CN106641135B - A kind of 12 speed automatic transmissions - Google Patents
A kind of 12 speed automatic transmissions Download PDFInfo
- Publication number
- CN106641135B CN106641135B CN201611169038.7A CN201611169038A CN106641135B CN 106641135 B CN106641135 B CN 106641135B CN 201611169038 A CN201611169038 A CN 201611169038A CN 106641135 B CN106641135 B CN 106641135B
- Authority
- CN
- China
- Prior art keywords
- clutch
- planet
- gear ring
- brake
- 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.)
- Active
Links
- 230000005540 biological transmission Effects 0.000 title claims abstract description 23
- 239000000969 carrier Substances 0.000 claims description 115
- 230000000694 effects Effects 0.000 description 17
- 230000001360 synchronised Effects 0.000 description 7
- 238000002485 combustion reaction Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000006011 modification reaction Methods 0.000 description 1
- 230000001264 neutralization Effects 0.000 description 1
- 230000000630 rising Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
-
- 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
-
- 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
-
- 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
-
- 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
Abstract
The invention discloses a kind of 12 speed automatic transmissions, including input shaft, clutch assembly and planet row assembly；Clutch assembly includes first clutch and second clutch, and second clutch is located on the outside of first clutch and shares a piston shell；Planet row assembly includes that the first planet row, the second planet row, third planet row and fourth planet arrange four planet rows；Four first brake, second brake, third brake and the 4th brake brakes.The power output of 12 drive shifts and two reverse gears can be achieved in the present invention, while complete machine structure can be made more compact.And have the advantages that simple and compact for structure, reduce gearbox the space occupied；Additionally have many advantages, such as gear range it is wide, than small.
Description
Technical field
The present invention relates to mechanical speed change transmission technical fields, and in particular to a kind of 12 speed automatic transmissions.
Background technique
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 as required, transmission system will also realize reversing and the parking etc. of vehicle.Speed changer is transmission
Critically important a part in system.As vehicle automatic transmission, the power such as internal combustion engine reach planet certainly through fluid torque-converter
The input shaft of dynamic speed changer exports power from output shaft, and reach left and right driving through differential mechanism after current gear speed change
Wheel, and the speed changer scheme that most of speed changer is made of multiple planet rows, brake and clutch.Currently, market is got on the bus
Less with planetary automatic transmission gear, ratio coverage is smaller, and for the vacancy for making up market, need to design a kind of has more gear
Planetary automatic transmission.
Summary of the invention
The present invention is intended to provide a kind of gear range is big, has excellent performance and can meet wheeled heavy-duty vehicle requirement
12 gear planetary automatic transmissions, the technical issues of to solve in the presence of the prior art.
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 on the outside of first clutch and shares a piston shell；
The planet row assembly includes that the first planet row, the second planet row, third planet row and fourth planet arrange four rows
Star row；
Four first brake, second brake, third brake and the 4th brake brakes；
First planet row includes the first sun gear, the first gear ring, first planet carrier, and second planet row includes the
Two sun gears, the second gear ring, the second planet carrier, the third planet row includes third sun gear, third gear ring, third planet
Frame, the fourth planet row includes the 4th sun gear, the 4th gear ring, fourth line carrier；
It further include third clutch, jackshaft, connecting shaft and output shaft；
The first clutch and intermediate axis connection, second clutch are connect with the first sun gear, the drive of second clutch
Dynamic hub is connect with the second planet carrier, and the first gear ring is connect by the first brake, first planet carrier with the second gear ring；Second
Gear ring is braked by second brake, and the second sun gear and intermediate axis connection, the second planet carrier are connect with third gear ring；Third tooth
Circle is by third brake, third sun gear and intermediate axis connection, third planet carrier with connect axis connection；Connecting shaft and the
The connection of three clutches, third clutch are connect with the 4th gear ring；4th gear ring by the 4th brake, the 4th sun gear with
Axis connection is connected, 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, third too
Between sun wheel and jackshaft, between third planet carrier and connecting shaft, between connecting shaft and third clutch, the 4th sun gear and company
It is connected by spline between spindle.
Between second gear ring and second brake, between third gear ring and third brake, the 4th gear ring and the 4th
It is all made of retaining ring between brake and carries out axially position.
The first planet carrier is connect with the second gear ring by helical teeth, and carries out axially position by thrust bearing.
Second planet carrier is connect with third gear ring by helical teeth, and carries out axially position by thrust bearing.
First gear ring is floating gear ring.
The beneficial effects of the present invention are:
Compared with prior art, 12 speed automatic transmission provided by the invention, using four planet rows, four brakes
12 drive shifts and 2 retroversion gears are realized with the scheme of three clutches, not only solve existing automatic transmission for vehicles gear
Less, the problems such as ratio coverage is smaller, reduces change due also to reducing components to realize the integrally-built compactedness of gearbox
The volume and weight of fast case, and then realize lightweight；And transmission ratio is uniform, has excellent performance.
Detailed description of the invention
Fig. 1 is structural schematic diagram of the invention；
In figure: 1- input shaft, the first sun gear of 2-, 3- first planet carrier, the first gear ring of 4-, the second sun gear of 5-, 6-
Two planet carriers, the second gear ring of 7-, 8- jackshaft, 9- the third line gear ring, 10- third planet carrier, 11- third sun gear, 12- connection
Axis, the 4th gear ring of 13-, 14- fourth line carrier, the 4th sun gear of 15-, 16- output shaft, the first planet row of P1-, the second row of P2-
Star row, P3- third planet row, P4- fourth planet row, the first brake of Z1-, Z2- second brake, Z3- third brake,
The 4th brake of Z4-, L1- first clutch, L2- second clutch, L3- third clutch, A- clutch assembly, B- planet row
Assembly.
Specific embodiment
Technical solution of the present invention is described further with reference to the accompanying drawings and embodiments, but required protection scope
It is not limited to described；
As shown in Figure 1,12 speed automatic transmission provided by the invention, including input shaft 1, clutch assembly A and planet
Arrange assembly B；The clutch assembly A includes first clutch L1 and second clutch L2, second clutch L2 be located at first from
On the outside of clutch L1 and share a piston shell；
The planet row assembly B includes the first planet row P1, the second planet row P2, third planet row P3 and fourth planet row
Tetra- planet rows of P4；
Tetra- first brake Z1, second brake Z2, third brake Z3 and the 4th brake Z4 brakes；
The first planet row P1 includes the first sun gear 2, the first gear ring 4, first planet 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 third sun gear 11, third
Gear ring 9, third planet carrier 10, the fourth planet row P4 includes the 4th sun gear 15, the 4th gear ring 13, fourth line carrier 14；
It further include third clutch L3, jackshaft 8, connecting shaft 12 and output shaft 16；
The first clutch L1 is connect with jackshaft 8, and second clutch L2 is connect with the first sun gear 2, the second clutch
The drive hub of device L2 is connect with the second planet carrier 6, and the first gear ring 4 is braked by the first brake Z1, first planet 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 connect with jackshaft 8, the second planet carrier 6
It is connect with third gear ring 9；Third gear ring 9 is braked by third brake Z3, and third sun gear 11 is connect with jackshaft 8, third
Planet carrier 10 is connect with connecting shaft 12；Connecting shaft 12 is connect with third clutch L3, and third clutch L3 and the 4th gear ring 13 connect
It connects；4th gear ring 13 is braked by the 4th brake Z4, and the 4th sun gear 15 connect 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 third planet carrier 10 and connecting shaft 12, connecting shaft 12 and third clutch L3 it
Between, pass through spline between the 4th sun gear 15 and connecting shaft 12 and connect.
Between second gear ring 7 and second brake Z2, between third gear ring 9 and third brake Z3, the 4th gear ring
13 and the 4th are all made of retaining ring between brake Z4 and carry out axially position.
The first planet carrier 3 is connect with the second gear ring 7 by helical teeth, and carries out axially position by thrust bearing.
Second planet carrier 6 is connect with third gear ring 9 by helical teeth, and carries out axially position by thrust bearing.
First gear ring 4 is floating gear ring.
Embodiment: 1 clutch assembly A of input shaft is connected, and when first clutch L1 or second clutch L2 is combined, turns round
Square is passed at planet row assembly B.It, can be with by the combination of control different braking device and clutch in planet row assembly B
Realize that each shelves torque transmits, the combination of each gear brake and clutch is as shown in table 1.
1, neutral gear, third brake Z3 are combined under pressure oil effect, and third gear ring 9 is braked, and the 4th brake Z4 is being pressed
The effect of power oil is lower to be combined, the braking of the 4th gear ring 13.Since first clutch L1 and second clutch L2 is in disengaged condition, input
The torque that axis 1 inputs cannot pass to planet assembly B, entire speed changer inactivity output.
2, one grade, first clutch L1, third brake Z3, the 4th brake Z4 are combined under pressure oil effect, third
Gear ring 9 and the braking of the 4th gear ring 13.The torque inputted by input shaft 1 passes to jackshaft 8 through first clutch L1, passes through third
The third sun gear 11 of planet row P3 passes to third planet carrier 10, passes to connecting shaft 12 by third planet carrier 10, passes through
The 4th sun gear 15 of four planet row P4 passes to fourth line carrier 14, output shaft 16 finally connected due to fourth line carrier 14
Torque is exported.
3, two grades, first clutch L1, second brake Z2 and the 4th brake Z4 are combined under pressure oil effect, and second
Gear ring 7 and the braking of the 4th gear ring 13.The torque inputted by input shaft 1 passes to jackshaft 8 by first clutch L1, a part
Torque passes to the second planet carrier 6 by the second sun gear 5 of the second planet row P2, passes to third tooth by the second planet carrier 6
Circle 9, another part torque are directly passed to the third sun gear 11 of third planet row P3 through jackshaft 8, since third planet is arranged
The third gear ring 9 of P3 is differential with third sun gear 11, and torque passes to connecting shaft 12 through third planet carrier 10, passes through fourth line
The 4th sun gear 15 of star row P4 passes to fourth line carrier 14, is finally exported torque by fourth line carrier 14.
4, third gear, first clutch L1, the first brake Z1 and the 4th brake Z4 are combined under pressure oil effect, and first
Gear ring 4 and the braking of the 4th gear ring 13.The torque a part inputted by input shaft 1 passes to first sun by second clutch L2
Wheel 2 passes to the second gear ring 7 through first planet carrier 3, and another part torque passes on jackshaft the by first clutch L1
The third sun gear 11 of the second sun gear 5 and third planet the row P3 of two planet row P2, due to the second planet row P2 second too
Sun wheel 5 is differential with the second gear ring 7, and the second planet row P2 passes to third planet row P3 by 6 output torque of the second planet carrier
Third gear ring 9, due to third planet row P3 third gear ring 9 and third planet row P3 third sun gear 11 it is differential, torsion
Square passes to connecting shaft 12 through third planet carrier 10, passes to fourth line carrier by the 4th sun gear 15 that fourth planet arranges P4
14, finally torque is exported by fourth line carrier 14.
5, fourth gear, first clutch L1, second clutch L2 and the 4th brake 13 combine under pressure oil effect, and the 4th
Gear ring 13 is braked.The torque a part inputted by input shaft 1 passes to third tooth through the second planet carrier 6 by second clutch L2
Circle 9, another part torque passs the third sun gear 11 that third planet arranges P3 by first clutch L1, due to third sun gear
11, third gear ring 9 and third planet carrier 10 and input shaft 1 rotate at the same speed, and torque is transmitted by third planet carrier 10 in the ratio of 1:1
To connecting shaft 12, fourth line carrier 14 is passed to by the 4th sun gear 15 that fourth planet arranges P4, finally by fourth line carrier
14 export torque.
6, five grades, first clutch L1, third brake Z3, third clutch L3 are combined under pressure oil effect, third
Gear ring 9 is braked.The torque inputted by input shaft 1 passes to jackshaft 8 through first clutch L1, arranges the of P3 by third planet
Three sun gears 11 pass to third planet carrier 10, are passed by torque a part that third planet carrier 10 inputs by third clutch L3
Fourth planet row the 4th gear ring 13 of P4 is passed, another part torque passes to the 4th of fourth planet row P4 by connecting shaft 12
Sun gear 15, fourth planet arrange the synchronized rotation of the 4th gear ring 13 and the 4th sun gear 15 of P4, and torque passes to fourth planet
Frame 14 is finally exported torque by fourth line carrier 14.
7, six grades, second clutch L2, the first brake Z1 and the 4th brake Z4 are combined under pressure oil effect, and first
Gear ring 4 and the braking of the 4th gear ring 13.The torque a part inputted by input shaft 1 passes to first sun by second clutch L2
Wheel 2, passes to the second gear ring 7 through first planet carrier 4, passes to second through the planetary gear of the second planet row P2 by the second gear ring 7
Sun gear 5 passes to third sun gear 11 through jackshaft 8 by the second sun gear 5, and another part torque passes through second clutch L2
Pass to the second planet carrier 6, then pass to third gear ring 9, it is differential due to third gear ring 9 and third sun gear 11, torque by
Third planet carrier 10 passes to connecting shaft 12, passes to fourth line carrier 14 by the 4th sun gear 15 that fourth planet arranges P4,
Finally torque is exported by fourth line carrier 14.
8, seven grades, second clutch L2, second brake Z2 and the 4th brake Z4 are combined under pressure oil effect, and second
Gear ring 4 and the braking of the 4th gear ring 13.The torque inputted by input shaft 1 passes to the second planet carrier 6 by second clutch L2, so
Third gear ring 9 and the second sun gear 5 are delivered separately to by the second planet carrier 6 afterwards, the torque of the second sun gear 5 is again through jackshaft 8
Third sun gear 11 is passed to, differential due to third gear ring 9 and third sun gear 11, torque is passed to by third planet carrier 10
Connecting shaft 12 passes to fourth line carrier 14 by the 4th sun gear 15 that fourth planet arranges P4, finally by fourth line carrier 14
Torque is exported.
9, eight grades, first clutch L1, second brake Z2 and third clutch L3 are combined under pressure oil effect, and second
Gear ring 7 is braked.The torque inputted by input shaft 1 passes to jackshaft 8 by first clutch L1, and a part of torque passes through second
The second sun gear 5 of planet row P2 passes to the second planet carrier 6, passes to third gear ring 9, another part by the second planet carrier 6
Torque is directly passed to the third sun gear 11 of third planet row P3 through jackshaft 8, due to the third gear ring 9 of third planet row P3
Differential with third sun gear 11, torque passes to third planet carrier 10, and the torque a part inputted by third planet carrier 10 is led to
The 4th gear ring 13 that third clutch L3 passes to fourth planet row P4 is crossed, another part torque passes to the by connecting shaft 12
The 4th sun gear 15 of four planet row P4, due to the synchronized rotation of the 4th gear ring 13 and the 4th sun gear 15 of fourth planet row P4
Turn, torque passes to fourth line carrier 14, is finally exported torque by fourth line carrier 14.
10, nine grades, first clutch L1, the first brake Z1 and third clutch L3 are combined under pressure oil effect, the
The braking of one gear ring 4.The torque a part inputted by input shaft 1 passes to the first sun gear 2 by second clutch L2, through first
Planet carrier 3 passes to the second gear ring 7, and another part torque passes to the second planet row P2 on jackshaft by first clutch L1
The second sun gear 5 and third planet row P3 third sun gear 11, due to the second sun gear 5 and second of the second planet row P2
Gear ring 7 it is differential, the second planet row P2 by 6 output torque of the second planet carrier, and pass to third planet row P3 third gear ring
9, since the third gear ring 9 and third planet of third planet row P3 arrange the differential of the third sun gear 11 of P3, torque passes to the
Three planet carriers 10, the torque a part inputted by third planet carrier 10 pass to fourth planet by third clutch L3 and arrange P4's
4th gear ring 13, another part torque passes to the 4th sun gear 15 that fourth planet arranges P4 by connecting shaft 12, due to the 4th
The synchronized rotation of the 4th gear ring 13 and the 4th sun gear 15 of planet row P4, torque pass to fourth line carrier 14, finally by
Four planet carriers 14 export torque.
11, ten grades, first clutch L1, second clutch L2 and third clutch L3 are combined under pressure oil effect.By
Torque a part that input shaft 1 inputs passes to third gear ring 9, another part through the second planet carrier 6 by second clutch L2
Torque passs the third sun gear 11 that third planet arranges P3 by first clutch L1, due to third sun gear 11, third gear ring 9
And third planet carrier 10 and input shaft 1 rotate at the same speed, torque passes to third planet carrier 10 in the ratio of 1:1, by third planet
Torque a part that frame 10 inputs passes to the 4th gear ring 13 that fourth planet arranges P4 by third clutch L3, and another part is turned round
Square passes to the 4th sun gear 15 that fourth planet arranges P4 by connecting shaft 12, due to fourth planet row P4 the 4th gear ring 13 with
The synchronized rotation of 4th sun gear 15, torque pass to fourth line carrier 14, finally will in the ratio of 1:1 by fourth line carrier 14
Torque output.
12,11 grades, second clutch L2, the first brake Z1 and third clutch L3 are combined under pressure oil effect,
The braking of first gear ring 4.The torque a part inputted by input shaft 1 passes to the first sun gear 2 by second clutch L2, through
One planet carrier 4 passes to the second gear ring 7, passes to the second sun gear 5 through the planetary gear of the second planet row P2 by the second gear ring 7,
Third sun gear 11 is passed to through jackshaft 8 by the second sun gear 5, another part torque passes to by second clutch L2
Two planet carriers 6, then pass to third gear ring 9, differential due to third gear ring 9 and third sun gear 11, torque passes to third
Planet carrier 10, the torque a part inputted by third planet carrier 10 pass to that fourth planet arranges P4 by third clutch L3 the
Four gear rings 13, another part torque passes to the 4th sun gear 15 that fourth planet arranges P4 by connecting shaft 12, due to fourth line
Star arranges the synchronized rotation of the 4th gear ring 13 and the 4th sun gear 15 of P4, and torque passes to fourth line carrier 14, finally by the 4th
Planet carrier 14 exports torque.
13,12 grades, second clutch L2, the first brake Z1 and third clutch L3 are combined under pressure oil effect,
The braking of first gear ring 4.The torque a part inputted by input shaft 1 passes to the first sun gear 2 by second clutch L2, through
One planet carrier 4 passes to the second gear ring 7, passes to the second sun gear 5 through the planetary gear of the second planet row P2 by the second gear ring 7,
Third sun gear 11 is passed to through jackshaft 8 by the second sun gear 5, another part torque passes to by second clutch L2
Two planet carriers 6, then pass to third gear ring 9, differential due to third gear ring 9 and third sun gear 11, torque passes to third
Planet carrier 10, the torque a part inputted by third planet carrier 10 pass to that fourth planet arranges P4 by third clutch L3 the
Four gear rings 13, another part torque passes to the 4th sun gear 15 that fourth planet arranges P4 by connecting shaft 12, due to fourth line
Star arranges the synchronized rotation of the 4th gear ring 13 and the 4th sun gear 15 of P4, and torque passes to fourth line carrier 14, finally by the 4th
Planet carrier 14 exports torque.
14, fall one grade, the first brake Z1, third brake Z3 and the 4th brake Z4 are combined under pressure oil effect,
First gear ring 4, third gear ring 9 and the braking of the 4th gear ring 13, the torque inputted by input shaft 1 are passed to by second clutch L2
Then first sun gear 2 passes to the second gear ring 7, then the row by the second gear ring 7 through the second planet row P2 through first planet carrier 3
Star-wheel passes to the second sun gear 5, and since the second planet carrier 6 and third gear ring 9 are braked, the second sun gear 5 is reversely rotated, and band
Dynamic jackshaft 8 and third sun gear 11 reversely rotate, so that third planet carrier 10 be made also to reversely rotate, torque is by third planet carrier
10 pass to connecting shaft 12, fourth line carrier 14 are passed to by the 4th sun gear 15 that fourth planet arranges P4, finally by the 4th
Planet carrier 14 exports torque, realizes reverse gear function.
15, fall two grades, the first brake Z1, third brake Z3 and the 4th brake Z4 are combined under pressure oil effect,
First gear ring 4, third gear ring 9 and the braking of the 4th gear ring 13, the torque inputted by input shaft 1 are passed to by second clutch L2
Then first sun gear 2 passes to the second gear ring 7, then the row by the second gear ring 7 through the second planet row P2 through first planet carrier 3
Star-wheel passes to the second sun gear 5, and since the second planet carrier 6 and third gear ring 9 are braked, the second sun gear 5 is reversely rotated, and band
Dynamic jackshaft 8 and third sun gear 11 reversely rotate, thus reversely rotate third planet carrier 10 also, it is defeated by third planet carrier 10
The torque a part entered passes to the 4th gear ring 13 that fourth planet arranges P4 by third clutch L3, and another part torque passes through
Connecting shaft 12 passes to the 4th sun gear 15 of fourth planet row P4, due to fourth planet row P4 the 4th gear ring 13 and the 4th too
The synchronized rotation of sun wheel 15, torque pass to fourth line carrier 14, finally export torque by fourth line carrier 14, realize down
Shelves function.
Table 1: the combination situation table of each gear clutch and brake
" ★ " indicates that controls combines in table.
Simple principle is controlled to make to meet, each gear according to the form below 2 can also be combined.Under this combination,
It can be achieved with rising a shelves or drop one by adjusting a clutch or brake in high-grade and low-grade each drive shift
A grade of function.
Table 2: the combination situation table of each gear clutch and brake.
" ★ " indicates that controls combines in table.
Above-described embodiment is only a preferred embodiment of the invention, and in for limiting the scope of protection of the present invention, all
Deformation, modification or equivalent replacement for being made on the basis of technical solution of the present invention etc. should all fall into protection model of the invention
It encloses.
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 located at the
On the outside of one clutch (L1) and share a piston shell；
The planet row assembly (B) includes the 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), third 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), first planet carrier (3), second row
It includes the second sun gear (5), the second gear ring (7), the second planet carrier (6) that star, which arranges (P2), and third planet row (P3) includes the
Three sun gears (11), third gear ring (9), third planet carrier (10), fourth planet row (P4) include the 4th sun gear (15),
4th gear ring (13), fourth line carrier (14)；
It further include third clutch (L3), jackshaft (8), connecting shaft (12) and output shaft (16)；
The first clutch (L1) connect with jackshaft (8), and second clutch (L2) is connect with the first sun gear (2), and second
The drive hub of clutch (L2) is connect 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 connect with the second gear ring (7)；Second gear ring (7) by second brake (Z2) brake, the second sun gear (5) with
Jackshaft (8) connection, the second planet carrier (6) are connect with third gear ring (9)；Third gear ring (9) is made by third brake (Z3)
Dynamic, third sun gear (11) is connect with jackshaft (8), and third planet carrier (10) is connect with connecting shaft (12)；Connecting shaft (12) with
Third clutch (L3) connection, third clutch (L3) are connect with the 4th gear ring (13)；4th gear ring (13) passes through the 4th braking
Device (Z4) braking, the 4th sun gear (15) are connect 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), third sun gear (11) and jackshaft (8)
Between, between third planet carrier (10) and connecting shaft (12), between connecting shaft (12) and third clutch (L3), the 4th sun gear
(15) it is connect by spline between connecting shaft (12).
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 third gear ring (9) and third brake (Z3), between the 4th gear ring (13) and the 4th brake (Z4)
It is all made of retaining ring and carries out axially position.
4. 12 speed automatic transmission according to claim 1, it is characterised in that: the first planet 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 third
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 CN106641135A (en) | 2017-05-10 |
| CN106641135B true CN106641135B (en) | 2019-05-14 |
Family
ID=58823105
Family Applications (1)
| 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 |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN106641135B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111536211B (en) * | 2020-06-23 | 2020-10-16 | 北京航空航天大学 | Multi-gear planetary gear speed change device |
| 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 |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4798022B2 (en) * | 2007-02-28 | 2011-10-19 | アイシン・エィ・ダブリュ株式会社 | Automatic transmission |
| JP6171777B2 (en) * | 2013-09-19 | 2017-08-02 | アイシン精機株式会社 | Automatic transmission |
-
2016
- 2016-12-16 CN CN201611169038.7A patent/CN106641135B/en active Active
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
Also Published As
| Publication number | Publication date |
|---|---|
| CN106641135A (en) | 2017-05-10 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US9599195B2 (en) | Multi-speed gearbox | |
| CN103807379B (en) | Quad-clutch multi-speed transmission | |
| US9482318B2 (en) | Multi-speed gearbox | |
| CN102913597B (en) | Seven-level planet automatic speed changer | |
| US9267576B2 (en) | Multi-speed gearbox | |
| CN103527732B (en) | A kind of seven gear planetary automatic transmissions | |
| US8282524B2 (en) | Transmission device for distributing a drive torque to at least two output shafts | |
| CN104271984B (en) | Multiple-speed gear-box | |
| CN106641135B (en) | A kind of 12 speed automatic transmissions | |
| CN106499790A (en) | A kind of coaxial-type bi-motor electric drive axle | |
| US20150119187A1 (en) | Multi-speed gearbox | |
| CN106523628B (en) | A kind of eight-gear planetary automatic speed changer | |
| CN106763568B (en) | One kind six keeps off planetary automatic transmission | |
| CN103511565A (en) | Automatic six-gear planetary transmission | |
| CN104364559A (en) | Transmission for a motor vehicle | |
| CN104696450A (en) | Triple clutch multi-speed transmission | |
| CN106884936A (en) | The gear transmission of three planet row six and automobile | |
| CN106402293A (en) | Eight-gear automatic planetary transmission | |
| CN109737190A (en) | A kind of two double clutch two-row planetary gear fourth gear automatic transmissions | |
| CN102628495A (en) | Six-gear planet automatic gearbox | |
| CN106438878A (en) | Nine-gear planet automatic transmission | |
| US9366320B2 (en) | Multi-speed gearbox | |
| CN106286727B (en) | A kind of transmission system of eight-speed automatic transmission | |
| CN101446332B (en) | Planetary gearbox with multi-gear power gear shifting | |
| CN201359059Y (en) | Multi-gear power shift planetary gearbox |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |