CN101649889A - Six-gear gearbox for vehicle and transmission system thereof - Google Patents
Six-gear gearbox for vehicle and transmission system thereof Download PDFInfo
- Publication number
- CN101649889A CN101649889A CN200910107899A CN200910107899A CN101649889A CN 101649889 A CN101649889 A CN 101649889A CN 200910107899 A CN200910107899 A CN 200910107899A CN 200910107899 A CN200910107899 A CN 200910107899A CN 101649889 A CN101649889 A CN 101649889A
- Authority
- CN
- China
- Prior art keywords
- clutch
- break
- vehicle
- gear
- transmission system
- 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 40
- 238000006243 chemical reaction Methods 0.000 description 3
- 238000000034 method Methods 0.000 description 2
- 238000011160 research Methods 0.000 description 2
- 230000000052 comparative effect Effects 0.000 description 1
- 238000000605 extraction Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
Images
Classifications
-
- 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 six-gear gearbox for a vehicle and a transmission system thereof. A first clutch and a second clutch of the transmission system are distributed at the rear part of a shell; apower input shaft is connected with a sun gear of a retroaction planetary gear system by the first clutch and connected with a planetary carrier of the retroaction planetary gear system by the secondclutch; the first clutch is also connected with the shell by a second brake; the second brake is positioned at the periphery of the first clutch and shares a hub with the first clutch; a first brakeis positioned at the periphery of an output planetary gear system, and the output planetary gear system is connected with the shell by the first brake; a third brake is positioned at the periphery ofthe retroaction planetary gear system, and the retroaction planetary gear system is connected with the shell by the third brake; and a one-way clutch is positioned at one end of the third brake and also connected with the retroaction planetary gear system. The six-gear gearbox for a vehicle of the transmission system has more compact gearbox structure, shorter power transfer path and less power loss due to reasonable arrangement of all gear shift parts.
Description
Technical field
The invention belongs to automobile technical field, particularly vehicular transmission relates in particular to a kind of transmission system of six-gear gearbox for vehicle, and the six-gear gearbox for vehicle that comprises this transmission system.
Background technique
The gear of automobile-used gearbox 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 vehicular transmission of more grades of numbers always.
As everyone knows, in vehicular transmission, 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 speed changers, the problem of bringing is increasing of friction element, and the efficient of being brought by frictional loss reduces also unavoidable.Simultaneously the volume of speed changer also constantly increases thereupon, and for concerning the horizontal forerunner's formula speed changer at full stretch of front deck space, it is particularly evident that this problem shows.Therefore, people are compacter, simple at research structure, easy to assembly always, the vehicular transmission that power loss is littler.
Summary of the invention
The transmission system that the purpose of this invention is to provide a kind of six-gear gearbox for vehicle, and the six-gear gearbox for vehicle that comprises described transmission system, the problem that the structure that solves present six-gear gearbox for vehicle is compact inadequately, power transmission line is long, power loss is bigger.
For achieving the above object, the present invention adopts following technological scheme:
The transmission system of six-gear gearbox for vehicle, comprise: power input shaft, pto, planet row, housing and gearshift parts, described power input shaft, pto, planet row and gearshift parts all are arranged in the described housing, power input shaft directly or indirectly is connected with planet row power by the gearshift parts, and planet row's output terminal is connected with pto 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 power input shaft also connects the planet carrier of retroaction planetary gear system 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; First break is positioned at the periphery of output planetary train, and the output planetary train is connected with housing by first break; The 3rd break is positioned at the periphery of retroaction planetary gear system, and 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 also is connected with retroaction planetary gear system.
Adopt the six-gear gearbox for vehicle of technical solution of the present invention transmission system, compared to existing technology, because the reasonable Arrangement of each gearshift parts, make the structure of six-gear gearbox for vehicle compact more, assembling is convenient, power transfer path is shorter, power loss is littler.
Description of drawings
Fig. 1 is the principle schematic of existing six-gear gearbox for vehicle transmission system.
Fig. 2 is the principle schematic of specific embodiment of the invention six-gear gearbox for vehicle transmission system.
Fig. 3 is the sectional structure schematic representation of specific embodiment of the invention six-gear gearbox for vehicle transmission system.
Embodiment
The six-gear gearbox for vehicle that provides a kind of performance more superior is provided in the present invention.Existing six-gear gearbox for vehicle transmission system as shown in Figure 1.Because the design of technology comparative maturity, the especially power transmission line of six-gear gearbox for vehicle transmission system is very complicated, and involves too much, it is very difficult therefore will wanting to design new power transmission line.The means that this embodiment is taked are by its transmission system of optimal design, concrete position by reasonable Arrangement clutch hub assembly, break and overrunning clutch, make the structure of six-gear gearbox for vehicle more compact, assembling is simpler, power loss is littler.Substantially do not change as for the composition of transmission system and the power transmission line that the order of connection determined between the each several part.
Six-gear gearbox for vehicle according to this embodiment, its transmission system as shown in Figures 2 and 3, comprise: power input shaft IP, pto OP, planet row, housing H, central authorities support CS, gearshift parts, and power output connecting plate 17, power output driving gear G1, biserial roller ball bearing and support, deceleration jack shaft and differential mechanism etc.
Described planet row comprises three planetary gear train for gear, 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 power input shaft IP, pto OP, 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 directly or indirectly passes through the controllable switching of gearshift parts, and is connected with planet row's appropriate section power, and the output planetary train is connected with pto OP 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 conversion, export by pto OP.
Described gearshift parts comprise: two clutches (being respectively first clutch C1, second clutch C2), overrunning clutch OWC and three breaks (being respectively the first break B1, the second break B2 and the 3rd break B3).Be that with the main difference part of existing six-speed gearbox described gearshift parts all are arranged in the periphery of planetary gear train.
Wherein, the shared hub of first clutch C1 and second clutch C2 (shown among Fig. 3 1) is arranged in housing H rear portion, and is positioned at planet row's a end.First clutch C1 and second clutch C2 axially are arranged side by side, radially alignment substantially, axially all the locating by the external webs 1a of hub of its friction plate group.Power input shaft IP also passes through the planet carrier (the first planet carrier PC1) 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 2 of first clutch C1 and the servo-system 4 of second clutch C2 are 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 1b on the hub median ventral plate 1a, by the oil duct 1b oil extraction on the hub median ventral plate 1a.
It is affixed by form such as key, spline or pin and housing H that described central authorities support CS, 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, its friction plate group supports CS by central authorities respectively the second sun gear S2 and the third line star frame PC3 is connected on the housing H, and the first break B1 and the 3rd break B3 lay respectively at the periphery of output planetary train IPG and retroaction planetary gear system RPG, thereby have shortened power transmission line.
The described second break B2 is positioned at first clutch C1 periphery, with the shared hub 1 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.
Described 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, saved arrangement space, make six-gear gearbox for vehicle structure compact more.And overrunning clutch OWC is fixed on the housing H inwall, and is connected with retroaction planetary gear system RPG, and like this, overrunning clutch OWC just brakes retroaction planetary gear system jointly with the 3rd break B3.When putting in first gear, the first break B1 and overrunning clutch OWC work, power is input to line of input star wheel series IPG 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 six-gear gearbox for vehicle.
Because the reasonable Arrangement of each gearshift parts, the six-gear gearbox for vehicle that makes this embodiment are compared to existing technology, structure is compact more, power transfer path is shorter, power loss is littler.And the described second planet carrier PC2 also links to each other by the driving gear G1 of a plate with biserial roller ball bearings 19, and Placement is preferentially selected for use and is end face spline 17a, and axial size is shortened, and makes structure compact more.
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 (9)
1, the transmission system of six-gear gearbox for vehicle, comprise: power input shaft, pto, planet row, housing and gearshift parts, described power input shaft, pto, planet row and gearshift parts 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 pto 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 power input shaft also connects the planet carrier of retroaction planetary gear system 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 also is connected with the planet carrier of retroaction planetary gear system.
2, the transmission system of six-gear gearbox for vehicle as claimed in claim 1 is characterized in that, described first clutch and second clutch axially are arranged side by side, and a shared hub.
3, the transmission system of six-gear gearbox for vehicle as claimed in claim 2 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.
4, the transmission system of six-gear gearbox for vehicle as claimed in claim 3 is characterized in that, the servo-system of described second break is positioned at the wall of housing afterbody.
5, the transmission system of six-gear gearbox for vehicle as claimed in claim 1, 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.
6, the transmission system of six-gear gearbox for vehicle 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 six-gear gearbox for vehicle 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.
8, the transmission system of six-gear gearbox for vehicle as claimed in claim 7 is characterized in that, the balance oil pocket of described first clutch and second clutch is communicated with oil duct on the hub median ventral plate.
9, six-gear gearbox for vehicle comprises transmission system, it is characterized in that, described transmission system is the transmission system of any described six-gear gearbox for vehicle in the claim 1 to 8.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910107899A CN101649889A (en) | 2009-06-23 | 2009-06-23 | Six-gear gearbox for vehicle and transmission system thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200910107899A CN101649889A (en) | 2009-06-23 | 2009-06-23 | Six-gear gearbox for vehicle and transmission system thereof |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101649889A true CN101649889A (en) | 2010-02-17 |
Family
ID=41672185
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200910107899A Pending CN101649889A (en) | 2009-06-23 | 2009-06-23 | Six-gear gearbox for vehicle and transmission system thereof |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN101649889A (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 (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1294992A (en) * | 1999-11-09 | 2001-05-16 | 现代自动车株式会社 | Automatic variable-speed drive system |
| US20040248694A1 (en) * | 2003-06-04 | 2004-12-09 | Jatco Ltd. | Multiple-speed transmission for automotive 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 |
| CN1743699A (en) * | 2004-09-01 | 2006-03-08 | 现代自动车株式会社 | Six-speed powertrain of an automatic transmission |
| CN1746530A (en) * | 2004-09-07 | 2006-03-15 | 现代自动车株式会社 | Six-speed powertrain of an automatic transmission |
-
2009
- 2009-06-23 CN CN200910107899A patent/CN101649889A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1294992A (en) * | 1999-11-09 | 2001-05-16 | 现代自动车株式会社 | Automatic variable-speed drive system |
| US20040248694A1 (en) * | 2003-06-04 | 2004-12-09 | Jatco Ltd. | Multiple-speed transmission for automotive 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 |
| CN1743699A (en) * | 2004-09-01 | 2006-03-08 | 现代自动车株式会社 | Six-speed powertrain of an automatic transmission |
| CN1746530A (en) * | 2004-09-07 | 2006-03-15 | 现代自动车株式会社 | Six-speed powertrain of an automatic transmission |
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 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102498318B (en) | Multi-ratio transmission | |
| CN101021251B (en) | Multi-gear transmission | |
| CN102840284B (en) | For the planetary train of the automatic transmission of vehicle | |
| CN202165536U (en) | Automatic transmission with six forward gears and reverse gear | |
| CN101970903B (en) | Multi-stage gearbox | |
| CN101021252B (en) | Multi-gear transmission | |
| CN102472371B (en) | Multi-ratio transmission | |
| CN101021255B (en) | Multi-gear transmission | |
| CN102900815A (en) | Planetary gear train of automatic transmission for vehicles | |
| CN102207176A (en) | Gear train of automatic transmission for vehicles | |
| CN102913597A (en) | Seven-level planet automatic speed changer | |
| CN103527732A (en) | Seven-gear planet automatic gearbox | |
| CN110822034A (en) | Nine-gear automatic transmission | |
| CN106884936A (en) | The gear transmission of three planet row six and automobile | |
| CN103511565A (en) | Automatic six-gear planetary transmission | |
| CN105299157B (en) | A kind of 9-speed transmission | |
| CN106523628A (en) | Eight-gear planetary automatic transmission | |
| CN106838153B (en) | A kind of seven previous planetary transmissions of falling four-degree-of-freedom | |
| CN101672350A (en) | Power transmission system for six-gear automatic gearbox | |
| CN102628495A (en) | Six-gear planet automatic gearbox | |
| CN105299156B (en) | A kind of multi-speed transmission | |
| CN106917850A (en) | Eight speed automatic transmissions | |
| CN101021248A (en) | Multi-gear transmission | |
| CN106763568A (en) | A kind of six keep off planetary automatic transmission | |
| CN103527731A (en) | Automatic six-speed planetary transmission |
Legal Events
| 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: 20100217 |