CN103486207A - Continuous power stepless variable-speed transmission mechanism - Google Patents
Continuous power stepless variable-speed transmission mechanism Download PDFInfo
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- CN103486207A CN103486207A CN201310480709.1A CN201310480709A CN103486207A CN 103486207 A CN103486207 A CN 103486207A CN 201310480709 A CN201310480709 A CN 201310480709A CN 103486207 A CN103486207 A CN 103486207A
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- speed
- planetary gear
- gear train
- wheel
- input shaft
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- 230000005540 biological transmission Effects 0.000 title abstract description 4
- 238000000034 method Methods 0.000 abstract description 22
- 230000000630 rising effect Effects 0.000 description 4
- 239000012530 fluid Substances 0.000 description 3
- 230000035939 shock Effects 0.000 description 3
- 230000009286 beneficial effect Effects 0.000 description 1
- 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 1
- 239000000969 carrier Substances 0.000 description 1
- 230000008034 disappearance Effects 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
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Classifications
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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
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
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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
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/76—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with an orbital gear having teeth formed or arranged for obtaining multiple gear ratios, e.g. nearly infinitely variable
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/2005—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with one sets of orbital gears
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/202—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set
- F16H2200/2023—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set using a Ravigneaux set with 4 connections
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2035—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with two engaging means
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
- Transmission Devices (AREA)
Abstract
The invention discloses a continuous power stepless variable-speed transmission mechanism. The continuous power stepless variable-speed transmission mechanism comprises a first planetary gear train, a second planetary gear train, an output wheel, a speed adjusting power input shaft, a continuous power input switching mechanism and a low-speed clutch, wherein the first planetary gear train and the second planetary gear train are connected by a shared planetary carrier; the output wheel is connected with the planetary carrier; the speed adjusting power input shaft is used as a solar wheel of the first planetary gear train; the continuous power input switching mechanism is used for driving the first planetary gear train and the second planetary gear train; the low-speed clutch is connected to the second planetary gear train; and the first planetary gear train and the second planetary gear train share a duplex planet gear. According to the mechanism, three gears of low speed, medium speed and high speed are set according to a characteristic that the speed-adjusting power input shaft generates different speed ratios for output of the planetary carrier based on different planetary mechanism elements. Under a condition that rotation speed from power source input to continuous power input switching mechanism thereof is kept unchanged, rotation speed and rotation direction changes of the speed-adjusting power input shaft are matched with gear switching to realize stepless speed change from zero to maximal rotation speed on the output wheel. In a whole speed raising process, the output rotation speed changes are smooth without power interruption. And a speed reducing process is also the same.
Description
Technical field
The present invention relates to gear drive, especially the walking driving mechanism of wheel machine.
Background technique
Gear-driven characteristics are that velocity ratio is fixed, if the gearbox that makes output element have larger slewing range often to need design to comprise a plurality of velocity ratios.When gear switch, due to the nonsynchronous reason of element speeds, two gears are transferring power simultaneously, need to first throw off rear engagement, causes the interruption of outputting power.Due to the nonsynchronous reason of speed, the gear shift meeting causes mechanical shock equally, if reduce, impacts and needs more velocity ratio, can make so again to 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 at traveling gear during in the large torque conditions of the slow-speed of revolution.Also to wheel machine, the operation on ramp has a significant impact power interruption during gear shift.
For the gear graduation technical field, especially to running mechanism actuation techniques field, the mechanical shock while 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 object of the present invention is to provide a kind of continuous power infinitely variable speed gearing, in the situation that the rotating speed that is input to its continuous driving force input switching mechanism by power source remains unchanged, the variation of leaning on speed governing power input shaft rotating speed and turning to, cooperation, with the switching of gear, just can realize from zero stepless change to maximum (top) speed on output wheel.In whole boosting velocity procedure, output speed changes level and smooth, and power failure-free.Moderating process is as the same.
In order to reach above-mentioned purpose, the present invention has adopted following technological scheme, a kind of continuous power infinitely variable speed gearing, comprise and pass through the first row star wheel series and the second planetary gear train, the output wheel be connected with planet carrier, the speed governing power input shaft as the first row star wheel series sun gear, the continuous driving force input switching mechanism for driving the first row star wheel series and the second planetary gear train, the low-speed clutch that is connected in the second planetary gear train that shared planet carrier is connected; Described the first row star wheel series and the second planetary gear train share double-planetary gear.
Described the first row star wheel series and the second planetary gear train include sun gear and internal gear.
Described the second planetary gear train comprises the planet idle wheel be arranged on planet carrier, and the internal gear of planet idle wheel and the second planetary gear train is that secondary annulus and double-planetary gear keep engagement simultaneously.
Be provided with low-speed clutch between described secondary annulus and casing.
Whether it is the first internal gear that the continuous driving force input shaft that described continuous driving force input switching mechanism can make it comprise drives the internal gear of described the first planetary mechanism with the speed ratio of fixing, by the middling speed Clutch Control, participated in driving.
Whether it is the second sun gear that the continuous driving force input shaft that described continuous driving force input switching mechanism can make it comprise drives the sun gear of described the second planetary mechanism with the speed ratio of fixing, by high-speed clutch, controlled and participated in driving.
Compared to prior art, the present invention has following beneficial effect:
Including five in the present invention and can take two planetary gear train centers and be the element of axle rotation, is respectively two planetary gear train internal gear, sun gear and shared planet carriers separately.Wherein, the sun gear of the first row star wheel series is as the speed governing power input shaft, and shared planet carrier is connected with output shaft as output element, other three elements when participating in work as the constant speed element.The speed of constant speed element and the work that whether participates in are controlled by low-speed clutch and continuous driving force input switching mechanism.Constant speed element based on different, can produce different speed ratios between speed governing power input shaft and planet carrier.Given three constant speed elements are with corresponding speed the present invention is had respectively three gears of corresponding three slewing ranges that mutually are connected respectively.And, for two adjacent gears, between speed governing power input shaft and planet carrier, the sign of speed ratio is contrary.Therefore in whole boosting velocity procedure, in the situation that the rotating speed of continuous driving force input shaft is constant, be that the rotating speed rising of speed governing power input shaft or reduction, forward or reversion all can cause the rising of planet carrier rotating speed, the performance of speed governing element is not fully exerted.The reduction of speed process is as the same.In addition, although have different element disengaging work on different gears, these elements are still done non-loaded driven running with planetary gear train.On the interface point of adjacent two slewing ranges, i.e. combining two non-loaded element synchronization, can first cut is combining two elements, then cuts out and be about to two elements that break away from.Therefore in gearshift procedure, speed is without impact, and power is without interruption.
The accompanying drawing explanation
The transmission principle figure that Fig. 1 is a kind of continuous power infinitely variable speed gearing of the present invention;
The output wheel rotating speed that Fig. 2 is a kind of continuous power infinitely variable speed gearing of the present invention and element speeds graph of a relation.
In figure: 1, the high speed driving wheel; 2, the continuous driving force input shaft; 3, secondary annulus; 4, planet carrier; 5, the high speed driven wheel; 6, high-speed clutch; 7, the second sun gears; 8, the planet idle wheel; 9, low-speed clutch; 10, double-planetary gear; 11, the speed governing power input shaft; 12, output wheel; 13, the first internal gears; 14, the middling speed driven wheel; 15, middle speed clutch; 16, the middling speed driving wheel.
Embodiment
Relevant detailed description of the present invention and technology contents, coordinate accompanying drawing to be described as follows, yet accompanying drawing only provides the use of reference with explanation, not is used for the present invention is limited.
Shown in Fig. 1 and Fig. 2, a kind of continuous power infinitely variable speed gearing, comprise and pass through the first row star wheel series and the second planetary gear train, the output wheel 12 be connected with planet carrier 4, the speed governing power input shaft 11 as the first row star wheel series sun gear, the continuous driving force input switching mechanism for driving the first row star wheel series and the second planetary gear train, the low-speed clutch 9 that is connected in the second planetary gear train that shared planet carrier 4 is connected; Described the first row star wheel series and the second planetary gear train share double-planetary gear 10.
Described the first row star wheel series and the second planetary gear train include internal gear and sun gear.
Described the second planetary gear train comprises the planet idle wheel 8 be arranged on planet carrier 4, and the internal gear of planet idle wheel 8 and the second planetary gear train is that secondary annulus 3 and double-planetary gear 10 keep engagement simultaneously
Described low-speed clutch 9 is located between secondary annulus 3 and casing, is designed to Normally closed type.
Described continuous driving force input switching mechanism comprises continuous driving force input shaft 2, high speed driving wheel 1, high speed driven wheel 5, high-speed clutch 6, middling speed driving wheel 16, middling speed driven wheel 14, middle speed clutch 15.Between described continuous driving force input shaft 2 and middling speed driving wheel 16 for being fixedly connected with; The internal gear that described middle speed clutch 15 is located at middling speed driven wheel 14 and the first row star wheel series is between the first internal gear 13, is designed to open in usual; Between described continuous driving force input shaft 2 and high speed driving wheel 1 for being fixedly connected with; The sun gear that described high-speed clutch 6 is located at high speed driven wheel 5 and the second planetary gear train is between the second sun gear 7, is designed to open in usual.
As shown in Figure 1, establish counterclockwise rotation of continuous driving force input shaft 2; 9 combinations of initial state low-speed clutch, middle speed clutch 15 is thrown off, and high-speed clutch 6 is thrown off, and whole mechanism is in low gear; When speed governing power input shaft 11 rotating speeds are zero, output wheel 12 rotating speeds are zero.
Above-mentioned rotary speed direction is to see from right to left according to Fig. 1, lower same; If be counterclockwise forward.
1., if make output wheel 12 speedups, process is as follows:
1.1, under the low gear state, forward increases the rotating speed of speed governing power input shaft 11;
Under this state, secondary annulus 3 is fixing, and the first internal gear 13 and the second sun gear 7 are freely driven.Based on secondary annulus 3, between speed governing power input shaft 11 and planet carrier 4, speed ratio is negative value, and planet carrier 4 will drive the reverse speedup of output wheel 12;
When the 11 rotating speed forwards risings of speed governing power input shaft make the rotating speed of its rotating speed and continuous driving force input shaft 2 reach a specific ratio, the rotating speed of output wheel 12 reaches the interface point of bottom gear and mid ranger slewing range, between the first internal gear 13 and middling speed driven wheel 14, is now homodyne speed;
1.2 speed clutch 15 combinations in order, owing to being now homodyne speed between the first internal gear 13 and middling speed driven wheel 14, so the cohesive process of middle speed clutch 15 is without impact;
Throw off low-speed clutch 9;
Now whole mechanism enters the mid ranger state, due to middle speed clutch 15 in conjunction with early than the disengagement of low-speed clutch 9, so power interruption does not appear in whole gearshift procedure;
1.3, under the middling speed range state, reduce the forward rotational speed of speed governing power input shaft 11 to zero-speed, then continue oppositely to increase its rotating speed;
Under this state, the first internal gear 13 has obtained a reverse fixed rotating speed by middling speed driving wheel 16 and middling speed driven wheel 14 from continuous driving force input shaft 2, and secondary annulus 3 and the second sun gear 7 are freely driven.Based on the first internal gear 13, between speed governing power input shaft 11 and planet carrier 4 speed ratio be on the occasion of, so speed governing power input shaft 11 forwards slow down and the process of reverse speedup in, planet carrier 4 will drive the reverse speedup of output wheel 12;
When the reverse rising of speed governing power input shaft 11 rotating speeds makes the rotating speed of its rotating speed and continuous driving force input shaft 2 reach another specific ratio, the rotating speed of output wheel 12 reaches the interface point of mid ranger and top gear slewing range, between the second sun gear 7 and high speed driven wheel 5, is now homodyne speed;
1.4, make high-speed clutch 6 combinations, owing to being now homodyne speed between the second sun gear 7 and high speed driven wheel 5, so the cohesive process of high-speed clutch 6 is without impact;
In disengagement, speed clutch 15;
Now whole mechanism enters the top gear state, due to high-speed clutch 6 in conjunction with early than the disengagement of middle speed clutch 15, so power interruption does not appear in whole gearshift procedure;
1.5, under the high gear state, reduce the reverse speed of speed governing power input shaft 11 to zero-speed, then continue forward and increase its rotating speed;
Under this state, the second sun gear 7 has obtained a reverse fixed rotating speed by high speed driving wheel 1 and high speed driven wheel 5 from continuous driving force input shaft 2, and the first internal gear 13 and secondary annulus 3 are freely driven.Based on the second sun gear 7, between speed governing power input shaft 11 and planet carrier 4, speed ratio is negative value, so, in the process of the reverse deceleration of speed governing power input shaft 11 and forward speedup, planet carrier 4 will drive the reverse speedup of output wheel 12;
In the process that rotating speed oppositely reduces or forward raises of speed governing power input shaft 11, the rotating speed of output wheel 12 will reach the high-end of top gear slewing range, namely the highest output speed of whole gear.
2., if make output wheel 12 slow down, its process is contrary with process 1.The main points of gearshift procedure are: first incision, rear disengagement, to avoid power interruption.
Fig. 2 has showed the rotating speed of each primary component in speed-change process and the corresponding relation between the output wheel rotating speed.Horizontal ordinate: output wheel rotating speed; Ordinate: element rotating speed.The 100 corresponding relation lines that are continuous driving force input shaft 2,101 for the corresponding relation line of speed governing power input shaft 11, the 102 corresponding relation lines that are the second sun gear 7, the 103 corresponding relation lines that are secondary annulus 3, the 104 corresponding relation lines that are planet carrier 4, the 105 corresponding relation lines that are the first internal gear 13.
Three gears of the present invention are different but slewing range that mutually be connected corresponding to three, and in low-speed range, speed changer is driven separately by speed governing power input shaft 11; In moderate speed range and high-speed range, speed changer is driven jointly by continuous driving force input shaft 2 and speed governing power input shaft 11.In the handoff procedure of adjacent two gears, two relevant elements of gear all participate in work therewith, make in gearshift procedure and keep power to continue.
If the present invention adopts engine-driving continuous driving force input shaft 2, with fluid motor-driven speed governing power input shaft 11 and set up changement at output terminal, the walking that is highly suitable for wheel machine drives.
The foregoing is only preferred embodiment of the present invention, non-in order to limit the scope of the claims of the present invention, other use the equivalence of patent spirit of the present invention to change, and all should all belong to the scope of the claims of the present invention.
Claims (9)
1. a continuous power infinitely variable speed gearing, it is characterized in that, comprise and pass through the first row star wheel series and the second planetary gear train, the output wheel be connected with planet carrier, the speed governing power input shaft as the first row star wheel series sun gear, the continuous driving force input switching mechanism for driving the first row star wheel series and the second planetary gear train, the low-speed clutch that is connected in the second planetary gear train that shared planet carrier is connected; Described the first row star wheel series and the second planetary gear train share double-planetary gear.
2. a kind of continuous power infinitely variable speed gearing according to claim 1, is characterized in that, described the first row star wheel series comprises internal gear, claims the first internal gear.
3. a kind of continuous power infinitely variable speed gearing according to claim 1, is characterized in that, described the second planetary gear train comprises internal gear, claims secondary annulus.
4. a kind of continuous power infinitely variable speed gearing according to claim 1, is characterized in that, described the second planetary gear train comprises sun gear, claims the second sun gear.
5. a kind of continuous power infinitely variable speed gearing according to claim 1, is characterized in that, described the second planetary gear train comprises and is arranged on planet carrier and keeps the planet idle wheel of engagement with double-planetary gear.
6. according to claim 1 or 3 or 5 described a kind of continuous power infinitely variable speed gearings, it is characterized in that, described planet idle wheel and described secondary annulus keep engagement.
7. according to the described a kind of continuous power infinitely variable speed gearing of claim 1 or 3, it is characterized in that, described low-speed clutch is located between secondary annulus and casing.
8. according to the described a kind of continuous power infinitely variable speed gearing of claim 1 or 4, it is characterized in that, described continuous driving force input switching mechanism comprises the continuous driving force input shaft, be installed on high speed driving wheel on the continuous driving force input shaft, by the second sun gear be connected in the second planetary gear train the high speed driven wheel, whether participate in the high-speed clutch of work for controlling high speed driving wheel and high speed driven wheel.
9. a kind of continuous power infinitely variable speed gearing according to claim 1 and 2, it is characterized in that, described continuous driving force input switching mechanism comprises the continuous driving force input shaft, be installed on middling speed driving wheel on the continuous driving force input shaft, by the first internal gear be connected in the first row star wheel series the middling speed driven wheel, whether participate in the speed clutch of work for controlling middling speed driving wheel and middling speed driven wheel.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310480709.1A CN103486207B (en) | 2013-03-12 | 2013-10-15 | A kind of power infinitely variable speed gearing continuously |
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310077340.X | 2013-03-12 | ||
| CN201310077340 | 2013-03-12 | ||
| CN201310480709.1A CN103486207B (en) | 2013-03-12 | 2013-10-15 | A kind of power infinitely variable speed gearing continuously |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103486207A true CN103486207A (en) | 2014-01-01 |
| CN103486207B CN103486207B (en) | 2015-12-23 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310480709.1A Active CN103486207B (en) | 2013-03-12 | 2013-10-15 | A kind of power infinitely variable speed gearing continuously |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN103486207B (en) |
| WO (1) | WO2014139066A1 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107339389A (en) * | 2016-04-29 | 2017-11-10 | 腓特烈斯港齿轮工厂股份公司 | Speed changer for motor vehicle and the power assembly system for including this speed changer for motor vehicle |
| CN109442009A (en) * | 2018-12-20 | 2019-03-08 | 潍柴动力股份有限公司 | A kind of variable transmission mechanism and in-wheel driving are mechanical |
| CN110159716A (en) * | 2018-03-30 | 2019-08-23 | 于世超 | A kind of driving of drum without interrupting three-range transmission |
| CN112279042A (en) * | 2020-11-04 | 2021-01-29 | 天津市航昊机电设备有限公司 | Control method of control equipment of lifting cage speed changer |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5135444A (en) * | 1989-02-28 | 1992-08-04 | Nissan Motor Co., Ltd. | Planetary gear system |
| WO1998022733A1 (en) * | 1996-11-20 | 1998-05-28 | Aprotech Co., Ltd. | Continuously variable transmission |
| KR100655121B1 (en) * | 2005-11-21 | 2006-12-08 | 현대자동차주식회사 | Power train of automatic transmission |
| 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 |
| 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 |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100494745C (en) * | 2004-05-10 | 2009-06-03 | 薛忠和 | Electromechanic stepless speed variator |
| CN201045403Y (en) * | 2006-08-24 | 2008-04-09 | 王亮 | Mixed power vehicle double input planetary gear train |
-
2013
- 2013-10-15 CN CN201310480709.1A patent/CN103486207B/en active Active
- 2013-10-30 WO PCT/CN2013/001315 patent/WO2014139066A1/en active Application Filing
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5135444A (en) * | 1989-02-28 | 1992-08-04 | Nissan Motor Co., Ltd. | Planetary gear system |
| WO1998022733A1 (en) * | 1996-11-20 | 1998-05-28 | Aprotech Co., Ltd. | Continuously variable transmission |
| KR100655121B1 (en) * | 2005-11-21 | 2006-12-08 | 현대자동차주식회사 | Power train of automatic transmission |
| 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 |
| 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 (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107339389A (en) * | 2016-04-29 | 2017-11-10 | 腓特烈斯港齿轮工厂股份公司 | Speed changer for motor vehicle and the power assembly system for including this speed changer for motor vehicle |
| CN110159716A (en) * | 2018-03-30 | 2019-08-23 | 于世超 | A kind of driving of drum without interrupting three-range transmission |
| CN109442009A (en) * | 2018-12-20 | 2019-03-08 | 潍柴动力股份有限公司 | A kind of variable transmission mechanism and in-wheel driving are mechanical |
| CN112279042A (en) * | 2020-11-04 | 2021-01-29 | 天津市航昊机电设备有限公司 | Control method of control equipment of lifting cage speed changer |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2014139066A1 (en) | 2014-09-18 |
| CN103486207B (en) | 2015-12-23 |
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