CN106641135A - Twelve-gear automatic transmission - Google Patents
Twelve-gear automatic transmission Download PDFInfo
- Publication number
- CN106641135A CN106641135A CN201611169038.7A CN201611169038A CN106641135A CN 106641135 A CN106641135 A CN 106641135A CN 201611169038 A CN201611169038 A CN 201611169038A CN 106641135 A CN106641135 A CN 106641135A
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- China
- Prior art keywords
- clutch
- gear ring
- planet
- gear
- brake
- 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.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
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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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
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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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0078—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratio comprising twelve or more forward speeds
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
- F16H2200/0086—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising two reverse speeds
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2048—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with seven engaging means
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention discloses a twelve-gear automatic transmission. The twelve-gear automatic transmission comprises an input shaft, a clutch assembly and a planet row assembly; the clutch assembly comprises a first clutch and a second clutch, and the second clutch is located outside the first clutch and shares a piston shell with the first clutch; the planet row assembly comprises a first planet row, a second planet row, a third planet row and a fourth planet row; and four brakes comprise the first brake, the second brake, the three brake and the fourth brake. According to the twelve-gear automatic transmission, power output of twelve forward gears and two reverse gears is achieved, and meanwhile, the structure of the whole twelve-gear automatic transmission can be more compact; the twelve-gear automatic transmission has the advantage of being simple and compact in structure, and the space occupied by a gearbox is reduced; and in addition, the twelve-gear automatic transmission has the advantages of being wide in drive ratio range, small in inter ratio and the like.
Description
Technical field
The present invention relates to mechanical speed change drive technology field, and in particular to a kind of 12 speed automatic transmissions.
Background technology
Transmission system is one of element of vehicle, for transmitting engine power, and the energy in straight-line travelling
Change the speed and tractive force of vehicle on request, transmission system will also realize reversing and parking of vehicle etc..Speed changer is transmission
A critically important part in system.Planet is reached as the power Jing fluid torque-converters such as vehicle automatic transmission, internal combustion engine certainly
The input shaft of dynamic speed changer, by current gear speed change after, power is exported from output shaft, and Jing differential mechanisms reach left and right driving
Wheel, and the speed changer scheme that speed changer great majority are made up of multiple planet rows, brake and clutch.At present, market is got on the bus
Less with planetary automatic transmission gear, ratio coverage is less, and to make up the vacancy in market, need to design a kind of has more gear
Planetary automatic transmission.
The content of the invention
The present invention is intended to provide a kind of gear range is big, excellent performance and can meet wheeled heavy-duty vehicle use requirement
12 gear planetary automatic transmissions, to solve prior art in the presence of technical problem.
The present invention is achieved by following technical solution：
A kind of 12 speed automatic transmissions, including input shaft, clutch assembly and planet row assembly；The clutch assembly
Including first clutch and second clutch, second clutch is located at first clutch outside and shares a piston shell；
The planet row assembly includes that first planet row, the second planet row, third planet row and fourth planet arrange four rows
Star is arranged；
First brake, second brake, four brakes of the 3rd brake and the 4th brake；
First planet row includes the first sun gear, the first gear ring, the first row carrier, and second planet row includes the
Two sun gears, the second gear ring, the second planet carrier, the third planet row includes the 3rd sun gear, the 3rd gear ring, third planet
Frame, the fourth planet row includes the 4th sun gear, the 4th gear ring, fourth line carrier；
Also include the 3rd clutch, jackshaft, connecting shaft and output shaft；
The first clutch is connected with jackshaft, and second clutch is connected with the first sun gear, the drive of second clutch
Dynamic hub is connected with the second planet carrier, and the first gear ring is connected by the first brake, the first row carrier with the second gear ring；Second
Gear ring is braked by second brake, and the second sun gear is connected with jackshaft, and the second planet carrier is connected with the 3rd gear ring；3rd tooth
Circle is connected by the 3rd brake, the 3rd sun gear with jackshaft, and the third line carrier is connected with connecting shaft；Connecting shaft and the
Three clutches connect, and the 3rd clutch is connected with the 4th gear ring；4th gear ring by the 4th brake, the 4th sun gear with
Connecting shaft connects, and fourth line carrier is connected with output shaft.
Between the drive hub of the second clutch and the second planet carrier, between the second sun gear and jackshaft, the 3rd too
Between sun wheel and jackshaft, between the third line carrier and connecting shaft, between connecting shaft and the 3rd clutch, the 4th sun gear and company
Pass through spline connection between spindle.
Between second gear ring and second brake, between the 3rd gear ring and the 3rd brake, the 4th gear ring and the 4th
Axially position is carried out using back-up ring between brake.
The first row carrier is connected with the second gear ring by helical teeth, and carries out axially position by thrust bearing.
Second planet carrier is connected with the 3rd gear ring by helical teeth, and carries out axially position by thrust bearing.
First gear ring is floating gear ring.
The invention has the beneficial effects as follows：
Compared with prior art, 12 speed automatic transmissions that the present invention is provided, using four planet rows, four brakes
12 drive shifts and 2 retroversion gears are realized with the scheme of three clutches, existing automatic transmission for vehicles gear is not only solved
It is less, the problems such as ratio coverage is less, due also to reducing parts to realize the integrally-built compactedness of gearbox, reduce change
The volume and weight of fast case, and then realize lightweight；And gearratio is uniform, excellent performance.
Description of the drawings
Fig. 1 is the structural representation of the present invention；
In figure：1- input shafts, the sun gears of 2- first, 3- the first row carrier, the gear rings of 4- first, the sun gears of 5- second, 6-
Two planet carriers, the gear rings of 7- second, 8- jackshafts, 9- the third line gear rings, 10- the third line carrier, the sun gears of 11- the 3rd, 12- connections
Axle, the gear rings of 13- the 4th, 14- fourth line carrier, the sun gears of 15- the 4th, 16- output shafts, P1- first planet row, the rows of P2- second
Star row, P3- third planets row, P4- fourth planets row, the brakes of Z1- first, Z2- second brakes, the brakes of Z3- the 3rd,
The brakes of Z4- the 4th, L1- first clutches, L2- second clutches, the clutches of L3- the 3rd, A- clutch assemblies, B- planet rows
Assembly.
Specific embodiment
Technical scheme is described further below in conjunction with drawings and Examples, but required protection domain
It is not limited to described；
As shown in figure 1,12 speed automatic transmissions that the present invention is provided, including input shaft 1, clutch assembly A and planet
Row assembly B；The clutch assembly A include first clutch L1 and second clutch L2, second clutch L2 be located at first from
Clutch L1 outside and a shared piston shell；
The planet row assembly B includes first planet row P1, the second planet row P2, third planet row P3 and fourth planet row
Tetra- planet rows of P4；
First brake Z1, second brake Z2, tetra- brakes of the 3rd brake Z3 and the 4th brake Z4；
The first planet row P1 includes the first sun gear 2, the first gear ring 4, the first row carrier 3, second planet row
P2 includes the second sun gear 5, the second gear ring 7, the second planet carrier 6, and the third planet row P3 includes the 3rd sun gear the 11, the 3rd
Gear ring 9, the third line carrier 10, the fourth planet row P4 includes the 4th sun gear 15, the 4th gear ring 13, fourth line carrier 14；
Also include the 3rd clutch L3, jackshaft 8, connecting shaft 12 and output shaft 16；
The first clutch L1 is connected with jackshaft 8, and second clutch L2 is connected with the first sun gear 2, the second clutch
The drive hub of device L2 is connected with the second planet carrier 6, and the first gear ring 4 is braked by the first brake Z1, the first row carrier 3 and second
Gear ring 7 connects；Second gear ring 7 is braked by second brake Z2, and the second sun gear 5 is connected with jackshaft 8, the second planet carrier 6
It is connected with the 3rd gear ring 9；3rd gear ring 9 is braked by the 3rd brake Z3, and the 3rd sun gear 11 is connected with jackshaft 8, and the 3rd
Planet carrier 10 is connected with connecting shaft 12；Connecting shaft 12 is connected with the 3rd clutch L3, and the 3rd clutch L3 connects with the 4th gear ring 13
Connect；4th gear ring 13 is braked by the 4th brake Z4, and the 4th sun gear 15 is connected with connecting shaft 12, fourth line carrier 14 with it is defeated
Shaft 16 is connected.
Between the drive hub of the second clutch L2 and the second planet carrier 6, between the second sun gear 5 and jackshaft 8,
Between three sun gears 11 and jackshaft 8, between the third line carrier 10 and connecting shaft 12, the clutch L3 of connecting shaft 12 and the 3rd it
Between, between the 4th sun gear 15 and connecting shaft 12 pass through spline connection.
Between second gear ring 7 and second brake Z2, between the 3rd gear ring 9 and the 3rd brake Z3, the 4th gear ring
13 and the 4th carry out axially position between brake Z4 using back-up ring.
The first row carrier 3 is connected with the second gear ring 7 by helical teeth, and carries out axially position by thrust bearing.
Second planet carrier 6 is connected with the 3rd gear ring 9 by helical teeth, and carries out axially position by thrust bearing.
First gear ring 4 is floating gear ring.
Embodiment：The clutch assembly A of input shaft 1 is connected, and when first clutch C1 or second clutch C2 are combined, turns round
Square is passed at planet row assembly B.In planet row assembly B, can be with by controlling the combination of different braking device and clutch
Realize that the combination of each shelves moment of torsion transmission, each gear brake and clutch is as shown in table 1.
1st, neutral gear, the 3rd brake Z3 is combined under pressure oil effect, and the 3rd gear ring 9 is braked, and the 4th brake Z4 is in pressure
The effect of power oil is lower to be combined, and the 4th gear ring 13 is braked.Because the first rotary clutch L1 and the second rotary clutch L2 is in disengagement
State, the moment of torsion of the input of input shaft 1 can not pass to planet assembly B, whole speed changer inactivity output.
2nd, one grade, the first rotary clutch L1, the 3rd brake Z3, the 4th brake Z4 are combined under pressure oil effect,
3rd gear ring 9 and the 4th gear ring 13 are braked.Moment of torsion Jing the first rotary clutch L1 being input into by input shaft 1 pass to jackshaft 8,
The 3rd sun gear 11 for arranging P3 by third planet passes to the third line carrier 10, and by the third line carrier 10 connecting shaft is passed to
12, the 4th sun gear 15 for arranging P4 by fourth planet passes to fourth line carrier 14, finally because fourth line carrier 14 is connected
Output shaft 16 by torque output.
3rd, two grades, the first rotary clutch L1, second brake Z2 and the 4th brake Z4 are combined under pressure oil effect,
Second gear ring 7 and the 4th gear ring 13 are braked.The moment of torsion being input into by input shaft 1 passes to jackshaft by the first rotary clutch L1
8, a part of moment of torsion passes to the second planet carrier 6 by second sun gear 5 of the second planet row P2, is transmitted by the second planet carrier 6
To the 3rd gear ring 9, another part moment of torsion Jing jackshafts 8 are directly passed to the 3rd sun gear 11 that third planet arranges P3, due to the
3rd gear ring 9 of three planet row P3 is differential with the 3rd sun gear 11, and moment of torsion Jing the third lines carrier 10 passes to connecting shaft 12, leads to
The 4th sun gear 15 for crossing fourth planet row P4 passes to fourth line carrier 14, finally by fourth line carrier 14 by torque output.
4th, third gear, the first rotary clutch L1, the first brake Z1 and the 4th brake Z4 are combined under pressure oil effect,
First gear ring 4 and the 4th gear ring 13 are braked.The moment of torsion part being input into by input shaft 1 is passed to by the second rotary clutch L2
First sun gear 2, Jing the first rows carrier 3 passes to the second gear ring 7, and another part moment of torsion is transmitted by the first rotary clutch L1
The second sun gear 5 and third planet to the second planet row P2 on jackshaft arranges the 3rd sun gear 11 of P3, due to the second planet
Second sun gear 5 of row P2 is differential with the second gear ring 7, and the second planet row P2 is passed to by the output torque of the second planet carrier 6
Third planet arranges the 3rd gear ring 9 of P3, and the 3rd gear ring 9 of P3 and the 3rd sun gear of third planet row P3 are arranged due to third planet
11 it is differential, moment of torsion Jing the third lines carrier 10 passes to connecting shaft 12, by fourth planet arrange P4 the 4th sun gear 15 transmit
To fourth line carrier 14, finally by fourth line carrier 14 by torque output.
5th, fourth gear, the first rotary clutch L1, the second rotary clutch L2 and the 4th brake 13 are under pressure oil effect
With reference to the 4th gear ring 13 is braked.The moment of torsion part being input into by input shaft 1 passes through second rotary clutch L2 the second planet carriers of Jing
6 pass to the 3rd gear ring 9, and another part moment of torsion passs the 3rd sun gear that third planet arranges P3 by the first rotary clutch L1
11, because the 3rd sun gear 11, the 3rd gear ring 9 and the third line carrier 10 and input shaft 1 rotate at the same speed, moment of torsion is by the third line carrier
10 press 1：1 ratio passes to connecting shaft 12, and the 4th sun gear 15 for arranging P4 by fourth planet passes to fourth line carrier 14,
It is last by fourth line carrier 14 by torque output.
6th, five grades, the first rotary clutch L1, the 3rd brake Z3, the 3rd rotary clutch L3 are tied under pressure oil effect
Close, the 3rd gear ring 9 is braked.Moment of torsion Jing the first rotary clutch L1 being input into by input shaft 1 pass to jackshaft 8, by the 3rd
3rd sun gear 11 of planet row P3 passes to the third line carrier 10, and the moment of torsion part being input into by the third line carrier 10 is by the
Three rotary clutch L3 pass to the 4th gear ring 13 that fourth planet arranges P4, and another part moment of torsion passes to the by connecting shaft 12
4th sun gear 15 of four planet row P4, the 4th gear ring 13 of fourth planet row P4 and the synchronized rotation of the 4th sun gear 15, turn round
Square passes to fourth line carrier 14, finally by fourth line carrier 14 by torque output.
7th, six grades, the second rotary clutch L2, the first brake Z1 and the 4th brake Z4 are combined under pressure oil effect,
First gear ring 4 and the 4th gear ring 13 are braked.The moment of torsion part being input into by input shaft 1 is passed to by the second rotary clutch L2
First sun gear 2, Jing the first rows carrier 4 passes to the second gear ring 7, is passed by the planetary gear of Jing the second planet row P2 of the second gear ring 7
The second sun gear 5 is passed, the 3rd sun gear 11 is passed to by the Jing jackshafts 8 of the second sun gear 5, another part moment of torsion passes through second
Rotary clutch L2 passes to the second planet carrier 6, then passes to the 3rd gear ring 9, due to the 3rd gear ring 9 and the 3rd sun gear 11
Differential, moment of torsion passes to connecting shaft 12 by the third line carrier 10, and the 4th sun gear 15 for arranging P4 by fourth planet passes to the
Four planet carriers 14, finally by fourth line carrier 14 by torque output.
8th, seven grades, the second rotary clutch L2, second brake Z2 and the 4th brake Z4 are combined under pressure oil effect,
Second gear ring 4 and the 4th gear ring 13 are braked.The moment of torsion being input into by input shaft 1 passes to the second row by the second rotary clutch L2
Carrier 6, is then delivered separately to the 3rd gear ring 9 and the second sun gear 5 by the second planet carrier 6, the moment of torsion of the second sun gear 5 Jing again
Jackshaft 8 passes to the 3rd sun gear 11, and because the 3rd gear ring 9 is differential with the 3rd sun gear 11, moment of torsion is by the third line carrier
10 pass to connecting shaft 12, and the 4th sun gear 15 for arranging P4 by fourth planet passes to fourth line carrier 14, finally by the 4th
Planet carrier 14 is by torque output.
9th, eight grades, the first rotary clutch L1, second brake Z2 and the 3rd clutch L3 are combined under pressure oil effect,
Second gear ring 7 is braked.The moment of torsion being input into by input shaft 1 passes to jackshaft 8, a part of moment of torsion by the first rotary clutch L1
Second planet carrier 6 is passed to by second sun gear 5 of the second planet row P2, the 3rd gear ring 9 is passed to by the second planet carrier 6,
Another part moment of torsion Jing jackshafts 8 are directly passed to the 3rd sun gear 11 that third planet arranges P3, because third planet arranges P3's
3rd gear ring 9 is differential with the 3rd sun gear 11, and moment of torsion passes to the third line carrier 10, the moment of torsion being input into by the third line carrier 10
A part passes to the 4th gear ring 13 that fourth planet arranges P4 by the 3rd rotary clutch L3, and another part moment of torsion is by connection
Axle 12 passes to the 4th sun gear 15 that fourth planet arranges P4, because fourth planet arranges the 4th gear ring 13 and the 4th sun gear of P4
15 synchronized rotation, moment of torsion passes to fourth line carrier 14, finally by fourth line carrier 14 by torque output.
10th, nine grades, the first rotary clutch L1, the first brake Z1 and the 3rd clutch L3 are tied under pressure oil effect
Close, the first gear ring 4 is braked.The moment of torsion part being input into by input shaft 1 passes to first sun by the second rotary clutch L2
Wheel 2, Jing the first rows carrier 3 passes to the second gear ring 7, and another part moment of torsion passes to jackshaft by the first rotary clutch L1
Second sun gear 5 of upper second planet row P2 and third planet arrange the 3rd sun gear 11 of P3, due to the of the second planet row P2
Two sun gears 5 are differential with the second gear ring 7, and the second planet row P2 passes to third planet by the output torque of the second planet carrier 6
3rd gear ring 9 of row P3, because the 3rd gear ring 9 that third planet arranges P3 arranges the difference of the 3rd sun gear 11 of P3 with third planet
Dynamic, moment of torsion passes to the third line carrier 10, and the moment of torsion part being input into by the third line carrier 10 passes through the 3rd rotary clutch L3
The 4th gear ring 13 that fourth planet arranges P4 is passed to, another part moment of torsion passes to fourth planet arranges P4 the by connecting shaft 12
Four sun gears 15, the 4th gear ring 13 of P4 and the synchronized rotation of the 4th sun gear 15 are arranged due to fourth planet, and moment of torsion passes to the
Four planet carriers 14, finally by fourth line carrier 14 by torque output.
11st, ten grades, the first rotary clutch L1, the second rotary clutch L2 and the 3rd clutch L3 are under pressure oil effect
With reference to.The moment of torsion part being input into by input shaft 1 passes to the 3rd gear ring by second the second planet carriers of rotary clutch L2 Jing 6
9, another part moment of torsion passs the 3rd sun gear 11 that third planet arranges P3 by the first rotary clutch L1, due to the 3rd sun
The 11, the 3rd gear ring 9 of wheel and the third line carrier 10 rotate at the same speed with input shaft 1, and moment of torsion presses 1：1 ratio passes to the third line carrier
10, the moment of torsion part being input into by the third line carrier 10 passes to the fourth planet arranges P4 the 4th by the 3rd rotary clutch L3
Gear ring 13, another part moment of torsion passes to the 4th sun gear 15 that fourth planet arranges P4 by connecting shaft 12, due to fourth planet
4th gear ring 13 of row P4 and the synchronized rotation of the 4th sun gear 15, moment of torsion passes to fourth line carrier 14, finally by fourth line
Carrier 14 presses 1：1 ratio is by torque output.
12nd, 11 grades, the second rotary clutch L2, the first brake Z1 and the 3rd clutch L3 are tied under pressure oil effect
Close, the first gear ring 4 is braked.The moment of torsion part being input into by input shaft 1 passes to first sun by the second rotary clutch L2
Wheel 2, Jing the first rows carrier 4 passes to the second gear ring 7, and by the planetary gear of Jing the second planet row P2 of the second gear ring 7 second is passed to
Sun gear 5, by the Jing jackshafts 8 of the second sun gear 5 the 3rd sun gear 11 is passed to, and another part moment of torsion passes through the second rotation clutch
Device L2 passes to the second planet carrier 6, then passes to the 3rd gear ring 9, because the 3rd gear ring 9 is differential with the 3rd sun gear 11, turns round
Square passes to the third line carrier 10, and the moment of torsion part being input into by the third line carrier 10 is passed to by the 3rd rotary clutch L3
Fourth planet arranges the 4th gear ring 13 of P4, and another part moment of torsion passes to the 4th sun that fourth planet arranges P4 by connecting shaft 12
Wheel 15, the 4th gear ring 13 of P4 and the synchronized rotation of the 4th sun gear 15 are arranged due to fourth planet, and moment of torsion passes to fourth planet
Frame 14, finally by fourth line carrier 14 by torque output.
13rd, 12 grades, the second rotary clutch L2, the first brake Z1 and the 3rd rotary clutch L3 are acted in pressure oil
Lower combination, the first gear ring 4 is braked.The moment of torsion part being input into by input shaft 1 passes to first by the second rotary clutch L2
Sun gear 2, Jing the first rows carrier 4 passes to the second gear ring 7, is passed to by the planetary gear of Jing the second planet row P2 of the second gear ring 7
Second sun gear 5, by the Jing jackshafts 8 of the second sun gear 5 the 3rd sun gear 11 is passed to, and another part moment of torsion is by the second rotation
Clutch L2 passes to the second planet carrier 6, then passes to the 3rd gear ring 9, due to the 3rd gear ring 9 and the difference of the 3rd sun gear 11
Dynamic, moment of torsion passes to the third line carrier 10, and the moment of torsion part being input into by the third line carrier 10 passes through the 3rd rotary clutch L3
The 4th gear ring 13 that fourth planet arranges P4 is passed to, another part moment of torsion passes to fourth planet arranges P4 the by connecting shaft 12
Four sun gears 15, the 4th gear ring 13 of P4 and the synchronized rotation of the 4th sun gear 15 are arranged due to fourth planet, and moment of torsion passes to the
Four planet carriers 14, finally by fourth line carrier 14 by torque output.
14th, fall one grade, the first brake Z1, the 3rd brake Z3 and the 4th brake Z4 pressure oil effect under combine,
First gear ring 4, the 3rd gear ring 9 and the 4th gear ring 13 are braked, and the moment of torsion being input into by input shaft 1 is passed by the second rotary clutch L2
The first sun gear 2 is passed, then Jing the first rows carrier 3 passes to the second gear ring 7, then by Jing the second planet row P2 of the second gear ring 7
Planetary gear pass to the second sun gear 5, because the second planet carrier 6 and the 3rd gear ring 9 are braked, the second sun gear 5 is reversely rotated,
And drive the sun gear 11 of jackshaft 8 and the 3rd to reversely rotate, so that the third line carrier 10 is also reversely rotated, moment of torsion is by the third line
Carrier 10 passes to connecting shaft 12, by fourth planet arrange P4 the 4th sun gear 15 pass to fourth line carrier 14, finally by
Torque output is realized reverse gear function by fourth line carrier 14.
15th, fall two grades, the first brake Z1, the 3rd brake Z3 and the 4th brake Z4 pressure oil effect under combine,
First gear ring 4, the 3rd gear ring 9 and the 4th gear ring 13 are braked, and the moment of torsion being input into by input shaft 1 is passed by the second rotary clutch L2
The first sun gear 2 is passed, then Jing the first rows carrier 3 passes to the second gear ring 7, then by Jing the second planet row P2 of the second gear ring 7
Planetary gear pass to the second sun gear 5, because the second planet carrier 6 and the 3rd gear ring 9 are braked, the second sun gear 5 is reversely rotated,
And drive the sun gear 11 of jackshaft 8 and the 3rd to reversely rotate, so that the third line carrier 10 is also reversely rotated, by the third line carrier
A moment of torsion part for 10 inputs passes to the 4th gear ring 13 that fourth planet arranges P4, another part by the 3rd rotary clutch L3
Moment of torsion passes to the 4th sun gear 15 that fourth planet arranges P4 by connecting shaft 12, because fourth planet arranges the 4th gear ring 13 of P4
With the synchronized rotation of the 4th sun gear 15, moment of torsion passes to fourth line carrier 14, finally by fourth line carrier 14 by torque output,
Realize reverse gear function.
Table 1：The combination situation table of each gear clutch and brake
" " represents that controls is combined in table.
To make satisfaction control simple principle, each gear according to the form below 2 can also be combined.Under this combination,
Can be achieved with rising a shelves or drop one by adjusting a clutch or brake in each high-grade and low-grade drive shift
The function of individual shelves.
Table 2：The combination situation table of each gear clutch and brake.
" " represents that controls is combined in table.
Above-described embodiment is only a preferred embodiment of the present invention, and in for limiting protection scope of the present invention, it is all
Deformation, modification or equivalent for being made on the basis of technical scheme etc., all should fall into the protection model of the present invention
Enclose.
Claims (6)
1. a kind of 12 speed automatic transmissions, it is characterised in that：Including input shaft (1), clutch assembly (A) and planet row assembly
(B)；The clutch assembly (A) includes first clutch (L1) and second clutch (L2), and second clutch (L2) is positioned at the
One clutch (L1) outside and a shared piston shell；
The planet row assembly (B) includes first planet row (P1), the second planet row (P2), third planet row (P3) and fourth line
Star arranges (P4) four planet rows；
First brake (Z1), second brake (Z2), the 3rd brake (Z3) and the 4th four brakes of brake (Z4)；
First planet row (P1) includes the first sun gear (2), the first gear ring (4), the first row carrier (3), second row
Star row (P2) includes the second sun gear (5), the second gear ring (7), the second planet carrier (6), and third planet row (P3) includes the
Three sun gears (11), the 3rd gear ring (9), the third line carrier (10), fourth planet row (P4) include the 4th sun gear (15),
4th gear ring (13), fourth line carrier (14)；
Also include the 3rd clutch (L3), jackshaft (8), connecting shaft (12) and output shaft (16)；
The first clutch (L1) is connected with jackshaft (8), and second clutch (L2) is connected with the first sun gear (2), and second
The drive hub of clutch (L2) is connected with the second planet carrier (6), and the first gear ring (4) is braked by the first brake (Z1), and first
Planet carrier (3) is connected with the second gear ring (7)；Second gear ring (7) by second brake (Z2) brake, the second sun gear (5) with
Jackshaft (8) connects, and the second planet carrier (6) is connected with the 3rd gear ring (9)；3rd gear ring (9) is made by the 3rd brake (Z3)
Dynamic, the 3rd sun gear (11) is connected with jackshaft (8), and the third line carrier (10) is connected with connecting shaft (12)；Connecting shaft (12) with
3rd clutch (L3) connects, and the 3rd clutch (L3) is connected with the 4th gear ring (13)；4th gear ring (13) is by the 4th braking
Device (Z4) is braked, and the 4th sun gear (15) is connected with connecting shaft (12), and fourth line carrier (14) is connected with output shaft (16).
2. 12 speed automatic transmission according to claim 1, it is characterised in that：The driving of the second clutch (L2)
Between hub and the second planet carrier (6), between the second sun gear (5) and jackshaft (8), the 3rd sun gear (11) and jackshaft (8)
Between, between the third line carrier (10) and connecting shaft (12), between connecting shaft (12) and the 3rd clutch (L3), the 4th sun gear
(15) spline connection is passed through and connecting shaft (12) between.
3. 12 speed automatic transmission according to claim 1, it is characterised in that：Second gear ring (7) and the second system
Between dynamic device (Z2), between the 3rd gear ring (9) and the 3rd brake (Z3), between the 4th gear ring (13) and the 4th brake (Z4)
Axially position is carried out using back-up ring.
4. 12 speed automatic transmission according to claim 1, it is characterised in that：The first row carrier (3) and second
Gear ring (7) is connected by helical teeth, and carries out axially position by thrust bearing.
5. 12 speed automatic transmission according to claim 1, it is characterised in that：Second planet carrier (6) and the 3rd
Gear ring (9) is connected by helical teeth, and carries out axially position by thrust bearing.
6. 12 speed automatic transmission according to claim 1, it is characterised in that：First gear ring (4) is floating tooth
Circle.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201611169038.7A CN106641135B (en) | 2016-12-16 | 2016-12-16 | A kind of 12 speed automatic transmissions |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201611169038.7A CN106641135B (en) | 2016-12-16 | 2016-12-16 | A kind of 12 speed automatic transmissions |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106641135A true CN106641135A (en) | 2017-05-10 |
| CN106641135B CN106641135B (en) | 2019-05-14 |
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ID=58823105
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201611169038.7A Active CN106641135B (en) | 2016-12-16 | 2016-12-16 | A kind of 12 speed automatic transmissions |
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| Country | Link |
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| CN (1) | CN106641135B (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109654180A (en) * | 2019-02-15 | 2019-04-19 | 络优集成科技(无锡)有限公司 | Planet and dead axle compound variable speed mechanism |
| CN111536211A (en) * | 2020-06-23 | 2020-08-14 | 北京航空航天大学 | Multi-gear planetary gear speed change device |
| CN111998043A (en) * | 2020-09-30 | 2020-11-27 | 宝能(西安)汽车研究院有限公司 | Multi-gear automatic transmission and vehicle with same |
| CN112081884A (en) * | 2020-09-11 | 2020-12-15 | 陕西法士特齿轮有限责任公司 | Eleven-gear transmission based on planetary gear train |
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|---|---|---|---|---|
| US20080207382A1 (en) * | 2007-02-28 | 2008-08-28 | Aisin Aw Co., Ltd. | Automatic transmission |
| CN103423336A (en) * | 2012-05-18 | 2013-12-04 | 通用汽车环球科技运作有限责任公司 | Electromechanical clutch and transmission |
| CN104033549A (en) * | 2014-06-11 | 2014-09-10 | 同济大学 | Eight-gear transmission |
| CN104033546A (en) * | 2014-06-11 | 2014-09-10 | 同济大学 | Eleven-gear transmission |
| JP2015059619A (en) * | 2013-09-19 | 2015-03-30 | アイシン精機株式会社 | Automatic transmission |
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- 2016-12-16 CN CN201611169038.7A patent/CN106641135B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20080207382A1 (en) * | 2007-02-28 | 2008-08-28 | Aisin Aw Co., Ltd. | Automatic transmission |
| CN103423336A (en) * | 2012-05-18 | 2013-12-04 | 通用汽车环球科技运作有限责任公司 | Electromechanical clutch and transmission |
| JP2015059619A (en) * | 2013-09-19 | 2015-03-30 | アイシン精機株式会社 | Automatic transmission |
| CN104033549A (en) * | 2014-06-11 | 2014-09-10 | 同济大学 | Eight-gear transmission |
| CN104033546A (en) * | 2014-06-11 | 2014-09-10 | 同济大学 | Eleven-gear transmission |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109654180A (en) * | 2019-02-15 | 2019-04-19 | 络优集成科技(无锡)有限公司 | Planet and dead axle compound variable speed mechanism |
| CN111536211A (en) * | 2020-06-23 | 2020-08-14 | 北京航空航天大学 | Multi-gear planetary gear speed change device |
| CN111536211B (en) * | 2020-06-23 | 2020-10-16 | 北京航空航天大学 | Multi-gear planetary gear speed change device |
| CN112081884A (en) * | 2020-09-11 | 2020-12-15 | 陕西法士特齿轮有限责任公司 | Eleven-gear transmission based on planetary gear train |
| CN112081884B (en) * | 2020-09-11 | 2021-07-27 | 陕西法士特齿轮有限责任公司 | Eleven-gear transmission based on planetary gear train |
| CN111998043A (en) * | 2020-09-30 | 2020-11-27 | 宝能(西安)汽车研究院有限公司 | Multi-gear automatic transmission and vehicle with same |
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| Publication number | Publication date |
|---|---|
| CN106641135B (en) | 2019-05-14 |
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