CN106838152A - A kind of multi-shifting speed variator of planetary gear construction mode - Google Patents
A kind of multi-shifting speed variator of planetary gear construction mode Download PDFInfo
- Publication number
- CN106838152A CN106838152A CN201710089321.7A CN201710089321A CN106838152A CN 106838152 A CN106838152 A CN 106838152A CN 201710089321 A CN201710089321 A CN 201710089321A CN 106838152 A CN106838152 A CN 106838152A
- Authority
- CN
- China
- Prior art keywords
- gear
- clutch
- brake
- axle
- planetary
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
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
-
- 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
- F16H2200/0065—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising nine 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
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention discloses a kind of multi-shifting speed variator of planetary gear construction mode, belong to automatic transmission technical field；Overcome complicated existing automatic transmission structure, quality weight and production cost high, be particularly difficult to provide problem that is slightly progressive, being classified the serial and good meshing efficiency of good gearratio；Including four planetary gear sets set along main rotating shaft successive；Six gear shift switching devices, gear shift switching device allows optionally to be manipulated so that formation nine forwards and a reverse gear between transmission input shaft and output shaft；Input shaft is realized releasably being connected by the 3rd clutch with the 5th axle for being connected to the 3rd, fourth line carrier；It is connected to the first sun gear, the 6th axle of the second sun gear is realized releasably being connected by second brake and housing；The 8th axle for being connected to the 3rd sun gear is realized releasably being connected by the 3rd brake and housing；Output shaft is connected with the 4th gear ring.
Description
Technical field
The invention belongs to automatic transmission technical field, it is related to a kind of automatic transmission unit, particularly for motor vehicle
PWTN, and in particular to a kind of multi-shifting speed variator of planetary gear construction mode.
Background technology
The dynamical system of motor vehicle includes that engine, multi-speed transmission and differential mechanism or main reducing gear are constituted.Multi-speed transmission
By allowing that engine improves the whole operation scope of vehicle in its torque range by multi-pass operation.Be can obtain in speed changer
Forward speed ratio (drive shift) quantity determine engine torque bands repeat number of times.The negligible amounts of drive shift will
The whole velocity interval of vehicle is limited, and therefore needs relatively large engine, speed and moment of torsion model wider can be produced
Enclose.
The automatic transmission of current fourth gear automatic transmission particularly planetary gear construction is constantly popularized in China, this
The a little transmissions improveds operating characteristics and fuel economy of vehicle.The quantity of forward speed ratio increase will reduce speed ratio it
Between step-length, and therefore by making in the case where normal vehicle accelerates operator be detectable speed substantially improve speed changer than replacing
Shift quality.Six grades, seven grades, eight grades, nine gear automatic speed variators compare in terms of vehicle acceleration and improved fuel economy
Fourth gear and five gear automatic speed variators have an obvious advantage, but because the size of these speed changers is big, the complexity of structure and into
This height, is also subject to certain restrictions in the popularization of these automatic transmission.
The vehicle automatic speed variator of the planetary gear construction mode that in general can automatically switch in the prior art by
Repeatedly describe and further developed all the time and improved.Such as ZF company CN104114902A and CN101970902A,
German DaimlerChrysler AG CN102203458A and GM companies of U.S. US7695398B2 disclose planetary gear construction mode
Multistage automatic transmission, the automatic transmission has input shaft, output shaft, four planetary gear sets and six gear shift controls
Element processed, by targetedly operating the kinetic current in these gearshift control elements four planetary gearsets of change, in input
Different gearratios are obtained between axle and output shaft.
The content of the invention
The technical problems to be solved by the invention are to overcome complicated existing automatic transmission structure, quality weight and be produced into
This height, is particularly difficult to provide load that is slightly progressive and being classified good gearratio series, automatic transmission each element
Minimize the problem with good meshing efficiency.
In order to solve the above technical problems, the present invention adopts the following technical scheme that realization, it is described with reference to the drawings as follows：
The present invention proposes a kind of automatic transmission unit, especially automatic speed changer for vehicle unit, the speed changer
Unit has：The four planetary gear sets i.e. first, second, third and fourth planetary gear set along main rotating shaft successive
Group；
Six gear shift switching devices, the gear shift switching device allows to be selectively engaged before speed changer can be made to realize nine
Enter gear；
Input shaft is connected relatively unrotatablely with the clutch of the first gear ring, second and the 3rd, then by the two clutches
Device engages the first planet carrier, the third line carrier and fourth line carrier respectively；
And power output shaft, the power output shaft is connected with the 4th gear ring.Thus a kind of automatic transmission can be provided
Unit, the automatic transmission unit has that numbers of gear steps is more, classification is good and gear range is enough, speed changer structure is compact.
It is interpreted as two components for " relatively unrotatable connect " to be connected by the form such as spline or rigidity, makes two
Individual component has equal angular speed when rotating.
For " clutch " be interpreted as being arranged for making two rotatably arranged with clutch element selectivity not
The unit that can be connected or separated in relative rotation.It is interpreted as being arranged for making rotatable brake unit for " brake "
Part and the fixed cell unit that especially case of transmission is connected or separated selectively relatively unrotatablely.
For " the first, second, third and fourth planetary gear set speed changer set along main rotating shaft successive "
Especially it is interpreted as putting in order for four planetary gear set speed changers under this meaning, these planetary gear set speed changers are with the row
Row order is set along main rotating shaft, wherein, the first planetary gear set speed changer is advantageously towards input shaft side, fourth line star-wheel group
Speed changer is advantageously towards output shaft side.In addition, to put it more simply, for " first to fourth sun gear ", " first to fourth planet
Wheel carrier ", " first to fourth gear ring " are interpreted as being respectively configured to the sun gear or row of first to fourth planetary gear change group speed device
Star wheel frame or gear ring, i.e., be for example interpreted as the planetary wheel carrier of the first planetary gear set speed changer for the first planetary wheel carrier.
A kind of multi-shifting speed variator of planetary gear construction mode, including it is arranged on four planetary gearsets, eight in housing G
The individual axle and six gear shift switching devices that can be rotated；
Four planetary gearsets be respectively the first planetary gear set P1, the second planetary gear set P2, the third line star-wheel group P3,
Fourth line star-wheel group P4；
The first, second, third and fourth planetary gearsets Pl, P2, P3, P4 are configured to negative ratio epicyclic gear
Group.But in the case where connection is allowed without the position for producing interference, single or multiple negative ratio epicyclic gear groups can be changed into
Positive drive changes gear ring and planet carrier annexation, and the value of fixed drive ratio is increased into 1 simultaneously than planetary gearsets；
Single or multiple positive drives can also be changed into negative ratio epicyclic gear group than planetary gearsets, i.e., simultaneously change gear ring and
Planet carrier annexation, and the value of fixed drive ratio is reduced 1.
The first planetary gear set P1 is arranged on input side, and the first planetary gear set Pl includes the first sun gear P11, the
One planetary wheel carrier P12 and the first gear ring P13；First planetary wheel carrier P12 guides the first planetary gear P14, first on circular orbit
Planetary gear P14 can on the first planetary wheel carrier P12 circular-rotation；First planetary gear P14 and the first sun gear P11 and with
One gear ring P13 is meshed；
The second planetary gear set P2, the third line star-wheel group P3 are successively set on centre；The second planetary gear set P2 bags
Include the second sun gear P21, the second planetary wheel carrier P22 and the second gear ring P23；Second planetary wheel carrier P22 is guided on circular orbit
Second planetary gear P24, the second planetary gear P24 can on the second planetary wheel carrier P22 circular-rotation；Second planetary gear P24 and
Two sun gear P21 and it is meshed with the second gear ring P23；
The third line star-wheel group P3 includes the 3rd sun gear P31, third planet wheel carrier P32 and the 3rd gear ring P33；3rd
Planetary wheel carrier P32 guides the third line star-wheel P34 on circular orbit, and the third line star-wheel P34 can be on third planet wheel carrier P32
Circular-rotation；The third line star-wheel P34 is meshed with the 3rd sun gear P31 and with the 3rd gear ring P33；
The fourth planet wheel speed P4 is arranged on outlet side, and the fourth line star-wheel group P4 includes the 4th sun gear
P41, fourth planet wheel carrier P42 and the 4th gear ring P43；Fourth planet wheel carrier P42 guides fourth line star-wheel on circular orbit
P44, fourth line star-wheel P44 can on fourth planet wheel carrier P42 circular-rotation；Fourth line star-wheel P44 and the 4th sun gear P41
And it is meshed with the 4th gear ring P43.
Described eight axles that can be rotated are respectively input shaft 1, output shaft 2, the 3rd axle 3, the 4th axle 4, the 5th axle the 5, the 6th
Axle 6, the 7th axle 7 and the 8th axle 8；
3rd axle 3 is connected relatively unrotatablely with the second planet carrier P22；
4th axle 4 is connected relatively unrotatablely with the first planet carrier P12；
5th axle 5 is connected relatively unrotatablely with the third line carrier P32, fourth line carrier P42；
6th axle 6 is connected relatively unrotatablely with the first sun gear P11, the second sun gear P21；
7th axle 7 is connected relatively unrotatablely with the second gear ring P23, the 3rd gear ring P33, the 4th sun gear P41；
8th axle 8 is connected relatively unrotatablely with the 3rd sun gear P31；
The output shaft 2 is connected relatively unrotatablely with the 4th gear ring P43.
Six gear shift switching devices are made up of three clutches and three brakes, and three clutches are respectively
First clutch C1, second clutch C2, the 3rd clutch C3, three brakes are respectively the first brake B1, second
Brake B2, second brake B3；
Six gear shift switching devices are selectively engaged so that being obtained between input shaft 1 and output shaft 2 different
Gearratio, so as to realize that nine forward gears and one reverse gear；
First clutch C1 is that transfer device is refused in steerable torsion, with selectively by the 4th axle 4 and the 7th axle 7
Couple together；
Second clutch C2 is that transfer device is refused in steerable torsion, with selectively by the axle 4 of the input shaft 1 and the 4th
Couple together；
3rd clutch C3 is that transfer device is refused in steerable torsion, with selectively by the axle 5 of the input shaft 1 and the 5th
Couple together；
First brake B1 is that transfer device is refused in steerable torsion, selectively to connect the 3rd axle 3 and housing G
Pick up and；
Second brake B2 is that transfer device is refused in steerable torsion, selectively to connect the 6th axle 6 and housing G
Pick up and；
3rd brake B3 is that transfer device is refused in steerable torsion, selectively to connect the 8th axle 8 and housing G
Pick up and.
First clutch C1 described in technical scheme includes first clutch a elements C11 and first clutch b element C12,
Second clutch C2 include second clutch a elements C21 and second clutch b elements C22, the 3rd clutch C3 include the 3rd from
Clutch a elements C31 and the 3rd clutch b elements C32；
The first brake B1 includes that the first brake a element B11, second brake B2 includes second brake a units
Part B21, the 3rd brake B3 include the 3rd brake a elements B31.
When being provided with the first clutch C1 and being manipulated, make the institute being connected relatively unrotatablely with the 4th axle 4
State first clutch a elements C11 and relatively unrotatable with the 7th axle 7 the first clutch b elements C12 being connected
Couple together；When being provided with the second clutch C2 and being manipulated, make the institute being connected relatively unrotatablely with the input shaft 1
State second clutch a elements C21 and relatively unrotatable with the 4th axle 4 the second clutch b elements C22 being connected
Couple together；When being provided with the 3rd clutch C3 and being manipulated, make the institute being connected relatively unrotatablely with the input shaft 1
State the 3rd clutch a elements C31 and relatively unrotatable with the 5th axle 5 the 3rd clutch b elements C32 being connected
Couple together；
When being provided with the first brake B1 and being manipulated, make the institute being connected relatively unrotatablely with the 3rd axle 3
The first brake a elements B11 and housing G is stated to couple together；When being provided with the second brake B2 and being manipulated, make and described
The second brake a elements B21 and housing G that six axles 6 are connected relatively unrotatablely are coupled together；It is provided with the described 3rd
When brake B3 is manipulated, make the 3rd brake a elements B21 being connected relatively unrotatablely with the 8th axle 8 and
Housing G is coupled together.
Input shaft 1 described in technical scheme and the first gear ring P13, first clutch a elements C11, the 3rd clutch a elements
C31 is connected relatively unrotatablely.
The first advance is obtained by closure first and the 3rd brake B1, B3 and first clutch C1 in technical scheme
Gear, the second forward gear is obtained by closure second and the 3rd brake B2, B3 and first clutch C1, is made by closure the 3rd
Dynamic device B3 and the first and second clutch C1, C2 obtains the 3rd forward gear, by closing the 3rd brake B3 and the first He
3rd clutch C1, C3 obtain the 4th forward gear, or by closing the 3rd brake B3 and second and the 3rd clutch C2,
C3 obtains the 4th forward gear, the 5th forward gear is obtained by closing first, second, and third clutch C1, C2, C3, by closure
Second brake B2 and first and the 3rd clutch C1, C3 obtain the 6th forward gear, by close the first brake B1 and
First and the 3rd clutch C1, C3 obtain the 7th forward gear, by closing the first and second brake B1, B2 and the 3rd clutch
Device C3 obtains the 8th forward gear, and the 9th advance is obtained by closing the first brake B1 and second and the 3rd clutch C2, C3
Gear, is reversed gear by closure first and the 3rd brake B1, B3 and second clutch C2.
First, second, third and fourth planetary gearsets described in technical scheme Pl, P2, P3, P4 are configured to negative gearratio
Planetary gearsets；
The planetary gearsets are observed by the first planetary gearsets Pl, the second planetary gearsets P2, third planet vertically
Gear train P3, the order of fourth planet gear train P4 are set.
Each gear shift switching device C1 of speed changer described in technical scheme, C2, C3, B1, B2, B3 are constructed to be permeable to as needed
The gear shift switching device of switching, is electromechanical and/or electro-hydraulic gear shift switching device.
The second clutch a elements (C21) are connected with the first gear ring (P13), second clutch b elements (C22) and the
One sun gear (P11) is connected.
The second clutch a elements (C21) are connected with the first planet carrier (P12), second clutch b elements (C22) with
First sun gear (P11) is connected.
Compared with prior art the beneficial effects of the invention are as follows：
The present invention can provide nine drive shifts and a reverse gear, with numbers of gear steps it is many, provide it is slightly progressive and classification
Good gearratio series, gear range is enough, it is adaptable to the overall gear range of the multidrive of car, from
And improve driving comfort and reduce oil consumption.Meanwhile, speed changer structure is compact, reduces the number of components and causes its weight and be produced into
This minimum.Transmission efficiency, each element load it is small, with low absolute and relative rotating speed and low planetary gearsets power
Square and gear shift switching device control moment, are conducive to improving the service life of speed changer.
Brief description of the drawings
The present invention is further illustrated below in conjunction with the accompanying drawings：
Fig. 1 is the explanatory view of automatic transmission unit according to one embodiment of present invention；
In figure：
G housings；
1 input shaft；
2 output shafts；
3 the 3rd axles；
4 the 4th axles；
5 the 5th axles；
6 the 6th axles；
7 the 7th axles；
8 the 8th axles；
C1 first clutches；
C2 second clutches；
The clutches of C3 the 3rd；
The brakes of B1 first；
B2 second brakes；
The brakes of B3 the 3rd；
The planetary gearsets of P1 first；
The planetary gearsets of P2 second；
P3 third planet gear trains；
P4 fourth planet gear trains；
The sun gears of P11 first；
The planet carriers of P12 first；
The gear rings of P13 first；
The planetary gears of P14 first；
The sun gears of P21 second；
The planet carriers of P22 second；
The gear rings of P23 second；
The planetary gears of P24 second；
The sun gears of P31 the 3rd；
P32 the third line carrier；
The gear rings of P33 the 3rd；
P34 the third line star-wheels；
The sun gears of P41 the 4th；
P42 fourth line carrier；
The gear rings of P43 the 4th；
P44 fourth line star-wheels；
C11 first clutch a elements；
C12 first clutch b elements；
C21 second clutch a elements；
C22 second clutch b elements；
The clutch a elements of C31 the 3rd；
The clutch b elements of C32 the 3rd；
B11 the first brake a elements；
B21 second brake a elements；
The brake a elements of B31 the 3rd；
1. first of second clutch replaceable position
2. second of second clutch replaceable position
Specific embodiment
The present invention is explained in detail below in conjunction with the accompanying drawings：
Fig. 1 shows an one embodiment for automatic transmission unit, and the automatic transmission unit is configured to motor vehicle
Automatic transmission unit.Automatic transmission unit has four planetary gear sets Pl, P2, P3, P4.First planetary gear set Pl, second
Planetary gear set P2, the third line star-wheel group P3 and fourth line star-wheel group P4 successives ground are set along main rotating shaft.Fluid drive
First, second, third and fourth planetary gear set Pl, P2 of device unit, P3, P4 are single-stage planetary wheel groups.Gearbox unit has
Six gear shift switching devices C1, C2, C3, B1, B2, B3.These gear shift switching devices are arranged for conversion just nine advances
A/T gear position Gl, G2, G3, G4, G5, G6, G7, G8, G9 and a reverse gear GR.But automatic transmission unit also can use only
Eight advance TRs carry out work, such as by not changing the first advance TR Gl or the 9th advance speed changer shelves
Position G9.
Automatic transmission unit is arranged for making the driving machine not being shown specifically of motor vehicle not detailed with motor vehicle
The driving wheel connection for showing.By means of the adjustable gear ratio between driving machine and driving wheel of gearbox unit.Gearbox unit
Can be connected with combination drive module, driving moment can be changed by means of the combination drive module.In addition, by means of combined drive dynamic model
Block and gearbox unit can realize CVT, thus can realize a gear ratio at least can in regional area step-less adjustment speed change
Device unit.
Automatic transmission unit has input shaft 1, and the input shaft is arranged for for driving moment being incorporated into speed changer list
In unit.A module not being shown specifically can be connected in input shaft 1, the module should especially be arranged for providing starting work(
Energy.Torque-converters or wet type start clutch are for example contemplated that as the module being connected to above.But will can also be set in principle
Module for starting to walk is integrated in gearbox unit such as is come using one of clutch unit C1, C2, C3, B1, B2, B3
Starting.
In addition, automatic transmission unit has power output shaft 2, the power output shaft be arranged for by driving moment from
Gearbox unit is drawn.Power output shaft 2 is arranged for being connected with the driving wheel of motor vehicle.Can be behind power output shaft 2
One module not being shown specifically of connection --- the torque drawn from automatic transmission unit can be by means of the module assignment to drive
Driving wheel, for example, be arranged for compensating the planetary gear of the speed discrepancy between driving wheel, or driving moment is distributed to
Two a11wheel drive units of different input shafts.Power input shaft 1 and power output shaft 2 can arbitrarily set toward each other in principle
Put.Herein, it may be particularly advantageous to be placed coaxially on the both sides opposite each other of automatic transmission unit, but also contemplate for setting
In the phase homonymy of gearbox unit.
First planetary gear set P1 is arranged on input side.First planetary gear set Pl has single-stage planetary wheel group.Single-stage planetary wheel
Group includes that the first planetary gear set Pl includes the first sun gear P11, the first planetary wheel carrier P12 and the first gear ring P13；First planetary gear
Frame P12 guided on circular orbit the first planetary gear P14, the first planetary gear P14 can on the first planetary wheel carrier P12 circumference turn
It is dynamic；First planetary gear P14 is meshed with the first sun gear P11 and with the first gear ring P13.The feature system of the first planetary gear set Pl
Number (gearratio in planetary gear set) K1=-2.2.
Second planetary gear set P2 is in middle setting in input side.Second planetary gear set P2 has single-stage planetary wheel group.Single-stage
Planetary gear set is successively set on centre including the second planetary gear set P2, the third line star-wheel group P3；The second planetary gear set P2 bags
Include the second sun gear P21, the second planetary wheel carrier P22 and the second gear ring P23；Second planetary wheel carrier P22 is guided on circular orbit
Second planetary gear P24, the second planetary gear P24 can on the second planetary wheel carrier P22 circular-rotation；Second planetary gear P24 and
Two sun gear P21 and it is meshed with the second gear ring P23.The characteristic coefficient (gearratio in planetary gear set) of the second planetary gear set P2
K2=-2.0.
The third line star-wheel group P3 is in middle setting in outlet side.The third line star-wheel group P3 has single-stage planetary wheel group.Single-stage
Planetary gear set includes the 3rd sun gear P31, third planet wheel carrier P32 and the 3rd gear ring P33.Third planet wheel carrier P32 is in circumference
The third line star-wheel P34 is guided on track.The third line star-wheel P34 is meshed with the 3rd sun gear P31 and with the 3rd gear ring P33.
The third line star-wheel P34 can on third planet wheel carrier P32 circular-rotation.Characteristic coefficient (the planetary gear set of the third line star-wheel group P3
Interior gearratio) K3=-2.0.
Fourth planet wheel speed P4 is arranged on outlet side.Fourth line star-wheel group P4 has single-stage planetary wheel group.Single-stage row
Star-wheel group includes the 4th sun gear P41, fourth planet wheel carrier P42 and the 4th gear ring P43.Fourth planet wheel carrier P42 is in circumference rail
Fourth line star-wheel P44 is guided on road.Fourth line star-wheel P44 is meshed with the 4th sun gear P41 and with the 4th gear ring P43.The
Four planetary gear P44 can on fourth planet wheel carrier P42 circular-rotation.The characteristic coefficient of fourth line star-wheel group P4 is (in planetary gear set
Gearratio) K4=-1.6.
Two clutches C2, C3 are configured to clutch unit.This two clutches have a rotatable clutch respectively
Device a elements C21, C31 and rotatable clutch b elements C22, a C32.Two clutch a elements C21, C31 each other can not
Connect in relative rotation.Clutch C1 has a rotatable clutch a elements C11 and a rotatable clutch b unit
Part C12.When clutch C1, C2, C3 are manipulated respectively, clutch a elements C11, C21, C31 respectively with clutch b elements
C12, C22, C32 are coupled together, and two elements have equal angular velocity of rotation.
Three brake units B1, B2, B3 are respectively configured to brake unit and only have a brake a unit respectively
Part B11, B21, B31.When brake B1, B2, B3 are manipulated respectively, brake a elements B11, B21, B31 respectively with speed changer
Housing G is connected, and the angular speed for rotating brake a elements is zero.
Multidrive of the present invention as shown in Figure 1, including it is arranged on the input shaft 1, in a housing G
Individual output shaft 2, four planetary gearsets Pl, P2, P3, P4 and the axle 1,2,3,4,5,6,7,8 that can be rotated including total of eight
With six gear shift switching device C1, C2, C3, B1, B2, B3, gear shift switching device include multiple clutch C1, C2, C3 and multiple
Brake B1, B2, B3, gear shift switching device are selectively engaged so that obtaining different biographies between input shaft 1 and output shaft 2
Dynamic ratio, so as to realize that nine forward gears and one reverse gear, wherein,
Input shaft 1 is by the 3rd clutch C3 and the reality of the 5th axle 5 for being connected to the third line carrier P32, fourth line carrier P42
Now releasably connect；Input shaft 1 is connected with the first gear ring P13；Input shaft 1 passes through second clutch C2 and is connected to the first row
4th axle 4 of carrier P12 is realized releasably connecting；And the 4th axle 4 passes through first clutch C1 and is connected to the second gear ring
P23, the 3rd gear ring P33, the 7th axle 7 of the 4th sun gear P41 are realized releasably connecting；It is connected to the second planet carrier P22's
3rd axle 3 is realized releasably being connected by the first brake B1 and housing G；It is connected to the first sun gear P11, the second sun gear
6th axle 6 of P21 is realized releasably being connected by second brake B2 and housing G；It is connected to the 8th of the 3rd sun gear P31 the
Axle 8 is realized releasably being connected by the 3rd brake B3 and housing G；Output shaft 2 is connected with the 4th gear ring P43.
As shown in Figure 1, the gear ring P13 of input shaft 1 and first, second clutch a elements C21, the 3rd clutch a elements C31
Connect relatively unrotatablely, output shaft 2 is connected relatively unrotatablely with the 4th gear ring P43, the 3rd axle 3 and the second planet carrier
P22, the first brake a elements B11 are connected relatively unrotatablely, and the 4th axle 4 and the first planet carrier P12, second clutch b are first
Part C22, first clutch a elements C11 are connected relatively unrotatablely, the 5th axle 5 and the third line carrier P32, fourth line carrier
P42, the 3rd clutch b elements C32 are connected relatively unrotatablely, the 6th axle 6 and the first sun gear P11, the second sun gear
P21, second brake a elements B21 are connected relatively unrotatablely, the 7th axle 7 and the second gear ring P23, the 3rd gear ring P33,
Four sun gear P41, first clutch b elements C12 are connected relatively unrotatablely, the 8th axle 8 and the 3rd sun gear P31, the 3rd
Brake a elements B31 is connected relatively unrotatablely.
Exemplary shift logic, each shelves gearratio and the transmission of multidrive according to Fig. 1 are shown in table 1
Than interval.Only need to close three gear shift switching devices for each gear.Can exemplarily be drawn from the gearshift schematic diagram
Ratio step (is kept off in other words for the gearshift jump of the respective gearratio of each gear and the gear higher downwards that can be thereby determined that
Gearratio ratio between position), its numerical value is total up to 9.992 ratio coverages for being speed changer.In table 1 "×" represent clutch,
Brake is manipulated (engagement), and " (×) " represents that clutch can be manipulated (engagement), it is also possible to be not manipulated (engagement), not
Gearratio of the influence speed changer in the gear.
Table 1
From table 1, in order gearshift mode, two adjacent gears must only connect a gear shift switching device respectively
With disconnect a switching device, it is constant that two other gear shift switching device connects situation, that is, two are shared when changing to adjacent gear
Gear shift switching device.In addition it is visible, less gearshift jump and larger gear range can be realized during gear shift.While each shelves
The transmission efficiency of position.
First forward gear is obtained by closure first and the 3rd brake B1, B3 and first clutch C1, by closure
Second and the 3rd brake B2, B3 and first clutch C1 obtain the second forward gear, by close the 3rd brake B3 and
First and second clutch C1, C2 obtain the 3rd forward gear, by closing the 3rd brake B3 and first and the 3rd clutch
C1, C3 obtain the 4th forward gear, or obtain the 4th by closing the 3rd brake B3 and second and the 3rd clutch C2, C3
Forward gear, by closing first, second, and third clutch C1, C2, C3 obtains the 5th forward gear, by closing second brake
B2 and first and the 3rd clutch C1, C3 obtain the 6th forward gear, by closing the first brake B1 and first and the 3rd
Clutch C1, C3 obtain the 7th forward gear, and the is obtained by closing the first and second brake B1, B2 and the 3rd clutch C3
Eight forward gears, obtain the 9th forward gear, by closure by closing the first brake B1 and second and the 3rd clutch C2, C3
First and the 3rd brake B1, B3 and second clutch C2 reversed gear.
According to the present invention, even if the difference depending on shift logic in identical speed changer schematic diagram also can obtain different biographies
Dynamic ratio interval, so as to can realize being applied to the specific flexible program of specific or vehicle.
As first alternative, the connected mode of second clutch C2 can will be changed in embodiment scheme, specifically
It is：Second clutch a elements C21 is connected with the first gear ring P13, and second clutch b elements C22 is connected with the first sun gear P11,
Remaining structure is constant, and shift logic is as shown in table 1.Second clutch C2 specifically replaces position such as symbol " 1. " institute in Fig. 1
Show.
As second alternative, embodiment can be changed the connected mode of second clutch C2, specifically：Second
Clutch a elements C21 is connected with the first planet carrier P12, and second clutch b elements C22 is connected with the first sun gear P11, remaining
Structure is constant, and shift logic is as shown in table 1.Second clutch C2 is specifically replaced shown in the symbol " 2. " of position such as Fig. 1.
In addition, alternatively specifying according to the present invention, set additional on each suitable position of multidrive
One-way clutch, for example in order to one between axle and housing connection or alternatively connect two axles.
In input shaft side or output shaft side, axle differential and/or Verteilerdifferential can be set.
It is advantageously improved in the range of scheme in one kind of the present invention, input shaft 1 can as required pass through a clutching member
Separated with drive motor, fluid torque-converter, hydraulic clutch, dry launch clutch, wet type can be used as clutching member
Starting clutch, magnetic powder cluth or centrifugal clutch.Also this initiating element can be arranged on change along direction of power flows
Fast device lower section, input shaft 1 is fixedly connected with the bent axle of drive motor in this case.
Additionally, multidrive of the invention allows for torsion vibration absorber to be arranged on drive motor and speed changer
Between.
In the range of another unshowned implementation method of the invention, can on each axle, preferably in input shaft 1 or
Brake without abrasion, such as fluid pressure type or electrodynamic retarder or the like are set on output shaft 2, and this is especially for used in business
With significant in car.Additionally, in order to drive the additional unit can be in each axle, preferably in input shaft 1 or output shaft 2
Upper setting auxiliary drive.
The friction type shifting switching device for being used is configured to the clutch or brake of powershift.Particularly
The clutch or brake, such as lamella clutch, band brake and/or cone clutch of force closure can be used.
Another advantage of proposed multidrive is that can install as generator on each axle herein
And/or as the motor of additional drive system.
Claims (8)
1. a kind of multi-shifting speed variator of planetary gear construction mode, it is characterised in that：Including four rows being arranged in housing (G)
Star gear train, eight axles that can be rotated and six gear shift switching devices；
Four planetary gearsets are respectively the first planetary gear set (P1), the second planetary gear set (P2), the third line star-wheel group
(P3), fourth line star-wheel group (P4)；
First planetary gear set (P1) is arranged on input side, first planetary gear set (Pl) include the first sun gear (P11),
First planetary wheel carrier (P12) and the first gear ring (P13)；First planetary wheel carrier (P12) guides the first planetary gear on circular orbit
(P14), the first planetary gear (P14) can on the first planetary wheel carrier (P12) circular-rotation；First planetary gear (P14) and first
Sun gear (P11) and it is meshed with the first gear ring (P13)；
Second planetary gear set (P2), the third line star-wheel group (P3) are successively set on centre；Second planetary gear set (P2)
Including the second sun gear (P21), the second planetary wheel carrier (P22) and the second gear ring (P23)；Second planetary wheel carrier (P22) is in circumference
Guide the second planetary gear (P24) on track, the second planetary gear (P24) can on the second planetary wheel carrier (P22) circular-rotation；The
Two planetary gears (P24) are meshed with the second sun gear (P21) and with the second gear ring (P23)；
The third line star-wheel group (P3) includes the 3rd sun gear (P31), third planet wheel carrier (P32) and the 3rd gear ring (P33)；
Third planet wheel carrier (P32) guides the third line star-wheel (P34) on circular orbit, and the third line star-wheel (P34) can be in the third line
Circular-rotation on star wheel frame (P32)；The third line star-wheel (P34) is mutually nibbled with the 3rd sun gear (P31) and with the 3rd gear ring (P33)
Close；
The fourth planet wheel speed (P4) is arranged on outlet side, and the fourth line star-wheel group (P4) includes the 4th sun gear
(P41), fourth planet wheel carrier (P42) and the 4th gear ring (P43)；Fourth planet wheel carrier (P42) guides the 4th on circular orbit
Planetary gear (P44), fourth line star-wheel (P44) can on fourth planet wheel carrier (P42) circular-rotation；Fourth line star-wheel (P44)
It is meshed with the 4th sun gear (P41) and with the 4th gear ring (P43)；
Described eight axles that can be rotated are respectively input shaft (1), output shaft (2), the 3rd axle (3), the 4th axle (4), the 5th axle
(5), the 6th axle (6), the 7th axle (7) and the 8th axle (8)；
3rd axle (3) is connected relatively unrotatablely with the second planet carrier (P22)；
4th axle (4) is connected relatively unrotatablely with the first planet carrier (P12)；
5th axle (5) is connected relatively unrotatablely with the third line carrier (P32), fourth line carrier (P42)；
6th axle (6) is connected relatively unrotatablely with the first sun gear (P11), the second sun gear (P21)；
7th axle (7) is with the second gear ring (P23), the 3rd gear ring (P33), the 4th sun gear (P41) relatively unrotatablely
Connection；
8th axle (8) is connected relatively unrotatablely with the 3rd sun gear (P31)；
The output shaft (2) is connected relatively unrotatablely with the 4th gear ring (P43)；
Six gear shift switching devices are made up of three clutches and three brakes, and three clutches are respectively first
Clutch (C1), second clutch (C2), the 3rd clutch (C3), two brakes be respectively the first brake (B1),
Second brake (B2), the 3rd brake (B3)；
Six gear shift switching devices are selectively engaged so that obtaining different between input shaft (1) and output shaft (2)
Gearratio, so as to realize that nine forward gears and one reverse gear；
First clutch (C1) is that transfer device is refused in steerable torsion, with selectively by the 4th axle (4) and the 7th axle
(7) couple together；
Second clutch (C2) is that transfer device is refused in steerable torsion, with selectively by the input shaft (1) and the 4th axle
(4) couple together；
3rd clutch (C3) is that transfer device is refused in steerable torsion, with selectively by the input shaft (1) and the 5th axle
(5) couple together；
First brake (B1) is that transfer device is refused in steerable torsion, with selectively by the 3rd axle (3) and housing (G)
Couple together；
Second brake (B2) is that transfer device is refused in steerable torsion, with selectively by the 6th axle (6) and housing (G)
Couple together；
3rd brake (B3) is that transfer device is refused in steerable torsion, with selectively by the 8th axle (8) and housing (G)
Couple together.
2. the multi-shifting speed variator of a kind of planetary gear construction mode according to claim 1, it is characterised in that：
The first clutch (C1) includes first clutch a elements (C11) and first clutch b elements (C12), the second clutch
Device (C2) include second clutch a elements (C21) and second clutch b elements (C22), the 3rd clutch (C3) including the 3rd from
Clutch a elements (C31) and the 3rd clutch b elements (C32)；
First brake (B1) includes the first brake a elements (B11), and second brake (B2) includes second brake a
Element (B21), the 3rd brake (B3) includes the 3rd brake a elements (B31)；
When being provided with the first clutch (C1) and being manipulated, make the institute being connected relatively unrotatablely with the 4th axle (4)
State first clutch a elements (C11) and relatively unrotatable with the 7th axle (7) the first clutch b units being connected
Part (C12) is coupled together；When being provided with the second clutch (C2) and being manipulated, make relative to turn with the input shaft (1)
The second clutch a elements (C21) that connect dynamicly and it is relatively unrotatable with the 4th axle (4) be connected described
Two clutch b elements (C22) are coupled together；When being provided with the 3rd clutch (C3) and being manipulated, make and the input shaft (1)
The 3rd clutch a elements (C31) that connects relatively unrotatablely and it is relatively unrotatable with the 5th axle (5) even
The 3rd clutch b elements (C32) for connecing couples together；
When being provided with first brake (B1) and being manipulated, make the institute being connected relatively unrotatablely with the 3rd axle (3)
State the first brake a elements (B11) and housing (G) is coupled together；When being provided with the second brake (B2) and being manipulated, make with
The second brake a elements (B21) and housing (G) that 6th axle (6) connects relatively unrotatablely couple together；If
When being equipped with the 3rd brake (B3) and being manipulated, make the be connected relatively unrotatablely with the 8th axle (8) the described 3rd
Brake a elements (B21) and housing (G) are coupled together.
3. the multi-shifting speed variator of a kind of planetary gear construction mode according to claim 1, it is characterised in that：The input
Axle (1) is with the first gear ring (P13), second clutch a elements (C21), the 3rd clutch a elements (C31) relatively unrotatablely
Connection.
4. the multi-shifting speed variator of a kind of planetary gear construction mode according to claim 1, it is characterised in that：
First forward gear is obtained by the brake (B1, B3) of closure first and the 3rd and first clutch (C1), by closure
Second and the 3rd brake (B2, B3) and first clutch (C1) obtain the second forward gear, by closing the 3rd brake
(B3) and the first and second clutches (C1, C2) obtain the 3rd forward gear, by closing the 3rd brake (B3) and first
Obtain the 4th forward gear with the 3rd clutch (C1, C3), or by close the 3rd brake (B3) and second and the 3rd from
Clutch (C2, C3) obtains the 4th forward gear, and the 5th advance is obtained by closing first, second, and third clutch (C1, C2, C3)
Gear, by close second brake (B2) and first and the 3rd clutch (C1, C3) obtain the 6th forward gear, by closure the
One brake (B1) and first and the 3rd clutch (C1, C3) obtain the 7th forward gear, by closure first and second brake
Device (B1, B2) and the 3rd clutch (C3) obtain the 8th forward gear, by closing the first brake (B1) and second and the
Three clutches (C2, C3) obtain the 9th forward gear, by the brake (B1, B3) of closure first and the 3rd and second clutch
(C2) reversed gear.
5. the multi-shifting speed variator of a kind of planetary gear construction mode according to claim 1, it is characterised in that：
The first, second, third and fourth planetary gearsets (Pl, P2, P3, P4) are configured to negative ratio epicyclic gear group；
The planetary gearsets are observed by the first planetary gearsets (Pl), the second planetary gearsets (P2), third planet vertically
Gear train (P3), the order of fourth planet gear train (P4) are set.
6. the multi-shifting speed variator of a kind of planetary gear construction mode according to claim 1, it is characterised in that：
The gear shift that each gear shift switching device (C1, C2, C3, B1, B2, B3) of the speed changer is constructed to be permeable to switch as needed is cut
Element is changed, especially electromechanical and/or electro-hydraulic gear shift switching device.
7. the multi-speed transmission of a kind of planetary gear construction mode according to claim 2, it is characterised in that：
The second clutch a elements (C21) are connected with the first gear ring (P13), and second clutch b elements (C22) is with first too
Sun wheel (P11) connection.
8. the multi-speed transmission of a kind of planetary gear construction mode according to claim 2, it is characterised in that：
The second clutch a elements (C21) are connected with the first planet carrier (P12), second clutch b elements (C22) and first
Sun gear (P11) is connected.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710089321.7A CN106838152A (en) | 2017-02-20 | 2017-02-20 | A kind of multi-shifting speed variator of planetary gear construction mode |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710089321.7A CN106838152A (en) | 2017-02-20 | 2017-02-20 | A kind of multi-shifting speed variator of planetary gear construction mode |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN106838152A true CN106838152A (en) | 2017-06-13 |
Family
ID=59127946
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710089321.7A Pending CN106838152A (en) | 2017-02-20 | 2017-02-20 | A kind of multi-shifting speed variator of planetary gear construction mode |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN106838152A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109340328A (en) * | 2018-12-10 | 2019-02-15 | 肇庆学院 | Multiple-speed gear-box |
| CN109372959A (en) * | 2018-12-10 | 2019-02-22 | 肇庆学院 | Nine speed automatic transmissions |
| CN113153988A (en) * | 2021-04-20 | 2021-07-23 | 中国北方车辆研究所 | Three-freedom nine-gear compound planetary transmission mechanism |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102005010210A1 (en) * | 2005-03-05 | 2006-09-14 | Zf Friedrichshafen Ag | Multi-speed transmission |
| DE102008041208A1 (en) * | 2008-08-13 | 2010-02-18 | Zf Friedrichshafen Ag | Multi-stage gearbox, particularly automatic gearbox for motor vehicle, comprises four planetary gear sets, which are arranged in housing, where eight rotating shafts include two drive shafts |
| CN101970902A (en) * | 2008-02-28 | 2011-02-09 | Zf腓德烈斯哈芬股份公司 | Multi-stage gearbox |
| CN104136807A (en) * | 2012-02-29 | 2014-11-05 | 腓特烈斯港齿轮工厂股份公司 | Multi-stage planetary vehicle transmission |
| CN106151415A (en) * | 2015-05-13 | 2016-11-23 | 现代自动车株式会社 | Epicyclic train for the automatic transmission of vehicle |
-
2017
- 2017-02-20 CN CN201710089321.7A patent/CN106838152A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102005010210A1 (en) * | 2005-03-05 | 2006-09-14 | Zf Friedrichshafen Ag | Multi-speed transmission |
| CN101970902A (en) * | 2008-02-28 | 2011-02-09 | Zf腓德烈斯哈芬股份公司 | Multi-stage gearbox |
| DE102008041208A1 (en) * | 2008-08-13 | 2010-02-18 | Zf Friedrichshafen Ag | Multi-stage gearbox, particularly automatic gearbox for motor vehicle, comprises four planetary gear sets, which are arranged in housing, where eight rotating shafts include two drive shafts |
| CN104136807A (en) * | 2012-02-29 | 2014-11-05 | 腓特烈斯港齿轮工厂股份公司 | Multi-stage planetary vehicle transmission |
| CN106151415A (en) * | 2015-05-13 | 2016-11-23 | 现代自动车株式会社 | Epicyclic train for the automatic transmission of vehicle |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109340328A (en) * | 2018-12-10 | 2019-02-15 | 肇庆学院 | Multiple-speed gear-box |
| CN109372959A (en) * | 2018-12-10 | 2019-02-22 | 肇庆学院 | Nine speed automatic transmissions |
| CN109372959B (en) * | 2018-12-10 | 2023-01-10 | 肇庆学院 | Nine-gear automatic transmission |
| CN109340328B (en) * | 2018-12-10 | 2023-01-10 | 肇庆学院 | Multi-speed transmission |
| CN113153988A (en) * | 2021-04-20 | 2021-07-23 | 中国北方车辆研究所 | Three-freedom nine-gear compound planetary transmission mechanism |
| CN113153988B (en) * | 2021-04-20 | 2023-11-28 | 中国北方车辆研究所 | Three-degree-of-freedom nine-gear compound planetary transmission mechanism |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN202468867U (en) | Parallel planetary gear transmission twin-countershaft transmission drive axle | |
| CN101463897B (en) | Automatic transmission for vehicles | |
| CN102844587B (en) | Double clutch group transmission and the method for operating dual clutch device group transmission | |
| CN102913597A (en) | Seven-level planet automatic speed changer | |
| CN105114558A (en) | Multi-gear automatic transmission | |
| CN105114561A (en) | Automatic nine-gear transmission | |
| CN105114562A (en) | Multi-gear transmission with planet gear structure mode | |
| CN103527732A (en) | Seven-gear planet automatic gearbox | |
| CN105114560A (en) | Multi-gear transmission achieved in mode of planetary gear structure | |
| CN103511565A (en) | Automatic six-gear planetary transmission | |
| CN205064722U (en) | Nine grades of automatic gearbox | |
| CN106838152A (en) | A kind of multi-shifting speed variator of planetary gear construction mode | |
| CN104755807B (en) | Double-clutch speed changer | |
| CN107199875B (en) | Hybrid vehicle transmission system | |
| CN106838153B (en) | A kind of seven previous planetary transmissions of falling four-degree-of-freedom | |
| CN106641135B (en) | A kind of 12 speed automatic transmissions | |
| CN105114559A (en) | Automatic nine-speed transmission | |
| CN204985566U (en) | Planetary gear configuration mode's many grades of derailleurs | |
| CN106763568A (en) | A kind of six keep off planetary automatic transmission | |
| CN109340327A (en) | The automatic gearbox of planetary gear construction mode | |
| CN205064720U (en) | Multi -step automatic gearbox | |
| CN204878554U (en) | Nine fast automatic gearbox | |
| CN205064721U (en) | Planetary gear configuration mode keeps off derailleur more | |
| CN106907468A (en) | Gearbox and automobile | |
| CN109340328A (en) | Multiple-speed gear-box |
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 | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20170613 |
|
| WD01 | Invention patent application deemed withdrawn after publication |