CN104948686A - Gear system with two transmission stages and vehicle - Google Patents
Gear system with two transmission stages and vehicle Download PDFInfo
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- CN104948686A CN104948686A CN201510129022.2A CN201510129022A CN104948686A CN 104948686 A CN104948686 A CN 104948686A CN 201510129022 A CN201510129022 A CN 201510129022A CN 104948686 A CN104948686 A CN 104948686A
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- speed changer
- clutch
- dissoluble
- transmission system
- gear
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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
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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
- F16H2200/0021—Transmissions for multiple ratios specially adapted for electric vehicles
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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
- F16H2200/003—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
- F16H2200/0086—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising two reverse speeds
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/2007—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
A gear system (GS) includes: a first gear (G1) having a driven shaft (WA), a first driving shaft (W1) for a first gear ratio of first gear (G1) and a second driving shaft (W2) for a second transmission ratio of the first gear (G1); a second gear (G2) having an input shaft (WE), a first output shaft (WA21) for a third gear ratio of the second gear (G1) and a second output shaft (WA22) for a fourth gear ratio of the second gear (G2) comprises; a first releasable coupling (K1), which is prepared for connecting the first driving shaft (W1) to the first output shaft (WA21) to connect; and a second releasable coupling (K2), which is prepared to connect the second driving shaft (W2) to the second output shaft (WA22). The invention also relates to a vehicle having an inventive gear system (GS).
Description
Technical field
The present invention relates to a kind of transmission system.This transmission system comprises the first speed changer, and this first speed changer driven shaft, for the first live axle of the first velocity ratio of the first speed changer.This transmission system can such as be applied in vehicle or in windmill (Windmuehle).
In addition, the present invention relates to a kind of vehicle with this transmission system.
Background technique
In DE 10 2,011 052 401 A1, disclose one there is La Wei move the transmission for vehicles that (Ravigneaux) organize.At this, small sun gear always runs as actuator and planetary gear carrier (commutator segment (Steg)) always runs as output member.In the first forward gears, the large sun gear that La Wei moves group is fixed (locking, stuck) by the first break.In the second forward gears, planetary gear carrier is tieed up the hollow wheels of moving group by clutch and is connected with drawing.In reverse gear, hollow wheels is fixed by second brake.
Summary of the invention
The object of the invention is to the speed changer of saving space when proposing a kind of equal-wattage and low cost.
According to the present invention, this object is realized by transmission system, and this transmission system comprises the first and second speed changers and the first and second dissoluble clutches.First speed changer has the second live axle of driven shaft, the first live axle for the first velocity ratio of the first speed changer and the second velocity ratio for the first speed changer.Second speed changer has the second output shaft of input shaft, the first output shaft for the 3rd velocity ratio of the second speed changer and the 4th velocity ratio for the second speed changer.First dissoluble clutch prepares to be used for the first live axle to be connected with the first output shaft.Second dissoluble clutch prepares to be used for the second live axle to be connected with the second output shaft.Typically, the first velocity ratio is better than the second velocity ratio.Do not rely on this, typically, the 3rd velocity ratio is also better than the 4th velocity ratio.Dissoluble clutch can comprise (separating) connecting sleeve and/or sync-body.
Correspondingly, vehicle according to the invention has according to transmission device of the present invention.
Concept of the present invention can be, namely the shift member (corresponding to the second dissoluble clutch) at least for transmitting the torque of the second velocity ratio (the second gear) is arranged in the side that the La Wei with higher rotation speed moves group, is namely arranged on the side that has compared with low torque.By making this shift member (the second dissoluble clutch) transmit the torque (namely less power) less than the clutch of the second gear being used for known transmission for vehicles, thus can be compacter and/or manufacture at an easy rate than known transmission for vehicles for the clutch of the second gear and then transmission device.
Favourable when the first dissoluble clutch has the first idle running.Thus, the conversion from idling conditions to the coupling access state of the first dissoluble clutch can realize when not having higher level's controlling functions.Optional or alternatively, the second dissoluble clutch has the second idle running.Thus, the conversion from idling conditions to the coupling access state of the second dissoluble clutch can realize when not having higher level's controlling functions.
Favourable when the first idle running is reversible and/or the second idle running is reversible.Thus, speed changer can be transformed into take-back model from drive pattern and be transformed into drive pattern from take-back model.
Optionally or alternatively, the first speed changer can comprise La Wei and move group, wherein the first live axle is tieed up the small sun gear moving group and is connected with drawing, and the second live axle is tieed up the large sun gear moving group and is connected with drawing.Thus, the first speed changer can compact especially, reliably and at an easy rate manufacture.
Particularly preferred when the second speed changer comprises planetary transmission.Thus, the second speed changer so that also have whole transmission device can especially economical space saving construct.
Another design proposal proposes, and the first output shaft of the second speed changer is connected with the commutator segment of planetary transmission.Utilize planetary transmission can provide first velocity ratio with the strongest deceleration thus.
Another design proposal proposes, and the second output shaft of the second speed changer is connected with the hollow wheels of planetary transmission.Utilize planetary transmission can provide the second velocity ratio thus.
An improvement project proposes, and the commutator segment for planetary transmission provides the first break.The first break for the commutator segment of planetary transmission can be contributed for realizing idle running and/or parking braking.
Another irrelevant therewith improvement project of transmission system proposes, for the hollow wheels of planetary transmission provides second brake.Second brake for the commutator segment of planetary transmission can be contributed equally for realizing idle running and/or parking braking.
Accompanying drawing explanation
The present invention is described in more detail with reference to the accompanying drawings.Shown in figure:
Fig. 1 is the indicative flowchart about transmission of torque in the transmission system of first embodiment with the first speed changer;
Fig. 2 is the indicative flowchart about transmission of torque in the transmission system of second embodiment with the first speed changer.
Embodiment
Next the embodiment further described presents preferred design of the present invention.
Transmission system GS shown in Fig. 1 comprises the first speed change level G1 and the second speed change level G2.The La Wei that first speed change level G1 comprises with driven shaft WA moves group.In addition, the first speed change level G1 comprises the first live axle W1 and the second live axle W2.Driven shaft WA ties up the hollow wheels H1 moving group and is connected with drawing.First live axle W1 ties up the small sun gear S11 moving group and is connected with drawing.Second live axle W2 ties up the large sun gear S12 moving group and is connected with drawing.The commutator segment St1 that La Wei moves group is fixed on the housing of the first speed changer G1.
Second speed change level G2 comprises the planetary transmission with input shaft WE and the first output shaft WA21 and the second output shaft WA22.First output shaft WA21 is connected with the commutator segment St2 of planetary transmission.Second output shaft WA22 is connected with the hollow wheels H2 of planetary transmission.For commutator segment St2 arranges the first break B1.For hollow wheels H2 arranges second brake B2.
First output shaft WA21 is connected with the first live axle W1 by the first dissoluble clutch K1.Second output shaft WA22 is connected with the second live axle W2 by the second dissoluble clutch K2.
In addition, transmission system GS comprises clutch synchronization device KS, and it guarantees two clutch K1, and K2 is relevant to the idle running direction of driving force flow path direction AKFR can not be opposite each other.Be relevant to from the second speed changer G2 to the first speed changer G1 the identical power flow path direction of (or when reclaiming from the first speed changer G1 to the second speed changer G2), the idle running direction of two clutch K1, K2 is pointed in the opposite rotation direction.Whereby, based on the commutator segment St2 of second clutch G2 and the reciprocal sense of rotation of hollow wheels H2, when identical driving force flow path direction AKFR (or at identical recovery power flow path direction RKFR), the first live axle W1 and the second live axle W2 also has reciprocal driving sense of rotation.The relativity of this sense of rotation compensates thus at slave end, and namely due to little planetary pinion P11, two sun gear S11, S12 also reciprocally rotates.
Chart 1: gearshift logic and velocity ratio.
Illustrate: DR-drives sense of rotation; The first advance gear of D1-in drive pattern; The first advance gear of D1.r-in take-back model; The second advance gear of D2-in drive pattern; The second advance gear of D2.r-in take-back model; The reverse gear of R-in drive pattern; L-is to anticlockwise; The reverse gear of R.r in take-back model; N-promptly runs (idle running); The variations of P1, P2, P3, P4-parking lock; E-is coupled access; The coupling access that e.inv-reverses; F-discharges; The idle running that f.inv-reverses; (f)-discharge optional necessity; N-is used for the prefix of rotating speed; The resultant gear ratio of nH1/nS2-transmission system GS; The velocity ratio of nH1/nW.-first speed changer G1; The velocity ratio of nWA2./nS2-second speed changer G2; ; R-runs to the right; The inessential state of x-.
The velocity ratio nWA2./nS2 provided in chart 1, nH1/nW. and nH1/nS2 are used for the calculating (embodiment) of following rotating speed: zH1=196; ZP11=24; ZP12=54; ZS11=48; ZS12=88; ZS2=44; ZH2=196; ZP2=76.At this, zH1 is the rotating speed of hollow wheels H1, and zP11 is the rotating speed of small planetary gear P11, and zP12 is the rotating speed of mafor planet gear P12, and zS11 is the rotating speed of small sun gear S11 and zS12 is the rotating speed of large sun gear S12.In addition, zH2 is the rotating speed of hollow wheels H2, and zP2 is the rotating speed of planetary pinion P2 and zS2 is the rotating speed of sun gear S2.
The functional mode of transmission system GS provides thus as follows, wherein suppose: in advance gear D1 and D2, the input shaft WE of the second speed changer G2 by drive unit A (such as motor) in a first direction (next it described as anticlockwise) to drive rotating speed nS2 to drive.
In the first gear D1, the first break B1 is released and the commutator segment St2 of the second speed changer G2 can rotate thus.Locked and the hollow wheels H2 that is the second speed changer G2 thus of second brake B2 just can not rotate.The sun gear S2 of the second speed changer G2 is then to drive rotating speed nS2 to anticlockwise.The planetary pinion P2 of the second speed changer G2 is to right rotation.The commutator segment St2 of the second speed changer G2 is to anticlockwise, and wherein its rotating speed is nSt2=nS2/ (1+zH2/zS2).
When driving torque is delivered to the first live axle W1 from the first output shaft WA21 of the second speed changer G2 by the first dissoluble clutch, the first dissoluble clutch K1 is coupled and accesses.When there is slave end moment when identical sense of rotation, the first dissoluble clutch K1 is idle running, and torque is delivered to the first output shaft WA21 from the first live axle W1 of the first speed changer G2 when first clutch K1 does not dally by this moment.
Therefore first dissoluble clutch K1 is coupled access.Because the commutator segment St2 of the second speed changer G2 is to anticlockwise, so the small sun gear S11 of the first speed changer G1 rotates with rotating speed nW1=nSt2=nS2/ (1+zH2/zS2) equally left.Because the commutator segment St1 of the first speed changer G1 is by locked constantly, so draw dimension to move the rotating speed nSt1=0 of the commutator segment St1 of group.Small planetary gear P11 is around fixing axial right rotation.Whereby, mafor planet gear P12 is around fixing axial anticlockwise.
Next, large sun gear S12 with rotating speed nS12=-nW1*zS11/zS12 to right rotation.Second dissoluble clutch K2 has contrary idle running direction in the method for operation of non-reverse as the first dissoluble clutch K1.Second dissoluble clutch K2 is coupled rotatably to the right and accesses and dally rotatably left in the method for operation of non-reverse on driving force flow path direction.On recovery power flow path direction, the second dissoluble clutch K2 is coupled rotatably left and accesses and dally rotatably to the right.Therefore second dissoluble clutch K2 dallies, this is because it is driven to the right rotatably by slave end.(the second output shaft WA22 is locked by second brake B2.)
Because mafor planet gear P12 is around fixing axial anticlockwise, therefore, the hollow wheels H1 of the first speed changer with rotating speed nH1=nW1 × zS11/zH1 to anticlockwise.
In the second gear D2, second brake B2 is released and the hollow wheels H2 of the second speed changer G2 is just rotatable thus.Locked and the commutator segment St2 that is the second speed changer G2 thus of first break B1 just can not rotate.The sun gear S2 of the second speed changer G2 is to drive rotating speed nS2 to anticlockwise.Because the commutator segment St2 of the second speed changer G2 is locked by the first break B1, therefore the rotating speed nSt2 of the commutator segment St2 of the second speed changer is nSt2=0.The planetary pinion P2 of the second speed changer G2 is around fixing axial right rotation.Whereby, hollow wheels H2 with rotating speed nH2=-nS2*zS2/zH2 to right rotation.Whereby the second output shaft WA22 of the second speed changer G2 just with rotating speed nWA22=nH2=-nS2*zS2/zH2 to right rotation.
When the second live axle W2 of driving moment from the second output shaft WA22 of the second speed changer G2 to the first speed changer G1 can transmit by the second dissoluble clutch, the second dissoluble clutch K2 drives rotatably to the right in the method for operation of non-reverse.Second dissoluble clutch K2 is coupling access.Because the second output shaft WA22 is to right rotation, therefore the large sun gear S12 of the first speed changer G1 equally with rotating speed nS12=nW2=-nS2 × zS2/zH2 to right rotation.Because the commutator segment St1 of the first speed changer G1 is by locked constantly, the rotating speed nSt1 therefore drawing dimension to move the commutator segment St1 of group is nSt1=0.Mafor planet gear P12 is around fixing axial anticlockwise.
Whereby, planetary pinion P11 is around fixing axial right rotation.Next, small sun gear S11 with rotating speed nS11=-nW2*zS12/zS11 (wherein nW2 is for negative and nS11 is just) to anticlockwise.First dissoluble clutch K1 has contrary idle running direction in the method for operation of non-reverse as the second dissoluble clutch K2.First dissoluble clutch K1 is coupled rotatably left and accesses and dally rotatably to the right in the method for operation of non-reverse on driving force flow path direction.On recovery power flow path direction, the first dissoluble clutch K1 is coupled rotatably to the right and accesses and dally rotatably left.Therefore first dissoluble clutch K2 dallies, this is because it is driven left rotatably by slave end.(the first output shaft WA21 is locked by the first break B2.)
Because mafor planet gear P12 is around fixing axial anticlockwise, therefore the hollow wheels H1 of the first speed changer G1 with rotating speed nH1=-nW2*zS12/zH1 (wherein nW2 is for negative and nH1 is negative) to anticlockwise.
For reverse gear R, oppositely (reversibly) and drive unit A (such as motor) run contrary sense of rotation (being in this example to right rotation) is upper on the contrary for the idle running of idle running.From this difference, the setting of the power stream in break B1, B2 and transmission system GS is all identical with the first gear D1.
At parking position P1, in P2, utilize the commutator segment St2 of the locked second speed changer G2 of the first break B1, and utilize the hollow wheels H2 of the locked second speed changer G2 of second brake B2.Whereby, two output shaft WA21 of the second speed changer G2, WA22 is locked.When in parking position the first speed changer G1 driven shaft WA also should by locked time, should following measures be considered.When the La Wei with fixing commutator segment St1 moves group, move two sun gear S11 of group at La Wei, S12 upper produce slave end apply torque and and then also at two live axle W1, W2 always produces the contrary torque of sense of rotation.Because two output shaft WA21 of the second speed changer G2, WA22 is locked by the first break B1 and second brake B2, and slave end apply torque at two live axle W1, W2 always causes contrary torque, therefore this is enough for locking driven shaft WA for parking lock, now two dissoluble clutch K1 in parking position, the idle running direction of K2 is directed upwards towards in identical idle running side, that is two dissoluble clutch K1, the sense of rotation of K2 is identical (that is or two dissoluble clutches simultaneously to anticlockwise or two clutches simultaneously to right rotation) on driving force flow path direction.When the driven shaft WA of the first speed changer G1 in parking position should locked in two rotational directions by the first break B1 and second brake B2 time, or two dissoluble clutch K1, one of K2 must be simultaneously locked in two rotational directions in parking position.Or two clutch K1, K2 are relevant to the idle running (namely with identical sense of rotation) that power flow path direction (being namely relevant to driving force flow path direction AKFR or the power of recovery flow path direction RKFR) has equidirectional in parking position.This such as can realize thus, and namely two dissoluble clutch K1, one of K2 run in the method for operation of non-reverse, and two dissoluble clutch K1, another in K2 runs in the method for operation reversed.
Run (idle running) for urgent, utilize the first break B1 to remove the commutator segment St2 of the second speed changer G2, and utilize second brake B2 to remove the hollow wheels H2 of the second speed changer G2.Thus, two output shaft WA21 of the second speed changer G2, WA22 idle running.Do not depend on the state of two dissoluble speed changer K1, K2, this is also applicable to the driven shaft WA of the first speed changer G1.Certainly, coupling access when should guarantee that two dissoluble clutch K1, K2 are different for so urgent operation.Velocity ratio between the small sun gear S11 and large sun gear S12 of the first speed changer G1 is usually different from the velocity ratio between the commutator segment St2 of the second speed changer G2 and hollow wheels H2.
When fixing commutator segment, planetary transmission has following velocity ratio: nH/nS=-zS/zH.
When fixing hollow wheels, planetary transmission has following velocity ratio: nSt/nS=1/ (1+zH/zS)=(zS/zH)/s, wherein, and s:=zS/zH* (1+zH/zS)=1+zS/zH.
Because s is always greater than one, the absolute value of the rotating speed nSt of therefore commutator contact pin | nSt| is always less than the absolute value of the rotating speed nH of the hollow wheels when fixing commutator segment when fixing hollow wheels | nH|.When the corresponding driven shaft of planetary type gear transmission unit is connected with commutator segment and hollow wheels is fixing, therefore the deceleration intensity of planetary transmission to be connected with the hollow shaft of the first speed changer than driven shaft and commutator segment is fixed time improve s doubly.
When transmitting torque by sun gear S2 with above-mentioned example value, obtain when fixing commutator segment: nH2/nS2=-zS2/zH2=-44/196=-0.224.When fixing hollow shaft H2, s=1.224 and nSt2/nS2=0.224/1.224=0.183.As commutator segment St2 driver output axle WA21 and hollow wheels H2 fixes time, the deceleration intensity of planetary transmission therefore than hollow shaft H2 driver output axle WA22 and commutator segment St2 fixes time improve (0.224/0.183-1)=22.4%.
Similar consideration is also applicable to have the first speed changer G1 that La Wei moves group.Figure 2 illustrates La Wei and move the configuration of group by commutator segment St1 and driven device.
S=1+zS11/zH1 in the first gear D1 of fixing hollow wheels H1; And the rotating speed nSt1/nS11 relevant to small sun gear S11 of commutator segment St1 is nSt1/nS11=-(zS11/zH1)/s, wherein s=1+zS11/zH1.Utilize the above-described number of teeth, s=1.245 and nSt1/nS11=-0.197.
S=1+zS12/zH1 in the second gear D2 of fixing hollow wheels H1; And commutator segment St1 to take turns the relevant rotating speed nSt1/nS12 of S12 to major planets be nSt1/nS12=(zS12/zH1)/s, wherein s=1+zS12/zH1.Utilize the above-described number of teeth, s=1.449 and nSt1/nS12=0.310.
Utilize the above-described number of teeth, when commutator segment St1 drive driven shaft WA and the hollow wheels H1 drawing dimension to move speed changer to be position fixing time, La Wei move the deceleration intensity of speed changer G1 when using asteroid wheel S11 therefore drive driven shaft WA than hollow wheels H1 and commutator segment St1 position is fixed time higher.Utilize the above-described number of teeth, by the strong about 24% (=0.197/0.244-1) of the deceleration of the reduction speed ratio in the driven situation of commutator segment St1 when driven by hollow wheels H1 in the first gear D1.In the second gear D2, utilize the above-mentioned number of teeth, the strong about 45% (=0.449/0.310-1) of the deceleration of the reduction speed ratio when driven by commutator segment St1 when driven by hollow wheels H2.
The velocity ratio shown in chart 2 is obtained when the hollow wheels H1 fixed 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 |
The gearshift logic of chart 2: the second embodiment and velocity ratio (illustrating as chart 1).
The advantage with the design proposal variant of fixing hollow wheels can be seen in larger deceleration strength conditions.See in the larger Kingpin inclination (Spreizung) of this another advantage with the design proposal variant of fixing hollow wheels between the first gear D1 and the second gear D2.Kingpin inclination when driven by hollow wheels H1 is about 1.84 and is only 1.92 when driven by commutator segment St1.
The design proposal of each description of transmission system G2 can be integrated with drive unit A completely or partially, such as, be integrated in the sleeve rotor of motor.At this, the hollow wheels H1 of the first speed changer G1 and/or the second speed changer G2, H2 are fixedly connected with the columniform wall of rotor or identical.
Transmission system GS can have the first speed changer G1 and the second speed changer G2 and the first dissoluble clutch K1 and the second dissoluble clutch K2.First speed changer G1 can have driven shaft WA, the first live axle W1 for first velocity ratio of the first speed changer G1, and the second live axle W2 of the second velocity ratio for the first speed changer G1.Second speed changer G2 can have the second output shaft WA22 of input shaft WE, the first output shaft WA21 for the 3rd velocity ratio of the second speed changer G2 and the 4th velocity ratio for the second gearbox G2.First dissoluble clutch K1 prepares to be used for the first live axle W1 to be connected with the first output shaft WA21.Second dissoluble clutch K2 prepares to be used for the second live axle W2 to be connected with the second output shaft WA22.Typically, the first velocity ratio is better than the second velocity ratio.Do not rely on this, typically, the 3rd velocity ratio is also better than the 4th velocity ratio.
Claims (10)
1. a transmission system (GS), described transmission system comprises:
-the first speed changer (G1), described first speed changer has driven shaft (WA), the second live axle (W2) for first live axle (W1) of the first velocity ratio of described first speed changer (G1) and the second velocity ratio for described first speed changer (G1);
-the second speed changer (G2), described second speed changer has input shaft (WE), the second output shaft (WA22) for first output shaft (WA21) of the 3rd velocity ratio of described second speed changer (G2) and the 4th velocity ratio for described second speed changer (G2);
-the first dissoluble clutch (K1), described first dissoluble clutch prepares to be used for described first live axle (W1) to be connected with described first output shaft (WA21); And
-the second dissoluble clutch (K2), described second dissoluble clutch prepares to be used for described second live axle (W2) to be connected with described second output shaft (WA22).
2. transmission system according to claim 1 (GS), it is characterized in that, described first dissoluble clutch (K1) comprises the first idle running and/or described second dissoluble clutch (K2) comprises the second idle running (K2).
3. transmission system according to claim 2 (GS), is characterized in that, described first idle running is reversible and/or described second idle running is reversible.
4. transmission system according to any one of claim 1 to 3 (GS), it is characterized in that, described first speed changer (G1) comprises La Wei and moves group, and described first live axle (W1) is tieed up the small sun gear (S11) moving group be connected with described being drawn, and described second live axle (W2) is tieed up the large sun gear (S12) moving group be connected with described being drawn.
5. transmission system according to any one of claim 1 to 4 (GS), is characterized in that, described second speed changer (G2) comprises planetary transmission.
6. transmission system according to claim 5 (GS), it is characterized in that, described first output shaft (WA21) of described second speed changer (G2) is connected with the commutator segment (St2) of described planetary transmission.
7. the transmission system (GS) according to claim 5 or 6, it is characterized in that, described second output shaft (WA22) of described second speed changer (G2) is connected with the hollow wheels (H2) of described planetary transmission.
8. the transmission system (GS) according to any one of claim 5 to 7, is characterized in that, for the commutator segment (St2) of described planetary transmission arranges the first break (B1).
9. the transmission system (GS) according to any one of claim 5 to 8, is characterized in that, for the hollow wheels (H2) of described second speed changer (G2) arranges second brake (B2).
10. a vehicle, is characterized in that, described vehicle comprises transmission system according to any one of claim 1 to 9 (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 true CN104948686A (en) | 2015-09-30 |
| CN104948686B 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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| CN (1) | CN104948686B (en) |
| DE (1) | DE102014205553B4 (en) |
Cited By (3)
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| CN108050222A (en) * | 2017-12-08 | 2018-05-18 | 合肥工业大学 | One kind two keeps off electric vehicle power-driven system |
| CN110062857A (en) * | 2016-09-30 | 2019-07-26 | 莱纳玛公司 | Multi-speed transmission |
| CN110182036A (en) * | 2018-12-14 | 2019-08-30 | 华南理工大学 | A kind of integrated form third gear power drive system |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102017004898A1 (en) * | 2017-05-20 | 2018-11-22 | Daimler Ag | Transmission device for an electric drive |
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| CN110182036A (en) * | 2018-12-14 | 2019-08-30 | 华南理工大学 | A kind of integrated form third gear power drive system |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102014205553A1 (en) | 2015-10-01 |
| CN104948686B (en) | 2018-06-29 |
| DE102014205553B4 (en) | 2020-08-06 |
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