CN105546058B - One kind six keeps off planetary gear automatic transmission - Google Patents
One kind six keeps off planetary gear automatic transmission Download PDFInfo
- Publication number
- CN105546058B CN105546058B CN201610048087.9A CN201610048087A CN105546058B CN 105546058 B CN105546058 B CN 105546058B CN 201610048087 A CN201610048087 A CN 201610048087A CN 105546058 B CN105546058 B CN 105546058B
- Authority
- CN
- China
- Prior art keywords
- clutch
- gear
- seat
- heel row
- 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.)
- Expired - Fee Related
Links
- 230000005540 biological transmission Effects 0.000 title claims abstract description 22
- 230000007246 mechanism Effects 0.000 claims abstract description 6
- 150000001875 compounds Chemical class 0.000 abstract description 2
- 238000006243 chemical reaction Methods 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- TVEXGJYMHHTVKP-UHFFFAOYSA-N 6-oxabicyclo[3.2.1]oct-3-en-7-one Chemical compound C1C2C(=O)OC1C=CC2 TVEXGJYMHHTVKP-UHFFFAOYSA-N 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
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
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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
- F16H2200/0052—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
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
Planetary gear automatic transmission, including power input shaft and power output shaft are kept off the invention discloses one kind six；First output end of the power input shaft is connected by the front-seat gear ring of first clutch and planetary gears, its second output end is connected by the front-seat sun gear of second clutch and planetary gears, its the 3rd output end is connected by the rear ring gear of the 3rd clutch and planetary gears, its the 4th output end is connected by the heel row planet carrier of the 4th clutch and planetary gears, and its 5th output end is connected by the heel row sun gear of the 5th clutch and planetary gears.The automatic transmission of the present invention is made up of the different compound planetary gearing of parameter, two rows of planetary gear mechanisms are relatively independent, the gear that 6 gearratio reasonable layouts can be formed is gone, and transmits power by simple planetary arrangement during each gear work, and power transmission line is simple.
Description
Technical field
Planetary gear automatic transmission is kept off the present invention relates to one kind six.
Background technology
Automatic transmission generally comprises friction engagement element, clutch and the brake of such as planetary gear unit.Automatically
Speed changer is to carry out energy conversion and power transmission by automatic transmission fluid, utilizes oil pump, oil circuit loop, clutch, planet
The parts such as gear train, multiple magnetic valves realize fluid drive, be people car steering bring light simplicity control impression.
Existing automatic transmission is mainly made up of ravigneaux type planetary gear structure or Simpson's gear structure, is 4 speed
Speed changer.The characteristics of drawing wiener planetary gear wheel construction：It is a kind of two-row structure, and front and rear row shares a gear ring and a row
Carrier；In planet carrier, layman's star-wheel is long planetary gear, is engaged with front-seat sun gear, and expert's star-wheel is short planetary gear, with heel row
Small sun gear and long planetary gear are engaged simultaneously.The characteristics of simpson planetary gear structure：The gear parameter of former and later two planet rows
It is identical, and the sun gear of former and later two planet rows is connected as an entirety, i.e., public sun gear, front-seat planet carrier and heel row
Gear ring is connected.But broader transmission can't be realized by single La Weina or the simpson planetary gear automatic transmission constituted
Than scope and more gear performance requirements, and the structure and power transmission route of traditional automatic transmission are complicated, perform member
Part is excessive, easily produces interference.
The content of the invention
One kind six, which is provided, the present invention seeks to the defect existed for prior art keeps off planetary gear automatic transmission.
The present invention to achieve the above object, is adopted the following technical scheme that：One kind six keeps off planetary gear automatic transmission, including
Power input shaft 1 and power output shaft 22；
First output end of the power input shaft 1 is connected by the front-seat gear ring 7 of first clutch 2 and planetary gears
Connect, its second output end is connected by second clutch 4 with the front-seat sun gear 5 of planetary gears, its 3rd output end is led to
Cross the 3rd clutch 10 to be connected with the rear ring gear 16 of planetary gears, its 4th output end passes through the 4th clutch 11 and row
The heel row planet carrier 17 of star gear mechanism is connected, the heel row that its 5th output end passes through the 5th clutch 13 and planetary gears
Sun gear 14 is connected；Wherein,
The front-seat planet carrier 8 with front-seat planetary gear 6 is provided between the front-seat sun gear 5 and front-seat gear ring 7；
The rear rows of planetary with heel row planetary gear 15 is provided between the heel row sun gear 14 and rear ring gear 16
Frame 17；
The output end that the first input end of the power output shaft 22 passes through the 6th clutch 23 and the front-seat planet carrier 8
Connection, its second input is connected by the 7th clutch 21 with the output end of the 3rd clutch 10, its 3rd input
It is connected by the 8th clutch 20 with the output end of the heel row planet carrier 17.
Further, the braked to the front-seat gear ring 7 is provided between the first clutch 2 and front-seat gear ring 7
One brake 3, is provided with the second system braked to the front-seat sun gear 5 between the second clutch 4 and front-seat sun gear 5
Dynamic device 9, is provided with the 3rd brake braked to the rear ring gear 16 between the 3rd clutch 10 and rear ring gear 16
12, the 4th brake braked to the heel row sun gear 14 is provided between the 5th clutch 13 and heel row sun gear 14
18, the 5th brake braked to the heel row planet carrier 17 is provided between the 8th clutch 20 and heel row planet carrier 17
19。
Beneficial effects of the present invention：The automatic transmission of the present invention is made up of the different compound planetary gearing of parameter,
Two rows of planetary gear mechanisms are relatively independent, can form the gear area of 6 gearratio reasonable layouts, and by single row during each gear work
Star gear mechanism transmits power, and power transmission line is simple.The automatic transmission have simple and compact for structure, cost it is low, perform
Element is few, gearshift when executive component conversion less, the characteristics of be difficult movement interference.
Brief description of the drawings
Fig. 1 the structural representation of present invention.
Embodiment
Shown in Fig. 1, it is related to one kind six and keeps off planetary gear automatic transmission, including power input shaft 1 and power output shaft 22；
First output end of the power input shaft 1 is connected by the front-seat gear ring 7 of first clutch 2 and planetary gears
Connect, its second output end is connected by second clutch 4 with the front-seat sun gear 5 of planetary gears, its 3rd output end is led to
Cross the 3rd clutch 10 to be connected with the rear ring gear 16 of planetary gears, its 4th output end passes through the 4th clutch 11 and row
The heel row planet carrier 17 of star gear mechanism is connected, the heel row that its 5th output end passes through the 5th clutch 13 and planetary gears
Sun gear 14 is connected；Wherein,
The front-seat planet carrier 8 with front-seat planetary gear 6 is provided between the front-seat sun gear 5 and front-seat gear ring 7；
The rear rows of planetary with heel row planetary gear 15 is provided between the heel row sun gear 14 and rear ring gear 16
Frame 17；
The output end that the first input end of the power output shaft 22 passes through the 6th clutch 23 and the front-seat planet carrier 8
Connection, its second input is connected by the 7th clutch 21 with the output end of the 3rd clutch 10, its 3rd input
It is connected by the 8th clutch 20 with the output end of the heel row planet carrier 17.
In further scheme, it is provided between the first clutch 2 and front-seat gear ring 7 and the front-seat gear ring 7 is made
The first dynamic brake 3, is provided with what the front-seat sun gear 5 was braked between the second clutch 4 and front-seat sun gear 5
Second brake 9, is provided with the 3rd braked to the rear ring gear 16 between the 3rd clutch 10 and rear ring gear 16
Brake 12, is provided with the 4th braked to the heel row sun gear 14 between the 5th clutch 13 and heel row sun gear 14
Brake 18, is provided with the 5th braked to the heel row planet carrier 17 between the 8th clutch 20 and heel row planet carrier 17
Brake 19.
In use, assuming that the front-seat sun gear number of teeth is ZBefore 1, the gear ring number of teeth is ZBefore 2, then α can be madeBefore=ZBefore 2/ZBefore 1；Heel row is too
Positive tooth number is ZAfter 1, the gear ring number of teeth is ZAfter 2, then α can be madeAfterwards=ZAfter 2/ZAfter 1；And αAfterwards＞ αBefore.It is each gear power transmission line below
And gear ratio calculation.
1 gear：3rd brake 12, the 5th clutch 13, the 8th clutch 20 work.Power from power input shaft 1 is through
Five clutches 13 are inputted by heel row sun gear 14, through heel row planetary gear 15, heel row planet carrier 17, the 8th clutch 20, power
Output shaft 22 exports power.Calculated according to movement relation formula, 1 gear gearratio i1=1+ αAfterwards。
2 gears：First brake 3, second clutch 4, the 6th clutch 23 work.Power from power input shaft 1 is through second
Clutch 4 is inputted by front-seat sun gear 5, premenstrual rows of planetary gear 6, front-seat planet carrier 8, the 6th clutch 23, power output shaft
22 output power.Calculated according to movement relation formula, 2 gear gearratio i2=1+ αBefore。
3 gears：First clutch 2, second brake 9, the 6th clutch 23 work.Power from power input shaft 1 is through first
Clutch 2 is transmitted to front-seat gear ring 7, then premenstrual rows of planetary gear 6, front-seat planet carrier 8, the 6th clutch 23, power output shaft 22
Export power.Calculated according to movement relation formula, 3 gear gearratio i3=1+1/ αBefore。
4 gears：3rd clutch 10, the 4th brake 18, the 8th clutch 20 work.Power from power input shaft 1 is through
Three clutches 10 are transmitted to rear ring gear 16, then defeated through heel row planetary gear 15, heel row planet carrier 17, the 8th clutch 20, power
Shaft 22 exports power.Calculated according to movement relation formula, 4 gear gearratio i4=1+1/ αAfterwards。
5 gears：First clutch 2, second clutch 4, the 6th clutch 23 work.Power from power input shaft 1 simultaneously by
First clutch 2 is transmitted to front-seat gear ring 7, front-seat sun gear 5 is transmitted to by second clutch 4, then premenstrual rows of planetary gear 6, front row
Planet carrier 8, the 6th clutch 23, the output power of power output shaft 22.Calculated according to movement relation formula, 5 gear gearratio i5=1.
6 gears：4th clutch 11, the 4th brake 18, the 7th clutch 21 work.Power is through power input shaft the 1, the 4th
Clutch 11 is transmitted to heel row planet carrier 17, through heel row planetary gear 15, rear ring gear 16, the 7th clutch 21, power output shaft
22 output power.Calculated according to movement relation formula, 6 gear gearratio i6After=α/(1+ αAfterwards)
Reverse gear [R gears]：5th clutch 13, the 5th brake 19, the 7th clutch 21 work.Power is through power input shaft
1st, the 5th clutch 13 is transmitted to heel row sun gear 14, through heel row planetary gear 15, rear ring gear 16, the 7th clutch 21, power
Output shaft 22 exports power.Calculated according to movement relation formula, back gear ratio iR=-αAfterwards。
The foregoing is only presently preferred embodiments of the present invention, be not intended to limit the invention, it is all the present invention spirit and
Within principle, any modification, equivalent substitution and improvements made etc. should be included in the scope of the protection.
Claims (1)
1. one kind six keeps off planetary gear automatic transmission, it is characterised in that
Including power input shaft (1) and power output shaft (22)；
First output end of the power input shaft (1) passes through first clutch (2) and the front-seat gear ring (7) of planetary gears
Connection, its second output end is connected by second clutch (4) with the front-seat sun gear (5) of planetary gears, and it is the 3rd defeated
Go out end be connected by the 3rd clutch (10) with the rear ring gear (16) of planetary gears, its 4th output end by the 4th from
Clutch (11) is connected with the heel row planet carrier (17) of planetary gears, and its 5th output end passes through the 5th clutch (13) and row
Heel row sun gear (14) connection of star gear mechanism；Wherein,
The front-seat planet carrier (8) with front-seat planetary gear (6) is provided between the front-seat sun gear (5) and front-seat gear ring (7)；
The rear seniority among brothers and sisters with heel row planetary gear (15) is provided between the heel row sun gear (14) and rear ring gear (16)
Carrier (17)；
The output that the first input end of the power output shaft (22) passes through the 6th clutch (23) and the front-seat planet carrier (8)
End connection, its second input is connected by the 7th clutch (21) with the output end of the 3rd clutch (10), and it the 3rd
Input is connected by the 8th clutch (20) with the output end of the heel row planet carrier (17)；The first clutch (2) with
Be provided with the first brake (3) to front-seat gear ring (7) braking between front-seat gear ring (7), the second clutch (4) with
The second brake (9) to front-seat sun gear (5) braking, the 3rd clutch are provided between front-seat sun gear (5)
(10) be provided between rear ring gear (16) to the rear ring gear (16) brake the 3rd brake (12), the described 5th from
The 4th brake (18) braked to the heel row sun gear (14), institute are provided between clutch (13) and heel row sun gear (14)
State the 5th braking for being provided with and being braked to the heel row planet carrier (17) between the 8th clutch (20) and heel row planet carrier (17)
Device (19).
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 CN105546058A (en) | 2016-05-04 |
| CN105546058B true 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 (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 automatic gearbox |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2778278B2 (en) * | 1991-03-14 | 1998-07-23 | 日産自動車株式会社 | Planetary gear transmission |
| KR100911405B1 (en) * | 2008-05-30 | 2009-08-07 | 현대자동차주식회사 | Gear train of automatic transmission for vehicles |
-
2016
- 2016-01-19 CN CN201610048087.9A patent/CN105546058B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 automatic gearbox |
Also Published As
| Publication number | Publication date |
|---|---|
| CN105546058A (en) | 2016-05-04 |
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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 |
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| 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. |
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| 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 |