CN205639497U - Single doublestage planetary gear set box -like five keeps off automatic gearbox - Google Patents
Single doublestage planetary gear set box -like five keeps off automatic gearbox Download PDFInfo
- Publication number
- CN205639497U CN205639497U CN201620542919.8U CN201620542919U CN205639497U CN 205639497 U CN205639497 U CN 205639497U CN 201620542919 U CN201620542919 U CN 201620542919U CN 205639497 U CN205639497 U CN 205639497U
- Authority
- CN
- China
- Prior art keywords
- clutch
- gear
- seat
- planet carrier
- planetary gear
- 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.)
- Withdrawn - After Issue
Links
Abstract
The utility model discloses a single doublestage planetary gear set box -like five keeps off automatic gearbox, include the front -seat single -stage planetary gear mechanism by front -seat planet carrier, front -seat planetary gear (7), front -seat sun gear and front -seat ring gear (9) constitution to reach the back row doublestage planetary gear mechanism by back row planet carrier, back row a planetary gear (11), back row the 2nd planetary gear (10), back row sun wheel and back row ring gear (18) component, wherein, front -seat planet carrier and back row planet carrier are made the front and back of sharing and are arranged planet carrier (6), front -seat sun gear and back row sun wheel make preceding back row sun wheel (8) of sharing. The utility model discloses an automatic gearbox has the simple structure compactness, processing part type is few, with low costs, execute component is few, when shifting execute component transform less, be difficult for movement interference's characteristics.
Description
Technical field
This utility model relates to a kind of single double pinions combination type five speed automatic transmission.
Background technology
Automatic transmission mainly includes planetary gear unit, clutch and brake.Automatic transmission is to pass through automatic transmission fluid
Carry out energy conversion and power transmits, utilize oil pump, oil circuit loop, clutch, planetary gearsets, multiple electromagnetic valves etc. zero
Part realizes fluid drive, brings for the car steering of people and the easiest controls impression.
And existing double-clutch automatic gearbox has two Input clutch, the dynamic of odd number shelves be responsible for by one of them clutch
Power inputs, and the power input of even gear is responsible for by another clutch, and it has, and gearshift is steady, comfortableness is good, the advantage of fuel-economizing.
At present, existing double-clutch automatic gearbox typically uses parallel-axis type gear structure, and the automatic transmission structure of this structure is inadequate
Compact, executive component is many, gearshift time executive component conversion is many, easily cause movement interference.
Utility model content
This utility model purpose is that the defect existed for prior art provides a kind of single double pinions combination type five to keep off change automatically
Speed device.
This utility model for achieving the above object, adopts the following technical scheme that a kind of single double pinions combination type five keeps off automatically
Variator, including the front-seat single-stage row being made up of front-seat planet carrier, front-seat planetary gear 7, front-seat sun gear and front-seat gear ring 9
Star gear mechanism, and by heel row planet carrier, heel row first planet gear 11, after ranked second planetary gear 10, heel row sun gear
The heel row double pinions mechanism constituted with rear ring gear 18；Wherein, described front-seat planet carrier and heel row planet carrier are made shared
Before and after rank carrier 6, described front-seat sun gear and heel row sun gear are made before and after sharing and are arranged sun gear 8；
First outfan of power input shaft 1 defeated with first clutch 2, second clutch 3 and the 3rd clutch 4 respectively
Entering end to connect, the outfan of described first clutch 2 is connected with described front-seat gear ring 9, the outfan of described second clutch 3
Being connected with described front and rear row planet carrier 6, the outfan of described 3rd clutch 4 is connected with described front and rear row sun gear 8；
The input of power output shaft 17 is connected with the 4th clutch the 14, the 5th clutch 15 and the 6th clutch 16 respectively；
The input of described 4th clutch 14 is connected with described front and rear row planet carrier 6, the input of described 5th clutch 15 and institute
Stating rear ring gear 18 to connect, the input of described 6th clutch 16 is connected with front-seat gear ring 9；
Wherein, it is provided with for described front and rear row sun gear 8 between described 3rd clutch 4 and described front and rear row sun gear 8
First brake 5 of braking；It is provided with between described 4th clutch 14 and described front and rear row planet carrier 6 for before and after described
The second brake 12 of seniority among brothers and sisters carrier 6 braking；It is provided with for right between described 6th clutch 16 and described front-seat gear ring 9
3rd brake 13 of described front-seat gear ring 9 braking.
The beneficial effects of the utility model: automatic transmission of the present utility model have simple and compact for structure, processing part type few,
Low cost, executive component be few, gearshift time executive component convert less, be difficult to the feature of movement interference.
Accompanying drawing explanation
Fig. 1 structural representation of the present utility model.
Detailed description of the invention
Shown in Fig. 1, relate to a kind of single double pinions combination type five speed automatic transmission, including by front-seat planet carrier, front row
The front-seat single-stage planetary gear train that planetary gear 7, front-seat sun gear and front-seat gear ring 9 are constituted, and by heel row planet carrier,
Heel row first planet gear 11, after ranked second planetary gear 10, heel row twin-stage row that heel row sun gear and rear ring gear 18 are constituted
Star gear mechanism；Wherein, described front-seat planet carrier and heel row planet carrier are made before and after sharing and are ranked carrier 6, and described front row is too
Sun wheel and heel row sun gear are made before and after sharing and are arranged sun gear 8；
First outfan of power input shaft 1 defeated with first clutch 2, second clutch 3 and the 3rd clutch 4 respectively
Entering end to connect, the outfan of described first clutch 2 is connected with described front-seat gear ring 9, the outfan of described second clutch 3
Being connected with described front and rear row planet carrier 6, the outfan of described 3rd clutch 4 is connected with described front and rear row sun gear 8；
The input of power output shaft 17 is connected with the 4th clutch the 14, the 5th clutch 15 and the 6th clutch 16 respectively；
The input of described 4th clutch 14 is connected with described front and rear row planet carrier 6, the input of described 5th clutch 15 and institute
Stating rear ring gear 18 to connect, the input of described 6th clutch 16 is connected with front-seat gear ring 9；
Wherein, it is provided with for described front and rear row sun gear 8 between described 3rd clutch 4 and described front and rear row sun gear 8
First brake 5 of braking；It is provided with between described 4th clutch 14 and described front and rear row planet carrier 6 for before and after described
The second brake 12 of seniority among brothers and sisters carrier 6 braking；It is provided with for right between described 6th clutch 16 and described front-seat gear ring 9
3rd brake 13 of described front-seat gear ring 9 braking.
Automatic transmission of the present utility model is made up of two-row planetary gear mechanism, clutch, brake, front-seat planetary gear machine
Structure is single stage type, and heel row planetary gears is stage type, and front and rear row planet carrier is integrated.Front row and heel row planetary gears
Sun gear identical with each parameter of gear ring, the configuration of its Rational Parameters can form the gear of 5 gear ratio reasonable layouts, and
During each gear work, power transmission line is simple.
During use, it is assumed that the number of teeth of sun gear is Z1, the gear ring number of teeth is Z2, then α=Z can be made2/Z1.It it is below the transmission of each gear power
Route and gear ratio calculation.
1 gear: the 3rd clutch the 4, the 3rd brake the 13, the 4th clutch 14 works.Power from power power shaft 1 through the 3rd from
Clutch 4 is inputted by front and rear row sun gear 8, premenstrual rows of planetary gear 7, front and rear row planet carrier the 6, the 4th clutch 14, power
Output shaft 17 exports power.Calculate according to movement relation formula, 1 gear gear ratio i1=1+ α.
2 gears: the 3rd clutch 4, second brake the 12, the 5th clutch 15 work.Power from power power shaft 1 through the 3rd from
Clutch 4 is inputted by front and rear row sun gear 8, through heel row first planet gear 11, after ranked second planetary gear 10, rear ring gear
18, the 5th clutch 15, power output shaft 17 export power.Calculate according to movement relation formula, 2 gear gear ratio i2=α.
3 gears: first clutch the 2, first brake the 5, the 4th clutch 14 works.Power from power power shaft 1 is through the first clutch
Device 2 is inputted by front-seat gear ring 9, premenstrual rows of planetary gear 7, front and rear row planet carrier the 6, the 4th clutch 14, power output shaft
17 output power.Calculate according to movement relation formula, 3 gear gear ratio i3=(1+ α)/α.
4 gears: first clutch the 2, the 3rd clutch the 4, the 4th clutch 14 works.Power from power power shaft 1 is simultaneously through first
Clutch 2 and the 3rd clutch 4 pass to front-seat gear ring 9 and front and rear row sun gear 8, more premenstrual rows of planetary gear 7, front and back rank
Carrier the 6, the 4th clutch 14, power output shaft 17 export power.Calculate according to movement relation formula, 4 gear gear ratio i4=1.
5 gears: second clutch the 3, first brake the 5, the 6th clutch 16 works.Power from power power shaft 1 is through the second clutch
Device 3 is inputted by front and rear row planet carrier 6, premenstrual rows of planetary gear 7, front-seat gear ring the 9, the 6th clutch 16, power output shaft
17 output power.Calculate according to movement relation formula, 5 gear gear ratio i5=α/(1+ α).
Reverse gear [R gear]: the 3rd clutch 4, second brake the 12, the 6th clutch 16 work.Power from power power shaft 1 warp
3rd clutch 4 is inputted by front and rear row sun gear 8, premenstrual rows of planetary gear 7, front-seat gear ring the 9, the 6th clutch 16, dynamic
Power output shaft 17 exports power.Calculate according to movement relation formula, back gear ratio iR=-α.
The foregoing is only preferred embodiment of the present utility model, not in order to limit this utility model, all in essence of the present utility model
God and principle within, any modification, equivalent substitution and improvement etc. made, should be included in protection domain of the present utility model it
In.
Claims (1)
1. single double pinions combination type five speed automatic transmission, it is characterised in that
Including the front-seat single-stage row being made up of front-seat planet carrier, front-seat planetary gear (7), front-seat sun gear and front-seat gear ring (9)
Star gear mechanism, and by heel row planet carrier, heel row first planet gear (11), after ranked second planetary gear (10), heel row
Sun gear and rear ring gear (18) are constituted heel row double pinions mechanism；Wherein, described front-seat planet carrier and rear rows of planetary
Frame is made and is ranked carrier (6) before and after sharing, and described front-seat sun gear and heel row sun gear are made before and after sharing and arranged sun gear (8)；
First outfan of power input shaft (1) respectively with first clutch (2), second clutch (3) and the 3rd clutch
The input of device (4) connects, and the outfan of described first clutch (2) is connected with described front-seat gear ring (9), and described second
The outfan of clutch (3) is connected with described front and rear row planet carrier (6), and the outfan of described 3rd clutch (4) is with described
Front and rear row sun gear (8) connects；
The input of power output shaft (17) respectively with the 4th clutch (14), the 5th clutch (15) and the 6th clutch (16)
Connect；The input of described 4th clutch (14) is connected with described front and rear row planet carrier (6), described 5th clutch (15)
Input be connected with described rear ring gear (18), the input of described 6th clutch (16) is connected with front-seat gear ring (9)；
Wherein, it is provided with for described front and rear row too between described 3rd clutch (4) and described front and rear row sun gear (8)
The first brake (5) that sun wheel (8) is braked；Set between described 4th clutch (14) and described front and rear row planet carrier (6)
It is equipped with the second brake (12) for described front and rear row planet carrier (6) is braked；Described 6th clutch (16) is with described
The 3rd brake (13) for described front-seat gear ring (9) is braked it is provided with between front-seat gear ring (9).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620542919.8U CN205639497U (en) | 2016-05-29 | 2016-05-29 | Single doublestage planetary gear set box -like five keeps off automatic gearbox |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620542919.8U CN205639497U (en) | 2016-05-29 | 2016-05-29 | Single doublestage planetary gear set box -like five keeps off automatic gearbox |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN205639497U true CN205639497U (en) | 2016-10-12 |
Family
ID=57051565
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201620542919.8U Withdrawn - After Issue CN205639497U (en) | 2016-05-29 | 2016-05-29 | Single doublestage planetary gear set box -like five keeps off automatic gearbox |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN205639497U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105864374A (en) * | 2016-05-29 | 2016-08-17 | 无锡商业职业技术学院 | Single-stage and double-stage planetary gear combined five-gear automatic transmission |
-
2016
- 2016-05-29 CN CN201620542919.8U patent/CN205639497U/en not_active Withdrawn - After Issue
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105864374A (en) * | 2016-05-29 | 2016-08-17 | 无锡商业职业技术学院 | Single-stage and double-stage planetary gear combined five-gear automatic transmission |
| CN105864374B (en) * | 2016-05-29 | 2018-01-09 | 无锡商业职业技术学院 | A kind of single speed automatic transmission of double pinions combined type five |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104033550B (en) | Multi-shifting speed variator | |
| CN104033545B (en) | Six shift transmissions | |
| CN202188084U (en) | 6AT transmission | |
| CN205639497U (en) | Single doublestage planetary gear set box -like five keeps off automatic gearbox | |
| CN104033549B (en) | Eight shift transmissions | |
| CN205663839U (en) | Single doublestage planetary gear set box -like six keeps off automatic gearbox | |
| CN205639496U (en) | Doublestage formula planetary gear auto transmission | |
| CN205663838U (en) | Single doublestage planetary gear set box -like seven keeps off automatic gearbox | |
| CN105840749B (en) | A kind of single speed automatic transmission of double pinions combined type four | |
| CN104033546A (en) | Eleven-gear transmission | |
| CN105927715B (en) | A kind of stage type planetary gear automatic transmission | |
| CN105546060B (en) | A kind of double speed automatic transmissions of clutch four of planetary gear type | |
| CN105927717B (en) | A kind of six speed automatic transmission of list double pinions combined type | |
| CN105546061B (en) | One kind seven keeps off planetary gear automatic transmission | |
| CN104964006A (en) | Eight-gear automobile automatic transmission | |
| CN105864374B (en) | A kind of single speed automatic transmission of double pinions combined type five | |
| CN105546062B (en) | One kind five keeps off planetary gear automatic transmission | |
| CN105952855B (en) | A kind of seven speed automatic transmission of list double pinions combined type | |
| CN107489744A (en) | More clutch speed changers | |
| CN104747666A (en) | Novel loader transmission | |
| CN205298433U (en) | Five keep off planetary gear auto transmission | |
| CN205298430U (en) | Two separation and reunion fourth speed automatic gearbox of planetary geared | |
| CN205298431U (en) | Planetary geared two separation and reunions no. 5 keep off automatic gearbox | |
| CN205298429U (en) | Six keep off planetary gear auto transmission | |
| CN205298432U (en) | Seven keep off planetary gear auto transmission |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20161012 Effective date of abandoning: 20180109 |
|
| AV01 | Patent right actively abandoned |