CN105299157B - A kind of 9-speed transmission - Google Patents
A kind of 9-speed transmission Download PDFInfo
- Publication number
- CN105299157B CN105299157B CN201510763324.5A CN201510763324A CN105299157B CN 105299157 B CN105299157 B CN 105299157B CN 201510763324 A CN201510763324 A CN 201510763324A CN 105299157 B CN105299157 B CN 105299157B
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- CN
- China
- Prior art keywords
- driving member
- brake
- clutch
- gear
- combined
- 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.)
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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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/04—Smoothing ratio shift
-
- 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
- F16H2200/0065—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising nine forward speeds
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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
- F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears
Abstract
The present invention provides a kind of 9-speed transmission, including planet row, be mounted on both ends respectively with corresponding input shaft, export input link, the output link of axis connection, driving member, brake and clutch.The planet row are as follows: planet row PGS1~planet row PGS4；The driving member are as follows: driving member (3)~driving member (7)；The brake includes brake B1~brake B4；The clutch includes clutch C1 and clutch C2.Speed changer provided by the invention has the advantages that gear is more, fuel economy is good, small in size and light-weight.
Description
Technical field
The present invention relates to a kind of transmission device, specially a kind of 9-speed transmission of automobile driving system.
Background technique
In vehicle automatic transmission, the power such as internal combustion engine reach the input shaft of speed changer through fluid torque-converter, by current
After gear speed-changing, power is exported from output shaft, and reach left and right driving wheel through differential mechanism, and automatic transmission is generally by more
A planet row, brake and clutch composition.Six more popular gear planetary automatic transmissions at present, gear range is relatively
It is small, it is unable to satisfy the demand of transmission ratio, so needing to provide a kind of 9-speed transmission, to meet requirement of the vehicle to gear.
The present inventor has found that existing vehicle automatic transmission suffers from the drawback that 1, adjacent shelves through long-term observation, research
Between rank is bigger, gear range is small, uneconomical.2, it shakes during the work time larger, influences the normal operation of speed changer,
There are security risk, maintenance cost is high.3, shift response speed is slow, shift pause and transition in rhythm or melody sense is obvious, the handling difference of automobile.
For this reason, it may be necessary to a kind of 9-speed transmission be provided, to increase the gear of automatic transmission, improve vehicle economy and behaviour
Control performance.
Summary of the invention
The deficiencies in the prior art are solved, the present invention provides following technical proposals to realize: a kind of nine grades of speed changes are provided
Device, including planet row, be mounted on both ends respectively with corresponding input shaft, export axis connection input link, output link；Transmission
Component, brake and clutch,
The planet row are as follows: planet row PGS1~planet row PGS4；
The driving member are as follows: 3~driving member of driving member 7；
The brake includes brake B1~brake B4；
The clutch includes clutch C1 and clutch C2.
The planet row PGS1 includes the sun gear S1 being connected with the input link 1, is connected with the driving member 3
The planet carrier CA1 and gear ring R1 being connected with the driving member 4；
The planet row PGS2 includes the sun gear S2 being connected with the driving member 4, is connected with the driving member 7
The planet carrier CA2 and gear ring R2 being connected with the input link 1；
The planet row PGS3 includes the sun gear S3 being connected with the driving member 4, is connected with the driving member 5
The planet carrier CA3 and gear ring R3 being connected with the output link 2；
The planet row PGS4 includes the sun gear S4 being connected with the driving member 6, is connected with the output link 2
The planet carrier CA4 and gear ring R4 being connected with the driving member 7.
The input link 1 is connect with the interior hub of the sun gear S1, gear ring R2 and clutch C2 respectively；
The output link 2 is connect with the outer hub of the gear ring R3, planet carrier CA4 and clutch C1 respectively.
The driving member 3 is connect with the planet carrier CA1；
The driving member 4 is connect with the outer hub of the gear ring R1, sun gear S2, sun gear S3 and clutch C2；
The driving member 5 is connect with the planet carrier CA3；
The driving member 6 is connect with the interior hub of the sun gear S4 and clutch C1；
The driving member 7 is connect with the planet carrier CA2 and gear ring R4；
3 endpoint of driving member is equipped with the brake B1；
4 endpoint of driving member is equipped with the brake B2；
5 endpoint of driving member is equipped with the brake B3；
6 endpoint of driving member is equipped with the brake B4.
The planet row be by a sun gear, a gear ring, a planet carrier and more than one planetary gear set at
Planetary gear transmission mechanism.
The input shaft is the turbine wheel shaft of fluid torque-converter, and engine is connected through fluid torque-converter with the planet row.
The brake and clutch are the multiple-piece friction manipulation part driven by hydraulic oil.
A kind of gear association schemes for speed changer, which comprises
When brake B3 and brake B1 is combined, driving member 5 and driving member 3 are braked, and realize one grade；
When brake B3 and clutch C1 is combined, driving member 5 is braked, output link 2 and the whole rotation of driving member 6
Turn, realizes two grades；
When brake B3 and brake B4 is combined, driving member 5 and driving member 6 are braked, and realize third gear；
When clutch C1 and brake B1 is combined, output link 2 and driving member 6 are rotated integrally, and driving member 3 is made
It is dynamic, realize fourth gear；
When clutch C1 and brake B2 is combined, output link 2 and driving member 6 are rotated integrally, and driving member 4 is made
It is dynamic, realize five grades；
When brake B1 and brake B4 is combined, driving member 3 and driving member 6 are braked, and realize six grades；
When clutch C1 and clutch C2 is combined, output link 2 and driving member 6 are rotated integrally, input link 1 and biography
Dynamic component 4 rotates integrally, and realizes seven grades；
When brake B2 and brake B4 is combined, driving member 4 and driving member 6 are braked, and realize eight grades；
When clutch C2 and brake B4 is combined, input link 1 and driving member 4 are rotated integrally, and driving member 6 is made
It is dynamic, realize nine grades；
When clutch C2 and brake B3 is combined, input link 1 and driving member 4 are rotated integrally, and driving member 5 is made
It is dynamic, realize reverse gear.
1 9-speed transmission gear association schemes of table and corresponding transmission ratio, rank compare schematic table
Zero indicates that controls combines
Each shelves transmission ratio is determined by the k value of four planet rows.For example, k1=2.236, k2=1.695, k3=3.293 and
When k4=-2.258, each shelves transmission ratio shown in table 1 can be obtained, the rank ratio of adjacent gear positions transmission ratio is less than between 2 grades~8 grades
1.36, meanwhile, the resultant gear ratio range (7.363/0.557) of drive shift reaches 13.2, and it is more excellent thus to obtain overall performance
Ratio characteristic.
Transmission ratio of the present invention refers to that the ratio between input shaft rotating speed and output shaft revolving speed, planet row k value refer to planet row
The gear ring number of teeth and the ratio between the sun gear number of teeth.
Compared with the latest prior art, technical solution provided by the invention has the following beneficial effects:
1,9-speed transmission provided by the invention is real using the scheme of four planet rows, four brakes and two clutches
Existing nine drive shifts, drive shift resultant gear ratio range can reach adjacent two grades of rank ratio between 13 or more, 2 grades~8 grades and be less than
1.36, have the advantages that VE Vehicle Economy is good.
2,9-speed transmission provided by the invention uses four planet rows, and the k value of four planet rows is small, and radial dimension is small,
Have the advantages that size is small, light-weight.
3,9-speed transmission provided by the invention has shift fast response time, shift pause and transition in rhythm or melody sense small, and automobile is handling good
The advantages of.
Detailed description of the invention
Fig. 1 is 9-speed transmission structural schematic diagram provided by the invention；
Wherein, 1-input link, 2-output links, 3-driving members, 4-driving members, 5-driving members, 6-
Driving member, 7-driving members.
Specific embodiment
Following will be combined with the drawings in the embodiments of the present invention, and technical solution in the embodiment of the present invention carries out clear, complete
Site preparation description, it is clear that described embodiment is only one embodiment of the present of invention, instead of all the embodiments.Based on this
The embodiment of invention, every other implementation obtained by those of ordinary skill in the art without making creative efforts
Example, shall fall within the protection scope of the present invention.
Embodiment 1:
As shown in Figure 1, a kind of 9-speed transmission, including planet row, be mounted on both ends respectively with corresponding input shaft, output
Input link 1, the output link 2 of axis connection；Driving member, brake and clutch,
The planet row are as follows: planet row PGS1~planet row PGS4；
The driving member are as follows: 3~driving member of driving member 7；
The brake includes brake B1~brake B4；
The clutch includes clutch C1 and clutch C2.
The planet row PGS1 includes the sun gear S1 being connected with the input link 1, is connected with the driving member 3
The planet carrier CA1 and gear ring R1 being connected with the driving member 4；
The planet row PGS2 includes the sun gear S2 being connected with the driving member 4, is connected with the driving member 7
The planet carrier CA2 and gear ring R2 being connected with the input link 1；
The planet row PGS3 includes the sun gear S3 being connected with the driving member 4, is connected with the driving member 5
The planet carrier CA3 and gear ring R3 being connected with the output link 2；
The planet row PGS4 includes the sun gear S4 being connected with the driving member 6, is connected with the output link 2
The planet carrier CA4 and gear ring R4 being connected with the driving member 7.
The input link 1 is connect with the interior hub of the sun gear S1, gear ring R2 and clutch C2 respectively；
The output link 2 is connect with the outer hub of the gear ring R3, planet carrier CA4 and clutch C1 respectively.
The driving member 3 is connect with the planet carrier CA1；
The driving member 4 is connect with the outer hub of the gear ring R1, sun gear S2, sun gear S3 and clutch C2；
The driving member 5 is connect with the planet carrier CA3；
The driving member 6 is connect with the interior hub of the sun gear S4 and clutch C1；
The driving member 7 is connect with the planet carrier CA2 and gear ring R4；
3 endpoint of driving member is equipped with the brake B1；
4 endpoint of driving member is equipped with the brake B2；
5 endpoint of driving member is equipped with the brake B3；
6 endpoint of driving member is equipped with the brake B4.
The planet row be by a sun gear, a gear ring, a planet carrier and more than one planetary gear set at
Planetary gear transmission mechanism.
The input shaft is the turbine wheel shaft of fluid torque-converter, and engine is connected through fluid torque-converter with the planet row.
The brake and clutch are the multiple-piece friction manipulation part driven by hydraulic oil.
A kind of gear association schemes for speed changer, which comprises
When brake B3 and brake B1 is combined, driving member 5 and driving member 3 are braked, and realize one grade；
When brake B3 and clutch C1 is combined, driving member 5 is braked, output link 2 and the whole rotation of driving member 6
Turn, realizes two grades；
When brake B3 and brake B4 is combined, driving member 5 and driving member 6 are braked, and realize third gear；
When clutch C1 and brake B1 is combined, output link 2 and driving member 6 are rotated integrally, and driving member 3 is made
It is dynamic, realize fourth gear；
When clutch C1 and brake B2 is combined, output link 2 and driving member 6 are rotated integrally, and driving member 4 is made
It is dynamic, realize five grades；
When brake B1 and brake B4 is combined, driving member 3 and driving member 6 are braked, and realize six grades；
When clutch C1 and clutch C2 is combined, output link 2 and driving member 6 are rotated integrally, input link 1 and biography
Dynamic component 4 rotates integrally, and realizes seven grades；
When brake B2 and brake B4 is combined, driving member 4 and driving member 6 are braked, and realize eight grades；
When clutch C2 and brake B4 is combined, input link 1 and driving member 4 are rotated integrally, and driving member 6 is made
It is dynamic, realize nine grades；
When clutch C2 and brake B3 is combined, input link 1 and driving member 4 are rotated integrally, and driving member 5 is made
It is dynamic, realize reverse gear.
The above embodiments are merely illustrative of the technical scheme of the present invention and are not intended to be limiting thereof, although referring to above-described embodiment pair
The present invention is described in detail, those of ordinary skill in the art still can to a specific embodiment of the invention into
Row modifies perhaps equivalent replacement and these exist without departing from any modification of spirit and scope of the invention or equivalent replacement
Within claims of the invention.
Claims (3)
1. a kind of 9-speed transmission, including planet row, be mounted on both ends respectively with corresponding input shaft, export the input of axis connection
Component (1), output link (2), driving member, brake and clutch, which is characterized in that
The planet row are as follows: planet row PGS1~planet row PGS4；
The driving member are as follows: third driving member, the 4th driving member, the 5th driving member, the 6th driving member and the 7th
Driving member；
The brake includes brake B1~brake B4；
The clutch includes clutch C1 and clutch C2；
The planet row PGS1 includes the sun gear S1 being connected with the input link (1), is connected with the third driving member
Planet carrier CA1 and the gear ring R1 that is connected with the 4th driving member；
The planet row PGS2 includes the sun gear S2 being connected with the 4th driving member, is connected with the 7th driving member
Planet carrier CA2 and the gear ring R2 that is connected with the input link (1)；
The planet row PGS3 includes the sun gear S3 being connected with the 4th driving member, is connected with the 5th driving member
Planet carrier CA3 and the gear ring R3 that is connected with the output link (2)；
The planet row PGS4 includes the sun gear S4 being connected with the 6th driving member, is connected with the output link (2)
Planet carrier CA4 and the gear ring R4 that is connected with the 7th driving member；
The planet row be by a sun gear, a gear ring, a planet carrier and more than one planetary gear set at planet
Gear drive；
The input shaft is the turbine wheel shaft of fluid torque-converter, and engine is connected through fluid torque-converter with the planet row；
The input link (1) connect with the interior hub of the sun gear S1, gear ring R2 and clutch C2 respectively；
The output link (2) connect with the outer hub of the gear ring R3, planet carrier CA4 and clutch C1 respectively；
4th driving member is connect with the outer hub of the gear ring R1, sun gear S2, sun gear S3 and clutch C2；
6th driving member is connect with the interior hub of the sun gear S4 and clutch C1；
The third driving member endpoint is equipped with the brake B1；
The 4th driving member endpoint is equipped with the brake B2；
The 5th driving member endpoint is equipped with the brake B3；
The 6th driving member endpoint is equipped with the brake B4.
2. speed changer as described in claim 1, which is characterized in that the brake and clutch are more to be driven by hydraulic oil
Plate friction controls.
3. a kind of transmission gear combination method for any one of 1~2 claim, which is characterized in that the described method includes:
When brake B3 and brake B1 is combined, the 5th driving member and the braking of third driving member realize one grade；
When brake B3 and clutch C1 is combined, the braking of the 5th driving member, output link (2) and the 6th driving member are whole
Rotation realizes two grades；
When brake B3 and brake B4 is combined, third gear is realized in the 5th driving member and the braking of the 6th driving member；
When clutch C1 and brake B1 is combined, output link (2) and the 6th driving member are rotated integrally, third driving member
Fourth gear is realized in braking；
When clutch C1 and brake B2 is combined, output link (2) and the 6th driving member are rotated integrally, the 4th driving member
Braking realizes five grades；
When brake B1 and brake B4 is combined, third driving member and the braking of the 6th driving member realize six grades；
When clutch C1 and clutch C2 is combined, output link (2) and the 6th driving member are rotated integrally, input link (1)
It is rotated integrally with the 4th driving member, realizes seven grades；
When brake B2 and brake B4 is combined, the 4th driving member and the braking of the 6th driving member realize eight grades；
When clutch C2 and brake B4 is combined, input link (1) and the 4th driving member are rotated integrally, the 6th driving member
Braking realizes nine grades；
When clutch C2 and brake B3 is combined, input link (1) and the 4th driving member are rotated integrally, the 5th driving member
Reverse gear is realized in braking.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510763324.5A CN105299157B (en) | 2015-11-10 | 2015-11-10 | A kind of 9-speed transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510763324.5A CN105299157B (en) | 2015-11-10 | 2015-11-10 | A kind of 9-speed transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105299157A CN105299157A (en) | 2016-02-03 |
| CN105299157B true CN105299157B (en) | 2019-01-25 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510763324.5A Active CN105299157B (en) | 2015-11-10 | 2015-11-10 | A kind of 9-speed transmission |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN105299157B (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106763550B (en) * | 2016-12-30 | 2023-09-08 | 中国第一汽车股份有限公司 | Nine-gear double clutch type automatic transmission |
| WO2018210400A1 (en) * | 2017-05-15 | 2018-11-22 | Volvo Construction Equipment Ab | A transmission for a vehicle |
| CN109538719A (en) * | 2018-12-21 | 2019-03-29 | 中国北方车辆研究所 | One kind seven keeps off planetary automatic transmission |
| CN111550532A (en) * | 2020-03-30 | 2020-08-18 | 中国北方车辆研究所 | Seven-gear planetary automatic transmission |
| CN113153988B (en) * | 2021-04-20 | 2023-11-28 | 中国北方车辆研究所 | Three-degree-of-freedom nine-gear compound planetary transmission mechanism |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101493135A (en) * | 2008-01-25 | 2009-07-29 | 通用汽车环球科技运作公司 | Multi-speed transmission |
| DE102009028702A1 (en) * | 2009-08-20 | 2011-02-24 | Zf Friedrichshafen Ag | Multi-stage gear, particularly automatic gear, has drive shaft, output shaft and four planetary sets which are arranged in housing, and eight rotatable shafts and six switching elements are also provided |
| CN102822567A (en) * | 2010-05-28 | 2012-12-12 | 宝马股份公司 | Planetary-gear automatic transmission |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7753820B2 (en) * | 2007-07-13 | 2010-07-13 | Gm Global Technology Operations, Inc. | Multi-speed transmission |
| US8047950B2 (en) * | 2009-02-17 | 2011-11-01 | GM Global Technology Operations LLC | Multi-speed transmission |
-
2015
- 2015-11-10 CN CN201510763324.5A patent/CN105299157B/en active Active
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101493135A (en) * | 2008-01-25 | 2009-07-29 | 通用汽车环球科技运作公司 | Multi-speed transmission |
| DE102009028702A1 (en) * | 2009-08-20 | 2011-02-24 | Zf Friedrichshafen Ag | Multi-stage gear, particularly automatic gear, has drive shaft, output shaft and four planetary sets which are arranged in housing, and eight rotatable shafts and six switching elements are also provided |
| CN102822567A (en) * | 2010-05-28 | 2012-12-12 | 宝马股份公司 | Planetary-gear automatic transmission |
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| Publication number | Publication date |
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| CN105299157A (en) | 2016-02-03 |
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