CN101705980A - Power transmission system of automatic transmission - Google Patents
Power transmission system of automatic transmission Download PDFInfo
- Publication number
- CN101705980A CN101705980A CN200910226348A CN200910226348A CN101705980A CN 101705980 A CN101705980 A CN 101705980A CN 200910226348 A CN200910226348 A CN 200910226348A CN 200910226348 A CN200910226348 A CN 200910226348A CN 101705980 A CN101705980 A CN 101705980A
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- CN
- China
- Prior art keywords
- clutch
- transmission system
- power transmission
- automatic gearbox
- mixing
- 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.)
- Pending
Links
- 230000005540 biological transmission Effects 0.000 title claims abstract description 33
- 230000009977 dual effect Effects 0.000 abstract 3
- 238000006243 chemical reaction Methods 0.000 description 3
- 238000000034 method Methods 0.000 description 2
- 230000008602 contraction Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
Images
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
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
- F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX
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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
- F16H2200/2002—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
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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
- F16H2200/202—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set
- F16H2200/2023—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set using a Ravigneaux set with 4 connections
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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
- F16H2200/2043—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with five engaging means
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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
- F16H2200/2079—Transmissions using gears with orbital motion using freewheel type mechanisms, e.g. freewheel clutches
- F16H2200/2082—Transmissions using gears with orbital motion using freewheel type mechanisms, e.g. freewheel clutches one freewheel mechanisms
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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
- F16H2200/2097—Transmissions using gears with orbital motion comprising an orbital gear set member permanently connected to the housing, e.g. a sun wheel permanently connected to the housing
Abstract
The invention relates to a power transmission system of an automatic transmission, which comprises a power input shaft, a power output gear, an output deceleration support, a simple planetary gear, a dual planetary gear and corresponding shifting components, wherein clutches C1 and C3 in the shifting components serve as the shifting components and are directly arranged between the simple planetary gear and the dual planetary gear; and the clutches C1 and C3 in the shifting components switch on and switch off the rotating speed and torque transmitted from the simple planetary gear to the dual planetary gear to achieve the aim of shifting.
Description
Technical field
The present invention relates to a kind of power transmission system of automatic gearbox, be specifically related to a kind of automatic transmission 6 shift power drive systems system.
Background technique
The gear of automatic transmission case is made up of a plurality of planetary gear set, receives from fluid torque converter and receives the rotating speed and the moment of coming, and torque conversion is become the multistage output shaft that sends to.The shelves number of the conversion shelves of realizing when speed changer is many more, and the speed ratio of speed changer just can design unreasonablely thinks that vehicle also just can have better fuel economy and better cornering ability.Just because of this, people are also studying the automatic transmission that realizes more grades of numbers always.
As everyone knows, in automatic transmission, conversion between gear is to be realized by the cooperation of two-part structure, a part is that gear is made up of a plurality of planetary gear set, another part is the friction element that transmits, changes rotating speed and moment of torsion, forms as each clutch, break and single clutch and servo-system thereof.Along with the continuous developments of people for six grades and more gear automatic transmission, the volume of gearbox constantly increases, and this is for front deck space nervous horizontal forerunner's automatic transmission case especially more, and it is particularly evident that this problem shows.Along with the increasing of friction element, the efficient of being brought by frictional loss reduces also unavoidable in addition.Therefore, it is compacter, simple in structure that people are studying assembling always, the speed changer that power loss is littler.
When designing automatic transmission case usually, be not the brand-new planetary gear set of kind of design, seek how clutch, break to be arranged in the combination of single-stage/twin-stage small planetary gear group, thereby make power loss minimum, structure more compact but design.
In sum, have following technical problem in the prior art: (1) gearbox volume constantly increases; (2) friction element brings efficient to reduce.
Summary of the invention
The object of the present invention is to provide a kind of vehicle automatic transmission, clutch C1 in its gearshift parts and C3 directly are positioned between simple planet row and the double planet wheel rows of mixing (La Weiniaoshi) as the gearshift parts, by optimizing the position of each clutch, break, the different types that reaches break makes that the structure of speed changer is more compact, simple, and power loss is littler.
Exemplary six powertrains of this vehicular automatic transmission comprise: comprise a power input shaft, a power output gear, an output is slowed down and is supported, a simple planet row, a double planet wheel rows of mixing (La Weiniaoshi) and corresponding gearshift parts, clutch C1 in the described gearshift parts and C3 reach the purpose of gear switch by engaging and cut off by the rotating speed and the moment of torsion of simple planet row biography toward double planet wheel rows of mixing (La Weiniaoshi).
Clutch C1 in the described gearshift parts and C3 directly are positioned between simple planet row and the double planet wheel rows of mixing (La Weiniaoshi) as the gearshift parts, have shortened the power path of propagation, have improved transmission efficiency.
The friction element layout straggly of clutch C1 in the described gearshift parts and C3, wherein the friction element of C1 is located immediately at simple planet row's outside, and the internal spline of its friction element links to each other with the hub that simple planet row's planet carrier forms; The friction element of C3 is positioned at the left front of C1 friction element, reserves enough spaces for using multi-plate brake B1, and the hub that a connecting element that stretches out on the internal spline of its friction element and the simple planet rows of planetary frame forms links to each other.
Clutch C3 pressure oil duct in the described gearshift parts directly slows down to support by output from valve body and enters its servo-system;
Break B1 in the described gearshift parts selects multi-plate brake for use, is located immediately at the periphery of clutch C3 and C1 servo-system, reasonably is arranged between C3 friction plate group and the output deceleration support, makes the structure of FCL simple more, reasonable compact.
Concrete technological scheme is as follows:
A kind of power transmission system of automatic gearbox, comprise conventional power input shaft, power output gear and output deceleration support, also comprise a simple planet row, a double planet wheel rows of mixing and corresponding gearshift parts, this shift component is set directly between simple planet row and the double planet wheel rows of mixing, and simple planet row is connected by the clutch in these gearshift parts with double planet wheel rows of mixing.
Described gearshift parts comprise clutch C1 and clutch C3, and this clutch C1 and clutch C3 are arranged between simple planet row and the double planet wheel rows of mixing, and simple planet row is connected with three-clutch C3 by this first clutch C1 respectively with double planet wheel rows of mixing.
Described power input shaft directly links to each other with simple planet row, and power input shaft is connected with described double planet wheel rows of mixing with a second clutch by one.
The servo-system of described clutch C1 and clutch C3 axially is arranged side by side, and is positioned at simple planet row's rear portion, is connected with big small sun gear in the double planet wheel rows of mixing respectively.
Described clutch C1 and C3 are used to engage/cut off rotating speed and the moment of torsion that is passed past double planet wheel rows of mixing by simple planet row, thus the switching gear.
Described gearshift parts also comprise break B1, are arranged on the periphery of clutch C3 and clutch C1 servo-system, slow down between the support in clutch C3 friction plate group and output.
Described break B1 is a multi-plate brake.
The friction element of clutch C3 is arranged on the periphery of the friction element of clutch C1.
The friction element of the friction element of clutch C3 and clutch C1 layout straggly, multi-plate brake B1 replenishes and is arranged on the space of staggering.
Described break B1 is a multidisc, and its friction element is connected by spline with the drum of clutch C3.
The friction element of clutch C1 is positioned at the exclusive portion of simple planet, and the internal spline of its friction element links to each other with the hub that simple planet row's planet carrier forms.
The hub that a connecting element that stretches out on the internal spline of the friction element of clutch C3 and the simple planet rows of planetary frame forms links to each other.
Described output is slowed down and is supported for described power output driving gear and provides support, and the described output web that supports that slows down is provided with oil duct, and described oil duct provides pressure oil for clutch C3 and break B1.
The pressure oil duct of described clutch C3 is arranged in its clutch drum, and the oil duct that described pressure oil slow down to support by output directly arrives in the oil duct on the drum of clutch C3.
Compare with present prior art, C1 of the present invention and C3 clutch are arranged between deceleration single planetary row and the double planet wheel rows of mixing (La Weiniaoshi), and the power transmission route is short, and power loss is littler, and overall structure is compact more.
Description of drawings
Fig. 1 is the structural representation of one embodiment of the invention
Fig. 2 is the structure sectional view of preferred embodiment of the present invention
Among the figure:
1:S1 single planetary row sun gear
2:PG1 single planetary row planet carrier
3:P1 single planetary row planet wheel
The 4:C3 three-clutch
The 5:C1 first clutch
6:B1 multidisc first break
7:R1 single planetary row gear ring
The 8:F overrunning clutch
9:B2 multidisc second break
The 10:C2 second clutch
Second of 11:SHAFT2
12,16:PG2 double planet wheel rows of mixing planet carrier
The big sun gear of 13:S2 double planet wheel rows of mixing
14:S3 double planet wheel rows of mixing small sun gear
15:P2 double planet wheel rows of mixing planet wheel
First of 17:SHAFT1
The 3rd of 18:SHAFT3
The 19:DIFF differential mechanism
The 20:C3 clutch hub
21:B1 brake pressure oil duct
22:C3 clutch pressure oil duct
23:CS output is slowed down and is supported
A: input
B, C: output
Embodiment
Describe the present invention with reference to the accompanying drawings below, it is a kind of preferred embodiment in the numerous embodiments of the present invention.
As depicted in figs. 1 and 2, this embodiment comprises a power input shaft, a power output driving gear, double-row conical bearing and output deceleration supporting frame thereof, a simple planet row, a double planet wheel rows of mixing (La Weiniaoshi), two multi-plate brakes, three clutches, an overrunning clutch, housing, a deceleration jack shaft and a differential mechanism.Wherein power input shaft directly links to each other with simple planet row, and is connected with double planet wheel rows of mixing with second clutch by second; Simple planet row links to each other with three-clutch by first clutch respectively with double planet wheel rows of mixing, and first clutch and three-clutch are arranged between simple planet row and the double planet wheel rows of mixing (La Weiniaoshi), other concrete connection is seen Fig. 1 for details, and the connection of related domain routine is not given unnecessary details one by one.
As shown in Figure 2, it is that power output driving gear provides support that CS slow down is supported in output, and promising clutch C3 and break B1 provide the oil duct of pressure oil on its web simultaneously;
As can be seen from the figure, the servo-system of clutch C1 and C3 axially is arranged side by side, and is positioned at simple planet row's rear portion, is connected with big small sun gear in the double planet wheel rows of mixing (La Weiniaoshi) respectively, makes the path contraction of transmission of power, the power loss minimizing.
The friction element of clutch C1 is positioned at the periphery of simple planet row PG1, and a connecting element C3 clutch hub that stretches out on the friction element of clutch C3 and the single planetary row planet carrier of conforming to the principle of simplicity links to each other, and is positioned at the periphery of clutch friction element C1;
The pressure oil duct of clutch C3 is arranged in its clutch drum, and the oil duct that pressure oil slow down to be supported by output by valve body directly arrives in the oil duct on the clutch drum;
Many formulas break B1 is located immediately at the periphery of clutch C3 and C1 servo-system, reasonably is arranged between C3 friction plate group and the output deceleration support.
The reasonable Arrangement of above shifting element makes the structure of FCL simple more, reasonable compact.
In conjunction with the accompanying drawings the present invention has been carried out exemplary description above; obviously specific implementation of the present invention is not subjected to the restriction of aforesaid way; as long as the various improvement of having adopted method design of the present invention and technological scheme to carry out; or directly apply to other occasion without improvement, all within protection scope of the present invention.
Claims (14)
1. power transmission system of automatic gearbox, comprise conventional power input shaft, power output gear and output deceleration support, it is characterized in that, also comprise a simple planet row, a double planet wheel rows of mixing and corresponding gearshift parts, this shift component is set directly between simple planet row and the double planet wheel rows of mixing, and simple planet row is connected by the clutch in these gearshift parts with double planet wheel rows of mixing.
2. power transmission system of automatic gearbox as claimed in claim 1, it is characterized in that, described gearshift parts comprise clutch C1 and clutch C3, this clutch C1 and clutch C3 are arranged between simple planet row and the double planet wheel rows of mixing, and simple planet row is connected with three-clutch C3 by this first clutch C1 respectively with double planet wheel rows of mixing.
3. power transmission system of automatic gearbox as claimed in claim 1 or 2 is characterized in that, described power input shaft directly links to each other with simple planet row, and power input shaft is connected with described double planet wheel rows of mixing with a second clutch by one.
4. power transmission system of automatic gearbox as claimed in claim 2 is characterized in that, the servo-system of described clutch C1 and clutch C3 axially is arranged side by side, and is positioned at simple planet row's rear portion, is connected with big small sun gear in the double planet wheel rows of mixing respectively.
5. power transmission system of automatic gearbox as claimed in claim 2 is characterized in that, described clutch C1 and C3 are used to engage/cut off rotating speed and the moment of torsion that is passed past double planet wheel rows of mixing by simple planet row, thus the switching gear.
6. as claim 1,2,4, each described power transmission system of automatic gearbox is characterized in that in 5, and described gearshift parts also comprise break B1, be arranged on the periphery of clutch C3 and clutch C1 servo-system, slow down between the support in clutch C3 friction plate group and output.
7. power transmission system of automatic gearbox as claimed in claim 6 is characterized in that, described break B1 is a multi-plate brake.
8. power transmission system of automatic gearbox as claimed in claim 6 is characterized in that the friction element of clutch C3 is arranged on the periphery of the friction element of clutch C1.
9. power transmission system of automatic gearbox as claimed in claim 6 is characterized in that, the friction element layout straggly of the friction element of clutch C3 and clutch C1, and multi-plate brake B1 replenishes and is arranged on the space of staggering.
10. power transmission system of automatic gearbox as claimed in claim 6 is characterized in that, described break B1 is a multidisc, and its friction element is connected by spline with the drum of clutch C3.
11. as claim 2,4,5, each described power transmission system of automatic gearbox among the 7-10, it is characterized in that the friction element of clutch C1 is positioned at the exclusive portion of simple planet, the internal spline of its friction element links to each other with the hub that simple planet row's planet carrier forms.
12. power transmission system of automatic gearbox as claimed in claim 11 is characterized in that, the hub that a connecting element that stretches out on the internal spline of the friction element of clutch C3 and the simple planet rows of planetary frame forms links to each other.
13. as claim 7-10, each described power transmission system of automatic gearbox in 12, it is characterized in that, described output deceleration is supported for described power output driving gear and provides support, the described output web that supports that slows down is provided with oil duct, and described oil duct provides pressure oil for clutch C3 and break B1.
14. power transmission system of automatic gearbox as claimed in claim 13, it is characterized in that, the pressure oil duct of described clutch C3 is arranged in its clutch drum, and the oil duct that described pressure oil slow down to support by output directly arrives in the oil duct on the drum of clutch C3.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910226348A CN101705980A (en) | 2009-07-06 | 2009-11-17 | Power transmission system of automatic transmission |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910144045.5 | 2009-07-06 | ||
| CN200910226348A CN101705980A (en) | 2009-07-06 | 2009-11-17 | Power transmission system of automatic transmission |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101705980A true CN101705980A (en) | 2010-05-12 |
Family
ID=42376224
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200910226348A Pending CN101705980A (en) | 2009-07-06 | 2009-11-17 | Power transmission system of automatic transmission |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN101705980A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102562968A (en) * | 2012-02-20 | 2012-07-11 | 天津同步动力科技有限公司 | Automatic transmission driving device for unpowered interrupted gear-shifting and gear-shifting control method thereof |
| CN102720810A (en) * | 2011-03-30 | 2012-10-10 | 比亚迪股份有限公司 | Automatic transmission, vehicle containing same and gearshift method thereof |
-
2009
- 2009-11-17 CN CN200910226348A patent/CN101705980A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102720810A (en) * | 2011-03-30 | 2012-10-10 | 比亚迪股份有限公司 | Automatic transmission, vehicle containing same and gearshift method thereof |
| CN102720810B (en) * | 2011-03-30 | 2016-03-02 | 比亚迪股份有限公司 | Automatic transmission, the vehicle comprising this automatic transmission and process for gear thereof |
| CN102562968A (en) * | 2012-02-20 | 2012-07-11 | 天津同步动力科技有限公司 | Automatic transmission driving device for unpowered interrupted gear-shifting and gear-shifting control method thereof |
| CN102562968B (en) * | 2012-02-20 | 2014-04-23 | 天津同步动力科技有限公司 | Automatic transmission driving device for unpowered interrupted gear-shifting and gear-shifting control method thereof |
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| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C02 | Deemed withdrawal of patent application after publication (patent law 2001) | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20100512 |