CN205663838U - Single doublestage planetary gear set box -like seven keeps off automatic gearbox - Google Patents
Single doublestage planetary gear set box -like seven keeps off automatic gearbox Download PDFInfo
- Publication number
- CN205663838U CN205663838U CN201620543013.8U CN201620543013U CN205663838U CN 205663838 U CN205663838 U CN 205663838U CN 201620543013 U CN201620543013 U CN 201620543013U CN 205663838 U CN205663838 U CN 205663838U
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- China
- Prior art keywords
- gear
- clutch
- row
- seat
- sun 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- Withdrawn - After Issue
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Abstract
The utility model discloses a single doublestage planetary gear set box -like seven keeps off automatic gearbox, include the front -seat doublestage planetary gear mechanism that constitutes by front -seat ring gear, front -seat sun gear, front -seat planet carrier, a front -seat planetary gear and the 2nd front -seat planetary gear, arrange a planetary gear in, by well row of ring gear, the well row of sun gear, the well row of planet carrier and arrange the well row of doublestage planetary gear mechanism that the 2nd planetary gear constitutes in and, the back row single -stage planetary gear mechanism that constitutes by back row ring gear, back row sun wheel, back row planet carrier and back row planetary gear, wherein, the preceding well sun gear of arranging of sharing is made to front -seat sun gear and well row of sun gear, the preceding well planet carrier of arranging of sharing is made to front -seat planet carrier and well row of planet carrier. The utility model discloses an automatic gearbox has the simple structure compactness, processing part type is few, with low costs, execute component is few, execute component alternaties less when shifting, be difficult for movement interference.
Description
Technical field
This utility model relates to a kind of single double pinions combination type seven speed automatic transmission.
Background technology
Automatic transmission mainly includes planetary gear unit, clutch and brake.Automatic transmission is by automatically becoming
Speed device oil carries out energy conversion and power transmits, and utilizes oil pump, oil circuit loop, clutch, planetary gearsets, multiple electromagnetic valves etc.
Parts realize fluid drive, bring for the car steering of people and the easiest control impression.
And existing double-clutch automatic gearbox has two Input clutch, odd number is responsible for by one of them clutch
The power of shelves inputs, and the power input of even gear is responsible for by another clutch, and it has, and gearshift is steady, comfortableness is good, fuel-economizing
Advantage.At present, existing double-clutch automatic gearbox typically uses parallel-axis type gear structure, the automatic transmission knot of this structure
Structure is the compactest, 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 seven
Speed automatic transmission.
This utility model for achieving the above object, adopts the following technical scheme that a kind of single double pinions combination type seven
Speed automatic transmission, including: by front-seat gear ring 8, front-seat sun gear, front-seat planet carrier, front-seat first planet gear 11 and front row
The front-seat double pinions mechanism that second planetary gear 9 is constituted；By intermediate row teeth circle 15, middle row's sun gear, middle seniority among brothers and sisters carrier, in
Ranked first planetary gear 13 and in ranked second that planetary gear 14 constitutes Zhong Pai double pinions mechanism；By rear ring gear 19,
The heel row single-stage planetary gear train that heel row sun gear 21, heel row planet carrier 18 and heel row planetary gear 20 are constituted；Wherein, described
Front-seat sun gear and middle row's sun gear make shared front middle row's sun gear 12, and described front-seat planet carrier and middle seniority among brothers and sisters carrier are made
The front middle seniority among brothers and sisters carrier 10 shared；
First outfan of power input shaft 1 respectively with first clutch 2, second clutch 3 and the 3rd clutch 4
Input connects；The outfan of described first clutch 2 is connected with described front-seat gear ring 8, the outfan of described second clutch 3
It is connected with described front middle seniority among brothers and sisters carrier 10；The outfan of described 3rd clutch 4 is connected with described front middle row's sun gear 12；
The outfan of described intermediate row teeth circle 15 is connected with described rear ring gear 19 by the 5th clutch 16；Row in before described
The outfan of planet carrier 10 is connected with described rear ring gear 19 and the 6th clutch 23 respectively by the 4th clutch 17；Described
The outfan of the 6th clutch 23 is connected with described heel row sun gear 21；The outfan of described heel row planet carrier 18 exports with power
Axle 24 connects；
Wherein, it is provided with between described first clutch 2 and described front-seat gear ring 8 for described front-seat gear ring 8 is braked
The first brake 6；Described second clutch 3 and described before in be provided with for ranking in before described between seniority among brothers and sisters carrier 10
The second brake 5 of carrier 10 braking；It is provided with for institute between described 3rd clutch 4 and described front middle row's sun gear 12
3rd brake 7 of row's sun gear 12 braking in before stating；Arrange between described 3rd clutch 4 and described front middle row's sun gear 12
Have for the 3rd brake 7 of row's sun gear 12 braking in before described；Described 6th clutch 23 and described heel row sun gear
The 4th brake 22 for described heel row sun gear 21 is braked it is provided with between 21.
The beneficial effects of the utility model: automatic transmission of the present utility model has simple and compact for structure, processing part
Type is few, low cost, executive component are 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 seven speed automatic transmission, including: by front-seat gear ring 8,
Front-seat sun gear, front-seat planet carrier, front-seat first planet gear 11 and the front front-seat double-pinion planetary that ranked second planetary gear 9 composition
Gear mechanism；By intermediate row teeth circle 15, middle row's sun gear, middle seniority among brothers and sisters carrier, in ranked first planetary gear 13 and in ranked second planet
The Zhong Pai double pinions mechanism that gear 14 is constituted；By rear ring gear 19, heel row sun gear 21, heel row planet carrier 18 and heel row
The heel row single-stage planetary gear train that planetary gear 20 is constituted；Wherein, described front-seat sun gear and middle row's sun gear are made shared
Front middle row's sun gear 12, described front-seat planet carrier and middle seniority among brothers and sisters carrier make shared front middle seniority among brothers and sisters carrier 10；
First outfan of power input shaft 1 respectively with first clutch 2, second clutch 3 and the 3rd clutch 4
Input connects；The outfan of described first clutch 2 is connected with described front-seat gear ring 8, the outfan of described second clutch 3
It is connected with described front middle seniority among brothers and sisters carrier 10；The outfan of described 3rd clutch 4 is connected with described front middle row's sun gear 12；
The outfan of described intermediate row teeth circle 15 is connected with described rear ring gear 19 by the 5th clutch 16；Row in before described
The outfan of planet carrier 10 is connected with described rear ring gear 19 and the 6th clutch 23 respectively by the 4th clutch 17；Described
The outfan of the 6th clutch 23 is connected with described heel row sun gear 21；The outfan of described heel row planet carrier 18 exports with power
Axle 24 connects；
Wherein, it is provided with between described first clutch 2 and described front-seat gear ring 8 for described front-seat gear ring 8 is braked
The first brake 6；Described second clutch 3 and described before in be provided with for ranking in before described between seniority among brothers and sisters carrier 10
The second brake 5 of carrier 10 braking；It is provided with for institute between described 3rd clutch 4 and described front middle row's sun gear 12
3rd brake 7 of row's sun gear 12 braking in before stating；Arrange between described 3rd clutch 4 and described front middle row's sun gear 12
Have for the 3rd brake 7 of row's sun gear 12 braking in before described；Described 6th clutch 23 and described heel row sun gear
The 4th brake 22 for described heel row sun gear 21 is braked it is provided with between 21.
Automatic transmission of the present utility model is made up of three rows of planetary gear mechanisms, clutch, brake, front-seat and middle row
Planetary gears is stage type, and heel row planetary gears is single stage type, and clutch, brake are slice structure.Front-seat,
Middle row is identical with each parameter of gear ring with the sun gear of heel row planetary gears, and the configuration of its Rational Parameters can form 7
The gear of gear ratio reasonable layout, and during each gear work, power transmission line is simple.It is tight that this automatic transmission has simple in construction
Gather, process that part type is few, low cost, executive component are few, gearshift time executive component convert less, be difficult to the feature of movement interference.
During use, it is assumed that the sun gear number of teeth is Z1, the gear ring number of teeth is Z2, then α=Z can be made2/Z1.It is below that each gear power passes
Pass route and gear ratio calculation.
1 gear: the 3rd clutch 4, second brake the 5, the 5th clutch the 16, the 4th brake 22 work.Power from power
Power shaft 1 is inputted by front middle row's sun gear 12 through the 3rd clutch 4, through in ranked first planetary gear 13, in ranked second planet tooth
The output of wheel 14, intermediate row teeth circle the 15, the 5th clutch 16, rear ring gear 19, heel row planetary gear 20, heel row planet carrier 18, power
Axle 24 exports power.Calculate according to movement relation formula, 1 gear gear ratio i1=1+ α.
2 gears: second clutch the 3, the 3rd brake the 7, the 5th clutch the 16, the 4th brake 22 works.Power from power
Power shaft 1 is inputted by front middle seniority among brothers and sisters carrier 10 through second clutch 3, ranked second planetary gear 14, intermediate row teeth circle the 15, the 5th in warp
Clutch 16, rear ring gear 19, heel row planetary gear 20, heel row planet carrier 18, power output shaft 24 export power.According to motion
Relational expression calculates, 2 gear gear ratio i2=(α+1)/(α-1).
3 gears: the 3rd clutch 4, second brake the 5, the 5th clutch the 16, the 6th clutch 23 work.Power from power
Power shaft 1 is inputted by front middle row's sun gear 12 through the 3rd clutch 4, through in ranked first planetary gear 13, in ranked second planet tooth
Wheel 14, intermediate row teeth circle the 15, the 5th clutch 16 pass to rear ring gear 19 and the 6th clutch 23, and the 6th clutch 23 is again by power
Pass to heel row sun gear 21, rear ring gear 19 and heel row sun gear 21 more simultaneously through heel row planetary gear 20, heel row planet carrier 18,
Power output shaft 24 exports power.Calculate according to movement relation formula, 3 gear gear ratio i3=α.
4 gears: second clutch the 3, the 3rd brake the 7, the 5th clutch the 16, the 6th clutch 23 works.Power from power
Power shaft 1 is inputted by front middle seniority among brothers and sisters carrier 10 through second clutch 3, ranked second planetary gear the 14, the 5th clutch 16 and pass in warp
To rear ring gear 19 and the 6th clutch 23, power is passed to heel row sun gear 21 by the 6th clutch 23 again, rear ring gear 19 with
Heel row sun gear 21 exports power through heel row planetary gear 20, heel row planet carrier 18, power output shaft 24 more simultaneously.According to motion
Relational expression calculates, 2 gear gear ratio i4=α/(α-1).
5 gears: second clutch the 3, the 3rd clutch the 4, the 5th clutch the 16, the 6th clutch 23 works.Power from power
Power shaft 1 middle seniority among brothers and sisters carrier 10 and front middle row's sun gear 12 before second clutch 3 and the 3rd clutch 4 are passed to simultaneously, then warp
In ranked first planetary gear 13, in ranked second planetary gear the 14, the 5th clutch 16 and pass to rear ring gear 19 and the 6th clutch
23, power is passed to heel row sun gear 21 by the 6th clutch 23 again, and rear ring gear 19 and heel row sun gear 21 are more simultaneously through heel row
Planetary gear 20, heel row planet carrier 18, power output shaft 24 export power.Calculate according to movement relation formula, 5 gear gear ratio i5=
1。
6 gears: first clutch the 2, the 3rd brake the 7, the 4th clutch the 17, the 4th brake 22 works.Power from power
Power shaft 1 is inputted by front-seat gear ring 8 through first clutch 2, the premenstrual planetary gear 9, front-seat first planet gear 11, front of ranked second
Middle seniority among brothers and sisters carrier the 10, the 4th clutch 17, rear ring gear 19, heel row planetary gear 20, heel row planet carrier 18, power output shaft 24
Output power.Calculate according to movement relation formula, 6 gear gear ratio i6=(α2-1)/α2
7 gears: first clutch the 2, the 3rd brake the 7, the 4th clutch the 17, the 6th clutch C23 works.Power from power
Power shaft 1 is inputted by front-seat gear ring 8 through first clutch 2, the premenstrual planetary gear 9, front-seat first planet gear 11, front of ranked second
Middle seniority among brothers and sisters carrier the 10, the 4th clutch 17, passing to rear ring gear 19 and the 6th clutch 23, power is passed by the 6th clutch 23 again
To heel row sun gear 21, rear ring gear 19 and heel row sun gear 21 are more simultaneously through heel row planetary gear 20, heel row planet carrier 18, dynamic
Power output shaft 24 exports power.Calculate according to movement relation formula, 7 gear gear ratio i7=(α-1)/α.
Reverse gear [R gear]: the 3rd clutch the 4, first brake the 6, the 4th clutch the 17, the 4th brake 22 works.Power
Inputted by front middle row's sun gear 12 through the 3rd clutch 4 from power input shaft 1, premenstrual ranked first planetary gear 11, front ranked second
Planetary gear 9, front middle seniority among brothers and sisters carrier the 10, the 4th clutch 17, rear ring gear 19, heel row planetary gear 20, heel row planet carrier 18,
Power output shaft 24 exports power.Calculate according to movement relation formula, back gear ratio iR=(1-α2)/α。
The foregoing is only preferred embodiment of the present utility model, not in order to limit this utility model, all in this practicality
Within novel spirit and principle, any modification, equivalent substitution and improvement etc. made, should be included in guarantor of the present utility model
Within the scope of protecting.
Claims (1)
1. single double pinions combination type seven speed automatic transmission, it is characterised in that
Including: by front-seat gear ring (8), front-seat sun gear, front-seat planet carrier, front-seat first planet gear (11) and before ranked second row
The front-seat double pinions mechanism that star gear (9) is constituted；By intermediate row teeth circle (15), middle row's sun gear, middle seniority among brothers and sisters carrier, middle row
First planet gear (13) and in ranked second that planetary gear (14) constitutes Zhong Pai double pinions mechanism；By rear ring gear
(19), the heel row single-pinion planetary gear machine that heel row sun gear (21), heel row planet carrier (18) and heel row planetary gear (20) are constituted
Structure；Wherein, described front-seat sun gear and middle row's sun gear make shared front middle row's sun gear (12), described front-seat planet carrier and
Middle seniority among brothers and sisters carrier makes shared front middle seniority among brothers and sisters carrier (10)；
First outfan of power input shaft (1) respectively with first clutch (2), second clutch (3) and the 3rd clutch
(4) input connects；The outfan of described first clutch (2) is connected with described front-seat gear ring (8), described second clutch
(3) outfan is connected with described front middle seniority among brothers and sisters carrier (10)；The outfan of described 3rd clutch (4) is with described front middle row too
Sun wheel (12) connects；
The outfan of described intermediate row teeth circle (15) is connected with described rear ring gear (19) by the 5th clutch (16)；In before described
Seniority among brothers and sisters carrier (10) outfan by the 4th clutch (17) respectively with described rear ring gear (19) and the 6th clutch
(23) connect；The outfan of described 6th clutch (23) is connected with described heel row sun gear (21)；Described heel row planet carrier
(18) outfan is connected with power output shaft (24)；
Wherein, it is provided with between described first clutch (2) and described front-seat gear ring (8) for described front-seat gear ring (8) system
Dynamic the first brake (6)；It is provided with for described between described second clutch (3) and described front middle seniority among brothers and sisters carrier (10)
The second brake (5) that in before, seniority among brothers and sisters carrier (10) is braked；Described 3rd clutch (4) with described before in row sun gear (12) it
Between be provided with the 3rd brake (7) for row's sun gear (12) in before described is braked；Described 3rd clutch (4) is with described
It is provided with between row sun gear (12) in before for arranging, in before described, the 3rd brake (7) that sun gear (12) is braked；Described
Be provided with between 6th clutch (23) and described heel row sun gear (21) for described heel row sun gear (21) is braked
Four brakes (22).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620543013.8U CN205663838U (en) | 2016-05-29 | 2016-05-29 | Single doublestage planetary gear set box -like seven keeps off automatic gearbox |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620543013.8U CN205663838U (en) | 2016-05-29 | 2016-05-29 | Single doublestage planetary gear set box -like seven keeps off automatic gearbox |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN205663838U true CN205663838U (en) | 2016-10-26 |
Family
ID=57157623
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201620543013.8U Withdrawn - After Issue CN205663838U (en) | 2016-05-29 | 2016-05-29 | Single doublestage planetary gear set box -like seven keeps off automatic gearbox |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN205663838U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105952855A (en) * | 2016-05-29 | 2016-09-21 | 无锡商业职业技术学院 | Single-stage planetary gear and two-stage planetary gear combined seven-gear automatic transmission |
-
2016
- 2016-05-29 CN CN201620543013.8U patent/CN205663838U/en not_active Withdrawn - After Issue
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105952855A (en) * | 2016-05-29 | 2016-09-21 | 无锡商业职业技术学院 | Single-stage planetary gear and two-stage planetary gear combined seven-gear automatic transmission |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20161026 Effective date of abandoning: 20180417 |
|
| AV01 | Patent right actively abandoned |