CN105299157A - Nine-stage transmission - Google Patents
Nine-stage transmission Download PDFInfo
- Publication number
- CN105299157A CN105299157A CN201510763324.5A CN201510763324A CN105299157A CN 105299157 A CN105299157 A CN 105299157A CN 201510763324 A CN201510763324 A CN 201510763324A CN 105299157 A CN105299157 A CN 105299157A
- Authority
- CN
- China
- Prior art keywords
- dirivig member
- break
- clutch
- gear
- dirivig
- 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
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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
- F16H3/62—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
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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
- 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
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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
- F16H2200/003—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 invention provides a nine-stage transmission which comprises planet rows, an input component, an output component, transmission components, brakes and clutches. The input component and the output component are arranged at the two ends and connected with a corresponding input shaft and a corresponding output shaft respectively. The planet rows comprise the planet row PGS1, the planet row PGS2, the planet row PGS3 and the planet row PGS4. The transmission components comprise the transmission component (3), the transmission component (4), the transmission component (5), the transmission component (6) and the transmission component (7). The brakes comprise the brake B1, the brake B2, the brake B3 and the brake B4. The clutches comprise the clutch C1 and the clutch C2. The transmission has the beneficial effects of having multiple gears and being good in fuel economical efficiency, small in size and light.
Description
Technical field
The present invention relates to a kind of transmission device, be 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, after current gear speed change, are exported by power from output shaft, and reach left and right driving wheel through differential mechanism, and automatic transmission is generally made up of multiple planet row, break and clutch.Six comparatively popular at present gear planetary automatic transmissions, gear range is relatively little, cannot meet the demand of velocity ratio, so need to provide a kind of 9-speed transmission, to meet the requirement of vehicle to gear.
Through long-term observation, research, the present inventor finds that existing vehicle automatic transmission exists following drawback: 1, between adjacent shelves, rank are larger, gear range is little, uneconomical.2, shake comparatively large in the course of the work, affect the normal operation of speed changer, there is potential safety hazard, maintenance expenses is high.3, speed of response of shifting gears is slow, gearshift pause and transition in rhythm or melody sense is obvious, the handling difference of automobile.
For this reason, need to provide a kind of 9-speed transmission, with increase automatic transmission gear, improve vehicle economy and handling.
Summary of the invention
Solve the deficiencies in the prior art, the invention provides following technical proposals to realize: a kind of 9-speed transmission is provided, comprises planet row, be arranged on input link, output link that two ends connect with corresponding input shaft, output shaft respectively; Dirivig member, break and clutch,
Described planet row is: planet row PGS1 ~ planet row PGS4;
Described dirivig member is: dirivig member 3 ~ dirivig member 7;
Described break comprises break B1 ~ break B4;
Described clutch comprises clutch C1 and clutch C2.
The gear ring R1 that described planet row PGS1 comprises the sun gear S1 be connected with described input link 1, the planet carrier CA1 be connected with described dirivig member 3 and is connected with described dirivig member 4;
The gear ring R2 that described planet row PGS2 comprises the sun gear S2 be connected with described dirivig member 4, the planet carrier CA2 be connected with described dirivig member 7 and is connected with described input link 1;
The gear ring R3 that described planet row PGS3 comprises the sun gear S3 be connected with described dirivig member 4, the planet carrier CA3 be connected with described dirivig member 5 and is connected with described output link 2;
The gear ring R4 that described planet row PGS4 comprises the sun gear S4 be connected with described dirivig member 6, the planet carrier CA4 be connected with described output link 2 and is connected with described dirivig member 7.
Described input link 1 is connected with hub in described sun gear S1, gear ring R2 and clutch C2 respectively;
Described output link 2 is connected with the outer hub of described gear ring R3, planet carrier CA4 and clutch C1 respectively.
Described dirivig member 3 is connected with described planet carrier CA1;
Described dirivig member 4 is connected with the outer hub of described gear ring R1, sun gear S2, sun gear S3 and clutch C2;
Described dirivig member 5 is connected with described planet carrier CA3;
Described dirivig member 6 is connected with the interior hub of described sun gear S4 and clutch C1;
Described dirivig member 7 is connected with described planet carrier CA2 and gear ring R4;
Described dirivig member 3 end points is provided with described break B1;
Described dirivig member 4 end points is provided with described break B2;
Described dirivig member 5 end points is provided with described break B3;
Described dirivig member 6 end points is provided with described break B4.
Described planet row is the planetary gear mechanism be made up of a sun gear, gear ring, a planet carrier and a more than one planet wheel.
Described input shaft is the turbine shaft of fluid torque converter, and motor is connected with described planet row through fluid torque converter.
Described break and clutch are the multidisc friction manipulation part driven by hydraulic oil.
For gear association schemes for speed changer, described method comprises:
When break B3 and break B1 in conjunction with time, dirivig member 5 and dirivig member 3 are braked, and realize one grade;
When break B3 and clutch C1 in conjunction with time, dirivig member 5 is braked, and output link 2 and dirivig member 6 integral-rotation, realize second gear;
When break B3 and break B4 in conjunction with time, dirivig member 5 and dirivig member 6 are braked, and realize third gear;
When clutch C1 and break B1 in conjunction with time, output link 2 and dirivig member 6 integral-rotation, dirivig member 3 is braked, and realizes fourth gear;
When clutch C1 and break B2 in conjunction with time, output link 2 and dirivig member 6 integral-rotation, dirivig member 4 is braked, and realizes five grades;
When break B1 and break B4 in conjunction with time, dirivig member 3 and dirivig member 6 are braked, and realize six grades;
When clutch C1 and clutch C2 in conjunction with time, output link 2 and dirivig member 6 integral-rotation, input link 1 and dirivig member 4 integral-rotation, realize seven grades;
When break B2 and break B4 in conjunction with time, dirivig member 4 and dirivig member 6 are braked, and realize eight grades;
When clutch C2 and break B4 in conjunction with time, input link 1 and dirivig member 4 integral-rotation, dirivig member 6 is braked, and realizes nine grades;
When clutch C2 and break B3 in conjunction with time, input link 1 and dirivig member 4 integral-rotation, dirivig member 5 is braked, and realizes reverse gear.
Table 1 9-speed transmission gear association schemes and corresponding velocity ratio, rank ratio signal table
Zero represents that operator combines
Each shelves velocity ratio is determined by the k value of four planet rows.Such as, when k1=2.236, k2=1.695, k3=3.293 and k4=-2.258, the each shelves velocity ratio shown in table 1 can be obtained, between 2 grades ~ 8 grades, the rank ratio of adjacent gear positions velocity ratio is less than 1.36, simultaneously, the resultant gear ratio scope (7.363/0.557) of forward gears reaches 13.2, so just obtains overall performance preferably ratio characteristic.
Velocity ratio of the present invention refers to the ratio of input shaft rotating speed and output shaft rotating speed, and planet row k value refers to the gear ring number of teeth of planet row and the ratio of the sun gear number of teeth.
With immediate prior art ratio, technological scheme provided by the invention has following beneficial effect:
1,9-speed transmission provided by the invention adopts the scheme of four planet rows, four breaks and two clutches to realize nine forward gearss, forward gears resultant gear ratio scope can reach more than 13, between 2 grades ~ 8 grades, the rank ratio of adjacent two grades is less than 1.36, has the advantage that VE Vehicle Economy is good.
2,9-speed transmission provided by the invention adopts four planet rows, and the k value of four planet rows is little, and radial dimension is little, has little, the lightweight advantage of size.
3,9-speed transmission provided by the invention has gearshift fast response time, gearshift pause and transition in rhythm or melody sense is little, the handling good advantage of automobile.
Accompanying drawing explanation
Fig. 1 is 9-speed transmission structural representation provided by the invention;
Wherein, 1-input link, 2-output link, 3-dirivig member, 4-dirivig member, 5-dirivig member, 6-dirivig member, 7-dirivig member.
Embodiment
Below in conjunction with the accompanying drawing in the embodiment of the present invention, be clearly and completely described the technological scheme in the embodiment of the present invention, obviously, described embodiment is only one embodiment of the present of invention, instead of whole embodiments.Based on embodiments of the invention, those of ordinary skill in the art, not making the every other embodiment obtained under creative work prerequisite, belong to the scope of protection of the invention.
Embodiment 1:
As shown in Figure 1, a kind of 9-speed transmission, comprises planet row, is arranged on input link 1, output link 2 that two ends connect with corresponding input shaft, output shaft respectively; Dirivig member, break and clutch,
Described planet row is: planet row PGS1 ~ planet row PGS4;
Described dirivig member is: dirivig member 3 ~ dirivig member 7;
Described break comprises break B1 ~ break B4;
Described clutch comprises clutch C1 and clutch C2.
The gear ring R1 that described planet row PGS1 comprises the sun gear S1 be connected with described input link 1, the planet carrier CA1 be connected with described dirivig member 3 and is connected with described dirivig member 4;
The gear ring R2 that described planet row PGS2 comprises the sun gear S2 be connected with described dirivig member 4, the planet carrier CA2 be connected with described dirivig member 7 and is connected with described input link 1;
The gear ring R3 that described planet row PGS3 comprises the sun gear S3 be connected with described dirivig member 4, the planet carrier CA3 be connected with described dirivig member 5 and is connected with described output link 2;
The gear ring R4 that described planet row PGS4 comprises the sun gear S4 be connected with described dirivig member 6, the planet carrier CA4 be connected with described output link 2 and is connected with described dirivig member 7.
Described input link 1 is connected with hub in described sun gear S1, gear ring R2 and clutch C2 respectively;
Described output link 2 is connected with the outer hub of described gear ring R3, planet carrier CA4 and clutch C1 respectively.
Described dirivig member 3 is connected with described planet carrier CA1;
Described dirivig member 4 is connected with the outer hub of described gear ring R1, sun gear S2, sun gear S3 and clutch C2;
Described dirivig member 5 is connected with described planet carrier CA3;
Described dirivig member 6 is connected with the interior hub of described sun gear S4 and clutch C1;
Described dirivig member 7 is connected with described planet carrier CA2 and gear ring R4;
Described dirivig member 3 end points is provided with described break B1;
Described dirivig member 4 end points is provided with described break B2;
Described dirivig member 5 end points is provided with described break B3;
Described dirivig member 6 end points is provided with described break B4.
Described planet row is the planetary gear mechanism be made up of a sun gear, gear ring, a planet carrier and a more than one planet wheel.
Described input shaft is the turbine shaft of fluid torque converter, and motor is connected with described planet row through fluid torque converter.
Described break and clutch are the multidisc friction manipulation part driven by hydraulic oil.
For gear association schemes for speed changer, described method comprises:
When break B3 and break B1 in conjunction with time, dirivig member 5 and dirivig member 3 are braked, and realize one grade;
When break B3 and clutch C1 in conjunction with time, dirivig member 5 is braked, and output link 2 and dirivig member 6 integral-rotation, realize second gear;
When break B3 and break B4 in conjunction with time, dirivig member 5 and dirivig member 6 are braked, and realize third gear;
When clutch C1 and break B1 in conjunction with time, output link 2 and dirivig member 6 integral-rotation, dirivig member 3 is braked, and realizes fourth gear;
When clutch C1 and break B2 in conjunction with time, output link 2 and dirivig member 6 integral-rotation, dirivig member 4 is braked, and realizes five grades;
When break B1 and break B4 in conjunction with time, dirivig member 3 and dirivig member 6 are braked, and realize six grades;
When clutch C1 and clutch C2 in conjunction with time, output link 2 and dirivig member 6 integral-rotation, input link 1 and dirivig member 4 integral-rotation, realize seven grades;
When break B2 and break B4 in conjunction with time, dirivig member 4 and dirivig member 6 are braked, and realize eight grades;
When clutch C2 and break B4 in conjunction with time, input link 1 and dirivig member 4 integral-rotation, dirivig member 6 is braked, and realizes nine grades;
When clutch C2 and break B3 in conjunction with time, input link 1 and dirivig member 4 integral-rotation, dirivig member 5 is braked, and realizes reverse gear.
Above embodiment is only in order to illustrate that technological scheme of the present invention is not intended to limit; although with reference to above-described embodiment to invention has been detailed description; those of ordinary skill in the field still can modify to the specific embodiment of the present invention or equivalent replacement; and these do not depart from any amendment of spirit and scope of the invention or equivalent replacement, it is all within claims of the present invention.
Claims (9)
1. a 9-speed transmission, comprises planet row, and be arranged on input link (1), output link (2) that two ends connect with corresponding input shaft, output shaft respectively, dirivig member, break and clutch, is characterized in that,
Described planet row is: planet row PGS1 ~ planet row PGS4;
Described dirivig member is: dirivig member (3) ~ dirivig member (7);
Described break comprises break B1 ~ break B4;
Described clutch comprises clutch C1 and clutch C2.
2. speed changer as claimed in claim 1, is characterized in that,
The gear ring R1 that described planet row PGS1 comprises the sun gear S1 be connected with described input link (1), the planet carrier CA1 be connected with described dirivig member (3) and is connected with described dirivig member (4);
The gear ring R2 that described planet row PGS2 comprises the sun gear S2 be connected with described dirivig member (4), the planet carrier CA2 be connected with described dirivig member (7) and is connected with described input link (1);
The gear ring R3 that described planet row PGS3 comprises the sun gear S3 be connected with described dirivig member (4), the planet carrier CA3 be connected with described dirivig member (5) and is connected with described output link (2);
The gear ring R4 that described planet row PGS4 comprises the sun gear S4 be connected with described dirivig member (6), the planet carrier CA4 be connected with described output link (2) and is connected with described dirivig member (7).
3. speed changer as claimed in claim 2, is characterized in that,
Described input link (1) is connected with hub in described sun gear S1, gear ring R2 and clutch C2 respectively;
Described output link (2) is connected with the outer hub of described gear ring R3, planet carrier CA4 and clutch C1 respectively.
4. speed changer as claimed in claim 2, is characterized in that,
Described dirivig member (3) is connected with described planet carrier CA1;
Described dirivig member (4) is connected with the outer hub of described gear ring R1, sun gear S2, sun gear S3 and clutch C2;
Described dirivig member (5) is connected with described planet carrier CA3;
Described dirivig member (6) is connected with the interior hub of described sun gear S4 and clutch C1;
Described dirivig member (7) is connected with described planet carrier CA2 and gear ring R4.
5. speed changer as claimed in claim 2, is characterized in that,
Described dirivig member (3) end points is provided with described break B1;
Described dirivig member (4) end points is provided with described break B2;
Described dirivig member (5) end points is provided with described break B3;
Described dirivig member (6) end points is provided with described break B4.
6. speed changer as claimed in claim 1, it is characterized in that, described planet row is the planetary gear mechanism be made up of a sun gear, gear ring, a planet carrier and a more than one planet wheel.
7. speed changer as claimed in claim 1, it is characterized in that, described input shaft is the turbine shaft of fluid torque converter, and motor is connected with described planet row through fluid torque converter.
8. speed changer as claimed in claim 1, it is characterized in that, described break and clutch are the multidisc friction manipulation part driven by hydraulic oil.
9. for Transmission gear association schemes for 1 ~ 8 any one claim, it is characterized in that, described method comprises:
When break B3 and break B1 in conjunction with time, dirivig member (5) and dirivig member (3) braking, realize one grade;
When break B3 and clutch C1 in conjunction with time, dirivig member (5) is braked, and output link (2) and dirivig member (6) integral-rotation realize second gear;
When break B3 and break B4 in conjunction with time, dirivig member (5) and dirivig member (6) braking, realize third gear;
When clutch C1 and break B1 in conjunction with time, output link (2) and dirivig member (6) integral-rotation, dirivig member (3) is braked, and realizes fourth gear;
When clutch C1 and break B2 in conjunction with time, output link (2) and dirivig member (6) integral-rotation, dirivig member (4) is braked, and realizes five grades;
When break B1 and break B4 in conjunction with time, dirivig member (3) and dirivig member (6) braking, realize six grades;
When clutch C1 and clutch C2 in conjunction with time, output link (2) and dirivig member (6) integral-rotation, input link (1) and dirivig member (4) integral-rotation, realize seven grades;
When break B2 and break B4 in conjunction with time, dirivig member (4) and dirivig member (6) braking, realize eight grades;
When clutch C2 and break B4 in conjunction with time, input link (1) and dirivig member (4) integral-rotation, dirivig member (6) is braked, and realizes nine grades;
When clutch C2 and break B3 in conjunction with time, input link (1) and dirivig member (4) integral-rotation, dirivig member (5) is braked, and realizes reverse gear.
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 |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510763324.5A CN105299157B (en) | 2015-11-10 | 2015-11-10 | A kind of 9-speed transmission |
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| Publication Number | Publication Date |
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| CN105299157A true CN105299157A (en) | 2016-02-03 |
| CN105299157B CN105299157B (en) | 2019-01-25 |
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| CN201510763324.5A Active CN105299157B (en) | 2015-11-10 | 2015-11-10 | A kind of 9-speed transmission |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106763550A (en) * | 2016-12-30 | 2017-05-31 | 中国第汽车股份有限公司 | Nine gear double-clutch automatic transmissions |
| 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 |
| CN113153988A (en) * | 2021-04-20 | 2021-07-23 | 中国北方车辆研究所 | Three-freedom nine-gear compound planetary transmission mechanism |
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| US20090017971A1 (en) * | 2007-07-13 | 2009-01-15 | Gm Global Technology Operations, Inc. | Multi-speed transmission |
| CN101493135A (en) * | 2008-01-25 | 2009-07-29 | 通用汽车环球科技运作公司 | Multi-speed transmission |
| US20100210403A1 (en) * | 2009-02-17 | 2010-08-19 | Gm Blobal Technology Operations, Inc. | 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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2015
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Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
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| US20090017971A1 (en) * | 2007-07-13 | 2009-01-15 | Gm Global Technology Operations, Inc. | Multi-speed transmission |
| CN101493135A (en) * | 2008-01-25 | 2009-07-29 | 通用汽车环球科技运作公司 | Multi-speed transmission |
| US20100210403A1 (en) * | 2009-02-17 | 2010-08-19 | Gm Blobal Technology Operations, Inc. | 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 |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106763550A (en) * | 2016-12-30 | 2017-05-31 | 中国第汽车股份有限公司 | Nine gear double-clutch automatic transmissions |
| 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 |
| CN113153988A (en) * | 2021-04-20 | 2021-07-23 | 中国北方车辆研究所 | Three-freedom nine-gear compound planetary transmission mechanism |
| 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 |
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|---|---|
| CN105299157B (en) | 2019-01-25 |
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