CN105485271A - Automatic transmission and planetary gear train thereof - Google Patents
Automatic transmission and planetary gear train thereof Download PDFInfo
- Publication number
- CN105485271A CN105485271A CN201410482453.2A CN201410482453A CN105485271A CN 105485271 A CN105485271 A CN 105485271A CN 201410482453 A CN201410482453 A CN 201410482453A CN 105485271 A CN105485271 A CN 105485271A
- Authority
- CN
- China
- Prior art keywords
- solid
- rotation
- clutch
- running shaft
- gear
- 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.)
- Granted
Links
Landscapes
- Structure Of Transmissions (AREA)
Abstract
The invention discloses a planetary gear train used for an automatic transmission. At least eight forwarding gears and at least two reversing gears can be obtained, and the planetary gear train comprises a first planet row, a second planet row, a third planet row and a fourth planet row. Each planet row is provided with a sun gear, a planetary frame and a gear ring; eight rotating bodies can be jointly formed by assemblies of the planet rows and connecting components; a gear shifting assembly comprises three clutches and three brakes, and the clutches are arranged between selected rotating bodies in the rotating bodies; and the brakes are arranged between the selected rotating bodies in the rotating bodies and fixing parts. The planetary gear train can have more gears and the more optimized speed ratio; the power transmission performance and the fuel economy of a vehicle can be obviously improved, the length is shorter, the whole design is more compact, and the requirements of the vehicle for durability, the power transmission rate, the size, the cost and the like of the transmission can be met well. The invention further discloses the automatic transmission provided with the planetary gear train.
Description
Technical field
The present invention relates to automobile technical field, be particularly applicable to the epicyclic train of vehicular automatic transmission.The invention still further relates to the automatic transmission being provided with described epicyclic train.
Background technique
Epicyclic train is the core institution that automatic transmission AT (AutomaticTransmission) carries out speed change, it forms primarily of planet row, clutch and break, by solenoidoperated cluthes and break, the component of planet row can be made with the interconnection of different combining forms, thus realize the conversion of multiple velocity ratio.
When speed changer has more optional gear, the design just more can optimized it, by more gears, the speed changer more optimizing speed ratio, motor can be made when efficient district works to meet the demand of the different speed of a motor vehicle, thus make vehicle can have more cost effective fuel consume and better power performance.
At present, the most common on market is four-speed and six gear transmissions, although it can realize expecting object to a certain extent.But, from the angle of technical development, in fuel economy, response power and stationarity etc., all there is narrow limitation, await the improvement carrying out continuing and upgrade design.
As mentioned above, speed changer realization that is more, that more optimize gear function depends on epicyclic train, and the position of the selection of the combining form of planet row, particularly planet row fastening member, power-transmitting part is arranged and layout, overall epicyclic train is made to have different characteristics.
Therefore, how epicyclic train is improved, make that its parts are less, gear is more, efficiency is higher and cost is lower, to meet the requirement of vehicle to aspects such as speed changer durability, power transmission efficiency, sizes, is those skilled in the art's technical issues that need to address.
Summary of the invention
The first object of the present invention is to provide a kind of epicyclic train.This epicyclic train has at least eight advance gears and two final shift speed of reversing gear, and can significantly improve transmission of power performance and the fuel economy of vehicle, meanwhile, also well solves above-mentioned other technologies problem.
The second object of the present invention is to provide a kind of automatic transmission being provided with described epicyclic train.
In order to realize above-mentioned first object, the invention provides a kind of epicyclic train, for automatic transmission, multiple gear can be obtained, comprising:
First planet is arranged, and has the first sun gear, the first row carrier and the first gear ring;
Second planet row, has the second sun gear, the second planet carrier and the second gear ring;
Dual planetary gear group, comprise third planet row and the fourth planet row of combination, described third planet row has the 3rd sun gear, the third line carrier and the 3rd gear ring, and described fourth planet row has the 4th sun gear, fourth line carrier and the 4th gear ring;
First solid of rotation, comprises input shaft and described the first row carrier;
Second solid of rotation, comprises described first sun gear, and optionally can be connected to fixed block;
3rd solid of rotation, comprises described first gear ring and the second planet carrier, and optionally can be connected to fixed block;
4th solid of rotation, comprises described second sun gear, and it optionally can be connected to described first solid of rotation;
5th solid of rotation, comprises described second gear ring and the 3rd sun gear;
6th solid of rotation, comprises described the third line carrier and the 4th gear ring, and optionally can be connected to fixed block or optionally be connected to described 4th solid of rotation;
7th solid of rotation, comprises described 4th sun gear, and optionally can be connected to described 4th solid of rotation;
8th solid of rotation, comprises described 3rd gear ring, fourth line carrier and output shaft;
Six gearshift assemblies, comprise clutch and break, described clutch is located between the selected solid of rotation in described solid of rotation, and described break is located between selected solid of rotation in described solid of rotation and fixed block.
Preferably, described input shaft is the first running shaft;
The first row carrier of described first solid of rotation is connected with described first running shaft;
First sun gear of described second solid of rotation is connected with the second running shaft;
First gear ring of described 3rd solid of rotation is connected by the 3rd running shaft with the second planet carrier;
Second sun gear of described 4th solid of rotation is connected with the 4th running shaft;
Second gear ring of described 5th solid of rotation is connected by the 5th running shaft with the 3rd sun gear;
The third line carrier of described 6th solid of rotation is connected by the 6th running shaft with the 4th gear ring;
4th sun gear of described 7th solid of rotation connects the 7th running shaft;
3rd gear ring of described 8th solid of rotation is connected output shaft with fourth line carrier;
Described output shaft is the 8th running shaft.
Preferably, described six gearshift assemblies comprise:
First clutch, is inserted between described first solid of rotation and the 4th solid of rotation;
Second clutch, is inserted between described 4th solid of rotation and the 6th solid of rotation;
3rd clutch, is inserted between described 4th solid of rotation and the 7th solid of rotation;
First break, is inserted between described second solid of rotation and fixed block;
Second brake, is inserted in the described 3rd between solid of rotation and fixed block;
3rd break, is inserted in the described 6th between solid of rotation and fixed block.
Preferably, described multiple gear comprise at least eight forward gears and at least two reverse gear:
Advance a gear, and described second brake, the 3rd break and first clutch combine;
Advance two gears, and described 3rd break, first clutch and the 3rd clutch combine;
Ahead three keeps off, and described second brake, first clutch and the 3rd clutch combine;
Advance four gears, and described first break, second clutch and the 3rd clutch combine;
Advance five gears, and described first break, first clutch and the 3rd clutch combine;
Advance six gears, and described first clutch, second clutch and the 3rd clutch combine;
Advance seven gears, and described first break, first clutch and second clutch combine;
Advance eight gears, and described second brake, first clutch and second clutch combine;
First reverses gear, and described first break, the 3rd break and first clutch combine;
Second reverses gear, and described first break, the 3rd break and second clutch combine.
Preferably, described clutch is friction clutch, and described break is friction brake.
Preferably, described second running shaft is hollow shaft, and by this hollow shaft, described first sun gear is connected with the motion side of the first break, and described first running shaft is positioned at described second interior of rotating shaft.
Preferably, described 4th running shaft comprises front rotary shaft and rear rotating shaft, by described front rotary shaft, described second sun gear is connected with the slave end of first clutch, by described rear rotating shaft, described second sun gear is connected with the slave end of described second clutch and the master end of described 3rd clutch simultaneously.
Preferably, described first planet row is single double-pinion planetary row, and described second planet row is that single single-stage planetary is arranged, and described third planet is arranged as single single-stage planetary is arranged, and described fourth planet row is that single single-stage planetary is arranged.
Preferably, described input shaft is configured to the component receiving moment of torsion and rotating speed input; Described output shaft is configured to export the component having changed moment of torsion and rotating speed.
Preferably, described fixed block is gearbox case.
In order to realize above-mentioned second object, the present invention also provides a kind of automatic transmission, comprise shell and be located at fluid torque converter and the epicyclic train of described enclosure, described fluid torque converter and epicyclic train are in transmission connection, it is characterized in that, described planetary pinion is the epicyclic train described in above-mentioned any one.
The planetary pinion being applied to vehicular automatic transmission provided by the present invention is the product of brand-new exploitation, it has the input shaft receiving power, the output shaft of outside outputting power, four planet rows being arranged in same axle and fastening, and six gearshift assemblies, wherein, each planet row is equipped with sun gear, gear ring and with several planetary planet carriers, be connected by running shaft or other connector elements between the assembly of planet row, eight solid of rotation can be formed, to realize the transmission of power, gearshift assembly can adopt the torque transmitter such as clutch and break, the degrees of freedom of epicyclic train can be changed by operation gearshift assembly, the combination of different gearshift assemblies makes to realize different speed ratio transmission between input shaft and output shaft from being separated, finally can obtain the shift speed of at least eight available advance gears and at least two available positions of reversing gear, compare with six speed planetary train of gearings with four-speed, its speed ratio that there is more gear and more optimize, motor can be made when efficient district works to meet the demand of the different speed of a motor vehicle, and then significantly improve transmission of power performance and the fuel economy of vehicle.
In addition, these epicyclic train component are less, gearshift assembly makes full use of the space between planet row, not only can obtain shorter speed changer length, and global design is compacter, the requirement of vehicle to aspects such as speed changer durability, power transmission efficiency, size, costs can well be met.
Automatic transmission provided by the present invention is provided with above-mentioned epicyclic train, and because above-mentioned epicyclic train has above-mentioned technique effect, the automatic transmission being provided with this epicyclic train also should possess corresponding technique effect.
Accompanying drawing explanation
Fig. 1 is the drive path sketch of planetary gear train provided by the present invention;
Fig. 2 is a kind of specific examples of applications sketch of planetary gear train provided by the present invention;
Fig. 3 is the catenation principle figure of each component of exemplifying planetary gear train;
Fig. 4 is each gear of exemplifying planetary gear train and the operation table of torque transmitter, in order to illustrate which gearshift assembly closes in each gear determined;
Fig. 5 is the lever principle figure of exemplary row star wheel series of the present invention.
In figure:
1. the first running shaft 2. second running shaft 3. the 3rd running shaft 4. the 4th running shaft 5. the 5th running shaft 6. the 6th running shaft 7. the 7th running shaft 8. the 8th running shaft
C1. the first friction clutch C2. second friction clutch C3. the 3rd friction clutch
B1. the first friction brake B2. second friction brake B3. the 3rd friction brake
PG1. first planet row PG2. second planet row PG3. third planet row PG4. fourth planet row
S1. the first sun gear PC1. the first row carrier P1. the first row star-wheel A1. first gear ring
S2. the second sun gear PC2. second planet carrier P2. second planet wheel A2. second gear ring
S3. the 3rd sun gear PC3. the third line carrier P3. the third line star-wheel A3. the 3rd gear ring
S4. the 4th sun gear PC4. fourth line carrier P4. fourth line star-wheel A4. the 4th gear ring
Embodiment
Core of the present invention is to provide one and comprises four planet rows and six torque transmitter mechanisms or control unit, can provide at least eight forward gears and at least two epicyclic trains reversed gear.
Another core of the present invention is to provide a kind of automatic transmission being provided with described epicyclic train.
In order to make those skilled in the art person understand the present invention program better, below in conjunction with the drawings and specific embodiments, the present invention is described in further detail.
Be only limitted to exemplifying embodiment scheme for the explanation in specification of the present invention, and omit unnecessary component representation, component same in the description of the present invention represents with identical mark on different accompanying drawing.In concrete enforcement describes, numeral and letter are used to distinguish the element with same term, and these numerals and letter do not have specific implication, do not represent any order yet.
Please refer to Fig. 1, Fig. 2, Fig. 1 is the drive path sketch of planetary gear train provided by the present invention; Fig. 2 is a kind of specific examples of applications sketch of planetary gear train provided by the present invention.
In a kind of embodiment, epicyclic train provided by the invention has setting first planet row PG1, the second planet row PG2 on the same axis, third planet row PG3 and fourth planet row PG4, first clutch C1, second clutch C2 on the same axis and the 3rd clutch C3 are set, and the first break B1, the second brake B2 that arrange on the same axis and the 3rd break B3.
First planet row PG1 is single double-pinion planetary row, it comprises the first row carrier PC1 inputted as this row, the first sun gear S1 and the first gear ring A1 at least three components, and the first row star-wheel P1 on the first row carrier PC1 is three groups, often organize two, amount to six planet wheels.
Second planet row PG2 is single single-stage planetary row, and it comprises the second sun gear S2 and the second planet carrier PC2 that input as this row, and the second gear ring A2 at least three components, and the quantity of the second planet wheel P2 on the second planet carrier PC2 is four.
Third planet row PG3 is single single-stage planetary wheel, and it comprises the 3rd sun gear S3 and the third line carrier PC3 that input as this row, and the 3rd gear ring A3 at least three components, and the quantity of the third line star-wheel P3 on the third line carrier PC3 is five.
Fourth planet row PG4 is single single-stage planetary wheel, and it comprises the 4th sun gear S4, fourth line carrier PC4, and the 4th gear ring A4 at least three components, and the quantity of the fourth line star-wheel P4 on fourth line carrier PC4 is three.
Third planet row PG3 and fourth planet arrange the two groups of forms that are connected existing between PG4 and formed by four components, therefore can be considered one group of dual planetary gear group in moment, export as unitary form.
Also comprise eight running shafts as connector element, the assembly of above-mentioned planet row is connected with running shaft, and is interconnected by running shaft, can form altogether eight solid of rotation:
First solid of rotation, is made up of the first running shaft 1 (i.e. input shaft) the first row carrier PC1 that is rigidly connected, and both rotate with identical rotating speed all the time, and the first running shaft 1 is constructed to the component receiving fluid torque converter moment of torsion and rotating speed.
Second solid of rotation, is connected and composed by the second running shaft 2 and the first sun gear S1, can optionally be connected on fixed block (such as housing).
3rd solid of rotation, is connected and composed by the first gear ring A1, the 3rd running shaft 3 and the second planet carrier PC2, can be selectively connected thereto on fixed block.
4th solid of rotation, is connected and composed by the 4th running shaft 4 and the second sun gear S2, can optionally be connected to the first solid of rotation.
5th solid of rotation, is connected and composed by the second gear ring A2, the 5th running shaft 5 and the 3rd sun gear S3.
6th solid of rotation, is connected and composed by the third line carrier PC3, the 6th running shaft 6 and the 4th gear ring A4, can optionally be connected on fixed block, or be optionally connected on the 4th solid of rotation.
7th solid of rotation, is connected and composed by the 7th running shaft 7 and the 4th sun gear S4, can optionally be connected on the 4th solid of rotation.
8th solid of rotation, connected and composed by the 3rd gear ring A3, fourth line carrier PC4 and the 8th running shaft 8 (i.e. output shaft), the 8th running shaft 8 is constructed to the component that moment of torsion and rotating speed have been changed in outside output.
According to the needs of above-mentioned Placement and actual assembled, the size of each running shaft and form will be not quite similar, and wherein the first running shaft 1 and the 8th running shaft 8 can be solid shaft; 2, second running shaft of the second solid of rotation is hollow shaft, and the first sun gear S1 is connected with the motion side of the first break B1 by this hollow shaft, and it is inner that the first running shaft 1 is positioned at the second running shaft 2; 3rd running shaft 3, the 5th running shaft 5 and the 6th running shaft 6 are the hollow shaft that diameter is larger, the planet row that inner accommodation connects and corresponding friction clutch, and meanwhile, it is also Step Shaft, to adapt to different radial dimension changes; 4th running shaft 4 and the 7th running shaft 7 both can be solid shaft, also can be hollow shaft, wherein, 4th running shaft 4 can be divided into again front rotary shaft and rear rotating shaft, second sun gear S2 is connected by the slave end of front rotary shaft with first clutch C1, is connected by rear rotating shaft with the slave end of second clutch C2 and the master end of the 3rd clutch C3 simultaneously.
Friction clutch is placed between the selected solid of rotation of above-mentioned solid of rotation, to carry out the transmission of moment of torsion and rotating speed.
First friction clutch C1 is arranged between the first solid of rotation and the 4th solid of rotation.Particularly, the 4th running shaft 4 comprises the front rotary shaft and rear rotating shaft that are positioned at the second sun gear S2 front and rear sides, and the first friction clutch C1 is plugged between the front rotary shaft of the first running shaft 1 and the 4th running shaft 4, operates as optionally input element.
Because the first running shaft 1 forms the first solid of rotation together with the first row carrier PC1, therefore, the first friction clutch C1 also can be considered as to be plugged between the front rotary shaft of the first row carrier PC1 and the 4th running shaft 4, lower same.
Second friction clutch C2 is arranged between the 4th solid of rotation and the 6th solid of rotation.Particularly, be plugged between the rear rotating shaft of the 4th running shaft 4 and the 6th running shaft 6, operate as optionally input element.
3rd friction clutch C3 is arranged between the 4th solid of rotation and the 7th solid of rotation.Particularly, be plugged between the rear rotating shaft of the 4th running shaft 4 and the 7th running shaft 7, operate as optionally input element.
Friction brake is placed in between the selected solid of rotation of above-mentioned solid of rotation and fixed block, is used for limiting the degrees of freedom of its place planet row, so that moment of torsion is along set path transmission.
First friction brake B1 is plugged between the second running shaft 2 and fixed block, operates as optionally fixed element.
Second friction brake B2 is plugged between the 3rd running shaft 3 and fixed block, operates as optionally fixed element.
3rd friction brake B3 is plugged between the 6th running shaft 6 and fixed block, operates as optionally fixed element.
Among the first running shaft 1 to the 8th running shaft 8, can be used as optionally input link and have the 4th running shaft 4, the 6th running shaft 6, the 7th running shaft 7, respectively by the first friction clutch C1, the second friction clutch C2 and the 3rd friction clutch C3, be optionally connected to the first running shaft 1 of input end.
Among the first running shaft 1 to the 8th running shaft 8, can be used as optionally fixed component and have the second running shaft 2, the 3rd running shaft 3, the 6th running shaft 6, respectively by the first friction brake B1, the second friction brake B2 and the 3rd friction brake B3, optionally corresponding solid of rotation is affixed on fixed block.
Please refer to Fig. 3, Fig. 3 is the catenation principle figure of each component of exemplifying planetary gear train.
As mentioned above, first planet row PG1 connects three in eight running shafts, and connect the first friction brake B1, the second friction brake B2 and the first friction clutch C1, its the first row carrier PC1 is connected with input shaft, and be optionally connected with the first friction clutch C1, in order to receive the moment of torsion of input shaft, first sun gear S1 is optionally connected to fixed block by the first friction brake B1, the second planet carrier PC2 of the first gear ring A1 and the second planet row PG2 is connected, and is optionally connected to fixed block by the second friction brake B2.Like this, first planet row PG1 just exportable two speed ratios, one is the speed ratio directly exported by the first friction clutch C1, and another is the speed ratio by the reduction exported after the first friction brake B1 effect.
Second planet row PG2 connects three in eight running shafts, and it is as the input planet row of power, receives and transmits from first planet row PG1 the moment of torsion of coming; Second sun gear S2 is optionally connected with the first running shaft 1 by the first friction clutch C1 with the 4th running shaft 4, and be optionally connected with the third line carrier PC3, the 4th sun gear S4 respectively by the second friction clutch C2, the 3rd friction clutch C3 so as the moment of torsion from input shaft to be outputted to the 3rd, fourth planet row; Second sun gear S2 is connected with the first running shaft 1 by the first friction clutch C1, receives input torque; Second planet carrier PC2 and the first gear ring A1 is connected, and receive the moment of torsion that first planet row PG1 transmits, the second gear ring A2 and the 3rd sun gear S3 is connected; Such second planet row PG2 just has two power input links, and has three power output member.Can when receive friction speed input, different choice output to the 3rd, the different speed ratio of fourth planet row output six, make the 3rd like this, fourth planet row have the input of more speed, to obtain more gear.
Three, fourth planet row is combined into the planetary gear set of a compound, and the third line carrier PC3 and the 4th gear ring A4 is connected, and the 3rd gear ring A3 and fourth line carrier PC4 is connected, and connects the 8th running shaft 8 output torque and rotating speed.This group dual planetary gear group is connected with four in eight running shafts; 3rd sun gear S3 is connected by the 5th running shaft 5 and the second gear ring A2, receive the moment of torsion that the second planet row PG2 exports, the third line carrier PC3 is optionally connected with the rear rotating shaft of the 4th running shaft 4, the second sun gear S2 by the second friction clutch C2, and is optionally connected with the first running shaft 1 by the front rotary shaft of the 4th running shaft 4, the first friction clutch C1; 4th sun gear S4 is optionally connected with the rear rotating shaft of the 4th running shaft 4 by the 3rd friction clutch C3; Such structural texture makes this group dual planetary gear group have the ability of an outputting ten speed ratio.
Please refer to Fig. 4, Fig. 5, Fig. 4 is each gear of exemplifying planetary gear train and the operation table of torque transmitter; Fig. 5 is the lever principle figure of exemplary row star wheel series of the present invention.
The differential numerical value between the speed ratio of each gear provided according to the number of teeth shown in Fig. 2 and gear is given, the gearshift assembly that the form district representative of stain is closed, the gearshift assembly that blank form district representative disconnects in form shown in Fig. 4.This form only embodies the numerical value in example planetary gear train situation, and often group numerical value can change.
Two horizontal lines in Fig. 5 are expressed as: " 0 " horizontal line representation speed is zero, and " 1 " representation speed is that input speed and rotating speed thereof are identical with the first running shaft 1.Character on horizontal line is with reference to the title in each component catenation principle figure shown in Fig. 3, its spacing is that the number of teeth between each component and mutual proportion relation are determined, straight line between each component represents the corresponding running shaft being fixedly connected with it, and this mode is the speed manner of comparison that those skilled in the art commonly uses.
Above-mentioned friction clutch is in and is input as on the horizontal corresponding plant position of " 1 ", and above-mentioned friction brake is on the corresponding plant position of fixing horizontal line " 0 "; Speed transfer line is by the friction brake by working or clutch, and the speed exported under the numerical value of speed transfer line finally on output shaft i.e. the 8th running shaft 8 is this group torque transmitter operational circumstances is relative to the ratio of input speed.
The present invention has three torque transmitters to operate under each gear simultaneously, below by each shift speed of planetary gear train of the present invention in each embodiment situation of detailed description and the speed conditions of each component.
(1) advance a gear
When advance one keeps off, operate the second friction brake B2, the 3rd friction brake B3 and the first friction clutch C1.
First running shaft 1 drives the second sun gear S2 to input as speed " 1 " by operation input the 4th running shaft the 4, four running shaft of the first friction clutch C1; 3rd running shaft 3 passes through the operation of second brake B2 as fixed element, forms a reduction speed be delivered to the 5th running shaft 5 by the effect of the second planet row PG2; 6th running shaft 6 by the operation of the 3rd friction brake B3 using the third line carrier PC3 as fixed element, be delivered to speed on the 3rd sun gear on S3 via the 5th running shaft 5 to form advance one by the effect of third planet row PG3 and keep off speed line, the intersection point D1 of itself and the 8th running shaft 8 is advance one and keeps off speed ratio.
(2) advance two gears
When advance two keeps off, unclamp the second friction brake B2 of operation when advance one keeps off, and operate the 3rd friction clutch C3.
Speed is delivered on the second sun gear S2 by the 4th running shaft 4 by operation first friction clutch C1 by the rotating speed of the first running shaft 1, makes it input as speed " 1 "; Speed is delivered to the 7th running shaft 7 by the 4th running shaft 4 by operation the 3rd friction clutch C3 simultaneously and is delivered to the 4th sun gear S4 by the rotating speed of the first running shaft 1, inputs as speed " 1 "; By operating the 3rd friction brake B3 using the 6th running shaft 6 as fixed element, thus form advance two and keep off speed line, the intersection point D2 of itself and the 8th running shaft 8 is advance two and keeps off speed ratio.
(3) ahead three gear
When ahead three keeps off, unclamp the 3rd friction brake B3 of operation when advance two keeps off, and operate the second friction catch B2.
Speed is delivered on the second sun gear S2 by the 4th running shaft 4 by operation first friction clutch C1 by the rotating speed of the first running shaft 1, inputs as speed " 1 "; Speed is delivered to the 7th running shaft 7 by the 4th running shaft 4 by operation the 3rd friction clutch C3 simultaneously and is delivered to the 4th sun gear S4 by the rotating speed of the first running shaft 1, inputs as speed " 1 "; By operating the second friction brake B2 using the 3rd running shaft 3 as fixed element, thus form ahead three gear speed line, the intersection point D3 of itself and the 8th running shaft 8 is ahead three and keeps off speed ratio.
(4) advance four gears
When advance four keeps off, unclamp the second friction brake B2 and the first friction clutch C1 of operation during ahead three gear, and operate the first friction catch B1 and the second friction clutch C2.
The rotating speed of the first running shaft 1 is delivered to the first row carrier PC1, inputs as speed " 1 "; Operate the first friction brake B1 by the first running shaft 1 using the first sun gear S1 as fixed element, make like this first gear ring A1 with one reduce speed export; Operate second, third friction clutch C2, C3, by the effect that is connected of the 5th running shaft 5, the 6th running shaft 6 and the 7th running shaft 7, each component of second planet row PG2, third planet row PG3, fourth planet row PG4 is connected, as direct transmit mode; Therefore the speed of the first gear ring A1 will directly export, thus form advance four and keep off speed line, and the intersection point D4 of itself and the 8th running shaft 8 is advance four and keeps off speed ratio.
(5) advance five gears
When advance five keeps off, unclamp the second friction clutch C2 of operation when advance four keeps off, and operate the first friction clutch C1.
Speed is delivered on the second sun gear S2 by the 4th running shaft 4 by operation first friction clutch C1 by the rotating speed of the first running shaft 1, inputs as speed " 1 "; By operating the 3rd friction clutch C3, the 4th running shaft 4 is connected with the 7th running shaft 7, and is delivered on the 4th sun gear S4, input as speed " 1 "; The rotating speed of the first running shaft 1 is delivered to the first row carrier PC1, input as speed " 1 ", by operate the first friction brake B1 using on the second running shaft 2 and the first sun gear S1 as fixed element, make like this first gear ring A1 with one reduce speed be delivered on the second planet carrier PC2 by the 3rd running shaft 3; Under the speed effect of three input links, form advance five like this and keep off speed line, the intersection point D5 of itself and the 8th running shaft 8 is advance five and keeps off speed ratio.
(6) advance six gears
When advance six keeps off, unclamp the first friction brake B1 of operation when advance five keeps off, operate the second friction clutch C2.
Rotating speed is delivered to the second sun gear S2 by the 4th running shaft by operation first friction clutch C1 by the first running shaft 1; And operate the second friction clutch C2, the 4th running shaft 4 is directly connected with the 6th running shaft 6, the 7th running shaft 7 by the 3rd friction clutch C3, make the second planet row PG2, third planet arrange PG3, fourth planet row PG4 becomes direct coupled condition, the speed of the first running shaft 1 will directly export, thus form advance six and keep off speed line, the intersection point D6 of itself and the 8th running shaft 8 is advance six and keeps off speed ratio.
(7) advance seven gears
When advance seven keeps off, unclamp the 3rd friction clutch C3 of operation when advance six keeps off, operate the first friction brake B1.
The rotating speed of the first running shaft 1 is delivered to the first row carrier PC1, inputs as speed " 1 "; Operate the first friction brake B1 by the first running shaft 1 using the first sun gear S1 as fixed element, make like this first gear ring A1 with one reduce speed be delivered to the second planet carrier PC2; Rotating speed is delivered to the second sun gear S2 by the 4th running shaft by operation first friction clutch C1 by the first running shaft 1; And operate the second friction clutch C2 the first running shaft 1 is directly connected with the 4th running shaft 4, rotating speed is directly delivered to the third line carrier PC3; Under the speed effect of three input links, form advance seven like this and keep off speed line, the intersection point D7 of itself and the 8th running shaft 8 is advance seven and keeps off speed ratio.
(8) advance eight gears
When advance eight keeps off, unclamp the first friction brake B1 of operation when advance seven keeps off, operate the second friction brake B2.
Second sun gear S2, by operation first friction clutch C1, is directly connected by the 4th running shaft 4 by the rotating speed of the first running shaft 1; And operate the second friction clutch C2 the first running shaft 1 is directly connected with the 4th running shaft 4, rotating speed is directly delivered to the third line carrier PC3; 3rd running shaft 3 as fixed element, is formed advance eight and keeps off speed line by the second friction brake B2 like this under the speed effect of two input links, and the intersection point D8 of itself and the 8th running shaft 8 is advance eight and keeps off speed ratio.
(9) first reverse gear
When first reverses gear, operate the first friction brake B1, the 3rd friction brake B3 and the first friction clutch C1.
By operating the first friction clutch C1, the first running shaft 1 is directly connected with the second sun gear S2 with the 4th running shaft 4 by the first friction clutch C1; By operating the first friction brake B1 using the second running shaft 2 and the first sun gear S1 as fixed element, due to the effect by first planet row PG1, the rotating speed reduced with is delivered to the second planet carrier PC2 by the 3rd running shaft 3 by the first gear ring A1; Second planet row PG2 exports a rotating speed reduced to the second gear ring A2 under the input action of two rotating speeds, and is delivered on the 3rd sun gear S3 by the 5th running shaft 5; By operating the 3rd friction brake B3 using the 6th running shaft 6 as fixed element, and the third line carrier PC3 is fixed, a reverse rotating speed is exported by the 3rd gear ring A3 by the effect of third planet row PG3, form the first reverse speed line, the intersection point R1 of itself and the 8th running shaft 8 is first and reverses gear speed ratio.
(10) second reverse gear
When second reverses gear, unclamp the first friction clutch C1 of the first operation when reversing gear, operate the second friction clutch C2.
By operating the first friction brake B1 using the second running shaft 2 and the first sun gear S1 as fixed element, due to the effect by first planet row PG1, the rotating speed reduced with is delivered to the second planet carrier PC2 by the 3rd running shaft 3 by the first gear ring A1; By operating the second friction clutch C2, the 4th running shaft 4 is directly connected with the 6th running shaft 6; By operating the 3rd break B3 using the 6th running shaft 6, the 4th running shaft 4 and coupled the second sun gear S2, the third line carrier PC3, the 4th gear ring A4 as fixed element; Second planet carrier PC2 transmits the speed reduced to the second planet row PG2, and is delivered to the 3rd sun gear S3 by the 5th running shaft 5 after speedup; Export a reverse rotating speed through the 3rd gear ring A3 that acts on of third planet row PG3, form the second reverse speed line, the intersection point R2 of itself and the 8th running shaft 8 is the 2nd and reverses gear speed ratio.
In Figure 5, each gear speed line is the speed conditions of this component in this gear situation with the intersection point of the vertical curve crossing each component name in each gear speed line display cited hereinabove.
Here it should be noted that, Fig. 2 is only exemplary gives a kind of specific structure, this component of the digitized representation below each component number of teeth in this special case.Because planet row can convert order, torque transmitter can be placed between different construction locations, and therefore the specific number of teeth is not as the qualifications of this patent.
In like manner, planetary gear set herein, forward gear, reverse gear, the number of running shaft, speed ratio, friction clutch, friction brake is all exemplary.Those skilled in the art will recognize, the present invention is not restricted to these example values, and each is organized concrete numerical value and can change.
Above-mentioned epicyclic train can provide the change of at least eight advance gears and at least two speed ratios that reverse gear, therefore can significantly improve power transfer efficiency and fuel economy, and component are less, length is shorter, structure is compacter, cost is lower, performance is more reliable.
In addition, due to two speed ratios that reverse gear can be provided, therefore performance of reversing gear can be significantly improved.
Except epicyclic train, the present invention also provides a kind of automatic transmission, comprise shell and be located at fluid torque converter and the epicyclic train of enclosure, wherein, fluid torque converter and epicyclic train are in transmission connection, planetary pinion is epicyclic train mentioned above, and all the other structures please refer to prior art, just repeat no more.
Above automatic transmission provided by the present invention and epicyclic train thereof are described in detail.Apply specific case herein to set forth principle of the present invention and mode of execution, the explanation of above embodiment just understands core concept of the present invention for helping.It should be pointed out that for those skilled in the art, under the premise without departing from the principles of the invention, can also carry out some improvement and modification to the present invention, these improve and modify and also fall in the protection domain of the claims in the present invention.
Claims (10)
1. an epicyclic train, for automatic transmission, can obtain multiple gear, it is characterized in that, comprise:
First planet is arranged, and has the first sun gear, the first row carrier and the first gear ring;
Second planet row, has the second sun gear, the second planet carrier and the second gear ring;
Third planet is arranged, and has the 3rd sun gear, the third line carrier and the 3rd gear ring;
Fourth planet is arranged, and has the 4th sun gear, fourth line carrier and the 4th gear ring;
First solid of rotation, comprises input shaft and described the first row carrier;
Second solid of rotation, comprises described first sun gear, and optionally can be connected to fixed block;
3rd solid of rotation, comprises described first gear ring and the second planet carrier, and optionally can be connected to fixed block;
4th solid of rotation, comprises described second sun gear, and it optionally can be connected to described first solid of rotation;
5th solid of rotation, comprises described second gear ring and the 3rd sun gear;
6th solid of rotation, comprises described the third line carrier and the 4th gear ring, and optionally can be connected to fixed block or optionally be connected to described 4th solid of rotation;
7th solid of rotation, comprises described 4th sun gear, and optionally can be connected to described 4th solid of rotation;
8th solid of rotation, comprises described 3rd gear ring, fourth line carrier and output shaft;
Six gearshift assemblies, comprise clutch and break, described clutch is located between the selected solid of rotation in described solid of rotation, and described break is located between selected solid of rotation in described solid of rotation and fixed block.
2. epicyclic train according to claim 1, is characterized in that, described input shaft is the first running shaft;
The first row carrier of described first solid of rotation is connected with described first running shaft;
First sun gear of described second solid of rotation is connected with the second running shaft;
First gear ring of described 3rd solid of rotation is connected by the 3rd running shaft with the second planet carrier;
Second sun gear of described 4th solid of rotation is connected with the 4th running shaft;
Second gear ring of described 5th solid of rotation is connected by the 5th running shaft with the 3rd sun gear;
The third line carrier of described 6th solid of rotation is connected by the 6th running shaft with the 4th gear ring;
4th sun gear of described 7th solid of rotation connects the 7th running shaft;
3rd gear ring of described 8th solid of rotation is connected output shaft with fourth line carrier;
Described output shaft is the 8th running shaft.
3. epicyclic train according to claim 1, is characterized in that, described six gearshift assemblies comprise:
First clutch, is inserted between described first solid of rotation and the 4th solid of rotation;
Second clutch, is inserted between described 4th solid of rotation and the 6th solid of rotation;
3rd clutch, is inserted between described 4th solid of rotation and the 7th solid of rotation;
First break, is inserted between described second solid of rotation and fixed block;
Second brake, is inserted in the described 3rd between solid of rotation and fixed block;
3rd break, is inserted in the described 6th between solid of rotation and fixed block.
4. epicyclic train according to claim 2, is characterized in that, described six gearshift assemblies comprise:
First clutch, is inserted between described first running shaft and the 4th running shaft;
Second clutch, is inserted between described 4th running shaft and the 6th running shaft;
3rd clutch, is inserted between described 4th running shaft and the 7th running shaft;
First break, is inserted between described second running shaft and fixed block;
Second brake, is inserted in the described 3rd between running shaft and fixed block;
3rd break, is inserted in the described 6th between running shaft and fixed block.
5. the epicyclic train according to claim 3 or 4, is characterized in that, described multiple gear comprise at least eight forward gears and at least two reverse gear:
Advance a gear, and described second brake, the 3rd break and first clutch combine;
Advance two gears, and described 3rd break, first clutch and the 3rd clutch combine;
Ahead three keeps off, and described second brake, first clutch and the 3rd clutch combine;
Advance four gears, and described first break, second clutch and the 3rd clutch combine;
Advance five gears, and described first break, first clutch and the 3rd clutch combine;
Advance six gears, and described first clutch, second clutch and the 3rd clutch combine;
Advance seven gears, and described first break, first clutch and second clutch combine;
Advance eight gears, and described second brake, first clutch and second clutch combine;
First reverses gear, and described first break, the 3rd break and first clutch combine;
Second reverses gear, and described first break, the 3rd break and second clutch combine.
6. epicyclic train according to claim 5, is characterized in that, described clutch is friction clutch, and described break is friction brake.
7. the epicyclic train according to claim 2 or 4, is characterized in that, described second running shaft is hollow shaft, and by this hollow shaft, described first sun gear is connected with the motion side of the first break, and described first running shaft is positioned at described second interior of rotating shaft.
8. the epicyclic train according to claim 2 or 4, it is characterized in that, described 4th running shaft comprises front rotary shaft and rear rotating shaft, by described front rotary shaft, described second sun gear is connected with the slave end of first clutch, by described rear rotating shaft, described second sun gear is connected with the slave end of described second clutch and the master end of described 3rd clutch simultaneously.
9. the epicyclic train according to any one of Claims 1-4, it is characterized in that, described first planet row is single double-pinion planetary row, and described second planet row is single single-stage planetary row, described third planet row is single single-stage planetary row, and described fourth planet row is single single-stage planetary row.
10. an automatic transmission, comprise shell and be located at fluid torque converter and the epicyclic train of described enclosure, described fluid torque converter and epicyclic train are in transmission connection, and it is characterized in that, described planetary pinion is the epicyclic train described in any one of the claims 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410482453.2A CN105485271B (en) | 2014-09-19 | 2014-09-19 | A kind of automatic transmission and its epicyclic train |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410482453.2A CN105485271B (en) | 2014-09-19 | 2014-09-19 | A kind of automatic transmission and its epicyclic train |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105485271A true CN105485271A (en) | 2016-04-13 |
| CN105485271B CN105485271B (en) | 2018-01-05 |
Family
ID=55672460
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410482453.2A Active CN105485271B (en) | 2014-09-19 | 2014-09-19 | A kind of automatic transmission and its epicyclic train |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN105485271B (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107514445A (en) * | 2017-08-28 | 2017-12-26 | 无锡职业技术学院 | Based on improvement lever method six speed transmission |
| CN107559391A (en) * | 2016-06-30 | 2018-01-09 | 现代自动车株式会社 | Epicyclic train for the automatic transmission of vehicle |
| CN107620786A (en) * | 2016-07-13 | 2018-01-23 | 现代自动车株式会社 | Epicyclic train for the automatic transmission of vehicle |
| WO2019128411A1 (en) * | 2017-12-29 | 2019-07-04 | 广州汽车集团股份有限公司 | Three-planet-row automatic transmission and vehicle |
| CN111637202A (en) * | 2020-06-28 | 2020-09-08 | 柳州职业技术学院 | Eight-speed automatic transmission and power transmission method thereof |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2620798Y (en) * | 2003-05-02 | 2004-06-16 | 李建国 | Planet transmission automatic speed variator |
| CN1746530A (en) * | 2004-09-07 | 2006-03-15 | 现代自动车株式会社 | Six-speed powertrain of an automatic transmission |
| JP2007187220A (en) * | 2006-01-12 | 2007-07-26 | Mazda Motor Corp | Automatic transmission |
| DE102006006638A1 (en) * | 2006-02-14 | 2007-09-06 | Zf Friedrichshafen Ag | Multi-speed transmission |
| US20090209386A1 (en) * | 2008-02-20 | 2009-08-20 | Hyundai Motor Company | Gear train of automatic transmission for vehicles |
| KR20090114635A (en) * | 2008-04-30 | 2009-11-04 | 현대 파워텍 주식회사 | Power train for automatic transmission |
| US20090312139A1 (en) * | 2008-06-13 | 2009-12-17 | Hyundai Motor Company | Powertrain of an Automatic Transmission |
-
2014
- 2014-09-19 CN CN201410482453.2A patent/CN105485271B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2620798Y (en) * | 2003-05-02 | 2004-06-16 | 李建国 | Planet transmission automatic speed variator |
| CN1746530A (en) * | 2004-09-07 | 2006-03-15 | 现代自动车株式会社 | Six-speed powertrain of an automatic transmission |
| JP2007187220A (en) * | 2006-01-12 | 2007-07-26 | Mazda Motor Corp | Automatic transmission |
| DE102006006638A1 (en) * | 2006-02-14 | 2007-09-06 | Zf Friedrichshafen Ag | Multi-speed transmission |
| US20090209386A1 (en) * | 2008-02-20 | 2009-08-20 | Hyundai Motor Company | Gear train of automatic transmission for vehicles |
| KR20090114635A (en) * | 2008-04-30 | 2009-11-04 | 현대 파워텍 주식회사 | Power train for automatic transmission |
| US20090312139A1 (en) * | 2008-06-13 | 2009-12-17 | Hyundai Motor Company | Powertrain of an Automatic Transmission |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107559391A (en) * | 2016-06-30 | 2018-01-09 | 现代自动车株式会社 | Epicyclic train for the automatic transmission of vehicle |
| CN107559391B (en) * | 2016-06-30 | 2021-04-23 | 现代自动车株式会社 | Planetary gear train of automatic transmission for vehicle |
| CN107620786A (en) * | 2016-07-13 | 2018-01-23 | 现代自动车株式会社 | Epicyclic train for the automatic transmission of vehicle |
| CN107514445A (en) * | 2017-08-28 | 2017-12-26 | 无锡职业技术学院 | Based on improvement lever method six speed transmission |
| CN107514445B (en) * | 2017-08-28 | 2024-01-09 | 无锡职业技术学院 | Six-speed transmission based on improved lever method |
| WO2019128411A1 (en) * | 2017-12-29 | 2019-07-04 | 广州汽车集团股份有限公司 | Three-planet-row automatic transmission and vehicle |
| CN111637202A (en) * | 2020-06-28 | 2020-09-08 | 柳州职业技术学院 | Eight-speed automatic transmission and power transmission method thereof |
| CN111637202B (en) * | 2020-06-28 | 2024-05-07 | 柳州职业技术学院 | Eight-speed automatic transmission and power transmission method thereof |
Also Published As
| Publication number | Publication date |
|---|---|
| CN105485271B (en) | 2018-01-05 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101871520B (en) | Multi-speed transmission | |
| CN101178112B (en) | Eight speed powertrain of automatic transmission for vehicle | |
| CN102434638B (en) | Multi-speed transmission having stacked planetary gear sets | |
| CN102644703B (en) | Multi-speed transmission | |
| CN101493134B (en) | Ten-speed transmission | |
| CN101344154B (en) | Multi-speed transmission | |
| CN104896038B (en) | Multi-shifting speed variator and its epicyclic train | |
| CN101303069B (en) | Multi-speed transmission | |
| CN101513836B (en) | Multi-speed transaxle for a front wheel drive vehicle | |
| CN101235879A (en) | Multi-speed transmission | |
| CN104024689A (en) | 10-shift power train of automatic transmission for vehicle | |
| CN101915289A (en) | Multi-speed transmission with four planetary gear set | |
| CN101349334B (en) | Multi-speed transmission | |
| KR20070095631A (en) | Automatic transmission's power train | |
| KR102406132B1 (en) | Planetary gear train of automatic transmission for vehicles | |
| KR102451907B1 (en) | Planetary gear train of automatic transmission for vehicles | |
| CN105485271A (en) | Automatic transmission and planetary gear train thereof | |
| CN106151416A (en) | Epicyclic train for the automatic transmission of vehicle | |
| CN101240833B (en) | Multi-speed transmission | |
| CN103775577A (en) | Planetary gear train of automatic transmission for vehicle | |
| CN205013605U (en) | Derailleurs that keep off more and epicyclie gear thereof | |
| KR102359923B1 (en) | Planetary gear train of automatic transmission for vehicles | |
| KR102518587B1 (en) | Planetary gear train of automatic transmission for vehicles | |
| CN102588534A (en) | Clutch and gear arrangement for a front wheel drive vehicle | |
| CN101782134B (en) | Multi-speed transmission having three planetary gear sets |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |