of short duration, jam is arranged, impact many, as to be not easy to shut down speed change occasions.2, in the input revolution and minimum use range of revolution in setting slewing range, with load variations, when the rotating speed automatic stepless changes, keep constant output characteristic, it is sensitive that reacting condition is wanted, and works in high power factor to guarantee prime mover, increases work efficiency.3, press the input revolution that original machine power is set need of work; The moment of torsion of input revolution is adjusted in calculating, and the asynchronous staggered gear mechanism of design strap cam mechanism, disregards under the situation of wearing power at prime mover; The high-power phenomenon with little load or the big load of small-power band of prime mover can not appear; The original machine power factor is high, nonoverload, high working efficiency.4, the control gear of designing minimum revolution installs non-return device additional, plays the power dividing effect simultaneously, and output shaft is dropped to the speed-change process of zero revolution by minimum revolution; Should be bordering on permanent torque condition; Power dividing has prevented that speed change (reduction of speed) rotating speed from leveling off to zero the time, and output torque infinitely strengthens, and guarantees that whole change system is not damaged; Safe in utilization, guarantee efficient operation.5, have wide range of applications.
The objective of the invention is to realize through following technological scheme: it comprises casing, input shaft, input prime mover gear, output shaft and output cylindrical gears; It is characterized in that: the doubly-linked that is rotationally connected on output shaft input gear and power dividing gear, and through key connection output cylindrical gears; The gearwheel of the doubly-linked input gear on prime mover gear engagement output shaft on the input shaft; The center noncircular gear that on output shaft, is rotationally connected, the center noncircular gear be fixed together with doubly-linked input gear; The planet carrier that on output shaft, is rotationally connected, the non-circular planetary gear that on planet carrier, is rotationally connected, non-circular planetary gear engagement center noncircular gear; In the extension hollow shaft of non-circular planetary gear, connect screw axis through spline; The doubly-linked planetary pinion that suit can rotate outside the extension hollow shaft of non-circular planetary gear; The planetary hollow shaft internal key of doubly-linked connects and the screw axis nut engaged, assembles polyurethane spring passing through between the lid of nut and the planetary hollow shaft of doubly-linked end; The non-circular planetary gear internal thread connects torque setting gear, the small gear of torque setting gear engagement doubly-linked input gear; In the extension hollow shaft of non-circular planetary gear, install dividing plate, between dividing plate and torque setting gear, assemble cam, cam is provided with endoporus, assembles polyurethane spring in the endoporus, and the adjustment wire ring is threaded in the outer end of cam; Between dividing plate and screw axis, polyurethane spring is set; The doubly-linked planetary pinion is provided with two gears, the output cylindrical gears on gear engagement output shaft, the power dividing gear on another gear engagement output shaft; Between the tank wall of the outrigger shaft of power dividing gear and casing, assemble non-return device.
Good effect of the present invention is: 1, can adapt to the load frequent changes, the peak power in changing is high and of short duration, jam is arranged, impact many, as to be not easy to shut down speed change occasions.2, in the input revolution and minimum use range of revolution in setting slewing range; With load variations, when the rotating speed automatic stepless changes, keep the weighing apparatus power characteristic, reacting condition is sensitive; Work in high power factor with assurance prime mover, increase work efficiency and work capacity.3, press the input revolution that original machine power is set need of work; The moment of torsion of input revolution is adjusted in calculating, and the asynchronous staggered gear mechanism of design strap cam mechanism, disregards under the situation of wearing power at prime mover; The high-power phenomenon with little load or the big load of small-power band of prime mover can not appear; The original machine power factor is high, nonoverload, high working efficiency.4, the control gear of designing minimum revolution installs non-return device additional, plays the power dividing effect simultaneously, and output shaft is dropped to the speed-change process of zero revolution by minimum revolution; Should be bordering on permanent torque condition; Power dividing has prevented that speed change (reduction of speed) rotating speed from leveling off to zero, and output torque infinitely strengthens, and guarantees that whole change system is not damaged; Safe in utilization, guarantee efficient operation.5, have wide range of applications.
Description of drawings
Fig. 1 is a structural representation of the present invention.
Fig. 2 is the I portion enlarged diagram of Fig. 1.
Fig. 3 is the II portion enlarged diagram of Fig. 1.
Fig. 4 is torque setting gear and cam set assembling structure part enlarged diagram.
Fig. 5 is torque setting gear and cam set assembling structure exploded perspective schematic representation.
Fig. 6 and Fig. 7 are respectively that the slope boss circumference on torque setting gear, the cam fitting surface launches schematic representation.
Fig. 8 is a speed change drive state schematic representation.
Fig. 9 is a self-locking state underdrive schematic representation.
Embodiment
See Fig. 1-4, concrete structure of the present invention is following: connect input shaft 19 and output shaft 1 through bearing in the casing 2, the input shaft 19 inner input prime mover gears 18 that connect.Through the bearing doubly-linked input gear 16 that is rotationally connected, and connect output cylindrical gears 17 on the output shaft 1 through key.On the doubly-linked input gear 16 gearwheel 28 and small gear 29 are set.The gearwheel 28 of prime mover gear 18 engagement doubly-linked input gears on the input shaft.Through the bearing center noncircular gear 31 that is rotationally connected, center noncircular gear 31 is fixed together through tapered internal and external threads and key with doubly-linked input gear 16 on output shaft 1.On output shaft 1 through the bearing planet carrier 12 that is rotationally connected, the non-circular planetary gear 10 that assembling is rotated on planet carrier 12, non-circular planetary gear 10 engagement center noncircular gears 31.In the extension hollow shaft of non-circular planetary gear 10, has spiral fluted screw axis 8 through the spline connection.The doubly-linked planetary pinion 9 that suit can rotate outside the extension hollow shaft of non-circular planetary gear 10; Both are through on inside and outside wall, offering the internal and external circumference raceway groove; In circumferential channels, fill steel ball 25 and realize rotating, and on outer wall, have load hole, assembling plug 24 on the hole.Doubly-linked planetary pinion 9 is provided with two gears, the output cylindrical gears 17 that gear 22 meshes on the output shafts, the power dividing gear 4 on another gear 23 engagement output shafts.Extending the hollow shaft internal key at doubly-linked planetary pinion 9 connects and screw axis 8 nut engaged 7; Cover 5 in that the hollow shaft end of doubly-linked planetary pinion 9 is affixed, at nut 7 and cover assembling polyurethane spring 6 (polyurethane spring is the column part of rubber-like polyurethane material) between 5 thoroughly.Connect torque setting gear 15 at non-circular planetary gear 10 internal threads, the small gear 29 of torque setting gear 15 engagement doubly-linked input gears.In the extension hollow shaft of non-circular planetary gear 10, install dividing plate 13; Assembling cam 26 between dividing plate 13 and torque setting gear 15; See Fig. 5,6,7, cam 26 is connected in the non-circular planetary gear 10 through spline 27, and the counterface of cam 26 is along two slope boss 14 circumferentially are set; (another slope boss among Fig. 5 at relative position, not shown).Torque setting gear 15 is provided with two slope boss 20, (see figure 7), and two slope boss 14 of two slope boss 20 slopes contacts, and the slip that can make progress along the slope, oppositely then both ends of the surface are blocked.Cam 26 is provided with endoporus, assembling polyurethane spring 32 in the endoporus, and adjustment wire ring 30 is threaded in the outer end of cam 26.Between dividing plate 13 and screw axis 8, polyurethane spring 11 is set; On output shaft 1 through the bearing power dividing gear 4 that is rotationally connected.Assembling ring gear 21 on the tank wall of casing 2, the ratchet 3 that assembling cooperates with ring gear 21 on the outrigger shaft of power dividing gear 4 constitutes non-return device, and non-return device is an existing technology.
Working principle:
1, stepless change:
See Fig. 8, non-circular planetary gear 10 is arranged on the planet carrier 12, output shaft 1 is provided with output cylindrical gears 17, center noncircular gear 31.Two noncircular gears 10 and 31 are congruent gear; Those gear 22 velocity ratios that are meshed with the output cylindrical gears in output cylindrical gears 17 and the doubly-linked planetary pinion are 1: 1.5-1: 2; The semi major axis of noncircular gear equates that with the Pitch radius of output cylindrical gears 17 short radius equates with gear 22 radiuses.See Fig. 9, when two gear pair velocity ratios equate when center noncircular gear 31 forwards semi major axis to, transmission generation self-locking, center noncircular gear 31 rotates with output cylindrical gears 17 synchronously, and velocity ratio is 1.When the load of output cylindrical gears 17 increases; Polyurethane spring 11 is actuated, and center noncircular gear 31 leaves self-locking area and gets into the speed change drive state, such self-locking, leaves; The speed change drive state that the alternate cycles variation is facilitated is along with load variations; Rotating speed rose when load reduced, and the row axle on the planet carrier 12 is equivalent to the II axle of two grade standard retarders, and difference is and can week changes into automatic stepless speed change; The flexible connection of planet axis can be actuated automatic stepless speed change, and it is sensitive to keep the even speed change of rotating speed.
2, the control of output shaft zero rotating speed, i.e. the unlimited control that increases of the zero rotating speed of output shaft and torque value etc.:
Power dividing gear 4 is paid 17,22 velocity ratios with gear 23 velocity ratios of doubly-linked planetary pinion 9 greater than output gear, and specific output gear pair rotating speed is low and be idle running, when output cylindrical gears 17 rotating speeds are reduced to the rotating speed of setting; The speed drop of power dividing gear 4 is to zero; When output cylindrical gears 17 rotating speeds continued to drop to the negative rotating speed of zero or setting, power dividing gear 4 forced planet carrier to quicken negative rotation under the non-return device effect, and the purpose of design is for making the kurtosis power dividing like this; Realized zero output; Prevented that moment of torsion from infinitely increasing, protected change system not to be damaged, kurtosis power is very of short duration.Prime mover nonoverload when zero output.
3, the adjustment of input torque:
After setting input speed and moment of torsion, noncircular gear pays 10,31, and torque setting gear is paid 15,29, two pairs central gear 31,29 and connected firmly and become the doubly-linked gear, and two pairs planetary pinion 10,15 is adjustable flexible connection, and two pairs velocity ratio is identical to be 1: 1.The cam 26 of splined is housed in the axle of non-circular planetary gear 10, and the slope boss 14 of cam 26 is set to cam with 20 pairs of slope boss on the torque setting gear 15 and pays.With externally threaded wire ring 30 spinning polyurethane spring 32, adjust to non-circular planetary gear 10 and can drive planet carrier 12 and rotate synchronously.Planet wheel does not all have rotation, starts that the back measures that output shaft 1 rotating speed is identical with the setting rotating speed, the moment of torsion of moment of torsion and setting is identical.Planet wheel is with planet carrier 12 week then till the no rotation, can guarantees after the adjustment to cause because of the inertia torque of planet carrier 12 state of rest to start difficulty, guarantee startup after, output shaft 1 does not have retardation phenomenon in the prescribed torque scope.
This engine efficiency: WW planetary reducer structure has been adopted in design, and during because of the transmission of this machine, planet carrier is not exported; When setting the maximum speed that uses, do not rotate mutually between each gear; Input output transmission in 1: 1, when the output shaft rotating speed dropped to a certain value, planet carrier was motionless; The planet axis rotation is not had enough to meet the need.When the output shaft rotating speed continue to reduce, planet carrier was accelerated and is negative rotating speed, and two planet axis are opposed, and centrifugal force reduces self-locking frictional force, the reduction that kept efficient not, and two planet axis have been kept very high efficient with respect to the II axle of two grade standard retarders.
Claims (3)
1. gear transmission automatic continuously variable transmission; It comprises casing, input shaft, input prime mover gear, output shaft and output cylindrical gears; It is characterized in that: the doubly-linked that is rotationally connected on output shaft input gear and power dividing gear, and through key connection output cylindrical gears; The gearwheel of the doubly-linked input gear on prime mover gear engagement output shaft on the input shaft; The center noncircular gear that on output shaft, is rotationally connected, the center noncircular gear be fixed together with doubly-linked input gear; The planet carrier that on output shaft, is rotationally connected, the non-circular planetary gear that on planet carrier, is rotationally connected, non-circular planetary gear engagement center noncircular gear; In the extension hollow shaft of non-circular planetary gear, connect screw axis through spline; The doubly-linked planetary pinion that suit can rotate outside the extension hollow shaft of non-circular planetary gear; The planetary hollow shaft internal key of doubly-linked connects and the screw axis nut engaged, assembles polyurethane spring passing through between the lid of nut and the planetary hollow shaft of doubly-linked end; The non-circular planetary gear internal thread connects torque setting gear, the small gear of torque setting gear engagement doubly-linked input gear; In the extension hollow shaft of non-circular planetary gear, install dividing plate, between dividing plate and torque setting gear, assemble cam, cam is provided with endoporus, assembles polyurethane spring in the endoporus, and the adjustment wire ring is threaded in the outer end of cam; Between dividing plate and screw axis, polyurethane spring is set; The doubly-linked planetary pinion is provided with two gears, the output cylindrical gears on gear engagement output shaft, the power dividing gear on another gear engagement output shaft; Between the tank wall of the outrigger shaft of power dividing gear and casing, assemble non-return device.
2. gear transmission automatic continuously variable transmission according to claim 1; It is characterized in that: the counterface of cam is along two slope boss circumferentially are set; Torque setting gear is along circumferentially being provided with two slope boss equally, and with two slope boss sliding contacts of cam along the slope.
3. gear transmission automatic continuously variable transmission according to claim 1 is characterized in that: center noncircular gear and non-circular planetary gear are congruent gear; In output cylindrical gears on the output shaft and the doubly-linked planetary pinion and that gear ratio its engagement are 1: 1.5-1: 2; The semi major axis of noncircular gear equates with the Pitch radius of output cylindrical gears, in short radius and the doubly-linked planetary pinion with export that tooth radius that cylindrical gears is meshed and equate.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009101882840A CN101699101B (en) | 2009-10-30 | 2009-10-30 | Gear transmission automatic continuously variable transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009101882840A CN101699101B (en) | 2009-10-30 | 2009-10-30 | Gear transmission automatic continuously variable transmission |
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| Publication Number | Publication Date |
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| CN101699101A CN101699101A (en) | 2010-04-28 |
| CN101699101B true CN101699101B (en) | 2012-02-22 |
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| CN2009101882840A Active CN101699101B (en) | 2009-10-30 | 2009-10-30 | Gear transmission automatic continuously variable transmission |
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Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108412982B (en) * | 2018-05-11 | 2024-01-26 | 中国人民解放军陆军军事交通学院 | Combined non-circular gear stepless speed change transmission device |
| CN110030338A (en) * | 2019-04-07 | 2019-07-19 | 罗灿 | Centre wheel planet row speed changer of the same race |
| CN110953306B (en) * | 2019-12-17 | 2021-06-18 | 清华大学 | Non-linear spring mechanism based on non-circular planetary gear |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4788891A (en) * | 1986-12-05 | 1988-12-06 | Japan Society For The Promotion Of Machine Industry | Planetary gear having non-circular gears |
| CN2276586Y (en) * | 1996-10-14 | 1998-03-18 | 李芳达 | Automatic speed variator consist of chain planet differental mechanism |
| CN2325304Y (en) * | 1998-01-24 | 1999-06-23 | 朱宝理 | Stepless dynamic periodic speed changing center shaft device for bicycle |
| CN201535349U (en) * | 2009-10-30 | 2010-07-28 | 沈阳龙德石油技术开发有限公司 | Gear mesh transmission automatic stepless speed changer |
-
2009
- 2009-10-30 CN CN2009101882840A patent/CN101699101B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4788891A (en) * | 1986-12-05 | 1988-12-06 | Japan Society For The Promotion Of Machine Industry | Planetary gear having non-circular gears |
| CN2276586Y (en) * | 1996-10-14 | 1998-03-18 | 李芳达 | Automatic speed variator consist of chain planet differental mechanism |
| CN2325304Y (en) * | 1998-01-24 | 1999-06-23 | 朱宝理 | Stepless dynamic periodic speed changing center shaft device for bicycle |
| CN201535349U (en) * | 2009-10-30 | 2010-07-28 | 沈阳龙德石油技术开发有限公司 | Gear mesh transmission automatic stepless speed changer |
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| CN101699101A (en) | 2010-04-28 |
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