CN101566217A - 6-speed automatic transmission and transmission system thereof - Google Patents
6-speed automatic transmission and transmission system thereof Download PDFInfo
- Publication number
- CN101566217A CN101566217A CNA2009101076401A CN200910107640A CN101566217A CN 101566217 A CN101566217 A CN 101566217A CN A2009101076401 A CNA2009101076401 A CN A2009101076401A CN 200910107640 A CN200910107640 A CN 200910107640A CN 101566217 A CN101566217 A CN 101566217A
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- clutch
- break
- speed automatic
- automatic transmission
- transmission
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 58
- 238000006243 chemical reaction Methods 0.000 description 3
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000000605 extraction Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
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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
- F16H3/62—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
Abstract
The invention discloses a 6-speed automatic transmission for automobile and a transmission system thereof. The first clutch and the second clutch of the transmission system are arranged on the back part of a casing; the first brake is located surrounding the first clutch and the second clutch; the second brake is a band brake, and is located surrounding a counteractive planetary gear train; the third brake is located surrounding an output planetary gear train; a unidirectional clutch is located surrounding the counteractive planetary gear train and between the second brake and the third brake. Because the second brake and the third brake are respectively located surrounding the counteractive planetary gear train and the output planetary gear train, and the second brake is a band brake, the 6-speed automatic transmission of the transmission system using the technical scheme according to the invention shortens the power transmission line, reduces the power loss, saves axial arrangement spacing of the gear shifting component, and effectively reduces the axial dimension of the 6-speed automatic transmission.
Description
Technical field
The invention belongs to automobile technical field, particularly automatic transmission for vehicles relates in particular to a kind of transmission system of 6-speed automatic transmission, and the 6-speed automatic transmission that comprises this transmission system.
Background technique
The gear of automobile-used automatic transmission case is made up of a plurality of planetary gear train.Gear receives rotating speed and the moment of torsion that passes over from fluid torque converter, and sends output shaft after the conversion to.The shelves number of speed changer is many more, and then its speed ratio just can design to such an extent that unreasonablely think that vehicle also just can have better fuel economy and cornering ability.Just because of this, people are also studying the automatic transmission for vehicles of more grades of numbers always.
As everyone knows, in automatic transmission for vehicles, conversion between gear cooperates realization, the gear that a part is made up of a plurality of planetary gear train, the gearshift parts that another part is made up of each clutch, break and single clutch and servo-system thereof by two-part structure.Because clutch and break all belong to friction element, along with increasing of friction element, the efficient of being brought by frictional loss reduces also unavoidable.Therefore, people are studying always that power loss is littler, more compact structure, simple, speed changer easy to assembly.
Summary of the invention
The objective of the invention is at the bigger problem of the power loss of 6-speed automatic transmission in the prior art,, make that the power loss of 6-speed automatic transmission is littler by the optimal design transmission system.
For achieving the above object, the present invention adopts following technological scheme:
The transmission system of 6-speed automatic transmission, comprise: power input shaft, planet row, housing, gearshift parts and one-level deceleration system, described power input shaft, planet row, gearshift parts and one-level deceleration system all are arranged in the described housing, power input shaft is connected with planet row power by the gearshift parts, and planet row's output terminal is connected with one-level deceleration system power; Described gearshift parts comprise first clutch, second clutch, overrunning clutch, first break, second break and the 3rd break; Line of input star wheel series, output planetary train and retroaction planetary gear system are drawn together in described planet package; Described first clutch and second clutch are arranged in the housing rear portion; Described first break is positioned at the periphery of first clutch and second clutch; Described second break is a band brake, and is positioned at the retroaction planetary gear system periphery; Described the 3rd break is positioned at the periphery of output planetary train; Described overrunning clutch is positioned at the retroaction planetary gear system periphery, and between second break and the 3rd break.
Technological scheme of the present invention is with respect to the beneficial effect of prior art:
Because second break and the 3rd break lay respectively at the periphery of retroaction planetary gear system and output planetary train, and second break adopted band brake, thereby shortened power transmission line, reduced kinetic equation loss, and saved the gearshift parts in axial arrangement space, effectively shortened the axial dimension of 6-speed automatic transmission.
Description of drawings
Fig. 1 is the principle schematic of the specific embodiment of the invention.
Fig. 2 is the structural representation that dissects of the specific embodiment of the invention.
Embodiment
The 6-speed automatic transmission that provides a kind of power loss littler is provided in the present invention.According to the 6-speed automatic transmission of this embodiment, its transmission system comprises as depicted in figs. 1 and 2: power input shaft IP, planet row, housing H, central authorities support CS, gearshift parts, and the one-level deceleration system.
Described planet row is the gear of 6-speed automatic transmission, comprises three planetary gear train (being represented by three frame of broken lines among Fig. 1), is respectively line of input star wheel series IPG, output planetary train OPG and retroaction planetary gear system RPG.Retroaction planetary gear system RPG comprises: the first sun gear S1, the first planet wheel P1, the first planet carrier PC1 and the first gear ring R1.Line of input star wheel series IPG comprises: the second sun gear S2, the second planet wheel P2, the second planet carrier PC2 and the second gear ring R2.Output planetary train OPG comprises: the 3rd sun gear S3, the third line star-wheel P3, the third line star frame PC3 and the 3rd gear ring R3.Described gearshift parts comprise: three clutches (being respectively first clutch C1, second clutch C2 and overrunning clutch OWC) and three breaks (being respectively the first break B1, the second break B2 and the 3rd break B3).Described one-level deceleration system comprises: one-level deceleration driving gear G1, Parking wheel PG, biserial roller ball bearing 15, bearing supporting body BS, one-level deceleration driven gear G2 and pto OP etc.
Described power input shaft IP, planet row and gearshift parts etc. all are arranged in the housing H.Power input shaft IP passes planet row and coaxial with planet row.Power input shaft IP is connected the turbine of its front end fluid torque converter with the sun gear of line of input star wheel series IPG (the second sun gear S2) power, and by the controllable switching of gearshift parts, and be connected with other appropriate section power of planet row, and output planetary train OPG is connected with one-level deceleration system power.So, by the power of power input shaft IP input, under the controllable switching of gearshift parts, carry out after the deceleration of conversion and one-level deceleration system through corresponding planetary gear train, finally the pto OP by the one-level deceleration system exports.
The interior hub of described first clutch C1 and the outer hub of second clutch C2 are structure as a whole, and fix by spline with coupling shaft.Coupling shaft then is connected with power input shaft IP by spline, and by the location of the snap ring on the power input shaft IP.The interior hub of the outer hub of first clutch C1 and the first break B1 also is an one, and fixedlys connected with the sun gear (the first sun gear S1) of retroaction planetary gear system RPG.The interior hub of second clutch C2 is connected by spline with the planet carrier of retroaction planetary gear system RPG (the first planet carrier PC1).
First clutch C1 and second clutch C2 axially are arranged side by side in housing H rear portion with the form of hub assembly, and are positioned at planet row's a end.First clutch C1 and second clutch C2 be alignment substantially radially, and the axial of its friction plate group all located by the web of hub.Power input shaft IP also passes through the gear ring (the second gear ring R2) that second clutch C2 connects line of input star wheel series IPG by the sun gear (the first sun gear S1) that first clutch C1 connects retroaction planetary gear system RPG.The servo-system of first clutch C1 and second clutch C2 is arranged in the inside groove of the hub below it; And the balance oil pocket of first clutch C1 and second clutch C2 is communicated with from the oil duct of hub median ventral plate, by the oil duct oil extraction of hub median ventral plate.
Described central authorities support CS fixedlys connected with housing H inwall by forms such as key, spline or pins, and it is axially fixed by an oblique snap ring with overrunning clutch OWC, thereby assembles simple and convenient.The friction plate group of described the 3rd break B3 and servo-system all are positioned at central authorities and support CS, and its friction plate group supports CS by central authorities respectively the 3rd sun gear S3 is connected on the housing H.The second break B2 and the 3rd break B3 lay respectively at the periphery of retroaction planetary gear system RPG and output planetary train OPG, and key is that the second break B2 has adopted band brake, thereby shortened power transmission line, reduced kinetic equation loss, and saved the gearshift parts in axial arrangement space, effectively shortened the axial dimension of 6-speed automatic transmission.
The described first break B1 is positioned at first clutch C1 periphery, and with the shared hub of first clutch C1.The friction plate group of the first break B1 is positioned at the periphery of first clutch C1 and second clutch C2, and its servo-system is positioned at the wall of housing H afterbody.
The braking hub of the described second break B2 and the inner ring of overrunning clutch OWC are one, and it is also fixedlyed connected with the first planet carrier PC1 of retroaction planetary gear system RPG.Overrunning clutch OWC is positioned at the periphery of retroaction planetary gear system, and between the second break B2 and the 3rd break B3, make the space between the second break B2 and the 3rd break B3 be fully utilized, reduce arrangement space, made the axial dimension of 6-speed automatic transmission can become littler.And overrunning clutch OWC also is connected with retroaction planetary gear system RPG, and like this, overrunning clutch OWC just brakes retroaction planetary gear system RPG jointly with the second break B2.In the time of automatic one grade, the second break B2 and overrunning clutch OWC work, power is input to line of input star wheel series IPG and retroaction planetary gear system RPG respectively from power input shaft IP.Because the quick response of overrunning clutch OWC, the planet carrier of retroaction planetary gear system RPG (the first planet carrier PC1) is fixed, transmission of power is to the gear ring (the 3rd gear ring R3) of output planetary train OPG, because the 3rd sun gear S3 is fixed, power is exported by the third line star frame PC3.Therefore, the second break B2 need not work in the time of one grade, makes that the control of each clutch becomes simply, responds rapidly, thereby make that one grade self shifter response time is shorter; Also make the frequency of usage of the second break B2 reduce simultaneously, thus the life-span of having improved 6-speed automatic transmission.
The important inventive point of another one of the present invention is the one-level deceleration system.Described one-level deceleration system comprises: one-level deceleration driving gear G1, biserial roller ball bearing 15, bearing supporting body BS, one-level deceleration driven gear G2, Parking wheel GP, pto OP and connecting plate 5.One-level deceleration driving gear G1 is arranged in series connection planet row front, and connecting plate 5 connects by spline with the third line star frame PC3, and one-level deceleration driving gear G1 and connecting plate 5 connect by spline.One-level deceleration driven gear G2 and pto OP connect by spline, and one-level deceleration driven gear G2 and Parking wheel GP is one.One-level deceleration system driving gear G1 supports by the angular contact ball bearing (biserial roller ball bearing 15) of the back-to-back installation of biserial, and bearing outer ring is installed in one-level deceleration system driving gear G1 inside, and bearing outer ring is by slope snap ring location.Specialization is that the bearing supporting body BS among the present invention is special the setting, and it is by being bolted on the housing H.Biserial roller ball bearing 15 is arranged on the bearing supporting body BS, and G1 is coaxial with the one-level deceleration driving gear.Because bearing supporting body BS is arranged in the oil pump back, separates with oil pump, has reduced the volume of oil pump.
Above content be in conjunction with concrete preferred implementation to further describing that the present invention did, can not assert that concrete enforcement of the present invention is confined to these explanations.For the general technical staff of the technical field of the invention, without departing from the inventive concept of the premise, can also make some simple deduction or replace, all should be considered as belonging to protection scope of the present invention.
Claims (10)
1, the transmission system of 6-speed automatic transmission, comprise: power input shaft, planet row, housing, gearshift parts and one-level deceleration system, described power input shaft, planet row, gearshift parts and one-level deceleration system all are arranged in the described housing, power input shaft is connected with planet row power by the gearshift parts, and planet row's output terminal is connected with one-level deceleration system power; Described gearshift parts comprise first clutch, second clutch, overrunning clutch, first break, second break and the 3rd break; Line of input star wheel series, output planetary train and retroaction planetary gear system are drawn together in described planet package; It is characterized in that described first clutch and second clutch are arranged in the housing rear portion; Described first break is positioned at the periphery of first clutch and second clutch; Described second break is a band brake, and is positioned at the retroaction planetary gear system periphery; Described the 3rd break is positioned at the periphery of output planetary train; Described overrunning clutch is positioned at the retroaction planetary gear system periphery, and between second break and the 3rd break.
2, the transmission system of 6-speed automatic transmission as claimed in claim 1 is characterized in that, first clutch and second clutch axially are arranged side by side with the form of hub assembly.
3, the transmission system of 6-speed automatic transmission as claimed in claim 2 is characterized in that, the shared hub of described first break and first clutch; The friction plate group of first break is positioned at the periphery of first clutch and second clutch.
4, the transmission system of 6-speed automatic transmission as claimed in claim 3 is characterized in that, the servo-system of described first break is positioned at the wall of housing afterbody.
5, the transmission system of 6-speed automatic transmission as claimed in claim 1, it is characterized in that, comprise that also central authorities support, the friction plate group of described the 3rd break and servo-system all are positioned at central authorities and support, and the friction plate group is connected on the housing by the sun gear that central authorities support the output planetary train.
6, the transmission system of 6-speed automatic transmission as claimed in claim 5 is characterized in that, described central authorities support by key, spline or pin and housing affixed; What central authorities supported is axially fixed by an oblique snap ring with overrunning clutch.
7, the transmission system of 6-speed automatic transmission as claimed in claim 1 is characterized in that, the servo-system of described first clutch and second clutch is arranged in the inside groove of the hub below it; The balance oil pocket of described first clutch and second clutch is communicated with the oil duct of hub median ventral plate.
8, the transmission system of 6-speed automatic transmission as claimed in claim 1 is characterized in that, the braking hub of second break and the inner ring of overrunning clutch are one, and also fixedly connected with the planet carrier of retroaction planetary gear system.
9, the transmission system of 6-speed automatic transmission as claimed in claim 1 is characterized in that, described one-level deceleration system comprises: one-level deceleration driving gear, one-level deceleration driven gear, Parking wheel, output shaft, bearing, connecting plate and bearing supporting body; Described one-level deceleration driving gear is positioned at planet row front, is connected by the planet carrier of connecting plate with the output planetary train, and by described bearings; One-level deceleration driven gear and Parking wheel are structure as a whole, and are installed in together on the pto; Described bearing is fixedlyed connected with housing by bearing supporting body.
10,6-speed automatic transmission comprises transmission system, it is characterized in that, described transmission system is the transmission system of any described 6-speed automatic transmission in the claim 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNA2009101076401A CN101566217A (en) | 2009-06-03 | 2009-06-03 | 6-speed automatic transmission and transmission system thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNA2009101076401A CN101566217A (en) | 2009-06-03 | 2009-06-03 | 6-speed automatic transmission and transmission system thereof |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101566217A true CN101566217A (en) | 2009-10-28 |
Family
ID=41282534
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2009101076401A Pending CN101566217A (en) | 2009-06-03 | 2009-06-03 | 6-speed automatic transmission and transmission system thereof |
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| Country | Link |
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| CN (1) | CN101566217A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2011044818A1 (en) * | 2009-10-14 | 2011-04-21 | 奇瑞汽车股份有限公司 | Power transmission system of six-speed automatic transmission |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0478352A (en) * | 1990-07-19 | 1992-03-12 | Kayseven Co Ltd | Automatic transmission gear |
| CN1294992A (en) * | 1999-11-09 | 2001-05-16 | 现代自动车株式会社 | Automatic variable-speed drive system |
| US20040014549A1 (en) * | 2002-07-16 | 2004-01-22 | Jatco Ltd | Speed change gear for automatic transmission |
| CN1661262A (en) * | 2004-02-26 | 2005-08-31 | 现代自动车株式会社 | Six-speed powertrain of an automatic transmission for a vehicle |
| CN1667296A (en) * | 2004-03-09 | 2005-09-14 | 现代自动车株式会社 | Power train for 7-speed automatic transmission for vehicles |
| US6960150B2 (en) * | 2003-10-24 | 2005-11-01 | General Motors Corporation | Power transmission for a vehicle |
| CN101149092A (en) * | 2006-09-20 | 2008-03-26 | 马自达汽车股份有限公司 | Automatic transmission |
-
2009
- 2009-06-03 CN CNA2009101076401A patent/CN101566217A/en active Pending
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0478352A (en) * | 1990-07-19 | 1992-03-12 | Kayseven Co Ltd | Automatic transmission gear |
| CN1294992A (en) * | 1999-11-09 | 2001-05-16 | 现代自动车株式会社 | Automatic variable-speed drive system |
| US20040014549A1 (en) * | 2002-07-16 | 2004-01-22 | Jatco Ltd | Speed change gear for automatic transmission |
| US6960150B2 (en) * | 2003-10-24 | 2005-11-01 | General Motors Corporation | Power transmission for a vehicle |
| CN1661262A (en) * | 2004-02-26 | 2005-08-31 | 现代自动车株式会社 | Six-speed powertrain of an automatic transmission for a vehicle |
| CN1667296A (en) * | 2004-03-09 | 2005-09-14 | 现代自动车株式会社 | Power train for 7-speed automatic transmission for vehicles |
| CN101149092A (en) * | 2006-09-20 | 2008-03-26 | 马自达汽车股份有限公司 | Automatic transmission |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2011044818A1 (en) * | 2009-10-14 | 2011-04-21 | 奇瑞汽车股份有限公司 | Power transmission system of six-speed automatic transmission |
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| 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: 20091028 |