CN105546058A - Six-gear planetary gear automatic transmission - Google Patents
Six-gear planetary gear automatic transmission Download PDFInfo
- Publication number
- CN105546058A CN105546058A CN201610048087.9A CN201610048087A CN105546058A CN 105546058 A CN105546058 A CN 105546058A CN 201610048087 A CN201610048087 A CN 201610048087A CN 105546058 A CN105546058 A CN 105546058A
- Authority
- CN
- China
- Prior art keywords
- gear
- clutch
- seat
- planetary gear
- planetary
- 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.)
- Granted
Links
- 230000005540 biological transmission Effects 0.000 title claims abstract description 26
- 230000007246 mechanism Effects 0.000 abstract description 9
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 150000001875 compounds Chemical class 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000009466 transformation Effects 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
-
- 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
- F16H2200/0052—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising six 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
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two 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
Abstract
The invention discloses a six-gear planetary gear automatic transmission. The six-gear planetary gear automatic transmission comprises a power input shaft and a power output shaft. The first output end of the power input shaft is connected with a front-row gear ring of a planetary gear mechanism through a first clutch, the second output end of the power input shaft is connected with a front-row sun gear of the planetary gear mechanism through a second clutch, the third output end of the power input shaft is connected with a rear-row gear ring of the planetary gear mechanism through a third clutch, the fourth output end of the power input shaft is connected with a rear-row planetary frame of the planetary gear mechanism through a fourth clutch, and the fifth output end of the power input shaft is connected with a rear-row sun gear of the planetary gear mechanism through a fifth clutch. The automatic transmission is composed of double row planetary gear mechanisms with different parameters, the double row planetary gear mechanisms are relatively independent, and six gears with reasonably-distributed transmission ratios can be formed; and when all the gears work, power is transmitted by a single row planetary gear mechanism, a power transmission line is simple.
Description
Technical field
The present invention relates to a kind of six gear planetary gear automatic transmissions.
Background technique
Automatic transmission generally comprises the friction engagement element of such as planetary gear unit, clutch and break.Automatic transmission carries out transformation of energy and transmission of power by automatic transmission fluid, utilize the component such as oil pump, oil circuit loop, clutch, planetary gear set, multiple solenoid valves to realize automatic speed changing, the car steering for people brings easily easyly controls impression.
Existing automatic transmission is mainly made up of ravigneaux type planetary gear structure or Simpson's gear structure, is 4 speed transmissions.The feature of La Weina planetary gear wheel construction: it is a kind of two-row structure, front and rear row shares a gear ring and a planet carrier; On planet carrier, layman's star-wheel is long row star-wheel, engages with front-seat sun gear, and expert's star-wheel is short planet wheel, engages with rear row's small sun gear and long row star-wheel simultaneously.The feature of simpson planetary gear structure: the gear parameter of former and later two planet rows is identical, and the sun gear of former and later two planet rows connects as a whole, i.e. public sun gear, front-seat planet carrier is connected with the gear ring of rear row.But the automatic transmission be made up of single La Weina or simpson planetary gear can't realize wider gear range and more gear performance requirement, and the structure of traditional automatic transmission and power transmission route complexity, executive component is too much, easily produces interference.
Summary of the invention
The defect that the present invention seeks to exist for prior art provides a kind of six gear planetary gear automatic transmissions.
The present invention for achieving the above object, adopts following technological scheme: a kind of six gear planetary gear automatic transmissions, comprise power input shaft 1 and pto＝power take-off 22;
First output terminal of described power input shaft 1 is connected with the front-seat gear ring 7 of planetary gears by first clutch 2, its second output terminal is connected with the front-seat sun gear 5 of planetary gears by second clutch 4, its the 3rd output terminal is connected with the rear ring gear 16 of planetary gears by the 3rd clutch 10, its the 4th output terminal is connected with the rear seniority among brothers and sisters carrier 17 of planetary gears by four clutches 11, and its 5th output terminal is connected with rear row's sun gear 14 of planetary gears by the 5th clutch 13; Wherein,
The front-seat planet carrier 8 being with front-seat planetary pinion 6 is provided with between described front-seat sun gear 5 and front-seat gear ring 7;
The described rear seniority among brothers and sisters carrier 17 of rows of planetary gear 15 after being with is provided with between described rear row's sun gear 14 and rear ring gear 16;
The first input end of described pto＝power take-off 22 is connected with the output terminal of described front-seat planet carrier 8 by the 6th clutch 23, its second input end is connected with the output terminal of described 3rd clutch 10 by the 7th clutch 21, and its 3rd input end is connected with the output terminal of described rear seniority among brothers and sisters carrier 17 by the 8th clutch 20.
Further, the first break 3 that described front-seat gear ring 7 is braked is provided with between described first clutch 2 and front-seat gear ring 7, the second brake 9 that described front-seat sun gear 5 is braked is provided with between described second clutch 4 and front-seat sun gear 5, the 3rd break 12 that described rear ring gear 16 is braked is provided with between described 3rd clutch 10 and rear ring gear 16, the 4th break 18 that described rear row's sun gear 14 is braked is provided with between described 5th clutch 13 and rear row's sun gear 14, the 5th break 19 that described rear seniority among brothers and sisters carrier 17 is braked is provided with between described 8th clutch 20 and rear seniority among brothers and sisters carrier 17.
Beneficial effect of the present invention: automatic transmission of the present invention is made up of the compound planetary gearing that parameter is different, two rows of planetary gear mechanisms are relatively independent, the gear district of 6 velocity ratio reasonable layouts can be formed, and by simple planetary arrangement transferring power during each gear work, power transmission line is simple.This automatic transmission have simple and compact for structure, cost is low, executive component is few, gearshift time executive component conversion less, the feature of not easily movement interference.
Accompanying drawing explanation
Fig. 1 structural representation of the present invention.
Embodiment
Shown in Fig. 1, relate to a kind of six gear planetary gear automatic transmissions, comprise power input shaft 1 and pto＝power take-off 22;
First output terminal of described power input shaft 1 is connected with the front-seat gear ring 7 of planetary gears by first clutch 2, its second output terminal is connected with the front-seat sun gear 5 of planetary gears by second clutch 4, its the 3rd output terminal is connected with the rear ring gear 16 of planetary gears by the 3rd clutch 10, its the 4th output terminal is connected with the rear seniority among brothers and sisters carrier 17 of planetary gears by four clutches 11, and its 5th output terminal is connected with rear row's sun gear 14 of planetary gears by the 5th clutch 13; Wherein,
The front-seat planet carrier 8 being with front-seat planetary pinion 6 is provided with between described front-seat sun gear 5 and front-seat gear ring 7;
The described rear seniority among brothers and sisters carrier 17 of rows of planetary gear 15 after being with is provided with between described rear row's sun gear 14 and rear ring gear 16;
The first input end of described pto＝power take-off 22 is connected with the output terminal of described front-seat planet carrier 8 by the 6th clutch 23, its second input end is connected with the output terminal of described 3rd clutch 10 by the 7th clutch 21, and its 3rd input end is connected with the output terminal of described rear seniority among brothers and sisters carrier 17 by the 8th clutch 20.
In further scheme, the first break 3 that described front-seat gear ring 7 is braked is provided with between described first clutch 2 and front-seat gear ring 7, the second brake 9 that described front-seat sun gear 5 is braked is provided with between described second clutch 4 and front-seat sun gear 5, the 3rd break 12 that described rear ring gear 16 is braked is provided with between described 3rd clutch 10 and rear ring gear 16, the 4th break 18 that described rear row's sun gear 14 is braked is provided with between described 5th clutch 13 and rear row's sun gear 14, the 5th break 19 that described rear seniority among brothers and sisters carrier 17 is braked is provided with between described 8th clutch 20 and rear seniority among brothers and sisters carrier 17.
During use, suppose that the front-seat sun gear number of teeth is Z
before 1, the gear ring number of teeth is Z
before 2, then α can be made
before=Z
before 2/ Z
before 1; Rear row's sun gear number of teeth is Z
after 1, the gear ring number of teeth is Z
after 2, then α can be made
after=Z
after 2/ Z
after 1; And α
after> α
before.Be below each gear power transmission line and gear ratio calculation.
1 gear: the 3rd break 12, the 5th clutch 13, the 8th clutch 20 work.Power from power input shaft 1 through the 5th clutch 13 by after arrange sun gear 14 and input, through after rows of planetary gear 15, after rank carrier 17, the 8th clutch 20, pto＝power take-off 22 outputting power.Calculate according to kinematic relation formula, 1 gear velocity ratio i
1=1+ α
after.
2 gears: the first break 3, second clutch 4, the 6th clutch 23 work.Power from power input shaft 1 is inputted by front-seat sun gear 5 through second clutch 4, premenstrual rows of planetary gear 6, front-seat planet carrier 8, the 6th clutch 23, pto＝power take-off 22 outputting power.Calculate according to kinematic relation formula, 2 gear velocity ratio i
2=1+ α
before.
3 gears: first clutch 2, second brake 9, the 6th clutch 23 work.Power from power input shaft 1 passes to front-seat gear ring 7 through first clutch 2, more premenstrual rows of planetary gear 6, front-seat planet carrier 8, the 6th clutch 23, pto＝power take-off 22 outputting power.Calculate according to kinematic relation formula, 3 gear velocity ratio i
3=1+1/ α
before.
4 gears: the 3rd clutch 10, the 4th break 18, the 8th clutch 20 work.Power from power input shaft 1 passes to rear ring gear 16 through the 3rd clutch 10, then through after rows of planetary gear 15, after rank carrier 17, the 8th clutch 20, pto＝power take-off 22 outputting power.Calculate according to kinematic relation formula, 4 gear velocity ratio i
4=1+1/ α
after.
5 gears: first clutch 2, second clutch 4, the 6th clutch 23 work.Power from power input shaft 1 is passed to front-seat gear ring 7 by first clutch 2, is passed to front-seat sun gear 5 by second clutch 4 simultaneously, more premenstrual rows of planetary gear 6, front-seat planet carrier 8, the 6th clutch 23, pto＝power take-off 22 outputting power.Calculate according to kinematic relation formula, 5 gear velocity ratio i
5=1.
6 gears: four clutches 11, the 4th break 18, the 7th clutch 21 work.Power ranks carrier 17 through power input shaft 1, four clutches 11 after passing to, through after rows of planetary gear 15, rear ring gear 16, the 7th clutch 21, pto＝power take-off 22 outputting power.Calculate according to kinematic relation formula, 6 gear velocity ratio i
6after=α/(1+ α
after)
Reverse gear [R gear]: the 5th clutch 13, the 5th break 19, the 7th clutch 21 work.Power arranges sun gear 14 through power input shaft 1, the 5th clutch 13 after passing to, through after rows of planetary gear 15, rear ring gear 16, the 7th clutch 21, pto＝power take-off 22 outputting power.Calculate according to kinematic relation formula, back gear ratio i
r=-α
after.
The foregoing is only preferred embodiment of the present invention, not in order to limit the present invention, within the spirit and principles in the present invention all, any amendment done, equivalent replacement, improvement etc., all should be included within protection scope of the present invention.
Claims (2)
1. six gear planetary gear automatic transmissions, is characterized in that,
Comprise power input shaft (1) and pto＝power take-off (22);
First output terminal of described power input shaft (1) is connected with the front-seat gear ring (7) of planetary gears by first clutch (2), its second output terminal is connected with the front-seat sun gear (5) of planetary gears by second clutch (4), its the 3rd output terminal is connected with the rear ring gear (16) of planetary gears by the 3rd clutch (10), its the 4th output terminal is connected with the rear seniority among brothers and sisters carrier (17) of planetary gears by four clutches (11), its the 5th output terminal is connected with rear row's sun gear (14) of planetary gears by the 5th clutch (13), wherein,
The front-seat planet carrier (8) being with front-seat planetary pinion (6) is provided with between described front-seat sun gear (5) and front-seat gear ring (7);
The described rear seniority among brothers and sisters carrier (17) of rows of planetary gear (15) after being with is provided with between described rear row's sun gear (14) and rear ring gear (16);
The first input end of described pto＝power take-off (22) is connected with the output terminal of described front-seat planet carrier (8) by the 6th clutch (23), its second input end is connected with the output terminal of described 3rd clutch (10) by the 7th clutch (21), and its 3rd input end is connected with the output terminal of described rear seniority among brothers and sisters carrier (17) by the 8th clutch (20).
2. a kind of six gear planetary gear automatic transmissions as claimed in claim 1, it is characterized in that, the first break (3) that described front-seat gear ring (7) is braked is provided with between described first clutch (2) and front-seat gear ring (7), the second brake (9) that described front-seat sun gear (5) is braked is provided with between described second clutch (4) and front-seat sun gear (5), the 3rd break (12) that described rear ring gear (16) is braked is provided with between described 3rd clutch (10) and rear ring gear (16), the 4th break (18) that described rear row's sun gear (14) is braked is provided with between described 5th clutch (13) and rear row's sun gear (14), the 5th break (19) that described rear seniority among brothers and sisters carrier (17) is braked is provided with between described 8th clutch (20) and rear seniority among brothers and sisters carrier (17).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610048087.9A CN105546058B (en) | 2016-01-19 | 2016-01-19 | One kind six keeps off planetary gear automatic transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610048087.9A CN105546058B (en) | 2016-01-19 | 2016-01-19 | One kind six keeps off planetary gear automatic transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105546058A true CN105546058A (en) | 2016-05-04 |
| CN105546058B CN105546058B (en) | 2017-10-31 |
Family
ID=55825486
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610048087.9A Expired - Fee Related CN105546058B (en) | 2016-01-19 | 2016-01-19 | One kind six keeps off planetary gear automatic transmission |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN105546058B (en) |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH04285347A (en) * | 1991-03-14 | 1992-10-09 | Nissan Motor Co Ltd | Planetary gear transmission mechanism |
| KR100911405B1 (en) * | 2008-05-30 | 2009-08-07 | 현대자동차주식회사 | Gear train of automatic transmission for vehicles |
| CN201651191U (en) * | 2010-02-11 | 2010-11-24 | 哈尔滨东安汽车发动机制造有限公司 | Automatic transmission planetary mechanism |
| CN202100668U (en) * | 2011-05-28 | 2012-01-04 | 长城汽车股份有限公司 | Gear speed control mechanism of automotive six-speed automatic transmission |
| CN104896040A (en) * | 2015-05-14 | 2015-09-09 | 南宁学院 | Multi-gear line control planetary gear automatic transmission |
| CN205298429U (en) * | 2016-01-19 | 2016-06-08 | 无锡商业职业技术学院 | Six keep off planetary gear auto transmission |
-
2016
- 2016-01-19 CN CN201610048087.9A patent/CN105546058B/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH04285347A (en) * | 1991-03-14 | 1992-10-09 | Nissan Motor Co Ltd | Planetary gear transmission mechanism |
| KR100911405B1 (en) * | 2008-05-30 | 2009-08-07 | 현대자동차주식회사 | Gear train of automatic transmission for vehicles |
| CN201651191U (en) * | 2010-02-11 | 2010-11-24 | 哈尔滨东安汽车发动机制造有限公司 | Automatic transmission planetary mechanism |
| CN202100668U (en) * | 2011-05-28 | 2012-01-04 | 长城汽车股份有限公司 | Gear speed control mechanism of automotive six-speed automatic transmission |
| CN104896040A (en) * | 2015-05-14 | 2015-09-09 | 南宁学院 | Multi-gear line control planetary gear automatic transmission |
| CN205298429U (en) * | 2016-01-19 | 2016-06-08 | 无锡商业职业技术学院 | Six keep off planetary gear auto transmission |
Also Published As
| Publication number | Publication date |
|---|---|
| CN105546058B (en) | 2017-10-31 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104033550B (en) | Multi-shifting speed variator | |
| CN104033548B (en) | Ten shift transmissions | |
| CN104033545B (en) | Six shift transmissions | |
| CN104033549B (en) | Eight shift transmissions | |
| CN104033546B (en) | 11 shift transmissions | |
| CN105546061A (en) | Seven-gear planetary gear automatic transmission | |
| CN205298432U (en) | Seven keep off planetary gear auto transmission | |
| CN205298429U (en) | Six keep off planetary gear auto transmission | |
| CN105546062A (en) | Five-gear planetary gear automatic transmission | |
| CN205298433U (en) | Five keep off planetary gear auto transmission | |
| CN105546060A (en) | Planetary gear type double-clutch four-gear automatic transmission | |
| CN105546058A (en) | Six-gear planetary gear automatic transmission | |
| CN107489744A (en) | More clutch speed changers | |
| CN205298431U (en) | Planetary geared two separation and reunions no. 5 keep off automatic gearbox | |
| CN105840749B (en) | A kind of single speed automatic transmission of double pinions combined type four | |
| CN105546098A (en) | Planetary gear type double-clutch six-gear automatic transmission | |
| CN205298430U (en) | Two separation and reunion fourth speed automatic gearbox of planetary geared | |
| CN205639497U (en) | Single doublestage planetary gear set box -like five keeps off automatic gearbox | |
| CN105927715B (en) | A kind of stage type planetary gear automatic transmission | |
| CN205663839U (en) | Single doublestage planetary gear set box -like six keeps off automatic gearbox | |
| CN205639496U (en) | Doublestage formula planetary gear auto transmission | |
| RU2290551C1 (en) | Hydromechanical gear box | |
| RU2283979C1 (en) | Hydromechanical transmission | |
| WO2006107233A1 (en) | Hydromechanical gearbox | |
| CN205298484U (en) | Planetary geared two separation and reunions six keep off automatic gearbox |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20191008 Address after: 314500, building 288, 2 Avenue, Indus street, Tongxiang, Zhejiang, Jiaxing Patentee after: ZHEJIANG MAIZHI NETWORK TECHNOLOGY CO.,LTD. Address before: 214153 Jiangsu, Huishan Province, Hu Hu Road,, No. 809, Wuxi Institue of Commerce Patentee before: Wuxi Institute of Commerce |
|
| TR01 | Transfer of patent right | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20191030 Address after: 314500 No.1 xc1001-3, Gongnong Road, Nanmen, Chongfu Town, Tongxiang City, Jiaxing City, Zhejiang Province Patentee after: JIAXING YUNSHIJIAO ELECTRONIC COMMERCE Co.,Ltd. Address before: 314500, building 288, 2 Avenue, Indus street, Tongxiang, Zhejiang, Jiaxing Patentee before: ZHEJIANG MAIZHI NETWORK TECHNOLOGY CO.,LTD. |
|
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20171031 |