CN104948686B - There are two the transmission systems and vehicle of speed change grade for tool - Google Patents
There are two the transmission systems and vehicle of speed change grade for tool Download PDFInfo
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- CN104948686B CN104948686B CN201510129022.2A CN201510129022A CN104948686B CN 104948686 B CN104948686 B CN 104948686B CN 201510129022 A CN201510129022 A CN 201510129022A CN 104948686 B CN104948686 B CN 104948686B
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- speed changer
- clutch
- gearratio
- dissoluble
- output shaft
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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
- F16H3/64—Gearings having three or more central gears composed of a number of gear trains, the drive always passing through all the trains, each train having not more than one connection for driving another train
-
- 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
- F16H2200/0021—Transmissions for multiple ratios specially adapted for electric vehicles
-
- 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
- F16H2200/0043—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising four 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
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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
- F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two 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
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three 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
- F16H2200/202—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set
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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
- F16H2200/202—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set
- F16H2200/2023—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set using a Ravigneaux set with 4 connections
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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
- F16H2200/2035—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with two engaging means
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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
- F16H2200/2069—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes using two freewheel mechanism
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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
- F16H2200/2079—Transmissions using gears with orbital motion using freewheel type mechanisms, e.g. freewheel clutches
- F16H2200/2084—Transmissions using gears with orbital motion using freewheel type mechanisms, e.g. freewheel clutches two freewheel mechanisms
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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
- F16H2200/2097—Transmissions using gears with orbital motion comprising an orbital gear set member permanently connected to the housing, e.g. a sun wheel permanently connected to the housing
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The present invention relates to a kind of transmission system (GS), including with lower component：First speed changer (G1), with driven shaft (WA), for the first drive shaft (W1) of the first gearratio of the first speed changer (G1) and the second drive shaft (W2) of the second gearratio for the first speed changer (G1)；Second speed changer (G2), it is with input shaft (WE), the second output shaft (WA22) of the 4th gearratio for the first output shaft (WA21) of the third gearratio of the second speed changer (G2) and for the second speed changer (G2)；First dissoluble clutch (K1) prepares the first drive shaft (W1) connecting with the first output shaft (WA21)；And the second dissoluble clutch (K2), prepare the second drive shaft (W2) connecting with the second output shaft (WA22).The invention further relates to a kind of vehicle, with drive train according to the present invention (GS).
Description
Technical field
The present invention relates to a kind of transmission systems.The transmission system includes the first speed changer, which uses
In the first drive shaft of the first gearratio of the first speed changer.The transmission system can be for example using in the car or windmill
(Windmuehle) in.
In addition, the present invention relates to a kind of vehicles with the transmission system.
Background technology
A kind of vehicle speed variation for having and dimension being drawn to move (Ravigneaux) group is disclosed in 10 2,011 052 401 A1 of DE
Device.Here, small sun gear is always run as actuator and planetary gear carrier (commutator segment (Steg)) is always as defeated
Go out part operation.In the first drive shift, the big sun gear that La Wei moves group is fixed (locking, stuck) by the first brake.
In two drive shifts, planetary gear carrier is connect by clutch with the hollow wheel that dimension is drawn to move group.In reverse gear, hollow wheel passes through
Two brakes are fixed.
Invention content
Space and low-cost speed changer are saved in the case of it is an object of the invention to propose a kind of equal-wattage.
According to the present invention, which is realized by transmission system, the transmission system include the first and second speed changers and
First and second dissoluble clutches.First speed changer have driven shaft, for the first speed changer the first gearratio the
Second drive shaft of one drive shaft and the second gearratio for the first speed changer.Second speed changer has input shaft, is used for
Second output shaft of the first output shaft of the third gearratio of the second speed changer and the 4th gearratio for the second speed changer.
First dissoluble clutch prepares the first drive shaft and first exporting axis connection.Second dissoluble clutch prepares
For the second drive shaft and second to be exported axis connection.Typically, the first gearratio is better than the second gearratio.Independent of
This, it is typical that third gearratio is also better than the 4th gearratio.Dissoluble clutch can include (separated) connector sleeve
And/or sync-body.
Correspondingly, vehicle according to the invention has transmission device according to the present invention.
Idea of the invention can be, i.e., at least for the shift member of the torque of the second gearratio of transmission (the second gear)
(corresponding to the second dissoluble clutch) is arranged in the La Wei with higher rotation speed and moves on the side of group, that is, be arranged in tool
Have on the side compared with low torque.By the way that the shift member (the second dissoluble clutch) is made to transmit than for known vehicle speed variation
The smaller torque of clutch (namely smaller power) of second gear of device, for the clutch and then transmission dress of the second gear
It puts it is possible thereby to more compacter than known transmission for vehicles and/or be manufactured inexpensively.
It is advantageous when the first dissoluble clutch has the first idle running.It can be solved from idling conditions to first as a result,
The conversion of the coupling access state of the clutch removed can be realized in the case of no higher level's control function.It is optional or can replace
It changes, the second dissoluble clutch has the second idle running.As a result, from idling conditions to the coupling of the second dissoluble clutch
Closing the conversion of access state can realize in the case of no higher level's control function.
It is advantageous when the first idle running is reversible and/or the second idle running is reversible.Speed changer can be from drive as a result,
Dynamic model formula is transformed into take-back model and is transformed into drive mode from take-back model.
Optionally or alternatively, the first speed changer can include dimension is drawn to move group, wherein the first drive shaft is tieed up with drawing
The small sun gear connection of group is moved, and the second drive shaft is connect with the big sun gear that dimension is drawn to move group.The first speed changer can as a result,
It is particularly compact, reliable and be manufactured inexpensively.
When the second speed changer include planetary transmission when be particularly preferred.As a result, the second speed changer so that also have
Entire transmission device especially can be constructed economical space saving.
Another designing scheme proposes that the first output shaft of the second speed changer and the commutator segment of planetary transmission connect
It connects.Thus it is capable of providing the first gearratio with most strong deceleration using planetary transmission.
Another designing scheme proposes that the second output shaft of the second speed changer and the hollow wheel of planetary transmission connect
It connects.Thus it is capable of providing the second gearratio using planetary transmission.
One improvement project proposes that the commutator segment for planetary transmission provides the first brake.For planet tooth
First brake of the commutator segment of wheel speed, which can be contributed, is used to implement idle running and/or parking braking.
Another improvement project unrelated with this of transmission system propose, the hollow wheel for planetary transmission provides the
Two brakes.For the commutator segment of planetary transmission second brake can equally contribute be used to implement idle running and/
Or parking braking.
Description of the drawings
The present invention is described in more detail with reference to the accompanying drawings.It is shown in figure：
Fig. 1 is the schematic stream transmitted about torque in the transmission system of the first embodiment with the first speed changer
Cheng Tu；
Fig. 2 is the schematic stream transmitted about torque in the transmission system of the second embodiment with the first speed changer
Cheng Tu.
Specific embodiment
Next the embodiment further described presents the preferred design of the present invention.
The transmission system GS shown in Fig. 1 includes the first speed change grade G1 and the second speed change grade G2.First speed change grade G1 includes
La Wei with driven shaft WA moves group.In addition, the first speed change grade G1 includes the first drive shaft W1 and the second drive shaft W2.Driven shaft
WA is connect with the hollow wheel H1 that dimension is drawn to move group.First drive shaft W1 is connect with the small sun gear S11 that dimension is drawn to move group.Second drive shaft
W2 is connect with the big sun gear S12 that dimension is drawn to move group.La Wei moves the housing that the commutator segment St1 organized is fixed on the first speed changer G1
On.
Second speed change grade G2 includes having input shaft WE and the planet of the first output shaft WA21 and the second output shaft WA22
Gear-shift mechanism.The commutator segment St2 connections of first output shaft WA21 and planetary transmission.Second output shaft WA22 and row
The hollow wheel H2 connections of star gear-shift mechanism.For commutator segment St2, the first brake B1 is set.For the second system of hollow wheel H2 settings
Dynamic device B2.
First output shaft WA21 is connect by the first dissoluble clutch K1 with the first drive shaft W1.Second output shaft
WA22 is connect by the second dissoluble clutch K2 with the second drive shaft W2.
In addition, transmission system GS includes clutch synchronization device KS, ensure that two clutches K1, K2 are relevant to driving force
The idle running direction for flowing direction AKFR will not be opposite each other.Be relevant to from the second speed changer G2 to the first speed changer G1 (or return
Time receiving is from the first speed changer G1 to the second speed changer G2) identical force flow direction, the idle running direction of two clutches K1, K2 exist
It is directed toward on opposite direction of rotation.Whereby, the commutator segment St2's based on second clutch G2 and hollow wheel H2 is reciprocal
Direction of rotation, in identical driving force flow direction AKFR (or in identical recycling force flow direction RKFR), the first drive shaft
W1 and the second drive shaft W2 also has reciprocal driving direction of rotation.Thus the relativity of the direction of rotation is mended in slave end
It repays, i.e., due to small planetary gear P11, two sun gears S11, S12 also reciprocally rotate.
Chart 1：Shift logic and gearratio.
Explanation：DR- drives direction of rotation；First forwards of the D1- in drive mode；D1.r- is in take-back model
The first forward；Second forwards of the D2- in drive mode；Second forwards of the D2.r- in take-back model；
Reverse gears of the R- in drive mode；L- is to anticlockwise；Reverse gears of the R.r in take-back model；N- urgent operations (idle running)；P1, P2,
The variations of P3, P4- parking lock；E- coupling accesses；The coupling access that e.inv- is reversed；F- discharges；What f.inv- was reversed
Idle running；(f)-release is optional necessary；N- is used for the prefix of rotating speed；The resultant gear ratio of nH1/nS2- transmission systems GS；nH1/
The gearratio of the first speed changers of nW.- G1；The gearratio of the second speed changers of nWA2./nS2- G2；；R- is run to the right；X- is inessential
State.
The gearratio nWA2./nS2, nH1/nW. and nH1/nS2 provided in chart 1 is (real for the calculating of following rotating speed
Apply example)：ZH1=196；ZP11=24；ZP12=54；ZS11=48；ZS12=88；ZS2=44；ZH2=196；ZP2=76.
Here, zH1 is the rotating speed of hollow wheel H1, zP11 is the rotating speed of small planetary gear P11, and zP12 is the rotating speed of mafor planet gear P12,
ZS11 is the rotating speed of small sun gear S11 and zS12 is the rotating speed of big sun gear S12.In addition, zH2 is the rotating speed of hollow wheel H2,
ZP2 is the rotating speed of planetary gear P2 and zS2 is the rotating speed of sun gear S2.
Thus the functional mode of transmission system GS is given below, wherein assuming：In forward D1 and D2, the second speed change
The input shaft WE of device G2 by driving device A (such as motor) in a first direction (next it is being described as anticlockwise)
Rotating speed nS2 to be driven to drive.
In the first gear D1, the first brake B1 is released and thus the commutator segment St2 of the second speed changer G2 can
With rotation.Second brake B2 is locked and thus the hollow wheel H2 of the second speed changer G2 cannot rotate.Second speed changer G2
Sun gear S2 then to drive rotating speed nS2 to anticlockwise.The planetary gear P2 of second speed changer G2 is to right rotation.Second speed changer
The commutator segment St2 of G2 is to anticlockwise, and wherein its rotating speed is nSt2=nS2/ (1+zH2/zS2).
When driving torque is transmitted to by the first dissoluble clutch from the first output shaft WA21 of the second speed changer G2
During one drive shaft W1, the first dissoluble clutch K1 couplings access.When occurring slave end torque at identical direction of rotation,
First dissoluble clutch K1 is idle running, which becomes torque from first in the case where first clutch K1 does not dally
The first drive shaft W1 of fast device G2 is transmitted to the first output shaft WA21.
Therefore first dissoluble clutch K1 couples access.Because the commutator segment St2 of the second speed changer G2 is to left-handed
Turn, so the small sun gear S11 of the first speed changer G1 is equally rotated with rotating speed nW1=nSt2=nS2/ (1+zH2/zS2) to the left.
Because the commutator segment St1 of the first speed changer G1 is constantly locked, dimension is drawn to move the rotating speed nSt1 of the commutator segment St1 of group
=0.Small planetary gear P11 is around fixed axial right rotation.Whereby, mafor planet gear P12 is around fixed axial anticlockwise.
Next, big sun gear S12 with rotating speed nS12=-nW1*zS11/zS12 to right rotation.Second dissoluble clutch
Device K2 has opposite idle running direction in the method for operation of non-reverse as the first dissoluble clutch K1.Second can solve
The clutch K2 removed rotatably coupling accesses and to left-handed to the right on driving force flow direction in the method for operation of non-reverse
Turn ground idle running.On recycling force flow direction, the second dissoluble clutch K2 rotatably coupling accesses and to right rotation to the left
It dallies on ground.Therefore second dissoluble clutch K2 dallies, this is because it is rotatably driven to the right by slave end.(second is defeated
Shaft WA22 is locked by second brake B2.)
Because mafor planet gear P12 is around fixed axial anticlockwise, therefore, the hollow wheel H1 of the first speed changer is with rotating speed
NH1=nW1 × zS11/zH1 is to anticlockwise.
In the second gear D2, second brake B2 is released and thus the hollow wheel H2 of the second speed changer G2 can revolve
Turn.First brake B1 is locked and thus the commutator segment St2 of the second speed changer G2 cannot rotate.Second speed changer G2's
Sun gear S2 is to drive rotating speed nS2 to anticlockwise.Because the commutator segment St2 of the second speed changer G2 is locked by the first brake B1
Extremely, therefore the rotating speed nSt2 of the commutator segment St2 of the second speed changer is nSt2=0.The planetary gear P2 of second speed changer G2 encloses
Around fixed axial right rotation.Whereby, hollow wheel H2 with rotating speed nH2=-nS2*zS2/zH2 to right rotation.Second speed change whereby
The second output shaft WA22 of device G2 is just with rotating speed nWA22=nH2=-nS2*zS2/zH2 to right rotation.
When the second dissoluble clutch can be by driving moment from the second output shaft WA22 of the second speed changer G2 to
When the second drive shaft W2 of one speed changer G1 is transmitted, the second dissoluble clutch K2 is in the method for operation of non-reverse to dextrorotation
Turn ground driving.Second dissoluble clutch K2 is coupling access.Because the second output shaft WA22 is to right rotation, therefore first
The big sun gear S12 of speed changer G1 is equally with rotating speed nS12=nW2=-nS2 × zS2/zH2 to right rotation.Because the first speed change
The commutator segment St1 of device G1 is constantly locked, therefore the rotating speed nSt1 of commutator segment St1 that dimension is drawn to move group is nSt1=0.Greatly
Planetary gear P12 is around fixed axial anticlockwise.
Whereby, planetary gear P11 is around fixed axial right rotation.Next, small sun gear S11 is with rotating speed nS11=-
NW2*zS12/zS11 (wherein nW2 is negative and nS11 is just) is to anticlockwise.First dissoluble clutch K1 is in non-reverse
There is opposite idle running direction in the method for operation as the second dissoluble clutch K2.First dissoluble clutch K1 exists
Rotatably coupling is accessed and is rotatably dallied to the right to the left on driving force flow direction in the method for operation of non-reverse.It is recycling
On force flow direction, rotatably coupling is accessed and is rotatably dallied to the left the first dissoluble clutch K1 to the right.First can solve
Therefore the clutch K2 removed dallies, this is because it is rotatably driven to the left by slave end.(the first output shaft WA21 passes through first
Brake B2 is locked.)
Because mafor planet gear P12 is around fixed axial anticlockwise, therefore the hollow wheel H1 of the first speed changer G1 is to turn
Fast nH1=-nW2*zS12/zH1 (wherein nW2 is that negative and nH1 is negative) is to anticlockwise.
For reverse gear R, the idle running of idle running is reversely on the contrary (reversibly) and driving device A (such as motor) is opposite
Direction of rotation (in this example be to right rotation) on run.In terms of the difference, brake B1, B2 and transmission system GS
In force flow setting it is all identical with the first gear D1.
In parking position P1, P2, the commutator segment St2 of the second speed changer G2 is locked using the first brake B1, and
The hollow wheel H2 of the second speed changer G2 is locked using second brake B2.Whereby, two output shaft WA21 of the second speed changer G2,
WA22 is locked.When the first speed changer G1 in parking position driven shaft WA also should by it is locked when, it is contemplated that it is following
Measure.In the case of the La Wei with fixed commutator segment St1 moves group, two sun gears S11, S12 of group are moved in La Wei
It is upper to generate the torque applied in slave end simultaneously and then opposite turn in direction of rotation is also always generated on two drive shafts W1, W2
Square.Because two the output shafts WA21, WA22 of the second speed changer G2 are locked by the first brake B1 and second brake B2, and
And always lead to opposite torque on two drive shafts W1, W2 in the torque that slave end applies, therefore this is for parking lock
For be sufficiently used for locking driven shaft WA, two dissoluble clutch K1 in parking position, the idle running direction of K2 exist at this time
Identical idle running side is directed upwards towards, that is to say, that the direction of rotation of two dissoluble clutch K1, K2 are in driving force flow direction
On be it is identical (that is either two dissoluble clutches simultaneously to anticlockwise or two clutches simultaneously to dextrorotation
Turn).When the driven shaft WA of the first speed changer G1 should be existed in parking position by the first brake B1 and second brake B2
When being locked on two direction of rotation or one of two dissoluble clutch K1, K2 must be simultaneously two in parking position
It is locked on a direction of rotation.Or two clutch K1, K2 are relevant to force flow direction and (are namely relevant to drive in parking position
Direction of power flows AKFR or recycling force flow direction RKFR) there is the idle running of the same direction (namely with identical rotation side
To).This can for example be achieved in, i.e. one of two dissoluble clutch K1, K2 are run in the method for operation of non-reverse,
And another in two dissoluble clutch K1, K2 is run in the method for operation of reverse.
For urgent operation (idle running), the commutator segment St2 of the second speed changer G2 is released using the first brake B1, and
The hollow wheel H2 of the second speed changer G2 is released using second brake B2.Two output shaft WA21 of second speed changer G2 as a result,
WA22 dallies.Two dissoluble speed changer K1 are not dependent on, the state of K2, this is also applied for the driven shaft of the first speed changer G1
WA.Certainly, for such urgent operation it should be ensured that two dissoluble clutch K1, coupling access during K2 differences.
Commutator segment of the gearratio usually with the second speed changer G2 between the small sun gear S11 of one speed changer G1 and big sun gear S12
Gearratio between St2 and hollow wheel H2 is different.
In the case of fixed commutator segment, planetary transmission has following gearratio：NH/nS=-zS/zH.
In the case of fixed hollow wheel, planetary transmission has following gearratio：NSt/nS=1/ (1+zH/
ZS)=(zS/zH)/s, wherein, s:=zS/zH* (1+zH/zS)=1+zS/zH.
Because s is always greater than one, therefore the absolute value of the rotating speed nSt of commutator contact pin | nSt | in fixed hollow wheel
Always it is less than the absolute value of the rotating speed nH of the hollow wheel in the case of fixed commutator segment in situation | nH |.Work as planetary gear
When the corresponding driven shaft of transmission device is connect with commutator segment and hollow wheel is fixed, the deceleration of planetary transmission
Intensity improves s times when therefore being fixed than the hollow axis connection and commutator segment of driven shaft and the first speed changer.
When by sun gear S2 with above-mentioned example value transmission torque, obtained in fixed commutator segment：nH2/nS2
=-zS2/zH2=-44/196=-0.224.In fixed hollow shaft H2, s=1.224 and nSt2/nS2=0.224/
1.224=0.183.When commutator segment St2 drives output shaft WA21 and hollow wheel H2 is fixed, planetary transmission subtracts
Fast intensity improves (0.224/0.183-1) when therefore driving output shaft WA22 and commutator segment St2 fixations than hollow shaft H2
=22.4%.
The considerations of similar, is also applied for the first speed changer G1 that dimension is drawn to move group.La Wei is shown in FIG. 2 and moves to organize and leads to
Cross the configuration of commutator segment St1 and slave unit.
The s=1+zS11/zH1 in the first gear D1 of fixed hollow wheel H1；And commutator segment be St1's and Sunny
It is nSt1/nS11=- (zS11/zH1)/s, wherein s=1+zS11/zH1 to take turns the relevant rotating speed nSt1/nS11 of S11.It is more than utilization
The number of teeth, s=1.245 and nSt1/nS11=-0.197.
The s=1+zS12/zH1 in the second gear D2 of fixed hollow wheel H1；And commutator segment be St1's and major planet
It is nSt1/nS12=(zS12/zH1)/s, wherein s=1+zS12/zH1 to take turns the relevant rotating speed nSt1/nS12 of S12.It is more than utilization
The number of teeth, s=1.449 and nSt1/nS12=0.310.
Using the above-described number of teeth, when commutator segment St1 drives driven shaft WA and dimension is drawn to move the hollow wheel of speed changer
H1 be fixed in position when, La Wei move deceleration intensity of the speed changer G1 in the case of asteroid wheel S11 is used therefore than hollow
Higher when taking turns H1 driving driven shaft WA and the fixation of commutator segment St1 positions.Using the above-described number of teeth, in the first gear D1
In it is strong by about 24% by deceleration of reduction ratio of the commutator segment St1 in the case of driven when driven by hollow wheel H1
(=0.197/0.244-1).In the second gear D2, using the above-mentioned number of teeth, in the case of driven by commutator segment St1
The strong about 45% (=0.449/0.310-1) of deceleration of the reduction ratio when driven by hollow wheel H2.
The gearratio shown in chart 2 is obtained in the case of the fixed hollow wheel H1 of the first speed changer G1.
| DR | B1 | B2 | K1 | K2 | nWA2./nS2 | nSt1/nW. | nSt1/nS2 | |
| D1 | l | f | b | e | f | 0.183 | 0.197 | 0.0361 |
| D1.r | l | f | b | f | e | 0.183 | 0.197 | 0.0361 |
| D2 | l | b | f | f | e | 0.224 | 0.310 | 0.0694 |
| D2.r | l | b | f | e | f | 0.224 | 0.310 | 0.0694 |
| R | r | f | b | e.inv | f.inv | 0.183 | 0.197 | 0.0361 |
| R.r | r | f | b | f.inv | e.inv | 0.183 | 0.197 | 0.0361 |
Chart 2：The shift logic and gearratio (explanation such as chart 1) of second embodiment.
The designing scheme variant for having the advantages that fixed hollow wheel can be seen in larger deceleration strength conditions.It should
Another advantage of designing scheme variant with fixed hollow wheel is larger between the first gear D1 and the second gear D2
Kingpin inclination (Spreizung) in see.Kingpin inclination when driven by hollow wheel H1 is about 1.84 and logical
Cross commutator segment St1 it is driven when only 1.92.
The designing scheme each described of transmission system G2 can be integrated completely or partially with driving device A, example
Such as it is integrated into the sleeve rotor of motor.Here, the hollow wheel H1, H2 of the first speed changer G1 and/or the second speed changer G2 with
The cylindrical wall of rotor is fixedly connected either identical.
Transmission system GS can have the first speed changer G1 and dissoluble clutch K1 of the second speed changer G2 and first
With the second dissoluble clutch K2.First speed changer G1 can have driven shaft WA, be passed for the first of the first speed changer G1
The second drive shaft W2 of first drive shaft W1 of dynamic ratio and the second gearratio for the first speed changer G1.Second speed changer
G2 can have input shaft WE, for the second speed changer G2 third gearratio the first output shaft WA21 and for second become
Second output shaft WA22 of the 4th gearratio of fast case G2.First dissoluble clutch K1 prepares for by the first drive shaft W1
It is connect with the first output shaft WA21.Second dissoluble clutch K2 prepares for by the second drive shaft W2 and the second output shaft
WA22 connections.Typically, the first gearratio is better than the second gearratio.Independent of this, it is typical that third gearratio is also strong
In the 4th gearratio.
Claims (5)
1. a kind of transmission system (GS), the transmission system include：
- the first speed changer (G1), first speed changer have driven shaft (WA), first for first speed changer (G1)
The second drive shaft (W2) of the first drive shaft (W1) of gearratio and the second gearratio for first speed changer (G1)；
- the second speed changer (G2), second speed changer have input shaft (WE), the third for second speed changer (G2)
Second output shaft of the first output shaft (WA21) of gearratio and the 4th gearratio for second speed changer (G2)
(WA22)；
- the first dissoluble clutch (K1), the first dissoluble clutch prepare to be used for first drive shaft
(W1) it is connect with first output shaft (WA21)；And
- the second dissoluble clutch (K2), the second dissoluble clutch prepare to be used for second drive shaft
(W2) it is connect with second output shaft (WA22),
Wherein described first gearratio is more than second gearratio and/or the third gearratio is more than the described 4th transmission
Than,
Second speed changer (G2) includes planetary transmission,
First output shaft (WA21) of second speed changer (G2) and the commutator segment of the planetary transmission
(St2) it connects,
Second output shaft (WA22) of second speed changer (G2) and the hollow wheel (H2) of the planetary transmission
Connection,
Commutator segment (St2) for the planetary transmission sets the first brake (B1),
Hollow wheel (H2) for second speed changer (G2) sets second brake (B2).
2. transmission system (GS) according to claim 1, which is characterized in that first dissoluble clutch (K1) packet
It includes the first idle running and/or the second dissoluble clutch (K2) and includes the second idle running (K2).
3. transmission system (GS) according to claim 2, which is characterized in that first idle running is reversible and/or institute
The second idle running is stated to be reversible.
4. transmission system (GS) according to any one of claim 1 to 3, which is characterized in that first speed changer
(G1) including dimension is drawn to move group, and first drive shaft (W1) is connect with the small sun gear (S11) that dimension is drawn to move group, and
Second drive shaft (W2) connect with the big sun gear (S12) that dimension is drawn to move group.
5. a kind of vehicle, which is characterized in that the vehicle includes transmission system according to any one of claim 1 to 4
(GS)。
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102014205553.9A DE102014205553B4 (en) | 2014-03-25 | 2014-03-25 | Transmission system with two gear stages and vehicle |
| DE102014205553.9 | 2014-03-25 |
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| CN104948686A CN104948686A (en) | 2015-09-30 |
| CN104948686B true CN104948686B (en) | 2018-06-29 |
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| CN201510129022.2A Active CN104948686B (en) | 2014-03-25 | 2015-03-23 | There are two the transmission systems and vehicle of speed change grade for tool |
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| DE (1) | DE102014205553B4 (en) |
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| JP7042257B2 (en) * | 2016-09-30 | 2022-03-25 | リナマー・コーポレーション | Multi-speed transmission |
| DE102017004898A1 (en) * | 2017-05-20 | 2018-11-22 | Daimler Ag | Transmission device for an electric drive |
| CN108050222B (en) * | 2017-12-08 | 2021-04-02 | 合肥工业大学 | Two keep off electric automobile electric drive system |
| CN110182036A (en) * | 2018-12-14 | 2019-08-30 | 华南理工大学 | A kind of integrated form third gear power drive system |
Family Cites Families (14)
| Publication number | Priority date | Publication date | Assignee | Title |
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| US3482469A (en) | 1966-11-29 | 1969-12-09 | Nissan Motor | Automatic speed change gear |
| DE10221095A1 (en) | 2002-05-11 | 2004-07-22 | Zf Friedrichshafen Ag | Multi-speed transmission |
| JP3751915B2 (en) * | 2002-07-16 | 2006-03-08 | ジヤトコ株式会社 | Gear transmission for automatic transmission |
| KR100559336B1 (en) * | 2004-02-26 | 2006-03-15 | 현대자동차주식회사 | A six-speed power train of an automatic transmission for a vehicle |
| US7294089B2 (en) | 2005-08-15 | 2007-11-13 | Ford Global Technologies, Llc | Multiple-speed automatic transmission |
| US7766785B2 (en) * | 2007-01-25 | 2010-08-03 | Ford Global Technologies, Llc | Multiple speed automatic transmission |
| US7942781B2 (en) | 2007-10-12 | 2011-05-17 | Means Industries, Inc. | High-efficiency vehicular transmission |
| KR100916774B1 (en) * | 2007-11-02 | 2009-09-14 | 현대자동차주식회사 | Power train of automatic transmission |
| JP4720898B2 (en) | 2008-11-21 | 2011-07-13 | トヨタ自動車株式会社 | Hybrid drive device for vehicle |
| JP5221505B2 (en) | 2009-12-07 | 2013-06-26 | ジヤトコ株式会社 | Automatic transmission |
| KR101234655B1 (en) * | 2010-11-24 | 2013-02-19 | 기아자동차주식회사 | continuous variable transmission for use a vehicle |
| KR101251532B1 (en) * | 2011-12-09 | 2013-04-05 | 현대자동차주식회사 | Planetary gear train of automatic transmission for vehicles |
| DE102012201374A1 (en) | 2012-01-31 | 2013-08-01 | Zf Friedrichshafen Ag | Hybrid powertrain for a motor vehicle |
| CN103158526B (en) * | 2013-02-28 | 2015-12-02 | 长城汽车股份有限公司 | A kind of drive apparatus for hybrid vehicle |
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| CN104948686A (en) | 2015-09-30 |
| DE102014205553A1 (en) | 2015-10-01 |
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