CN202746512U - Continuous power stepless speed-changing transmission mechanism - Google Patents
Continuous power stepless speed-changing transmission mechanism Download PDFInfo
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- CN202746512U CN202746512U CN 201220398188 CN201220398188U CN202746512U CN 202746512 U CN202746512 U CN 202746512U CN 201220398188 CN201220398188 CN 201220398188 CN 201220398188 U CN201220398188 U CN 201220398188U CN 202746512 U CN202746512 U CN 202746512U
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Abstract
The utility model discloses a continuous power stepless speed-changing transmission mechanism, which comprises an inverse synchronous gear, a forward synchronous gear, a first planetary gear train, a second planetary gear train and a transmission gear, wherein the inverse synchronous gear and the forward synchronous gear are respectively engaged with a continuous power input shaft maintaining gear, the first planetary gear train and the second planetary gear train are connected with each other through a speed-adjusting power input shaft, and the transmission gear is engaged with an output shaft maintaining gear; a two-direction synchronous clutch is arranged between the inverse synchronous gear and the forward synchronous gear, the inverse synchronous gear and the forward synchronous gear are connected to the second planetary gear train through the two-direction synchronous clutch, the transmission gear is connected with the first planetary gear train through an output switching clutch on one hand, and the transmission gear is connected with the second planetary gear train through a second inner gear on the other hand. Under the situation that the rotation speed and the rotation direction of the continuous power input shaft are maintained constant, the entire stepless speed change of the output shaft from the inverse maximal speed to the forward maximal speed can be realized only through the speed variation of the speed-adjusting power input shaft and the engaging and the disengaging of the clutch, the entire process is stable in variation of the output speed and free from power interruption. The speed changing in the inverse direction is also stable and free from power interruption.
Description
Technical field
The utility model relates to driving mechanism, specifically a kind of continuous power infinitely variable speed gearing for wheel machine.
Background technique
Gear-driven characteristics are that velocity ratio is fixed, if make output element have larger slewing range often to need to 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 first to mesh, 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, can make so again control more complicated.
On wheel machine, fluid torque converter and the hand shift gear-boxes of adopting as walking speed-regulating device more at present.Although fluid torque converter can absorb shifting shock well, its working efficiency is lower, especially when traveling gear is in the large torque conditions of the slow-speed of revolution.Also the operation on the ramp has a significant impact power interruption during gear shift to wheel machine.
For the gear graduation technical field, especially to running mechanism actuation techniques field, the 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, for 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 purpose of this utility model is to provide a kind of continuous power infinitely variable speed gearing, in the situation that 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 the output of process velocity variations is steady, power failure-free.Speed change is as the same in the other direction.
In order to reach above-mentioned purpose, the utility model has adopted following technological scheme, a kind of continuous power infinitely variable speed gearing, keeps the driving gear of gear engagement with output shaft at the first row star wheel series and the second planetary gear train that comprises respectively the reverse sync gear that keeps the gear engagement with the continuous driving force input shaft and forward synchromesh gear, is connected by the speed governing power input shaft; Be provided with the bi-directional synchronization clutch between described reverse sync gear and the forward synchromesh gear and be connected to the second planetary gear train by this clutch, described driving gear is connected with the first row star wheel series by the output switching clutch on the one hand, is connected with the second planetary gear train by secondary annulus on the other hand.
Described the first row star wheel series and the 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 the described the first row star wheel series i.e. the first internal gear is fixing design, and the internal gear in described the second planetary gear train is that secondary annulus is fixedly connected with driving gear.
Describedly be used for throwing off with forward and reverse synchromesh gear or planet carrier that the bi-directional synchronization clutch of combination is connected to the second planetary gear train namely on the second planet carrier; Describedly be used for throwing off with driving gear or planet carrier that the output switching clutch of combination is connected to the first row star wheel series namely on the first planet carrier.
Described reverse sync gear keeps the gear engagement by tumbler gear and continuous driving force input shaft.
Described reverse sync gear and forward synchromesh gear all keep the gear engagement with fixed speed ratio and continuous driving force input shaft; Keep the gear engagement with fixed speed ratio between the described driving gear output shaft.
Compared to prior art, the utlity model has following beneficial effect:
The utility model takes full advantage of the characteristic of Gear Planet Transmission, at different gear shift stages with different planetary mechanism element drives output shafts, so that the speed of speed governing power input shaft raises or reduces the rising that all causes output shaft speed, and second cover planetary mechanism speed change be that terminal point take first set planetary mechanism slewing range is as starting point, realized the cumulative of slewing range, so that the speed regulation capacity of speed governing power input element obtains maximum performance.Simultaneously, be provided with a bi-directional synchronization clutch at the second planet carrier, not only guaranteed the switching without impact and power failure-free of two cover planetary mechanisms, also can make forward and reverse output of speed changer that same large slewing range is 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 first set planetary gear train and the second cover planetary gear train slewing range.On node, the bi-directional synchronization clutch during speedup on the second planet carrier is with synchromesh gear speed is synchronous forward or backwards; Powershift clutch and transmission gear speeds during deceleration on the first planet carrier are synchronous.Because clutch two rotating part speed are synchronous, can first with being about to the clutch combination of a cover planetary mechanism of the work of entering, will soon break away from the throw-out-of clutch of the another set of planetary mechanism of work again.The power that has guaranteed the mechanical gear shift process is continuous, and without impact.
Description of drawings
Fig. 1 is the structure driven schematic diagram of a kind of continuous power infinitely variable speed gearing of the utility model;
Fig. 2 is output line speed and the element speeds graph of a relation of a kind of continuous power infinitely variable speed gearing of the utility model.
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 switching clutch; 11, driving gear; 12, the continuous driving force input shaft; 13, tumbler gear.
Embodiment
Relevant detailed description of the present utility model and technology contents cooperate description of drawings as follows, yet accompanying drawing only provides the usefulness of reference with explanation, and the utility model is limited.
According to Fig. 1-shown in Figure 2, a kind of continuous power infinitely variable speed gearing, keeps the driving gear 11 of gears engagement with output shaft 6 at the first row star wheel series and the second planetary gear train that comprises respectively the reverse sync gear 1 that keeps the gears engagement with continuous driving force input shaft 12 and forward synchromesh gear 3, is connected by speed governing power input shaft 8; Be provided with bi-directional synchronization clutch 2 between described reverse sync gear and the forward synchromesh gear and be connected to the second planetary gear train by this clutch, described driving gear is connected with the first row star wheel series by output switching clutch 10 on the one hand, is connected with the second planetary gear train by secondary annulus 5 on the other hand.Described reverse sync gear 1 keeps the gear engagement by tumbler gear 13 and continuous driving force input shaft 12.
The first row star wheel series and the 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 the first row star wheel series i.e. the first internal gear 9 is fixing design, and the internal gear in described the second planetary gear train is that secondary annulus 5 is fixedly connected with driving gear 11.Be used for throwing off with forward and reverse synchromesh gear or planet carrier that the bi-directional synchronization clutch of combination is connected to the second planetary gear train namely on the second planet carrier; Describedly be used for throwing off with driving gear or planet carrier that the output switching clutch of combination is connected to the first row star wheel series namely on the first planet carrier.Reverse sync gear and forward synchromesh gear all keep the gear engagement with fixed speed ratio and continuous driving force input shaft; Keep the gear engagement with fixed speed ratio between the described driving gear output shaft.
As shown in Figure 1, establish counterclockwise rotation of continuous driving force input shaft 12; Initial state speed governing power input shaft 8 rotating speeds are zero, and bi-directional synchronization clutch 2 and output switching clutch 10 all are in disengaged condition, 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, and is lower same; If be forward counterclockwise.
1, if make output gear shaft 6 forward speedups, process is as follows:
1.1, output switching clutch 10 closures, the first row star wheel series enters working state;
1.2, oppositely increase the rotating speed of speed governing power input shaft 8;
1.3 because the first internal gear 9 is fixing, speed governing power input shaft 8 can drive the first planet carrier 7 reverse speedups; Because the input switch clutch is closed, driving gear 11 and secondary annulus 5 are also along with the first planet carrier 7 reverse speedups; Driving gear 11 driver output axles 6 forward speedups;
1.4 secondary annulus 5 and speed governing power input shaft 8 drive the second planet carrier 4 reverse speedups jointly simultaneously;
1.5, when the second planet carrier 4 speed increase to forward synchromesh gear 3 synchronously, first with bi-directional synchronization clutch 2 and 3 combinations of forward synchromesh gear, again output switching clutch 10 is thrown off.This moment, mechanical gear shift was finished, and the first row star wheel series breaks away from working state, and the second planetary gear train enters working state.Interrupt in this gearshift procedure medium power output nothing.
1.6, reducing speed governing power input shaft 8 rotating speeds and continue again speedup to the forward maximum (top) speed to zero, secondary annulus 5 and driving gear 11 continue reverse speedups in this process, thus driver output axle 6 continues the forward speedups.
2, if output shaft 6 is slowed down, its process is opposite with process 1.The main points in mechanical gear shift stage are: the closed output switching clutch 10 of elder generation, throw off again bi-directional synchronization clutch 2.
3, the process of the 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 the first planet carrier 7, and 103 is the corresponding relation line of output shaft 6, and 104 is the corresponding relation line of the 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 driven separately by the speed governing power input shaft; In high-speed range, speed changer is driven jointly by continuous driving force input shaft and speed governing power input shaft.On certain velocity node, two planetary gear train switch, the common driver output axle of two planetary gear train on the switching point.If this type of belt drive adopts engine-driving continuous driving force input shaft, fluid motor-driven speed governing power input shaft, the walking that then is highly suitable for wheel machine drives.
The above only is preferred embodiment of the present utility model, and non-in order to limit claim of the present utility model, other use the equivalence of patent spirit of the present utility model to change, and all should all belong to claim of the present utility model.
Claims (6)
1. continuous power infinitely variable speed gearing, it is characterized in that, the first row star wheel series and the second planetary gear train that comprises respectively the reverse sync gear that keeps the gear engagement with the continuous driving force input shaft and forward synchromesh gear, is connected by the speed governing power input shaft, keep the driving gear of gear engagement with output shaft; Be provided with the bi-directional synchronization clutch between described reverse sync gear and the forward synchromesh gear and be connected to the second planetary gear train by this clutch, described driving gear is connected with the first row star wheel series by the output switching clutch on the one hand, is connected with the second planetary gear train by 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, described the first row star wheel series and the 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 the described the first row star wheel series i.e. the first internal gear is fixing design, and the internal gear in described the 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, describedly is used for throwing off with forward and reverse synchromesh gear or planet carrier that the bi-directional synchronization clutch of combination is connected to the second planetary gear train namely on the second planet carrier; Describedly be used for throwing off with driving gear or planet carrier that the output switching clutch of combination is connected to the first row star wheel series namely on the first planet carrier.
5. a kind of continuous power infinitely variable speed gearing according to claim 1 is characterized in that, described reverse sync gear keeps the gear engagement by 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, described reverse sync gear and forward synchromesh gear all keep the gear engagement with fixed speed ratio and continuous driving force input shaft; Keep the gear engagement with fixed speed ratio between the described driving gear output shaft.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220398188 CN202746512U (en) | 2012-08-13 | 2012-08-13 | Continuous power stepless speed-changing transmission mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220398188 CN202746512U (en) | 2012-08-13 | 2012-08-13 | Continuous power stepless speed-changing transmission mechanism |
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| Publication Number | Publication Date |
|---|---|
| CN202746512U true CN202746512U (en) | 2013-02-20 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201220398188 Withdrawn - After Issue CN202746512U (en) | 2012-08-13 | 2012-08-13 | Continuous power stepless speed-changing transmission mechanism |
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| CN (1) | CN202746512U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102777555A (en) * | 2012-08-13 | 2012-11-14 | 山东常林机械集团股份有限公司 | Continuous power infinitely variable speed transmission mechanism |
| 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 |
-
2012
- 2012-08-13 CN CN 201220398188 patent/CN202746512U/en not_active Withdrawn - After Issue
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102777555A (en) * | 2012-08-13 | 2012-11-14 | 山东常林机械集团股份有限公司 | Continuous power infinitely variable speed transmission mechanism |
| CN102777555B (en) * | 2012-08-13 | 2015-04-22 | 山东常林机械集团股份有限公司 | Continuous power infinitely variable speed transmission mechanism |
| 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 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20130220 Effective date of abandoning: 20150422 |