CN103486207B - A kind of power infinitely variable speed gearing continuously - Google Patents
A kind of power infinitely variable speed gearing continuously Download PDFInfo
- Publication number
- CN103486207B CN103486207B CN201310480709.1A CN201310480709A CN103486207B CN 103486207 B CN103486207 B CN 103486207B CN 201310480709 A CN201310480709 A CN 201310480709A CN 103486207 B CN103486207 B CN 103486207B
- Authority
- CN
- China
- Prior art keywords
- speed
- planetary gear
- train
- planet
- input shaft
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 238000000034 method Methods 0.000 abstract description 22
- 239000012530 fluid Substances 0.000 description 3
- 230000000630 rising effect Effects 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
- 230000005540 biological transmission Effects 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
Classifications
-
- 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
-
- 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
-
- 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
-
- 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
Abstract
The invention discloses a kind of power infinitely variable speed gearing continuously, comprise pass through first planet train that shared planet carrier is connected and the second planetary gear train, the output wheel be connected with planet carrier, as the speed governing power input shaft of first planet train sun gear, for driving the continuous driving force of first planet train and the second planetary gear train to input switching mechanism, being connected to the low-speed clutch of the second planetary gear train; Described first planet train and the second planetary gear train share double-planetary gear.The present invention utilizes speed governing power input shaft producing this feature of different speed ratio to the output of planet carrier based on during different planetary mechanism elements, is provided with low speed, middling speed and high speed three gears.When the rotating speed being input to its continuous driving force input switching mechanism by power source remains unchanged, by speed governing power input shaft rotating speed and the change that turns to, coordinate the switching with gear, just can realize on output wheel from zero to the stepless change of maximum (top) speed.In whole boosting velocity procedure, output speed change is level and smooth, and power failure-free.Moderating process is as the same.
Description
Technical field
The present invention relates to gear drive, especially the hoofing part mechanism of wheel machine.
Background technique
Gear-driven feature is that velocity ratio is fixed, if make output element have larger slewing range often to need to design the gearbox comprising multiple velocity ratio.When gear switch, due to the nonsynchronous reason of element speeds, two gears can not transferring power simultaneously, needs first to throw off rear engagement, causes the interruption of outputting power.Same due to speed nonsynchronous reason, gear shift can cause mechanical shock, impacts, need more velocity ratio, manipulation can be made so again more complicated if reduce.
On wheel machine, fluid torque converter and the hand shift gear-box 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.Power interruption during gear shift also has a significant impact the operation of wheel machine on ramp.
For gear graduation technical field, especially to running mechanism actuation techniques field, mechanical shock when solving gear shift and power interruption are for raising device operability, steadily travelling comfort and to reduce energy consumption all very necessary.
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 power infinitely variable speed gearing continuously, when the rotating speed being input to its continuous driving force input switching mechanism by power source remains unchanged, by speed governing power input shaft rotating speed and the change that turns to, coordinate with the switching of gear, just can realize on output wheel from zero to the stepless change of maximum (top) speed.In whole boosting velocity procedure, output speed change is level and smooth, and power failure-free.Moderating process is as the same.
In order to reach above-mentioned purpose, present invention employs following technological scheme, a kind of power infinitely variable speed gearing continuously, comprise pass through first planet train that shared planet carrier is connected and the second planetary gear train, the output wheel be connected with planet carrier, as the speed governing power input shaft of first planet train sun gear, for driving the continuous driving force of first planet train and the second planetary gear train to input switching mechanism, being connected to the low-speed clutch of the second planetary gear train; Described first planet train and the second planetary gear train share double-planetary gear.
Described first planet train and the second planetary gear train include sun gear and internal gear.
Described 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 and secondary annulus and double-planetary gear keep engaging simultaneously.
Low-speed clutch is provided with between described secondary annulus and casing.
Whether the continuous driving force input shaft that described continuous driving force input switching mechanism can make it comprise drives internal gear i.e. first internal gear of described first planet mechanism with fixing speed ratio, participated in driving by middling speed Clutch Control.
Whether the continuous driving force input shaft that described continuous driving force input switching mechanism can make it comprise drives sun gear i.e. second sun gear of described second planetary mechanism with fixing speed ratio, controlled to participate in driving by high-speed clutch.
Compared to prior art, the present invention has following beneficial effect:
Include five elements that can rotate for axle with two planetary gear train centers in the present invention, be two planetary gear train internal gear separately respectively, sun gear and the planet carrier that shares.Wherein, the sun gear of first planet train as speed governing power input shaft, the planet carrier that shares be connected with output shaft as output element, other three elements when the work of participation as constant speed element.The speed of constant speed element and the work that whether participates in input switching mechanism by low-speed clutch and continuous driving force and control.Based on different constant speed elements, speed governing power input shaft can produce different speed ratios between planet carrier.Given three constant speed elements are with three gears of corresponding speed made the present invention have respectively corresponding three slewing ranges be mutually connected respectively.And for adjacent two gears, speed governing power input shaft is contrary with the sign of speed ratio between planet carrier.Therefore in whole boosting velocity procedure, when the rotating speed of continuous driving force input shaft is constant, be the rising of speed governing power input shaft rotating speed or reduction, rotate forward or reverse and all can cause the rising of planet carrier rotating speed, the performance of speed governing element is not fully exerted.Down speeding procedure is as the same.In addition, although have different element disengaging work on different gears, non-loaded driven running done by these elements still planet wheels system.On the interface point of adjacent two slewing ranges, i.e. combining two non-loaded element synchronization, first can cut i.e. combining two elements, then cut out two elements being about to depart from.Therefore, in gearshift procedure, speed is without impact, and power is without interruption.
Accompanying drawing explanation
Fig. 1 is the transmission principle figure of a kind of continuous power infinitely variable speed gearing of the present invention;
Fig. 2 is output wheel rotating speed and the element speeds graph of a relation of a kind of continuous power infinitely variable speed gearing of the present invention.
In figure: 1, high speed driving wheel; 2, continuous driving force input shaft; 3, secondary annulus; 4, planet carrier; 5, high speed driven wheel; 6, high-speed clutch; 7, second sun gear; 8, planet idle wheel; 9, low-speed clutch; 10, double-planetary gear; 11, speed governing power input shaft; 12, output wheel; 13, first internal gear; 14, middling speed driven wheel; 15, middle speed clutch; 16, middling speed driving wheel.
Embodiment
Detailed description for the present invention and technology contents, coordinate accompanying drawing to be described as follows, but accompanying drawing only provides with reference to the use with explanation, is not used for being limited the present invention.
According to Fig. 1 and Fig. 2, a kind of power infinitely variable speed gearing continuously, comprise pass through first planet train that shared planet carrier 4 is connected and the second planetary gear train, the output wheel 12 be connected with planet carrier 4, as the speed governing power input shaft 11 of first planet train sun gear, for driving the continuous driving force of first planet train and the second planetary gear train to input switching mechanism, being connected to the low-speed clutch 9 of the second planetary gear train; Described first planet train and the second planetary gear train share double-planetary gear 10.
Described first planet train and the second planetary gear train include internal gear and sun gear.
Described 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 and secondary annulus 3 and double-planetary gear 10 keep engaging 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.Described continuous driving force input shaft 2 with between middling speed driving wheel 16 for being fixedly connected with; Described middle speed clutch 15 is located at the internal gear of middling speed driven wheel 14 and first planet train that is between the first internal gear 13, is designed to open in usual; Described continuous driving force input shaft 2 with between high speed driving wheel 1 for being fixedly connected with; Described high-speed clutch 6 is located at the sun gear of high speed driven wheel 5 and the second planetary gear train that is between the second sun gear 7, is designed to open in usual.
As shown in Figure 1, if continuous driving force input shaft 2 counterclockwise rotates; Initial state low-speed clutch 9 combines, and 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 speed is zero, output wheel 12 rotating speed is zero.
Above-mentioned rotary speed direction sees from right to left according to Fig. 1, lower same; If be counterclockwise forward.
1., if make output wheel 12 speedup, process is as follows:
1.1, under low gear state, forward increases the rotating speed of speed governing power input shaft 11;
Under this state, secondary annulus 3 is fixed, the first internal gear 13 and the second sun gear 7 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 output wheel 12 oppositely speedup;
When the rising of speed governing power input shaft 11 rotating speed forward makes 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, is now homodyne speed between the first internal gear 13 and middling speed driven wheel 14;
1.2, in order, speed clutch 15 combines, 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 mid ranger state, because the combination of middle speed clutch 15 is early than the disengagement of low-speed clutch 9, so whole gearshift procedure does not occur power interruption;
1.3, under 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 obtains 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 forward slow down and reverse speedup process in, planet carrier 4 will drive the reverse speedup of output wheel 12;
When speed governing power input shaft 11 rotating speed oppositely raise make the rotating speed of its rotating speed and continuous driving force input shaft 2 reach another specific ratio time, the rotating speed of output wheel 12 reaches the interface point of mid ranger and top gear slewing range, is now homodyne speed between the second sun gear 7 and high speed driven wheel 5;
1.4, make high-speed clutch 6 combine, 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;
Speed clutch 15 in disengagement;
Now whole mechanism enters High gear state, because the combination of high-speed clutch 6 is early than the disengagement of middle speed clutch 15, so whole gearshift procedure does not occur power interruption;
1.5, under 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 obtains 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, thus speed governing power input shaft 11 oppositely slow down and forward speedup process in, planet carrier 4 will drive the reverse speedup of output wheel 12;
In the process that the rotating speed of speed governing power input shaft 11 oppositely reduces or forward raises, the rotating speed of output wheel 12 will reach the high-end of top gear slewing range, the 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 cut, rear disengagement, to avoid power interruption.
Fig. 2 has showed the corresponding relation between the rotating speed of each primary component in speed-change process and output wheel rotating speed.Horizontal ordinate: output wheel rotating speed; Ordinate: element rotating speed.100 is the corresponding relation line of continuous driving force input shaft 2,101 is the corresponding relation line of speed governing power input shaft 11,102 is the corresponding relation line of the second sun gear 7,103 is the corresponding relation line of secondary annulus 3,104 is the corresponding relation line of planet carrier 4, and 105 is the corresponding relation line of the first internal gear 13.
Three gears of the present invention correspond to three different but slewing ranges that are that be mutually connected, 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, the element that two gears are relevant therewith all participates in work, makes to keep power to continue in gearshift procedure.
The present invention sets up changement according to engine-driving continuous driving force input shaft 2, with fluid motor-driven speed governing power input shaft 11 at output terminal, be then highly suitable for the hoofing part of wheel machine.
The foregoing is only preferred embodiment of the present invention, be not used 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 (5)
1. a continuous power infinitely variable speed gearing, it is characterized in that, comprise pass through first planet train that shared planet carrier is connected and the second planetary gear train, the output wheel be connected with planet carrier, as the speed governing power input shaft of first planet train sun gear, for driving the continuous driving force of first planet train and the second planetary gear train to input switching mechanism, being connected to the low-speed clutch of the second planetary gear train; Described first planet train and the second planetary gear train share double-planetary gear; Described second planetary gear train comprises and is arranged on planet carrier and keeps with double-planetary gear the planet idle wheel that engages.
2. the continuous power infinitely variable speed gearing of one according to claim 1, is characterized in that, described second planetary gear train comprises internal gear, claims secondary annulus; Described low-speed clutch is located between secondary annulus and casing.
3. the continuous power infinitely variable speed gearing of one according to claim 2, is characterized in that, described secondary annulus and planet idle wheel keep engaging.
4. the continuous power infinitely variable speed gearing of one according to claim 1, it is characterized in that, described continuous driving force input switching mechanism comprises continuous driving force input shaft, the high speed driving wheel be installed on continuous driving force input shaft, being connected to the high speed driven wheel of the second planetary gear train by the second sun gear, whether participating in the high-speed clutch of work for controlling high speed driving wheel and high speed driven wheel.
5. the continuous power infinitely variable speed gearing of one according to claim 1, it is characterized in that, described continuous driving force input switching mechanism comprises continuous driving force input shaft, the middling speed driving wheel be installed on continuous driving force input shaft, be connected to by the first internal gear first planet train middling speed driven wheel, for controlling middling speed driving wheel and whether middling speed driven wheel participates in speed clutch in work.
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 | 2013-03-12 | ||
| CN201310077340.X | 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 CN103486207A (en) | 2014-01-01 |
| CN103486207B true CN103486207B (en) | 2015-12-23 |
Family
ID=49826694
Family Applications (1)
| 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) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102016207440A1 (en) * | 2016-04-29 | 2017-11-02 | Zf Friedrichshafen Ag | Transmission for a motor vehicle, and drive train for a motor vehicle with such a transmission |
| CN110159716B (en) * | 2018-03-30 | 2023-06-06 | 于世超 | Wire coil driven uninterrupted three-stage 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 |
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 |
Also Published As
| Publication number | Publication date |
|---|---|
| CN103486207A (en) | 2014-01-01 |
| WO2014139066A1 (en) | 2014-09-18 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN106740046B (en) | Hybrid power system based on engine and motor and power output method thereof | |
| CN109764107B (en) | Variable speed transmission device | |
| CN104121346B (en) | Single planetary row confluxes hydraulic machinery compound split path transmission wheel box | |
| CN103486207B (en) | A kind of power infinitely variable speed gearing continuously | |
| CN102748435B (en) | Planetary gear transmission based on double brakes | |
| US8585531B2 (en) | Independently controllable transmission mechanism with an identity-ratio series type | |
| CN102602277A (en) | Multi-power-source multi-mode coupling drive system | |
| CN102720809B (en) | A kind of speed changer and comprise the vehicle of this speed changer | |
| CN102777555B (en) | Continuous power infinitely variable speed transmission mechanism | |
| CN104329433A (en) | Double-flow transmission gearbox for hydraulic machine of tractor | |
| KR101373443B1 (en) | Hydrostatic Mechanical Transmission for Automatic shifting of sub-gearshift | |
| CN104329434A (en) | Hydraulic mechanical dual-power flow transmission gearbox | |
| CN103335075A (en) | Electronic control speed regulating stepless speed changing system and control method | |
| CN203926645U (en) | A kind of electrically driven (operated) planetary transmission | |
| CN103453103A (en) | Step transition type stepless speed changer | |
| CN202518081U (en) | Multi-power source and multi-mode coupling driving system | |
| CN109578544B (en) | Single-planet-row multi-mode hydraulic mechanical stepless speed changer | |
| CN109751381B (en) | Multifunctional stepless speed change transmission device | |
| CN202746512U (en) | Continuous power stepless speed-changing transmission mechanism | |
| CN103711846B (en) | Ten gear gearboxes of a kind of dead axle and planet Composite Transmission | |
| CN102797808B (en) | Speed control system | |
| CN202251790U (en) | Transverse multifunctional transmission | |
| CN104534037A (en) | Two-gear automatic transmission for pure electric vehicle | |
| CN203892480U (en) | Longitudinally-arranged hybrid dual-clutch transmission gearing device | |
| CN202690911U (en) | Planetary gearbox based on double brakes |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| PP01 | Preservation of patent right |
Effective date of registration: 20160616 Granted publication date: 20151223 |
|
| RINS | Preservation of patent right or utility model and its discharge | ||
| PD01 | Discharge of preservation of patent |
Date of cancellation: 20161216 Granted publication date: 20151223 |
|
| PP01 | Preservation of patent right |
Effective date of registration: 20161216 Granted publication date: 20151223 |
|
| RINS | Preservation of patent right or utility model and its discharge | ||
| PD01 | Discharge of preservation of patent |
Date of cancellation: 20201216 Granted publication date: 20151223 |
|
| PD01 | Discharge of preservation of patent | ||
| PP01 | Preservation of patent right |
Effective date of registration: 20201216 Granted publication date: 20151223 |
|
| PP01 | Preservation of patent right | ||
| PD01 | Discharge of preservation of patent |
Date of cancellation: 20210616 Granted publication date: 20151223 |
|
| PD01 | Discharge of preservation of patent | ||
| PP01 | Preservation of patent right |
Effective date of registration: 20210616 Granted publication date: 20151223 |
|
| PP01 | Preservation of patent right |