CN101566216A - 6-speed automatic transmission for automobile and transmission system thereof - Google Patents
6-speed automatic transmission for automobile and transmission system thereof Download PDFInfo
- Publication number
- CN101566216A CN101566216A CNA2009101076399A CN200910107639A CN101566216A CN 101566216 A CN101566216 A CN 101566216A CN A2009101076399 A CNA2009101076399 A CN A2009101076399A CN 200910107639 A CN200910107639 A CN 200910107639A CN 101566216 A CN101566216 A CN 101566216A
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- clutch
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- automobile
- automatic transmission
- speed automatic
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 66
- 238000009434 installation Methods 0.000 claims description 3
- 230000008878 coupling Effects 0.000 description 4
- 238000010168 coupling process Methods 0.000 description 4
- 238000005859 coupling reaction Methods 0.000 description 4
- 238000006243 chemical reaction Methods 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000011160 research Methods 0.000 description 1
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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
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
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Abstract
The invention discloses a 6-speed automatic transmission for automobile and transmission system thereof. The transmission system includes a casing, which is equipped with a power input shaft, a planetary gear, a gear shifting component, a one-level deceleration system and a bearing supporting body; the power input shaft and the planetary gear is connected with the planetary gear in a power connection by the gear shifting component, the planetary gear is connected with the one-level deceleration system in a power connection; the one-level deceleration system includes: a one-level deceleration main drive gear and a bearing; the casing includes a oil pump rear lid located in front of the casing; the one-level deceleration main drive gear supports on the bearing supporting body by the bearing; and the bearing supporting body is connected with the casing in a permanent connection by the oil pump rear lid. Because the one-level deceleration main drive gear supports on the oil pump rear lid by the bearing and the bearing supporting body, and the clutch is arranged in front of the planetary gear connected in series, and the brake is arranged surrounding the planetary gear, the 6-speed automatic transmission for automobile of the transmission system using the technical scheme according to the invention solves the problem of one-level deceleration main drive gear positioning and long axial dimension.
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 for automobile, and the 6-speed automatic transmission for automobile 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, and it 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.Along with the continuous researchs of people for six grades and more gear automatic transmission, the problem of bringing is that the volume of speed changer also constantly increases thereupon.For concerning the horizontal forerunner's formula automatic transmission at full stretch of front deck space, it is particularly evident that this problem shows.Therefore, people are studying always that axial dimension is littler, the automatic transmission for vehicles of more compact structure.
Summary of the invention
The objective of the invention is by optimal design, provides a kind of transmission system at the bigger problem of the axial dimension of 6-speed automatic transmission for automobile in the prior art, makes that the axial dimension of 6-speed automatic transmission for automobile is littler.
For achieving the above object, the present invention adopts following technological scheme:
6-speed automatic transmission for automobile comprises the transmission system of 6-speed automatic transmission for automobile.Described transmission system comprises: power input shaft, planet row, housing, gearshift parts, one-level deceleration system and bearing supporting body, and described power input shaft, planetary gear train, gearshift parts and one-level deceleration system are arranged in the housing; Power input shaft is connected with planet row power by the gearshift parts, and planet row be connected with one-level deceleration system power; Described one-level deceleration system comprises one-level deceleration driving gear and bearing, and described housing comprises the oil pump rear lid that is positioned at its front end; Described one-level deceleration driving gear by bearings on described bearing supporting body; Described bearing supporting body is fixedlyed connected with housing by oil pump rear lid.
In the optimized technical scheme, 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 power input shaft also connects the gear ring of line of input star wheel series by the sun gear of first clutch connection retroaction planetary gear system by second clutch; Described first clutch also is connected with housing by second break; Described second break is positioned at the first clutch periphery, with the shared hub of first clutch; Described first break is positioned at the periphery of output planetary train, and the sun gear of output planetary train is connected with housing by first break; The 3rd break is positioned at the periphery of retroaction planetary gear system, and the planet carrier of retroaction planetary gear system is connected with housing by the 3rd break; Described overrunning clutch is positioned at an end of the 3rd break, and is connected with the planet carrier of retroaction planetary gear system.
Technological scheme of the present invention is with respect to the beneficial effect of prior art:
Owing to the one-level deceleration driving gear is supported on the oil pump rear lid by bearing and bearing supporting body, has solved the location and the long problem of axial dimension of one-level deceleration driving gear effectively.Because clutch is arranged in series connection planet row front, and break is arranged in that planet is exclusive to be enclosed, thereby has further saved the gearshift parts in axial arrangement space, has effectively shortened the axial dimension of 6-speed automatic transmission for automobile.
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 for automobile that provides a kind of axial dimension littler is provided in the present invention.According to the 6-speed automatic transmission for automobile 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 for automobile, comprises three planetary gear train, is respectively line of input star wheel series IPG, output planetary train OPG and retroaction planetary gear system RPG.Line of input star wheel series IPG comprises: the first sun gear S1, the first planet wheel P1, the first planet carrier PC1 and the first gear ring R1.Output planetary train OPG comprises: the second sun gear S2, the second planet wheel P2, the second planet carrier PC2 and the second gear ring R2.Retroaction planetary gear system RPG 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 (angular contact ball bearings of two back-to-back installations) 100, bearing supporting body BS, one-level deceleration driven gear 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 S1 power of line of input star wheel series IPG, 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, after the corresponding planetary gear train of process carries out speed change, by pto OP, give the driving gear G1 of one-level deceleration system with transmission of power, finally pass to transmission output shaft.
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 power input shaft IP is by snap ring and coupling shaft axially locating.Coupling shaft and input shaft are by being positioned at the thrust-bearing location of both sides.The interior hub of the outer hub of first clutch C1 and the second break B2 also is an one, and fixedlys connected with the sun gear (the 3rd sun gear S3) 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 third line star frame PC3).
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 first gear ring R1) that second clutch C2 connects line of input star wheel series IPG by the sun gear (the 3rd sun gear S3) 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 fuel feeding 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 first break B1 and 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 second sun gear S2 and the third line star frame PC3 are connected on the housing H.The first break B1 and the 3rd break B3 lay respectively at the periphery of output planetary train OPG and retroaction planetary gear system RPG, thereby shortened power transmission line, and saved the gearshift parts in axial arrangement space, effectively shortened the axial dimension of 6-speed automatic transmission for automobile.
The described second break B2 is positioned at first clutch C1 periphery, and with the shared hub of first clutch C1.The friction plate group of the second break B2 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 described the 3rd break B3 and the inner ring of overrunning clutch OWC are one, and it is also fixedlyed connected with the third line star frame PC3 of retroaction planetary gear system PPG.Overrunning clutch OWC is positioned at the end of the 3rd break B3, 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 for automobile 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 3rd break B3.In the time of automatic one grade, the first break B1 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 third line star frame PC3) is fixed, transmission of power is to the gear ring (the second gear ring R2) of output planetary train OPG, because the second sun gear S2 is fixed, power is exported by the second planet carrier PC2.Therefore, the 3rd break B3 need not work in the time of one grade, makes that the control of clutch becomes simply, responds rapidly, thereby make that one grade self shifter response time is shorter; Also make the frequency of usage of the 3rd break B3 reduce simultaneously, thus the life-span of having improved 6-speed automatic transmission for automobile.
The 6-speed automatic transmission for automobile of this embodiment, because its clutch is arranged in series connection planet row front, and break is arranged in that planet is exclusive to be enclosed, thereby has saved the gearshift parts in axial arrangement space, has effectively shortened the axial dimension of 6-speed automatic transmission for automobile.
The important inventive point of another one of the present invention is, described pto OP is connected with one-level deceleration driving gear G1 power by the third line star frame PC3, preferably is connected by spline between the third line star frame PC3 and the one-level deceleration driving gear G1.Parking wheel PG is connected as a single entity by spline and one-level deceleration driving gear G1, and locatees by snap ring between one-level deceleration driving gear G1 and output planetary train OPG.One-level deceleration system driving gear G1 supports by the angular contact ball bearing 100 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.Another inventive point of one-level deceleration system is, be provided with a bearing supporting body BS especially, oil pump rear lid on bearing supporting body BS and the housing H is made one, and coaxial with one-level deceleration driving gear G1, and bearing supporting body BS is bolted on the housing H by oil pump rear lid.
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 for automobile comprises: power input shaft, planet row, housing, gearshift parts and one-level deceleration system, and described power input shaft, planet row, gearshift parts and one-level deceleration system are arranged in the housing; Power input shaft is connected with planet row power by the gearshift parts, and planet row be connected with one-level deceleration system power; Described one-level deceleration system comprises one-level deceleration driving gear and bearing, and described housing comprises the oil pump rear lid that is positioned at its front end; It is characterized in that the transmission system of described 6-speed automatic transmission for automobile also comprises bearing supporting body; Described one-level deceleration driving gear by bearings on described bearing supporting body; Described bearing supporting body is fixedlyed connected with housing by oil pump rear lid.
2, the transmission system of 6-speed automatic transmission for automobile as claimed in claim 1 is characterized in that, described bearing supporting body and oil pump rear lid are one-body molded.
3, the transmission system of 6-speed automatic transmission for automobile as claimed in claim 1 is characterized in that, described bearing is the angular contact ball bearing of two back-to-back installations.
4, as the transmission system of any described 6-speed automatic transmission for automobile in the claim 1 to 3, it is characterized in that 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 power input shaft also connects the gear ring of line of input star wheel series by the sun gear of first clutch connection retroaction planetary gear system by second clutch; Described first clutch also is connected with housing by second break; Described second break is positioned at the first clutch periphery, with the shared hub of first clutch; Described first break is positioned at the periphery of output planetary train, and the sun gear of output planetary train is connected with housing by first break; The 3rd break is positioned at the periphery of retroaction planetary gear system, and the planet carrier of retroaction planetary gear system is connected with housing by the 3rd break; Described overrunning clutch is positioned at an end of the 3rd break, and is connected with the planet carrier of retroaction planetary gear system.
5, the transmission system of 6-speed automatic transmission for automobile as claimed in claim 4 is characterized in that, described first clutch and second clutch axially are arranged side by side with the form of hub assembly.
6, the transmission system of 6-speed automatic transmission for automobile as claimed in claim 5, it 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, and the balance oil pocket of first clutch and second clutch is communicated with the oil duct of hub median ventral plate.
7, the transmission system of 6-speed automatic transmission for automobile as claimed in claim 4, it is characterized in that, comprise that also central authorities support, the friction plate group of described first break and the 3rd break and servo-system all are positioned at central authorities and support, and the friction plate group is connected to the sun gear of output planetary train and the planet carrier of retroaction planetary gear system on the housing by central authorities' support.
8, the transmission system of 6-speed automatic transmission for automobile as claimed in claim 7 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.
9, the transmission system of 6-speed automatic transmission for automobile as claimed in claim 4 is characterized in that, the shared hub of described second break and first clutch; The friction plate group of second break is positioned at the periphery of first clutch and second clutch.
10,6-speed automatic transmission for automobile comprises transmission system, it is characterized in that, described transmission system is the transmission system of any described 6-speed automatic transmission for automobile in the claim 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNA2009101076399A CN101566216A (en) | 2009-06-03 | 2009-06-03 | 6-speed automatic transmission for automobile and transmission system thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNA2009101076399A CN101566216A (en) | 2009-06-03 | 2009-06-03 | 6-speed automatic transmission for automobile and transmission system thereof |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101566216A true CN101566216A (en) | 2009-10-28 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2009101076399A Pending CN101566216A (en) | 2009-06-03 | 2009-06-03 | 6-speed automatic transmission for automobile and transmission system thereof |
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| Country | Link |
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| CN (1) | CN101566216A (en) |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0478352A (en) * | 1990-07-19 | 1992-03-12 | Kayseven Co Ltd | Automatic transmission gear |
| US6309322B1 (en) * | 1999-10-29 | 2001-10-30 | Hyundai Motor Company | Power train of automatic transmission |
| 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 CNA2009101076399A patent/CN101566216A/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 |
| US6309322B1 (en) * | 1999-10-29 | 2001-10-30 | Hyundai Motor Company | Power train of automatic transmission |
| 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 |
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Application publication date: 20091028 |