CN103244627A - Dual-wheel eccentricity-adjusting balancing stepless speed changing device - Google Patents
Dual-wheel eccentricity-adjusting balancing stepless speed changing device Download PDFInfo
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- CN103244627A CN103244627A CN 201210028414 CN201210028414A CN103244627A CN 103244627 A CN103244627 A CN 103244627A CN 201210028414 CN201210028414 CN 201210028414 CN 201210028414 A CN201210028414 A CN 201210028414A CN 103244627 A CN103244627 A CN 103244627A
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- stepless speed
- tuningout
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Abstract
The invention relates to a dual-wheel eccentricity-adjusting balancing stepless speed changing device. The device is mainly composed of a central input shaft, a central output shaft, a plurality of intermediate shafts, a reverse gear shaft, an eccentricity-adjusting driving wheel, a unidirectional overrunning clutch and gear assembly, gears and an eccentricity-adjusting actuating mechanism. The operating principle of the main structure of the device includes that the plurality of intermediate shafts are uniformly distributed around a central shaft in the unified radius within a 360-degree range to form a round ordinary gear train. Two adjustable eccentric wheels are arranged on the central input shaft and comprise the driving wheel and the balancing wheel, a round groove on the driving wheel is connected with unidirectional overrunning clutch casings on intermediate shafts through universal sliding blocks, and gears on the plurality of intermediate shafts are meshed with a gear on the unidirectional overrunning gear assembly on the central input shaft to conduct alternate transmission, so that the uninterrupted pulse-free constant-speed stepless speed changing can be achieved. The device is applicable to motor vehicles, main clutches and planetary gear differential mechanisms are not required to be arranged, and the device is simple in structure, low in cost, safe, convenient, energy-saving and capable of reducing emission.
Description
Affiliated technical field
The present invention relates to a kind of stepless speed variator, especially a kind of speed ratio torque is very big, can adapt to various motor vehicle, the stepless speed variator on boats and ships and the various machine.
Background technique
Used stepless speed variator is to adopt two band or sprocket wheels that working diameter is variable on the present known automobile, be friction type stepless speed changer, shortcoming is easily to skid, and torque is limited, can not adapt to the big required stepless change of torque on medium-sized, large-scale, heavy-duty car and other the various machines.Other crankrocker mechanism, shortcoming are that speed ratio is limited, can not adapt to high rotating speed because the pulse vibration is big.Night, power bending moment type ratio coverage was very narrow, the energy consumption height.
Summary of the invention
Easily skid in order to overcome existing stepless speed variator, speed ratio, torque be limited can not to adapt to big torque, high rotating speed stepless change is required.The invention provides a kind of stepless speed variator, as use on the automobile, exempt to establish main clutch, exempt to establish the planetary gear type differential mechanism, also can exempt to use friction-type brake apparatus, the non-constant width of ratio coverage can be from zero-speed to required high speed, torque can reach required peak torque, can adapt to various motor vehicle and all size boats and ships and the required stepless change of various machine.
The technological scheme that technical solution problem of the present invention adopts is: exempt to establish connecting rod, exempt to establish band or chain-driven unit, only adopt eccentric, slide-block mechanism, just realized that speed ratio is very big, the very big stepless change of torque.The center input shaft is provided with two adjustable eccentric stabilizers in housing, and the wheel outer side surface is provided with the round recessed slideway.Be benchmark with the central shaft, unified radius is provided with some jack shafts on every side, comprise 1,2,3,4 are waited radical to be the circle fixed shaft gear train, axle head length is no more than adjustable eccentric balance driving wheel in the some jack shafts of this circle fixed shaft gear train, some unified 360 degree of jack shaft calibration are divided equally, unified mono-directional overrun clutch and the eccentric combination parts of all being provided with on the some jack shafts, some jack shafts unified all cogging with central shaft that cog is meshed, the off-centre of mono-directional overrun clutch and eccentric combination parts on some jack shafts, unified connect transmission by round concave shape slideway on universal slide block separately and the adjustable eccentric balance driving wheel.The degree of eccentricity size of two adjustable eccentric stabilizers is all can realize transferring degree of eccentricity size and balance by mechanical force or electric power, magnetic force, fluid power actuator.Regulating and controlling mechanism work is then by flyball centrifugal force size auto-control on the output shaft.Some jack shaft length are no more than adjustable eccentric balance driving wheel, could realize that eccentric shoe does not have the linkage mechanism transmission, could become pulsation into smooth-going, could realize at a high speed, just can make driven eccentric reciprocally swinging amplitude be increased to 180 degree maximum values, be advisable but should be slightly less than 180 degree during practical application.From zero amplitude of oscillation without acceptance of persons just zero-speed can replace main clutch for separating, from zero-speed begin to add gradually large eccentricity just from starting low speed to the realization of High Speed of setting the non-constant width of speed ratio, eccentric more little torque of transferring is just more big.Realized that because of stepless the speed ratio torque is very big, simultaneously also can stepless smooth-going deceleration, such result can play the skidding effect, also can exempt to use friction-type brake apparatus, reaching that brake is lubricated does not generate heat no locking, the purpose of smooth-going deceleration.
Beneficial effect of the present invention is that speed ratio is very big; can be from zero-speed to required high speed, torque is very big, can satisfy the required stepless change of all machines; can exempt to establish main clutch in the automobile use; exempt to establish the planetary gear type differential mechanism, exempt to establish differential lock, also can exempt to use friction-type brake apparatus; cost simple in structure is low; energy-saving and emission-reduction, protection environment, safe ready.
Description of drawings
The present invention is further described below in conjunction with drawings and Examples
Fig. 1 is diagonal-bracing type two-wheel tuningout heart balancing stepless speed changer general structure principle generalized section of the present invention.
Fig. 2 is that the present invention extremely fills in cylinder barrel two-wheel tuningout heart balancing stepless speed changer general structure principle generalized section alive.
Fig. 3 is three jack shafts of the present invention circle fixed shaft gear train unified and central shaft engagement generalized sections that cog that cog.
Fig. 4 is that unification is provided with mono-directional overrun clutch and eccentric combination part, assembles a tube schematic representation with universal slide block, round concave shape slideway on three jack shafts of the present invention.
Fig. 5 is that two jack shafts of the present invention, 360 degree are divided equally simple schematic representation.
Fig. 6 is that three jack shafts of the present invention, 360 degree are divided equally simple schematic representation.
Fig. 7 is that four jack shafts of the present invention, 360 degree are divided equally simple schematic representation.
Fig. 8 is that five jack shafts of the present invention, 360 degree are divided equally simple schematic representation.
Fig. 9 is that the universal roller slide block of the present invention master looks cut-away view.
Figure 10 is that cut-away view is looked on a universal roller slide block left side.
Figure 11 is that universal roller slide block is overlooked cut-away view.
Figure 12 is skewback tuningout heart equilibrium structure principle generalized section of the present invention.
Figure 13 is two-wheel tuningout heart balancing stepless speed changer of the present invention, two output shaft structural principle generalized sections.
Among the figure 1, the center input shaft, 2, bearing, 3, casing, 4, the hydraulic pressure oil ring, 5, the hydraulic pressure oil duct, 6, piston, 7, cylinder barrel, 8, piston rod, 9, tuningout heart stabilizer, 10, tuningout heart diagonal brace, 11, the connecting shaft wheel, 12, tuningout heart driving wheel, 13, drive samsara and end position dotted line without acceptance of persons, 14, the spacing dotted line of axle head length in the jack shaft, 15, universal slide block, 16, gear, 17, mono-directional overrun clutch and gear train component, 18, the forward gears gear, 19, the engage a gear gear, 20, jack shaft, 21, output shaft, 22, dead plug, 23, the dead stopper rod of connecting shaft, 24, cylinder barrel is set on the tuningout heart driving wheel claims the cylinder barrel of living, 25, round concave shape slideway on the tuningout heart driving wheel, 26, reverse gear shaft, 27, mono-directional overrun clutch and eccentric combination part, 28, cardan shaft, 29, tuningout heart slideway, 30, some jack shafts are unified radius, 31, some unified 360 degree of jack shaft are divided equally, 32, axle roller support body, 33, the axle roller, 34, awl tooth input shaft, 35, coupling angular wheel, 36, tuningout heart skewback, 37, weighting distribution wheel.
Embodiment
With reference to Fig. 5, Fig. 6, Fig. 7, Fig. 8, some jack shafts (20) are unified to be benchmark with center input shaft (1), and unified radius 360 degree are divided into round fixed shaft gear train.Place restrictions on reference to Fig. 1, Fig. 2, the axle head length unification of some jack shafts of Fig. 4 (20) lining and to be no more than the spacing line of jack shaft length (14), just realized on the some jack shafts that mono-directional overrun clutch and eccentric combination part (27) are gone up, mono-directional overrun clutch outer shroud reciprocally swinging amplitude, can reach 180 degree maximum values.Three jack shaft 120 degree divide distance, just 3 180 degree are that the effective work done handover free of discontinuities of 540 degree is finished 360 degree uniform rotation, can make output speed, have realized that from zero-speed to the required maximum speed of design speed ratio is very big, torque is very big, does not have and does not intermittently have the at the uniform velocity smooth-going transmission of impact.Output speed is low to moderate critical zero-speed and obtains peak torque, because realizing zero-speed without acceptance of persons, also can exempt to establish main clutch, reduces cost.With reference to Fig. 3, (20) unified gear (16) that is equipped with on the some jack shafts, unifying all cogs with gear train component (17) with the last mono-directional overrun clutch of center input axis (1) is meshed, the associating transmission, some jack shafts (20) cog (16) all be in the same way, synchronously naturally, uniform rotation.Center input shaft (1) is gone up because being provided with mono-directional overrun clutch and gear train component (17), so input speed can surmount output shaft (21) rotating speed that cogs, rotating speed can only slide below the input shaft rotating speed and this output shaft cogs, but can not surmount the input shaft rotating speed, such result just guarantees on the automobile to use this stepless change can slide energy-saving, and engine speed can control the speed of a motor vehicle and slide safely, can play the retarding braking effect again, also can exempt to use friction-type brake apparatus.
Claims (4)
1. two-wheel tuningout heart balancing stepless speed changer, mainly by the center input shaft, tuningout heart stabilizer, tuningout heart driving wheel, some jack shafts (driven shaft), mono-directional overrun clutch, gear, reverse gear shaft, output shaft, universal slide block, tuningout heart actuator forms, it is characterized in that: the unification of axle head length is no more than two-wheel tuningout heart balance driving wheel in the some jack shafts (driven shaft), and some jack shaft mono-directional overrun clutch outer shrouds are to connect transmission by universal slide block with driving wheel.
2. require some jack shafts of 1 described a kind of two-wheel tuningout heart balancing stepless speed changer according to profit, it is characterized in that some, comprise that many radicals such as 1,2,3 are some.
3. according to the described two-wheel tuningout of claim 1-2 heart balancing stepless speed changer, some jack shafts is characterized in that: some jack shafts unified equidistant, etc. degree be the circle fixed shaft gear train around central shaft.
4. according to the described two-wheel tuningout of claim 1-2-3 heart balancing stepless speed changer, some jack shafts is characterized in that: some jack shafts cog all to cog with the gear train component with the clutch of center input mono-directional overrun and are meshed.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201210028414 CN103244627A (en) | 2012-02-01 | 2012-02-01 | Dual-wheel eccentricity-adjusting balancing stepless speed changing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201210028414 CN103244627A (en) | 2012-02-01 | 2012-02-01 | Dual-wheel eccentricity-adjusting balancing stepless speed changing device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN103244627A true CN103244627A (en) | 2013-08-14 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201210028414 Pending CN103244627A (en) | 2012-02-01 | 2012-02-01 | Dual-wheel eccentricity-adjusting balancing stepless speed changing device |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN103244627A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105003611A (en) * | 2014-04-18 | 2015-10-28 | 本田技研工业株式会社 | Driving force transmission device |
| CN108502094A (en) * | 2018-05-14 | 2018-09-07 | 赵宁 | Step-less speed changing planetary gear system |
-
2012
- 2012-02-01 CN CN 201210028414 patent/CN103244627A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105003611A (en) * | 2014-04-18 | 2015-10-28 | 本田技研工业株式会社 | Driving force transmission device |
| CN105003611B (en) * | 2014-04-18 | 2017-06-23 | 本田技研工业株式会社 | Drive force transfering device |
| CN108502094A (en) * | 2018-05-14 | 2018-09-07 | 赵宁 | Step-less speed changing planetary gear system |
| CN108502094B (en) * | 2018-05-14 | 2024-04-02 | 赵宁 | Planetary gear stepless speed change system |
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| C06 | Publication | ||
| PB01 | Publication | ||
| C05 | Deemed withdrawal (patent law before 1993) | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20130814 |