CN105840749A - Single-stage and double-stage planet gear combined type four-speed-gear automatic transmission - Google Patents
Single-stage and double-stage planet gear combined type four-speed-gear automatic transmission Download PDFInfo
- Publication number
- CN105840749A CN105840749A CN201610394749.8A CN201610394749A CN105840749A CN 105840749 A CN105840749 A CN 105840749A CN 201610394749 A CN201610394749 A CN 201610394749A CN 105840749 A CN105840749 A CN 105840749A
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- China
- Prior art keywords
- gear
- row
- clutch
- seat
- sun gear
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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
- F16H3/46—Gearings having only two central gears, connected by orbital gears
- F16H3/58—Gearings having only two central gears, connected by orbital gears with sets of orbital gears, each consisting of two or more intermeshing orbital gears
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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
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention discloses a single-stage and double-stage planet gear combined type four-speed-gear automatic transmission. The single-stage and double-stage planet gear combined type four-speed-gear automatic transmission comprises a front-row single-stage planet gear mechanism composed of a front row planet carrier (6), a front row planet gear (7), a front row sun gear and a front row gear ring, and a rear-row double-stage planet gear mechanism composed of a rear row planet carrier (13), a rear row first planet gear (11), a rear row second planet gear (10), a rear row sun gear and a rear row gear ring, wherein the front row sun gear and the rear row sun gear are combined into a shared front and rear row sun gear (8), and the front row gear ring and the rear row gear ring are made into a shared front and rear row gear ring (9). The automatic transmission has the beneficial effects of being simple and compact in structure, small in number of types of machining parts, low in cost, small in number of execution elements, little in execution element conversion during gear shifting and not prone to movement interference.
Description
Technical field
The present invention relates to a kind of single double pinions combination type four 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.
Summary of the invention
The present invention seeks to provide a kind of single double pinions combination type four gear automatic speed changing for the defect that prior art exists
Device.
The present invention for achieving the above object, adopts the following technical scheme that a kind of single double pinions combination type four gear automatic speed changing
Device, including the front-seat single-pinion planetary gear being made up of front-seat planet carrier 6, front-seat planetary gear 7, front-seat sun gear and front-seat gear ring
Mechanism, and by heel row planet carrier 13, heel row first planet gear 11, after ranked second planetary gear 10, heel row sun gear and
The heel row double pinions mechanism that rear ring gear is constituted；Wherein, described front-seat sun gear and the conjunction of heel row sun gear are made shared
Front and rear row sun gear 8, described front-seat gear ring and rear ring gear make toothrow circle 9 before and after sharing；
First outfan of power input shaft 1 defeated with first clutch 2, second clutch 4 and the 3rd clutch 14 respectively
Entering end to connect, the outfan of described first clutch 2 is connected with described front-seat planet carrier 6, the output of described second clutch 4
End is connected with described front and rear row sun gear 8, and the outfan of described 3rd clutch 14 is connected with described heel row planet carrier 13；
The input of power output shaft 15 is connected with described front and rear row gear ring 9；
Wherein, it is provided with between described first clutch 2 and described front-seat planet carrier 6 for described front-seat planet carrier 6 is braked
The first brake 3；It is provided with for described front and rear row too between described second clutch 4 and described front and rear row sun gear 8
The second brake 5 of sun wheel 8 braking；It is provided with for institute between described 3rd clutch 14 and described heel row planet carrier 13
State the 3rd brake 12 of heel row planet carrier 13 braking.
Beneficial effects of the present invention: the automatic transmission of the present invention have simple and compact for structure, part type is few in processing, low cost,
Executive component is few, gearshift time executive component convert less, be difficult to the feature of movement interference.
Accompanying drawing explanation
The structural representation of Fig. 1 present invention.
Detailed description of the invention
Shown in Fig. 1, relate to a kind of single double pinions combination type four speed automatic transmission, including by front-seat planet carrier 6, front
The front-seat single-stage planetary gear train that rows of planetary gear 7, front-seat sun gear and front-seat gear ring are constituted, and by heel row planet carrier 13,
Heel row first planet gear 11, after ranked second planetary gear 10, heel row double-pinion planetary tooth that heel row sun gear and rear ring gear are constituted
Wheel mechanism；Wherein, described front-seat sun gear and the conjunction of heel row sun gear are made and are arranged sun gear 8 before and after sharing, described front-seat gear ring
Toothrow circle 9 before and after sharing is made with rear ring gear；
First outfan of power input shaft 1 defeated with first clutch 2, second clutch 4 and the 3rd clutch 14 respectively
Entering end to connect, the outfan of described first clutch 2 is connected with described front-seat planet carrier 6, the output of described second clutch 4
End is connected with described front and rear row sun gear 8, and the outfan of described 3rd clutch 14 is connected with described heel row planet carrier 13；
The input of power output shaft 15 is connected with described front and rear row gear ring 9；
Wherein, it is provided with between described first clutch 2 and described front-seat planet carrier 6 for described front-seat planet carrier 6 is braked
The first brake 3；It is provided with for described front and rear row too between described second clutch 4 and described front and rear row sun gear 8
The second brake 5 of sun wheel 8 braking；It is provided with for institute between described 3rd clutch 14 and described heel row planet carrier 13
State the 3rd brake 12 of heel row planet carrier 13 braking.
The automatic transmission of the present invention is made up of two-row planetary gear mechanism, clutch, brake, and front-seat planetary gears is
Single stage type, heel row planetary gears is stage type, front-seat complete with each parameter of gear ring with the sun gear of heel row planetary gears
Exactly the same, the configuration of its Rational Parameters can form the gear of 4 gear ratio reasonable layouts, and power transmission line letter during each gear work
Single.
During use, it is assumed that the front and rear row sun gear number of teeth is Z1, the front and rear row gear ring number of teeth is Z2, then α=Z can be made2/Z1.It is below
Each gear power transmission line and gear ratio calculation.
1 gear: second clutch the 4, the 3rd brake 12 works.Power from power power shaft 1 through second clutch 4 by front and back
Row sun gear 8 input, through heel row first planet gear 11, after ranked second planetary gear 10, front and rear row gear ring 9, power output
Axle 15 exports power.Calculate according to movement relation formula, 1 gear gear ratio i1=α.
2 gears: second brake the 5, the 3rd clutch 14 works.Power from power power shaft 1 through the 3rd clutch 14 by heel row
Planet carrier 13 inputs, through after ranked second planetary gear 10, front and rear row gear ring 9, power output shaft 15 export power.According to fortune
Dynamic relational expression calculates, 2 gear gear ratio i2=α/(α-1).
3 gears: first clutch 2, second clutch C24 work.Power from power power shaft 1 simultaneously through first clutch 2 with
Second clutch 4 passes to front-seat planet carrier 6 and front and rear row sun gear 8, more premenstrual rows of planetary gear 7 pass to front and rear row gear ring 9,
Power output shaft 15 exports power.Calculate according to movement relation formula, 3 gear gear ratio i3=1.
4 gears: first clutch 2, second brake 5 work.Power from power power shaft 1 passes to front row through first clutch 2
Planet carrier 6, then front and rear row gear ring 9 passed to by premenstrual rows of planetary gear 7, power output shaft 15 exports power.According to movement relation
Formula calculates, 4 gear gear ratio i4=α/(1+ α).
Reverse gear [R gear]: the first brake 3, second clutch 4 work.Power passes through power input shaft 1, second clutch 4
To front and rear row sun gear 8, then front and rear row gear ring 9 passed to by premenstrual rows of planetary gear 7, power output shaft 15 exports power.According to
Movement relation formula calculates, back gear ratio iR=-α.
The foregoing is only presently preferred embodiments of the present invention, not in order to limit the present invention, all the spirit and principles in the present invention it
In, any modification, equivalent substitution and improvement etc. made, should be included within the scope of the present invention.
Claims (1)
1. single double pinions combination type four speed automatic transmission, it is characterised in that
Including the front-seat single-stage planetary being made up of front-seat planet carrier (6), front-seat planetary gear (7), front-seat sun gear and front-seat gear ring
Gear mechanism, and by heel row planet carrier (13), heel row first planet gear (11), after ranked second planetary gear (10), after
The heel row double pinions mechanism that row's sun gear and rear ring gear are constituted；Wherein, described front-seat sun gear and heel row sun gear close
Making and arrange sun gear (8) before and after sharing, described front-seat gear ring and rear ring gear make toothrow circle (9) before and after sharing；
First outfan of power input shaft (1) respectively with first clutch (2), second clutch (4) and the 3rd clutch
The input of device (14) connects, and the outfan of described first clutch (2) is connected with described front-seat planet carrier (6), described
The outfan of second clutch (4) is connected with described front and rear row sun gear (8), the outfan of described 3rd clutch (14)
It is connected with described heel row planet carrier (13)；
The input of power output shaft (15) is connected with described front and rear row gear ring (9)；
Wherein, it is provided with between described first clutch (2) and described front-seat planet carrier (6) for described front-seat planet carrier
(6) the first brake (3) braked；It is provided with use between described second clutch (4) and described front and rear row sun gear (8)
In the second brake (5) that described front and rear row sun gear (8) is braked；Described 3rd clutch (14) and described rear rows of planetary
The 3rd brake (12) for described heel row planet carrier (13) is braked it is provided with between frame (13).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610394749.8A CN105840749B (en) | 2016-05-29 | 2016-05-29 | A kind of single speed automatic transmission of double pinions combined type four |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610394749.8A CN105840749B (en) | 2016-05-29 | 2016-05-29 | A kind of single speed automatic transmission of double pinions combined type four |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105840749A true CN105840749A (en) | 2016-08-10 |
| CN105840749B CN105840749B (en) | 2018-01-02 |
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ID=56575516
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610394749.8A Active CN105840749B (en) | 2016-05-29 | 2016-05-29 | A kind of single speed automatic transmission of double pinions combined type four |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN105840749B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113474578A (en) * | 2019-03-12 | 2021-10-01 | 西格玛动力总成股份有限公司 | Transmission assembly and method of using the same |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5046999A (en) * | 1990-10-05 | 1991-09-10 | General Motors Corporation | 5-speed, compound, epicyclic transmission having a pair of planetary gear sets |
| JP2855786B2 (en) * | 1990-05-14 | 1999-02-10 | 日産自動車株式会社 | Planetary gear type multi-stage transmission |
| CN202937743U (en) * | 2012-11-20 | 2013-05-15 | 无锡商业职业技术学院 | Automatic gearbox of four-gear planetary gear |
| CN103154569A (en) * | 2010-10-20 | 2013-06-12 | 腓特烈斯港齿轮工厂股份公司 | Power-shiftable transmission |
| JP2013181585A (en) * | 2012-02-29 | 2013-09-12 | Aisin Aw Co Ltd | Automatic transmission device |
| US8622863B2 (en) * | 2010-06-07 | 2014-01-07 | Honda Motor Co., Ltd | Driving apparatus for hybrid vehicle |
-
2016
- 2016-05-29 CN CN201610394749.8A patent/CN105840749B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2855786B2 (en) * | 1990-05-14 | 1999-02-10 | 日産自動車株式会社 | Planetary gear type multi-stage transmission |
| US5046999A (en) * | 1990-10-05 | 1991-09-10 | General Motors Corporation | 5-speed, compound, epicyclic transmission having a pair of planetary gear sets |
| US8622863B2 (en) * | 2010-06-07 | 2014-01-07 | Honda Motor Co., Ltd | Driving apparatus for hybrid vehicle |
| CN103154569A (en) * | 2010-10-20 | 2013-06-12 | 腓特烈斯港齿轮工厂股份公司 | Power-shiftable transmission |
| JP2013181585A (en) * | 2012-02-29 | 2013-09-12 | Aisin Aw Co Ltd | Automatic transmission device |
| CN202937743U (en) * | 2012-11-20 | 2013-05-15 | 无锡商业职业技术学院 | Automatic gearbox of four-gear planetary gear |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113474578A (en) * | 2019-03-12 | 2021-10-01 | 西格玛动力总成股份有限公司 | Transmission assembly and method of using the same |
Also Published As
| Publication number | Publication date |
|---|---|
| CN105840749B (en) | 2018-01-02 |
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Effective date of registration: 20191009 Address after: 314500, building 288, 2 Avenue, Indus street, Tongxiang, Zhejiang, Jiaxing Patentee after: Zhejiang harvest 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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Effective date of registration: 20191024 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 harvest Network Technology Co., Ltd. |
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Effective date of registration: 20201216 Address after: 273300 No.207, East Second floor, Administration Committee of Shandong Pingyi Economic Development Zone, west section of Jinhua Road, Pingyi Economic Development Zone, Linyi City, Shandong Province Patentee after: Pingyi Economic Development Zone Investment Development Co.,Ltd. Address before: No.1 xc1001-3, Nanmen Gongnong Road, Chongfu Town, Tongxiang City, Jiaxing City, Zhejiang Province Patentee before: JIAXING YUNSHIJIAO ELECTRONIC COMMERCE Co.,Ltd. |