CN102777555A - Continuous power infinitely variable speed transmission mechanism - Google Patents
Continuous power infinitely variable speed transmission mechanism Download PDFInfo
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- CN102777555A CN102777555A CN2012102858215A CN201210285821A CN102777555A CN 102777555 A CN102777555 A CN 102777555A CN 2012102858215 A CN2012102858215 A CN 2012102858215A CN 201210285821 A CN201210285821 A CN 201210285821A CN 102777555 A CN102777555 A CN 102777555A
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- 230000007246 mechanism Effects 0.000 title abstract description 10
- 230000005540 biological transmission Effects 0.000 title abstract description 8
- 238000012423 maintenance Methods 0.000 claims description 3
- 238000000034 method Methods 0.000 abstract description 13
- 230000001360 synchronised effect Effects 0.000 abstract description 5
- 230000002457 bidirectional effect Effects 0.000 abstract 1
- 239000012530 fluid Substances 0.000 description 3
- 230000035939 shock Effects 0.000 description 3
- FFBHFFJDDLITSX-UHFFFAOYSA-N benzyl N-[2-hydroxy-4-(3-oxomorpholin-4-yl)phenyl]carbamate Chemical compound OC1=C(NC(=O)OCC2=CC=CC=C2)C=CC(=C1)N1CCOCC1=O FFBHFFJDDLITSX-UHFFFAOYSA-N 0.000 description 2
- 239000000969 carrier Substances 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
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Abstract
The invention discloses a continuous power infinitely variable speed transmission mechanism, which comprises a reverse synchronous gear and a positive synchronous gear which are respectively in gear engagement with a power keeping input shaft, a first planetary gear train and a second planetary gear train which are connected through a speed-regulating power input shaft, and a transmission gear engaged with an output shaft keeping gear, wherein a bidirectional synchronizing clutch is arranged between the reverse synchronous gear and the positive synchronous gear and is connected to the second planetary gear train through the clutch; and the transmission gear is connected with the first planetary gear train through an output switching clutch and is connected with the second planetary gear train through a second internal gear. The full-range infinitely variable speed of the output shaft from the reverse maximum speed to the positive maximum speed can be realized by means of the speed change of the speed-regulating power input shaft and the engagement and disengagement of the clutch only under the condition that the rotating speed and the rotating direction of the power keeping input shaft, the output speed is stably changed and no power is interrupted in the whole process. The variable speed in the reverse direction is performed in the same mode.
Description
Technical field
The present invention relates to driving mechanism, specifically a kind of continuous power infinitely variable speed gearing that is used for wheel machine.
Background technique
Gear-driven characteristics are that velocity ratio is fixed, if make output element have bigger slewing range often need design the gearbox that comprises a plurality of velocity ratios.When gear switch, owing to the nonsynchronous reason of element speeds, two gears are transferring power simultaneously, needs throw off afterwards earlier and meshes, and causes the interruption of outputting power.Owing to the nonsynchronous reason of speed, the gear shift meeting causes mechanical shock equally, then needs more velocity ratio if reduce to impact, and can make so again to control complicacy more.
On wheel machine, many at present employing fluid torque converters and hand shift gear-box are as walking speed-regulating device.Though fluid torque converter can absorb shifting shock well, its working efficiency is lower, especially when traveling gear is in the big torque conditions of the slow-speed of revolution.Also the operation on the ramp has very big influence to power interruption during gear shift to wheel machine.
For the gear graduation technical field, especially to running mechanism Driving technique field, mechanical shock when solving gear shift and power interruption are all very necessary for improving device operability, steady travelling comfort and reducing energy consumption.
In view of this, to the problems referred to above, propose a kind of reasonable in design and effectively improve the continuous power infinitely variable speed gearing of above-mentioned disappearance.
Summary of the invention
The object of the present invention is to provide a kind of continuous power infinitely variable speed gearing; Under the situation that the rotational velocity and the sense of rotation of continuous driving force input shaft all remains unchanged; Only depend on the velocity variations of speed governing power input shaft and the clutch of clutch just can realize the omnidistance stepless change of output shaft from reverse top speed to the forward top speed, whole process output speed changes steadily, power failure-free.Speed change is as the same in the other direction.
In order to reach above-mentioned purpose; The present invention has adopted following technological scheme; A kind of continuous power infinitely variable speed gearing, first planetary gear train that comprise respectively the reverse sync gear that keeps gear engagement with the continuous driving force input shaft and forward synchromesh gear, is connected through the speed governing power input shaft and second planetary gear train, with the driving gear of output shaft maintenance gear engagement; Be provided with the bi-directional synchronization clutch between said reverse sync gear and the forward synchromesh gear and be connected to second planetary gear train through this clutch; Said driving gear is connected with first planetary gear train through the output switch clutch on the one hand, is connected with second planetary gear train through secondary annulus on the other hand.
Said first planetary gear train and second planetary gear train include sun gear, planet carrier and internal gear, and the shared sun wheel shaft of two cover planetary gear train is as the speed governing power input shaft.
Internal gear in said first planetary gear train i.e. first internal gear is a Fixed Design, and the internal gear in said second planetary gear train is that secondary annulus is fixedly connected with driving gear.
The planet carrier that the said bi-directional synchronization clutch that is used for throwing off or combine with forward and reverse synchromesh gear is connected second planetary gear train is on second planet carrier; The planet carrier that the said output switch clutch that is used for throwing off or combine with driving gear is connected first planetary gear train is on first planet carrier.
Said reverse sync gear keeps gear engagement through tumbler gear and continuous driving force input shaft.
Said reverse sync gear and forward synchromesh gear all keep gear engagement with fixed speed ratio and continuous driving force input shaft; Keep gear engagement with fixed speed ratio between the said driving gear output shaft.
Compared to existing technology, the present invention has following beneficial effect:
The present invention makes full use of the characteristic of Gear Planet Transmission; At different gear shift stages with different planetary mechanism element drives output shafts; Make the speed rising of speed governing power input shaft still reduce the rising that all causes output shaft speed; And second cover planetary mechanism speed change be that terminal point with the first cover planetary mechanism slewing range is a starting point, realized adding up of slewing range, make the speed governing ability of speed governing power input element obtain maximum performance.Simultaneously, on second planet carrier, be provided with a bi-directional synchronization clutch, not only guaranteed the nothing impact of two cover planetary mechanisms and the switching of power failure-free, also can make forward and reverse output of speed changer that same big slewing range is all arranged.
No matter be that output shaft is rotated in the forward or counterrotating, two-way respectively have a specific velocity node, and this two node is the interface point of the first cover planetary gear train and the second cover planetary gear train slewing range.On node, bi-directional synchronization clutch during speedup on second planet carrier and synchromesh gear speed synchronization forward or backwards; Powershift clutch and transmission gear speeds during deceleration on first planet carrier are synchronous.Because clutch two rotating part speed synchronization can will soon break away from the throw-out-of clutch of the another set of planetary mechanism of work more earlier with the clutch combination of a cover planetary mechanism that will soon get into work.The power that has guaranteed the mechanical gear shift process is continuous, and does not have impact.
Description of drawings
Fig. 1 is the structure transmission principle figure of a kind of continuous power infinitely variable speed gearing of the present invention;
Fig. 2 is the output line speed and the element speeds graph of a relation of a kind of continuous power infinitely variable speed gearing of the present invention.
Among the figure: 1, the reverse sync gear; 2, the bi-directional synchronization clutch; 3, the forward synchromesh gear; 4, the second planet carriers; 5, secondary annulus; 6, output shaft; 7, the first planet carriers; 8, the speed governing power input shaft; 9, the first internal gears; 10, the output switch clutch; 11, driving gear; 12, the continuous driving force input shaft; 13, tumbler gear.
Embodiment
Relevant detailed description of the present invention and technology contents, conjunction with figs. are explained as follows, yet accompanying drawing only provides the usefulness of reference with explanation, are not to be used for the present invention is limited.
According to Fig. 1-shown in Figure 2; A kind of continuous power infinitely variable speed gearing, first planetary gear train that comprise respectively the reverse sync gear 1 that keeps gear engagement with continuous driving force input shaft 12 and forward synchromesh gear 3, is connected through speed governing power input shaft 8 and second planetary gear train, with the driving gear 11 of output shaft 6 maintenance gear engagement; Be provided with bi-directional synchronization clutch 2 between said reverse sync gear and the forward synchromesh gear and be connected to second planetary gear train through this clutch; Said driving gear is connected with first planetary gear train through output switch clutch 10 on the one hand, is connected with second planetary gear train through secondary annulus 5 on the other hand.Said reverse sync gear 1 keeps gear engagement through tumbler gear 13 and continuous driving force input shaft 12.
First planetary gear train and second planetary gear train include sun gear, planet carrier and internal gear, and the shared sun wheel shaft of two cover planetary gear train is as speed governing power input shaft 8.Internal gear in first planetary gear train i.e. first internal gear 9 is a Fixed Design, and the internal gear in said second planetary gear train is that secondary annulus 5 is fixedly connected with driving gear 11.The planet carrier that the bi-directional synchronization clutch that is used for throwing off or combine with forward and reverse synchromesh gear is connected second planetary gear train is on second planet carrier; The planet carrier that the said output switch clutch that is used for throwing off or combine with driving gear is connected first planetary gear train is on first planet carrier.Reverse sync gear and forward synchromesh gear all keep gear engagement with fixed speed ratio and continuous driving force input shaft; Keep gear engagement with fixed speed ratio between the said driving gear output shaft.
As shown in Figure 1, establish continuous driving force input shaft 12 rotation counterclockwise; Initial state speed governing power input shaft 8 rotating speeds are zero, and bi-directional synchronization clutch 2 all is in disengaged condition with output switch clutch 10, and output shaft 6 rotating speeds are zero under this state.
Above-mentioned rotary speed direction is to see from right to left according to Fig. 1, down together; If be forward counterclockwise.
1, if make output gear shaft 6 forward speedups, process is following:
1.1, output switch clutch 10 closures, first planetary gear train gets into working state;
1.2, oppositely increase the rotating speed of speed governing power input shaft 8;
1.3 because first internal gear 9 is fixing, speed governing power input shaft 8 can drive first planet carrier, 7 reverse speedups; Because the input switch clutch is closed, driving gear 11 and secondary annulus 5 are also along with first planet carrier, 7 reverse speedups; Driving gear 11 drives output shaft 6 forward speedups;
1.4, while secondary annulus 5 and speed governing power input shaft 8 driven in common second planet carrier 4 reverse speedups;
1.5, when second planet carrier, 4 speed increase to forward synchromesh gear 3 synchronously, earlier bi-directional synchronization clutch 2 is combined with forward synchromesh gear 3, will export switch clutch 10 again and throw off.This moment, mechanical gear shift was accomplished, and first planetary gear train breaks away from working state, and second planetary gear train gets into working state.There is not interruption in this gearshift procedure medium power output.
1.6, reducing speed governing power input shaft 8 rotating speeds and continue speedup to forward maximum (top) speed again to zero, secondary annulus 5 continues reverse speedups with driving gear 11 in this process, continues the forward speedup thereby drive output shaft 6.
2, if output shaft 6 is slowed down, its process is opposite with process 1.The main points in mechanical gear shift stage are: closed earlier output switch clutch 10, throw off bi-directional synchronization clutch 2 again.
3; The process of reverse speedup of output shaft and reduction of speed and process 1 and 2 are basic identical; Just the rotary speed direction of speed governing power input shaft 8 is opposite with its rotary speed direction in respective process, and in the mechanical gear shift process, bi-directional synchronization clutch 2 will combine with reverse sync gear 1 or throw off.
Fig. 2 has showed the rotational speed of each primary component in speed-change process and the corresponding relation between output speed.Horizontal ordinate: output line speed; Ordinate: transmission element rotating speed.101 are the corresponding relation line of speed governing power input shaft 8, and 102 is the corresponding relation line of first planet carrier 7, and 103 is the corresponding relation line of output shaft 6, and 104 is the corresponding relation line of second planet carrier 4, and 105 is the corresponding relation line of secondary annulus 5.
Two epicyclic trains work in different slewing ranges.In low-speed range, speed changer is by speed governing power input shaft single driving; In high-speed range, speed changer is by continuous driving force input shaft and speed governing power input shaft driven in common.On certain velocity node, two planetary gear train switch, two planetary gear train driven in common output shafts on the switching point.This type of belt drive is if adopt engine-driving continuous driving force input shaft, fluid motor-driven speed governing power input shaft, and the walking that then is highly suitable for wheel machine drives.
The above is merely preferred embodiment of the present invention, and non-in order to limit claim of the present invention, other use the equivalence of patent spirit of the present invention to change, and all should all belong to claim of the present invention.
Claims (6)
1. continuous power infinitely variable speed gearing; It is characterized in that, first planetary gear train that comprise respectively the reverse sync gear that keeps gear engagement with the continuous driving force input shaft and forward synchromesh gear, is connected through the speed governing power input shaft and second planetary gear train, with the driving gear of output shaft maintenance gear engagement; Be provided with the bi-directional synchronization clutch between said reverse sync gear and the forward synchromesh gear and be connected to second planetary gear train through this clutch; Said driving gear is connected with first planetary gear train through the output switch clutch on the one hand, is connected with second planetary gear train through secondary annulus on the other hand.
2. a kind of continuous power infinitely variable speed gearing according to claim 1; It is characterized in that; Said first planetary gear train and second planetary gear train include sun gear, planet carrier and internal gear, and the shared sun wheel shaft of two cover planetary gear train is as the speed governing power input shaft.
3. a kind of continuous power infinitely variable speed gearing according to claim 2; It is characterized in that; Internal gear in said first planetary gear train i.e. first internal gear is a Fixed Design, and the internal gear in said second planetary gear train is that secondary annulus is fixedly connected with driving gear.
4. a kind of continuous power infinitely variable speed gearing according to claim 2 is characterized in that, the planet carrier that the said bi-directional synchronization clutch that is used for throwing off or combine with forward and reverse synchromesh gear is connected second planetary gear train is on second planet carrier; The planet carrier that the said output switch clutch that is used for throwing off or combine with driving gear is connected first planetary gear train is on first planet carrier.
5. a kind of continuous power infinitely variable speed gearing according to claim 1 is characterized in that, said reverse sync gear keeps gear engagement through tumbler gear and continuous driving force input shaft.
6. a kind of continuous power infinitely variable speed gearing according to claim 1 is characterized in that, said reverse sync gear and forward synchromesh gear all keep gear engagement with fixed speed ratio and continuous driving force input shaft; Keep gear engagement with fixed speed ratio between the said driving gear output shaft.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210285821.5A CN102777555B (en) | 2012-08-13 | 2012-08-13 | Continuous power infinitely variable speed transmission mechanism |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201210285821.5A CN102777555B (en) | 2012-08-13 | 2012-08-13 | Continuous power infinitely variable speed transmission mechanism |
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| CN102777555A true CN102777555A (en) | 2012-11-14 |
| CN102777555B CN102777555B (en) | 2015-04-22 |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103486207A (en) * | 2013-03-12 | 2014-01-01 | 山东常林机械集团股份有限公司 | Continuous power stepless variable-speed transmission mechanism |
| CN103711847A (en) * | 2013-01-19 | 2014-04-09 | 龙宏元 | Multi-path driving continuous variable transmission for planetary gear |
| WO2020001589A1 (en) * | 2018-06-29 | 2020-01-02 | 比亚迪股份有限公司 | Transmission, power drive system and vehicle |
| CN110657203A (en) * | 2018-06-29 | 2020-01-07 | 比亚迪股份有限公司 | Transmission, power driving system and vehicle |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1998022733A1 (en) * | 1996-11-20 | 1998-05-28 | Aprotech Co., Ltd. | Continuously variable transmission |
| WO2006103294A1 (en) * | 2005-03-31 | 2006-10-05 | Torotrak (Development) Limited | Continuously variable transmission |
| CN101255915A (en) * | 2008-04-03 | 2008-09-03 | 常林股份有限公司 | Transmission mechanism of integral power shift hydraulic transmission for engineering machinery |
| CN202746512U (en) * | 2012-08-13 | 2013-02-20 | 山东常林机械集团股份有限公司 | Continuous power stepless speed-changing transmission mechanism |
-
2012
- 2012-08-13 CN CN201210285821.5A patent/CN102777555B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1998022733A1 (en) * | 1996-11-20 | 1998-05-28 | Aprotech Co., Ltd. | Continuously variable transmission |
| WO2006103294A1 (en) * | 2005-03-31 | 2006-10-05 | Torotrak (Development) Limited | Continuously variable transmission |
| CN101255915A (en) * | 2008-04-03 | 2008-09-03 | 常林股份有限公司 | Transmission mechanism of integral power shift hydraulic transmission for engineering machinery |
| CN202746512U (en) * | 2012-08-13 | 2013-02-20 | 山东常林机械集团股份有限公司 | Continuous power stepless speed-changing transmission mechanism |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103711847A (en) * | 2013-01-19 | 2014-04-09 | 龙宏元 | Multi-path driving continuous variable transmission for planetary gear |
| CN103486207A (en) * | 2013-03-12 | 2014-01-01 | 山东常林机械集团股份有限公司 | Continuous power stepless variable-speed transmission mechanism |
| CN103486207B (en) * | 2013-03-12 | 2015-12-23 | 山东常林机械集团股份有限公司 | A kind of power infinitely variable speed gearing continuously |
| WO2020001589A1 (en) * | 2018-06-29 | 2020-01-02 | 比亚迪股份有限公司 | Transmission, power drive system and vehicle |
| CN110657203A (en) * | 2018-06-29 | 2020-01-07 | 比亚迪股份有限公司 | Transmission, power driving system and vehicle |
| CN110657203B (en) * | 2018-06-29 | 2022-02-08 | 比亚迪股份有限公司 | Transmission, power driving system and vehicle |
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| Publication number | Publication date |
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| CN102777555B (en) | 2015-04-22 |
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