CN106523627A - Seven-gear planetary automatic transmission - Google Patents
Seven-gear planetary automatic transmission Download PDFInfo
- Publication number
- CN106523627A CN106523627A CN201611169019.4A CN201611169019A CN106523627A CN 106523627 A CN106523627 A CN 106523627A CN 201611169019 A CN201611169019 A CN 201611169019A CN 106523627 A CN106523627 A CN 106523627A
- Authority
- CN
- China
- Prior art keywords
- gear
- planet row
- planet
- driving member
- brake
- 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.)
- Pending
Links
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
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
-
- 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
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0056—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising seven forward speeds
-
- 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
- F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
- F16H2200/0086—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising two reverse speeds
-
- 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
- F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four 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
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention discloses a seven-gear planetary automatic transmission. The seven-gear planetary automatic transmission comprises an input component, an output component, five transmission components, four brakes, two clutches and four planetary gear trains. The automatic transmission adopts the scheme with the four planetary gear trains, the four brakes and the two clutches and is provided with seven forward gears and two reversing gears. The structure is simple and compact, and the space occupied by the transmission is reduced; and the transmission ratio range is wide, the clearance ratio is low, and power of an engine is fully and advantageously utilized under different working conditions.
Description
Technical field
The present invention relates to mechanical speed change drive technology field, and in particular to a kind of seven keep off planetary automatic transmission.
Background technology
Drive system is one of element of vehicle, for transmitting engine power, and the energy in straight-line travelling
Change speed and the pull strength of vehicle on request, drive system will also realize reversing and parking of vehicle etc..Variator is transmission
A critically important part in system.At present, the road vehicle of main flow kept off with seven gear planetary automatic transmissions one, two gear speed ratios between
Than larger, it is exactly that output speed fluctuation ratio is larger to be reflected on output speed, it is impossible to make finer regulation to slow-speed of revolution operating mode,
Working machine easily produces shifting shock in running, work the phenomenon such as unstable, that is, cause from one grade to be raised to two grades or from
Two grades can have greatly gearshift pause and transition in rhythm or melody when being down to one grade, have a strong impact on comfortableness and fuel economy.Such as U.S. ALLISON is public
The speed of five gears of the planetary gear mechanism of the HT750DRD Hydrodynamic transmissions of department's production compares for i1=7.97, i2=
3.19th, i3=2.07, i4=1.4, i5=1, wherein a notch speed ratio are more larger than differing with two notch speeds, are unfavorable for that some need Jing normal
The operation of the working machine switched between high rotating speed and the slow-speed of revolution.
The content of the invention
The present invention is intended to provide a kind of gear ratio is uniform, excellent performance can meet the use requirement of wheeled heavy-duty vehicle
Seven gear planetary automatic transmissions, to solve the technical problem in the presence of prior art.
The present invention is achieved by following technical solution：
A kind of seven keep off planetary automatic transmission, including first planet row, the second planet row, third planet row and fourth planet
Four planet rows of row, the first planet row include the first sun gear, the first gear ring, the first row carrier, second planet row
Including the second sun gear, the second gear ring, the second planet carrier, the third planet row include the 3rd sun gear, the 3rd gear ring, the 3rd
Planet carrier, the fourth planet row include the 4th sun gear, the 4th gear ring, fourth line carrier；
The input link being connected with input shaft and output shaft respectively and output link；
First driving member, the second driving member, the 3rd driving member, the 4th driving member and the 5th driving member five
Driving member；
First brake, second brake, four brakes of the 3rd brake and the 4th brake；
Two clutches of first clutch and second clutch；
The input link connects the outer hub of the first sun gear, the outer hub of first clutch and second clutch；It is described defeated
Go out component and connect the 4th sun gear and the third line carrier；First driving member connects the interior of the first gear ring and the first brake
Hub；The interior hub of the second driving member connection the first row carrier, the second gear ring and second brake；3rd driving member
Connect the interior hub of the second planet carrier, the 3rd gear ring, the 4th gear ring, the interior hub of second clutch and the 3rd brake；Described 4th
Driving member connects the interior hub of fourth line carrier and the 4th brake；5th driving member connect the second sun gear, the 3rd
The interior hub of sun gear and first clutch.
Planetary gear number in the first planet row, the second planet row, third planet row and fourth planet row is
Single star planet row.
The k value of the first planet row, the second planet row, third planet row and fourth planet row is 1.5～2.5.
The invention has the beneficial effects as follows：
Compared with prior art, the seven gear planetary automatic transmissions that the present invention is provided, using four planet rows, four brakings
The scheme of device and two clutches realizes seven drive shifts and two retroversion gears；Two fall back gear make vehicle in work backwards just
In the power for making full use of electromotor to do to export；Four planet rows are the simple planet row of single star, and the k value of four planet rows exists
In the range of 1.5～2.5, the integrally-built compactedness of change speed gear box is facilitated implementation, the volume and weight of change speed gear box, Jin Ershi is reduced
Existing lightweight；And have the advantages that gear ratio is uniform, excellent performance.
Description of the drawings
Fig. 1 is the structural representation of the present invention；
In figure：1- input links, 2- output links, the first driving members of 3-, the second driving members of 4-, the transmission structures of 5- the 3rd
Part, the 4th driving members of 6-, the 5th driving members of 7-, P1- first planet row, the second planet rows of P2-, P3- third planets row,
P4- fourth planets are arranged, the first sun gears of T1-, the second sun gears of T2-, the 3rd sun gears of T3-, the 4th sun gears of T4-, Q1- first
Gear ring, the second gear rings of Q2-, the 3rd gear rings of Q3-, the 4th gear rings of Q4-, J1- the first row carrier, the second planet carriers of J2-, J3- the 3rd
Planet carrier, J4- fourth line carrier, the first brakes of M1-, M2- second brakes, the 3rd brakes of M3-, the 4th brakes of M4-,
C1- first clutches, C2- second clutches.
Specific embodiment
Technical scheme is described further below in conjunction with drawings and Examples, but required protection domain
It is not limited to described；
As shown in figure 1, the seven gear planetary automatic transmissions that the present invention is provided, including first planet row P1, the second planet row
P2, third planet row P3 and fourth planet row's tetra- planet rows of P4, first planet row P1 include the first sun gear T1, first
Gear ring Q1, the first row carrier J1, the second planet row P2 include the second sun gear T2, the second gear ring Q2, the second planet carrier J2,
The third planet row P3 includes the 3rd sun gear T3, the 3rd gear ring Q3, the third line carrier J3, and the fourth planet row P4 includes
4th sun gear T4, the 4th gear ring Q4, fourth line carrier J4；
The input link 1 being connected with input shaft and output shaft respectively and output link 2；
First driving member 3, the second driving member 4, the 3rd driving member 5, the 4th driving member 6 and the 5th driving member
7 five driving members；
First brake Z1, second brake Z2, tetra- brakes of the 3rd brake Z3 and the 4th brake Z4；
Two clutches of first clutch C1 and second clutch C2；
The input link 1 connects the outer hub of the first sun gear T1, the outer hub of first clutch C1 and second clutch C2；
The output link 2 connects the 4th sun gear T4 and the third line carrier J3；First driving member 3 connect the first gear ring Q1 and
The interior hub of the first brake M1；The connection of second driving member 4 the first row carrier J1, the second gear ring Q2 and second brake M2
Interior hub；3rd driving member 5 connects the second planet carrier J2, the 3rd gear ring Q3, the 4th gear ring Q4, second clutch C2
The interior hub of interior hub and the 3rd brake M3；4th driving member 6 connection fourth line carrier J4 and the 4th brake M4's is interior
Hub；5th driving member 7 connects the second sun gear T2, the interior hub of the 3rd sun gear T3 and first clutch C1.
Planetary gear in the first planet row P1, the second planet row P2, third planet row P3 and fourth planet row P4
Number is single star planet row, can simplify gearbox designs, mitigates weight, realizes lightweight requirements.
The k value of the first planet row P1, the second planet row P2, third planet row P3 and fourth planet row P4 is 1.5
～2.5, the integrally-built compactedness of change speed gear box is facilitated implementation, the volume and weight of change speed gear box is reduced, and then is realized lightweight.
Embodiment：The planetary automatic transmission of this programme is applied to road vehicle.Wherein each planet row is arranged in order, respectively
Connected using driving member between individual planet row, input shaft is connected with input link 1, generally the turbine wheel shaft of fluid torque-converter,
For the power Jing fluid torque-converters of electromotor are reached variator.Output shaft is connected with output link 2, by transfer gear or difference
Power is reached forward and backward bridge or left and right driving wheel by fast device.The variator is full symmetric relative to center of rotation, is saved in Fig. 1
The latter half of center of rotation is omited, has no longer been explained when below describing.
First planet row P1 includes the first sun gear T1, the first gear ring Q1 and tri- revolving parts of the first row carrier J1, first
Sun gear T1 is connected with input link 1 with input power, can be braked by the first brake M1, and the first gear ring Q1 is so that the first row
The rotating speed of input link 1 is carried out deceleration output as middle output by carrier J1.
Second planet row P2 includes the second sun gear T2, the second gear ring Q2 and tri- revolving parts of the second planet carrier J2, can be
Reduction gear brakes gear ring Q2 so that the second planet carrier J2 is used as middle output by second sun by second brake M2 second
The rotating speed of wheel T2 carries out deceleration output., or the second planet carrier J2 is braked by the 3rd brake M3 so that second too in speedup shelves
The rotating speed of the second gear ring Q2 is carried out speedup output as middle output by sun wheel T2 in reverse gear.
Third planet row P3 includes the 3rd sun gear T3, the 3rd gear ring Q3 and tri- revolving parts of the third line carrier J3, can lead to
Cross the 3rd brake M3 the 3rd gear ring Q3 is braked so that the rotating speed of the 3rd sun gear T3 is entered as output by the third line carrier J3
Row slows down and exports, or the rotating speed of the 3rd gear ring Q3 and the 3rd sun gear T3 is entered as middle output by fourth line carrier J4
Row slows down and exports.
Fourth planet row P4 includes the 4th sun gear T4, the 4th gear ring Q4 and tri- revolving parts of fourth line carrier J4, can lead to
Cross the 4th brake M4 fourth line carrier J4 is braked so that the rotating speed of the 4th gear ring Q4 is entered as output by the 4th sun gear T4
Row speedup is exported.
First brake M1 is used for braking the first driving member 3, and second brake M2 is used for braking the second driving member 4,
3rd brake M3 is used for braking the 3rd driving member 5, and the 4th brake M4 is used for braking the 4th driving member 6.First clutch
Device C1 is used for connecting input link 1 and the 5th driving member 7, and second clutch C2 is used for connecting input link 1 and the 3rd transmission
Component 5.Brake and clutch are multiple-piece friction manipulation part, drive piston to be pressurizeed using hydraulic oil.The behaviour of each shelves
Vertical scheme is realized as shown in table 1：
Table 1：7-speed automatic transmission implementation and corresponding gear ratio, a ratio illustrate table
In table, " o " represents that controls is combined.
It is described in detail referring to 1 pair of example of the invention of Fig. 1 and Biao, it should be noted that, transmission described herein
Than referring to the ratio of input shaft rotating speed and output rotating speed, planet row k value refer to the gear ring number of teeth of planet row and the sun gear number of teeth it
Than.
When first clutch C1 and the 4th brake M4 are combined, the 5th driving member 7 and the input structure as input shaft
1 integral-rotation of part, the 4th driving member 6 are braked, and realize one grade " 1st ".
When first clutch C1 and the 3rd brake M3 are combined, the 5th driving member 7 and the input structure as input shaft
1 integral-rotation of part, the 3rd driving member 5 are braked, and realize two grade " 2nds " less than one grade of " 1st " gear ratio.
When first clutch C1 and second brake M2 are combined, the 5th driving member 7 and the input structure as input shaft
1 integral-rotation of part, the second driving member 4 are braked, and realize the third gear " 3rd " less than two grades of " 2nd " gear ratios.
When first clutch C1 and the 4th brake M1 are combined, the 5th driving member 7 and the input structure as input shaft
1 integral-rotation of part, the first driving member 3 are braked, and realize the fourth gear " 4th " less than third gear " 3rd " gear ratio.
When first clutch C1 and second clutch C2 are combined, the 3rd driving member 5 and the 5th driving member 7 simultaneously with
As 1 integral-rotation of input link of input shaft, five grade " 5th " less than fourth gear " 4th " gear ratio is realized.
When second clutch C2 and the first brake M1 are combined, the 3rd driving member 5 and the input structure as input shaft
1 integral-rotation of part, the first driving member 3 are braked, and realize six grade " 6ths " less than five grades of " 5th " gear ratios.
When second clutch C2 and second brake M2 are combined, the 3rd driving member 5 and the input structure as input shaft
1 integral-rotation of part, the second driving member 4 are braked, and realize seven grade " 7ths " less than six grades of " 6th " gear ratios.
When the first brake M1 and the 3rd brake M3 are combined, the first driving member 3 and the 3rd driving member 5 are braked,
Realize reverse gear " R1 ".
When the first brake M1 and the 4th brake M4 are combined, the first driving member 3 and the 4th driving member 6 are braked,
Realize reverse gear " R2 ".
Each shelves gear ratio is determined by the k value of four planet rows.For example, k1 ≈ 1.712, k2 ≈ 1.983,2.510 and of k3 ≈
During k3 ≈ 1.640, you can obtain each shelves gear ratio shown in table 1, between adjacent gear positions gear ratio than 1.153～1.841 it
Between, obtain overall performance preferably ratio characteristic.
Four planet rows in the present embodiment are the simple planet row of single star, and k value is in the range of 1.5～2.5, can make four
The radial dimension of individual planet row is less, meanwhile, obtain overall performance preferably ratio characteristic.
Above-described embodiment is only a preferred embodiment of the present invention, and in for limiting protection scope of the present invention, it is all
Deformation, modification or equivalent for being made on the basis of technical scheme etc., all should fall into the protection model of the present invention
Enclose.
Claims (3)
1. a kind of seven planetary automatic transmission is kept off, it is characterised in that：Including
First planet row (P1), the second planet row (P2), third planet row (P3) and fourth planet row's (P4) four planet rows, institute
Stating first planet row (P1) includes the first sun gear (T1), the first gear ring (Q1), the first row carrier (J1), second planet row
(P2) the second sun gear (T2), the second gear ring (Q2), the second planet carrier (J2) are included, third planet row (P3) includes the 3rd
Sun gear (T3), the 3rd gear ring (Q3), the third line carrier (J3), fourth planet row (P4) include the 4th sun gear (T4),
4th gear ring (Q4), fourth line carrier (J4)；
The input link (1) being connected with input shaft and output shaft respectively and output link (2)；
First driving member (3), the second driving member (4), the 3rd driving member (5), the 4th driving member (6) and the 5th transmission
(7) five driving members of component；
First brake (Z1), second brake (Z2), the 3rd brake (Z3) and the 4th four brakes of brake (Z4)；
Two clutches of first clutch (C1) and second clutch (C2)；
Described input link (1) connects the first sun gear (T1), the outer hub of first clutch (C1) and second clutch (C2)
Outer hub；Described output link (2) connect the 4th sun gear (T4) and the third line carrier (J3)；Described first driving member (3) connect
Connect the interior hub of the first gear ring (Q1) and the first brake (M1)；Described second driving member (4) connection the first row carrier (J1), the
The interior hub of two gear rings (Q2) and second brake (M2)；3rd driving member (5) connects the second planet carrier (J2), the 3rd tooth
The interior hub of circle (Q3), the 4th gear ring (Q4), the interior hub of second clutch (C2) and the 3rd brake (M3)；The 4th transmission structure
Part (6) connection fourth line carrier (J4) and the interior hub of the 4th brake (M4)；5th driving member (7) connects second sun
The interior hub of wheel (T2), the 3rd sun gear (T3) and first clutch (C1).
2. according to claim 1 seven planetary automatic transmission is kept off, it is characterised in that：First planet row (P1), the
Planetary gear number in two planet rows (P2), third planet row (P3) and fourth planet row (P4) is single star planet row.
3. according to claim 1 seven planetary automatic transmission is kept off, it is characterised in that：First planet row (P1), the
The k value of two planet rows (P2), third planet row (P3) and fourth planet row (P4) is 1.5～2.5.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201611169019.4A CN106523627A (en) | 2016-12-16 | 2016-12-16 | Seven-gear planetary automatic transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201611169019.4A CN106523627A (en) | 2016-12-16 | 2016-12-16 | Seven-gear planetary automatic transmission |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN106523627A true CN106523627A (en) | 2017-03-22 |
Family
ID=58340061
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201611169019.4A Pending CN106523627A (en) | 2016-12-16 | 2016-12-16 | Seven-gear planetary automatic transmission |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN106523627A (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110500390A (en) * | 2019-07-15 | 2019-11-26 | 中国北方车辆研究所 | One kind seven keeps off planetary automatic transmission |
| CN110594371A (en) * | 2019-09-24 | 2019-12-20 | 陕西法士特齿轮有限责任公司 | Seven-gear hydraulic automatic transmission |
| CN110608270A (en) * | 2019-09-24 | 2019-12-24 | 陕西法士特齿轮有限责任公司 | Hydraulic automatic transmission |
| CN110805666A (en) * | 2019-11-26 | 2020-02-18 | 贵州凯星液力传动机械有限公司 | Seven-gear planetary gear transmission |
| CN113108040A (en) * | 2021-03-29 | 2021-07-13 | 北方汤臣传动科技有限公司 | Eight-gear automatic transmission of mining truck integrating hydraulic retarber arranged in parallel shafts |
| CN115853977A (en) * | 2023-02-22 | 2023-03-28 | 潍柴动力股份有限公司 | Transmission system and transmission method |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4228461B2 (en) * | 1999-03-19 | 2009-02-25 | アイシン精機株式会社 | Transmission |
| CN102913597A (en) * | 2012-10-16 | 2013-02-06 | 中国北方车辆研究所 | Seven-level planet automatic speed changer |
| CN103511565A (en) * | 2013-10-17 | 2014-01-15 | 中国北方车辆研究所 | Automatic six-gear planetary transmission |
| CN104011431A (en) * | 2011-12-19 | 2014-08-27 | 艾里逊变速箱公司 | Automatic Transmission With Improved Gear Arrangement |
| CN104595436A (en) * | 2015-02-13 | 2015-05-06 | 中国北方车辆研究所 | Seven-gear planetary transmission for automatic transmission case |
| CN104728368A (en) * | 2015-02-13 | 2015-06-24 | 中国北方车辆研究所 | Six-gear planetary automatic transmission |
-
2016
- 2016-12-16 CN CN201611169019.4A patent/CN106523627A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4228461B2 (en) * | 1999-03-19 | 2009-02-25 | アイシン精機株式会社 | Transmission |
| CN104011431A (en) * | 2011-12-19 | 2014-08-27 | 艾里逊变速箱公司 | Automatic Transmission With Improved Gear Arrangement |
| CN102913597A (en) * | 2012-10-16 | 2013-02-06 | 中国北方车辆研究所 | Seven-level planet automatic speed changer |
| CN103511565A (en) * | 2013-10-17 | 2014-01-15 | 中国北方车辆研究所 | Automatic six-gear planetary transmission |
| CN104595436A (en) * | 2015-02-13 | 2015-05-06 | 中国北方车辆研究所 | Seven-gear planetary transmission for automatic transmission case |
| CN104728368A (en) * | 2015-02-13 | 2015-06-24 | 中国北方车辆研究所 | Six-gear planetary automatic transmission |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110500390A (en) * | 2019-07-15 | 2019-11-26 | 中国北方车辆研究所 | One kind seven keeps off planetary automatic transmission |
| CN110594371A (en) * | 2019-09-24 | 2019-12-20 | 陕西法士特齿轮有限责任公司 | Seven-gear hydraulic automatic transmission |
| CN110608270A (en) * | 2019-09-24 | 2019-12-24 | 陕西法士特齿轮有限责任公司 | Hydraulic automatic transmission |
| CN110594371B (en) * | 2019-09-24 | 2024-04-09 | 陕西法士特齿轮有限责任公司 | Seven-gear hydraulic automatic transmission |
| CN110608270B (en) * | 2019-09-24 | 2024-05-14 | 陕西法士特齿轮有限责任公司 | Hydraulic automatic transmission |
| CN110805666A (en) * | 2019-11-26 | 2020-02-18 | 贵州凯星液力传动机械有限公司 | Seven-gear planetary gear transmission |
| CN113108040A (en) * | 2021-03-29 | 2021-07-13 | 北方汤臣传动科技有限公司 | Eight-gear automatic transmission of mining truck integrating hydraulic retarber arranged in parallel shafts |
| CN115853977A (en) * | 2023-02-22 | 2023-03-28 | 潍柴动力股份有限公司 | Transmission system and transmission method |
| CN115853977B (en) * | 2023-02-22 | 2023-05-23 | 潍柴动力股份有限公司 | Transmission system and transmission method |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN106523627A (en) | Seven-gear planetary automatic transmission | |
| CN106523628B (en) | A kind of eight-gear planetary automatic speed changer | |
| CN102913597B (en) | Seven-level planet automatic speed changer | |
| CN103527732B (en) | A kind of seven gear planetary automatic transmissions | |
| CN202165536U (en) | Automatic transmission with six forward gears and reverse gear | |
| CN101852278B (en) | Nine-gear planetary automatic transmission | |
| CN104728368B (en) | One kind six keeps off planetary automatic transmission | |
| CN101487519B (en) | Full-gear speed self-adapting continuously variable transmission | |
| CN106763568B (en) | One kind six keeps off planetary automatic transmission | |
| CN106402293B (en) | Eight-gear planetary automatic transmission | |
| CN106939929A (en) | A kind of shift transmission of mono-tooth ring dry friction external control three | |
| CN103511565A (en) | Automatic six-gear planetary transmission | |
| CN106369133A (en) | Multi-gear hydrodynamic transmission | |
| CN105299157B (en) | A kind of 9-speed transmission | |
| CN106438878A (en) | Nine-gear planet automatic transmission | |
| CN106641135B (en) | A kind of 12 speed automatic transmissions | |
| CN202188084U (en) | 6AT transmission | |
| CN102628495A (en) | Six-gear planet automatic gearbox | |
| CN108105346A (en) | A kind of heavy vehicle or oil field eight-gear planetary automatic speed changer | |
| CN101922534B (en) | Electromagnetic planetary gear continuously variable transmission | |
| CN103527731B (en) | A kind of six gear planetary automatic transmissions | |
| CN105299156B (en) | A kind of multi-speed transmission | |
| CN104389960B (en) | Automatic seven-gear planetary transmission for tracked vehicle | |
| CN106678296A (en) | Seven-gear planet automatic transmission | |
| CN203431108U (en) | Combined type planetary gear set gearbox |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| RJ01 | Rejection of invention patent application after publication | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20170322 |