CN110067836A - Motor speed change gear - Google Patents
Motor speed change gear Download PDFInfo
- Publication number
- CN110067836A CN110067836A CN201811638566.1A CN201811638566A CN110067836A CN 110067836 A CN110067836 A CN 110067836A CN 201811638566 A CN201811638566 A CN 201811638566A CN 110067836 A CN110067836 A CN 110067836A
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- CN
- China
- Prior art keywords
- gear
- motor
- speed change
- pinion
- brake
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
-
- 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
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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
- F16H3/70—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/037—Gearboxes for accommodating differential gearings
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
- H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
- H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears
Abstract
The present invention provides a kind of motor speed change gear, in the case where using differential mechanism as differential attachment, can shorten axis direction length, realize the miniaturization of whole device.Motor of the invention carries out speed change with power of the speed change gear (1) to motor (2) and passes to differential mechanism (4).1st planetary gear mechanism (PG1) of double-pinion type includes the sun gear (S1) for being entered the power of motor；Support the tooth rest (C1) of multiple 1st and the 2nd pinion gears (P1, P2)；And gear ring (R1), tooth rest (C1) and gear ring (R1) are braked by the 1st and the 2nd brake (B2) respectively.Each 2nd pinion gear (P2) includes the base portion (P2B) engaged with the 1st pinion gear (P1) and gear ring；And the extension portion (P2E) extended from base portion to the opposite side of motor, differential mechanism (4) has the 2nd sun gear (S2) engaged with extension portion, and is configured in the inner space marked off by multiple extension portion.
Description
Technical field
The present invention relates to motor speed change gear, it is used to carry out speed change to the power of motor and by differential machine
The power is distributed to 2 output shafts by structure.
Background technique
As existing this motor speed change gear, such as known device disclosed in patent document 1.This is electronic
Machine with speed change gear (hereinafter referred to as " speed change gear ") be applied to electric car, in the example shown in Fig. 6, have with it is electronic
The gear and differential attachment of motor (hereinafter referred to as " motor ") connection, this 3 mechanisms are configured as being sequentially arranged in electronic
State on the axis direction of the output shaft of automobile, and be incorporated in shell.
Gear has the 1st and the 2nd clutch and planetary gear mechanism, they are configured as from motor-side successively
The state of arrangement in the axial direction.Planetary gear mechanism includes duplex pinion gear, and it is mutually different to be provided integrally with the number of teeth
1st and the 2nd pinion gear；And tooth rest, duplex pinion gear is rotatably supported.In addition, planetary gear mechanism includes
1st sun gear is linked by the rotor of the 1st clutch and motor, and engaged with above-mentioned 1st pinion gear；And the 1st tooth
Circle, is engaged, and be fixed on shell, and also include the 2nd sun gear with the 1st pinion gear, passes through the 2nd clutch and horse
The rotor connection reached, is engaged, and the number of teeth is greater than the number of teeth of the 1st sun gear with above-mentioned 2nd pinion gear；And the 2nd gear ring, with
The engagement of 2nd pinion gear, and the number of teeth is less than the number of teeth of the 1st gear ring.
Differential attachment is made of the planetary gear mechanism of double-pinion type, comprising: is linked with the 2nd gear ring of gear
Gear ring；The the 1st and the 2nd planetary gear successively engaged with gear ring；The gear that 1st and the 2nd planetary gear is rotatably supported
Frame；And the sun gear engaged with the 2nd planetary gear.The sun gear of the differential attachment and an output shaft of electric car connect
Another output shaft of knot, tooth rest and electric car links.
In the speed change gear, if engaging the 1st clutch and disconnecting the 2nd clutch, the power of motor is entered speed change
1st sun gear of mechanism is output to the gear ring of differential attachment by the 2nd gear ring after with defined reduction ratio speed change.It is another
Aspect, when disconnecting the 1st clutch and engaging the 2nd clutch, then the power of motor is entered the 2nd sun gear, above-mentioned to be less than
After the defined reduction ratio speed change of reduction ratio, the gear ring of differential attachment is output to by the 2nd gear ring.It is entered differential attachment
The power of motor is assigned to the sun gear and tooth rest, and is delivered to 2 output shafts.
Patent document 1: Japanese Unexamined Patent Publication 2002-104001 bulletin
Summary of the invention
As described above, in existing speed change gear, the differential attachment of the power as the motor after distribution speed change makes
Not common differential mechanism, but used the planetary gear mechanism of double-pinion type.The reason is that gear
1st and the 2nd clutch, 2 gear sets of planetary gear mechanism and differential attachment are arranged on the axis direction of output shaft,
For the relationship, using the planetary gear mechanism of the axis direction length double-pinion type smaller than differential mechanism for inhibiting axis side
Advantageously to length.
However, the planetary gear mechanism of double-pinion type is more complicated than differential design, thus it will lead to the knot of whole device
Structure complicates and high cost.According to this viewpoint, although as differential attachment, it is preferable to use differential mechanisms, in this feelings
It is that the big differential mechanism of axis direction length and gear are arranged side by side as a result, axis direction length becomes larger under condition, it causes to fill
Set whole enlargement.
The present invention be it is completed to solve the above problems, its purpose is to provide a kind of motor speed change gear,
In the case where using differential mechanism as differential attachment, axis direction length, the miniaturization of realization device entirety can be shortened.
In order to achieve the above objectives, the first aspect of the present invention is a kind of motor speed change gear 1, to motor 2
Power carries out speed change, and the power is distributed to 2 output shafts ((similarly hereinafter) drive shaft in embodiment by differential attachment
SL, SR), which is characterized in that, which has and output shaft arranged coaxial with speed change gear 1
Double-pinion type planetary gear mechanism (the 1st planetary gear mechanism PG1), planetary gear mechanism includes sun gear S1, motor
2 power is entered sun gear S1；Tooth rest C1, by the multiple 1st pinion gear P1 engaged with sun gear S1 and with it is multiple
Multiple 2nd pinion gear P2 that 1st pinion gear P1 is engaged respectively are rotatably supported；And gear ring R1, with multiple 2nd small teeth
P2 engagement is taken turns, which is also included the 1st brake (the 1st brake B1, one-way clutch OWC) with speed change gear 1, is used
It is braked in tooth rest C1；And the 2nd brake B2, it is used to brake gear ring R1, multiple 2nd pinion gear P2 are each
From including the base portion P2B engaged with the 1st pinion gear P1 and gear ring R1；And extend from base portion P2B to the opposite side of motor 2
Extension portion P2E, differential attachment are made of differential mechanism 4, which has the engaged with the extension portion P2E of the 2nd pinion gear P2
2 sun gear S2 are as input gear, and the differential attachment is configured in by the extension portion P2E of multiple 2nd pinion gear P2
In the inner space marked off.
As described above, motor of the invention has double small with speed change gear (hereinafter, being suitably referred to as " speed change gear ")
The planetary gear mechanism of gear type, differential attachment are made of differential mechanism.2nd pinion gear of planetary gear mechanism have base portion and from
The extension portion that base portion extends to the side opposite with motor, base portion are engaged with the 1st pinion gear and gear ring, extension portion and as difference
2nd sun gear of the input gear of fast device engages.The tooth rest and gear ring of planetary gear mechanism are carried out respectively in addition, being provided with
1st and the 2nd brake of braking.
According to this structure, the power of motor is input into the sun gear of planetary gear mechanism, and passes through the 1st pinion gear
Tooth rest and gear ring are input into the base portion of the 2nd pinion gear.As described later, using the 1st brake to tooth rest into
It has gone in the case where braking and in the case where being braked using the 2nd brake to gear ring, the power of motor is according to by going
Gear ratio between the rotary element of star gear mechanism and determination it is mutually different as defined in reduction ratio and slow down.Therefore, pass through
Switch the work and stopping of the 1st and the 2nd brake, the power of motor speed change in a manner of 2 grades of speed changes can be made.After speed change
Power is input into differential mechanism by the extension portion and the 2nd sun gear of the 2nd pinion gear, and distributes to 2 output shafts by differential mechanism.
In addition, according to the present invention, the base portion of 2 pinion gear of You Cong exists to the extension portion that the side opposite with motor extends
Its inside marks off space, and differential mechanism is configured and stored in the inner space.Exist as a result, with differential mechanism relative to gear
The case where being arranged on axis direction is compared, axis direction length can be shortened, it can be achieved that device entirety miniaturization.This
Outside, as differential attachment, due to the differential mechanism for having used structure more more simplified than the planetary gear mechanism of double-pinion type,
The structure that whole device can be achieved is simplified and cost effective.
The motor speed change gear that the second aspect of the present invention is recorded based on first aspect, which is characterized in that multiple 2
Each free duplex pinion gear of pinion gear P2 is constituted, which is provided integrally with: gear wheel P21, with base portion P2B and
Extension portion P2E；And pinion gear P22, the number of teeth of gear ratio gear wheel P21 is few, which also includes with speed change gear
2 gear ring R2, are engaged with pinion gear P22；And the 3rd brake B3, it is used to brake the 2nd gear ring R2.
According to this structure, in the case where being braked using the 3rd brake to the 2nd gear ring, as described later, electricity
The power of motivation according to it is above-mentioned the case where braking using the 1st brake to tooth rest with using the 2nd brake to gear ring
The defined reduction ratio of centre in the case where being braked and slow down.Therefore, pass through the work of the 1st to the 3rd brake of switching
And stopping, the power of motor speed change in a manner of 3 grades of speed changes can be made.
The motor speed change gear that the third aspect of the present invention is recorded based on second aspect, which is characterized in that the 2nd small tooth
The pinion gear P22 of wheel P2 configures the opposite side in motor 2 relative to gear wheel P21, and differential mechanism 4 is configured in by gear wheel P21
Extension portion P2E and the inner space that marks off of pinion gear P22 in.
According to this structure, it configures by the extension portion of the gear wheel of the 2nd pinion gear and relative to gear wheel in motor
The pinion gear of opposite side marks off longer and bigger inner space in the axial direction than first aspect present invention, interior at this
Differential mechanism is configured in the space of side.Thereby, it is possible to the more parts or whole in inner space storage differential mechanism.
The motor speed change gear that the fourth aspect of the present invention is recorded based on second or third aspect, which is characterized in that
Motor 2, planetary gear mechanism and differential mechanism 4 are incorporated in shell CA, and the 1st to the 3rd brake B1~B3 is configured at shell CA
Peripheral wall portion.
According to this structure, the configuration of the 1st to the 3rd brake is in storage motor, the shell of planetary gear mechanism and differential mechanism
The peripheral wall portion of body, therefore be arranged in the axial direction with the clutch of same purpose relative to planetary gear mechanism etc.
Existing situation is compared, and axis direction length can be shortened, and can further realize the miniaturization of whole device.
The fifth aspect of the present invention is used based on the motor that any one aspect of first aspect into fourth aspect is recorded
Speed change gear, which is characterized in that the motor speed change gear also has the 2nd planetary gear mechanism PG0 of single pinion type, should
2nd planetary gear mechanism PG0 and output shaft SL, SR are coaxially arranged between motor 2 and planetary gear mechanism, the 2nd planet tooth
Wheel mechanism PG0 includes sun gear S0, links with motor 2；Not revolvable gear ring R0；And tooth rest C0, it will be with the sun
The pinion gear P0 of wheel S0 and gear ring R0 engagement is rotatably supported, and is linked with the sun gear S1 of planetary gear mechanism.
According to this structure, the power of motor is input into the sun gear of the 2nd planetary gear mechanism, according to regulation
After reduction ratio is slowed down, the sun gear of planetary gear mechanism is input by tooth rest, therefore correspondingly with the deceleration, it can
Bigger reduction ratio is obtained in entire speed change gear.
Detailed description of the invention
Fig. 1 is the figure for the motor speed change gear that summary shows the 1st embodiment of the invention.
Fig. 2 is the figure for indicating the 1st planetary gear mechanism of motor speed change gear etc..
Fig. 3 is the table for indicating the setting example of the number of teeth of the main rotary element of motor speed change gear of Fig. 1.
Fig. 4 is the action schedule of the motor speed change gear of Fig. 1.
Fig. 5 is the relationship of the revolving speed between the rotary element under advance high speed (Hi) mode for indicating motor speed change gear
Speed line chart.
Fig. 6 is the pass of the revolving speed between the rotary element under advance low speed (Low) mode for indicating motor speed change gear
The speed line chart of system.
Fig. 7 is the speed line chart for concluding the movement for the motor speed change gear for showing Fig. 1.
Fig. 8 is the figure for the motor speed change gear that summary shows the 2nd embodiment of the invention.
Fig. 9 is the table for indicating the setting example of the number of teeth of the main rotary element of motor speed change gear of Fig. 8.
Figure 10 is the action schedule of the motor speed change gear of Fig. 8.
Figure 11 is turn between the rotary element under advance middling speed (Mid) mode for indicating the motor speed change gear of Fig. 8
The speed line chart of the relationship of speed.
Figure 12 is the speed line chart for concluding the movement for the motor speed change gear for showing Fig. 8.
Label declaration
1: motor speed change gear；2: motor (motor)；4: differential mechanism (differential attachment)；SL: left driving shaft (output
Axis)；SR: right driving axle (output shaft)；PG1: the 1 planetary gear mechanism (planetary gear mechanism)；S1: the 1 planetary gear mechanism
Sun gear (sun gear of planetary gear mechanism)；The 1st pinion gear (the of planetary gear mechanism of P1: the 1 planetary gear mechanism
1 pinion gear)；The 2nd pinion gear (the 2nd pinion gear of planetary gear mechanism) of P2: the 1 planetary gear mechanism；P2B: the 2 pinion gear
Base portion；The extension portion of P2E: the 2 pinion gear；Tooth rest (the gear of planetary gear mechanism of C1: the 1 planetary gear mechanism
Frame)；The gear ring (gear ring of planetary gear mechanism) of R1: the 1 planetary gear mechanism；B1: the 1 brake；OWC: one-way clutch
(the 1st brake)；B2: the 2 brake；S2: the 2 sun gear；51: motor speed change gear；The canine tooth of P21: the 2 pinion gear
Wheel；The pinion gear of P22: the 2 pinion gear；B3: the 3 brake；CA: shell；PG0: the 2 planetary gear mechanism；S0: the 2 planet
The sun gear of gear mechanism；The pinion gear of P0: the 2 planetary gear mechanism；The tooth rest of C0: the 2 planetary gear mechanism；R0: the 2
The gear ring of planetary gear mechanism.
Specific embodiment
Hereinafter, the preferred embodiment of the present invention is described in detail referring to attached drawing.Shown in FIG. 1 of the invention 1st
The motor speed change gear (hereinafter, being suitably referred to as " speed change gear ") 1 of embodiment is for example equipped on to as power source
The power of motor (hereinafter referred to as " motor ") 2 on four-wheel car (not shown) carries out speed change.Power after speed change is by differential
Device 4 distributes to drive shaft SL, SR of left and right coaxially to each other, and then is delivered to the driving wheel (not shown) of left and right.These horses
The state arranged in the axial direction is configured in the mode coaxial with drive shaft SL, SR up to 2, speed change gear 1 and differential mechanism 4,
And it is incorporated in shell CA.
Motor 2 has cricoid stator 2a and rotor 2b.Stator 2a is made of multiple iron cores and coil etc., and is fixed
On shell CA.Rotor 2b is made of multiple magnet etc., and be configured as it is opposed with stator 2a, by stator 2a supply electricity
Power, rotor 2b are driven to forward rotation direction or reverse directions rotation.
Speed change gear 1 is by the 1st planetary gear mechanism PG1, the 2nd planetary gear mechanism PG0, the braking of the 1st brake B1 and the 2nd
Device B2 etc. is constituted.These constituent elements be configured as it is coaxial with drive shaft SL, SR, in addition, the 2nd planetary gear mechanism PG0 and the 1st
Planetary gear mechanism PG1 is configured as the state being arranged successively from 2 side of motor.
2nd planetary gear mechanism PG0 makes the power of motor 2 slow down according to certain reduction ratio, and exports to the 1st planet tooth
Mechanism PG1 is taken turns, the 2nd planetary gear mechanism PG0 is by the list with sun gear S0, multiple pinion gear P0, tooth rest C0 and gear ring R0
The planetary gear mechanism of pinion type is constituted.
Sun gear S0 and the rotor 2b of motor 2 are wholely set.Multiple pinion gear P0 are rotatably supported by tooth rest C0,
And it is engaged with sun gear S0 and gear ring R0.The aftermentioned sun gear S1 of tooth rest C0 and the 1st planetary gear mechanism PG1 links.
In addition, gear ring R0 is fixed on shell CA.
On the other hand, the 1st planetary gear mechanism PG1 is the structure of double-pinion type, by sun gear S1, multiple (this example
In be 3) the 1st pinion gear P1, multiple (being 3 in this example) the 2nd pinion gear P2, tooth rest C1 and gear ring R1 etc. constitute.
As described above, the tooth rest C0 of sun gear S1 and the 2nd planetary gear mechanism PG0 link.1st and the 2nd pinion gear
P1, P2 are rotatably supported by the fulcrum of tooth rest C1 11,12 respectively, and the 1st pinion gear P1 is engaged with sun gear S1.2nd is small
Gear P2 has base portion P2B and extension portion P2E from base portion P2B to 4 side of differential mechanism that extends from, at base portion P2B and the 1st pinion gear
P1 and gear ring R1 engagement, is engaged at extension portion P2E with the 2nd sun gear S2 of the input gear as differential mechanism 4.
As shown in figure 3, tooth number Z S1, ZR1 of sun gear S1 and gear ring the R1 sun with the 2nd planetary gear mechanism PG0 respectively
Tooth number Z S0, ZR0 for taking turns S0 and gear ring R0 is equal.In addition, the tooth number Z S2 of the 2nd sun gear S2 be less than 2 above-mentioned sun gear S1,
Tooth number Z S1, ZS0 of S0.
The fulcrum 12 of tooth rest C1 further extends to 4 side of differential mechanism from the extension portion P2E of the 2nd pinion gear P2, and
The part is connected with the 1st brake B1.In addition, gear ring R1 and the 2nd brake B2 links.
1st and the 2nd brake B1, B2 is set to the peripheral wall portion of shell CA, such as is made of multi-plate friction clutch.
1st brake B1 includes cricoid internal component 13a, with multiple clutch plates；Cricoid external component 13b, has
The multiple clutch plates being alternately arranged with above-mentioned multiple clutch plates；And to the actuator that external component 13b is driven
(not shown) etc..The fulcrum 12 of internal component 13a and tooth rest C1 link, and external component 13b is by with can be in the axial direction
Mobile and not revolvable mode is arranged on shell CA.In addition, the movement of actuator is controlled by control device (not shown),
To be switched over to the work and stopping of the 1st brake B1.
Specifically, in the state that actuator stops, the clutch plate of internal component 13a and external component 13b from
Clutch plate is maintained as disengaged condition, so that tooth rest C1 is unlatched and is allowed to rotate.In addition, when actuator carries out work
When making, the clutch plate of not revolvable external component 13b moves in the axial direction, is being compressed against internal component 13a's
It is engaged in the state of on clutch plate, thus, tooth rest C1 is braked, and is fixed to rotate.
2nd brake B2 has external component 13b, external component 14b and the actuator equally constituted with the 1st brake B1
(not shown), external component 13b and gear ring R1 link, and external component 14b is by can move in the axial direction and cannot revolve
The mode turned is arranged on shell CA.Under the halted state of actuator, gear ring R1 is unlatched and is allowed to rotate, and works as actuating
When device is worked, gear ring R1 is braked, and is fixed to rotate.
In addition, being provided between the fulcrum 12 and shell CA of tooth rest C1 and the 1st concatenated one-way clutch of brake B1
Device OWC.One-way clutch OWC is common mechanical structure, have be wholely set with shell CA cricoid external component, with
And it is integrally formed at the cricoid internal component on fulcrum 12.In addition, one-way clutch OWC is set to: in tooth rest C1
When rotating to the direction for making drive shaft SL, SR advance, one-way clutch OWC will be cut off between shell CA and tooth rest C1, be allowed
The rotation of tooth rest C1, and when tooth rest C1 is rotated to the direction for retreating drive shaft SL, SR, one-way clutch OWC is by shell
It is connected between body CA and tooth rest C1, tooth rest C1 is fixed as to rotate.
Differential mechanism 4 is common structure, comprising: the differential carrier 4a rotated freely；It is supported in a way freely spinning way
Multiple pinion gear 4b on differential carrier 4a；And with side gear 4c, 4d of the left and right engaged pinion gear 4b.Left side face gear
4c is linked by left driving shaft SL and left driving wheel, and right side face gear 4d is linked by right driving axle SR and right driving wheel.
The 2nd sun gear S2 as input gear is wholely set on differential carrier 4a.As described above, the 2nd sun gear
S2 is engaged with the extension portion P2E of the 2nd pinion gear P2 of the 1st planetary gear mechanism PG1.In addition, as shown in Figure 1, differential mechanism 4 it is big
Part is configured at the inner space marked off by extension portion P2E, the 1st brake B1 and the one-way clutch OWC of the 2nd pinion gear P2
In, and be integrally incorporated in shell CA.Drive shaft SL, SR of left and right extends to outside by the opening of shell CA.
According to above structure, the power of motor 2 is input to the sun gear of the 2nd planetary gear mechanism PG0 from rotor 2b
S0 is entered in the state of after being slowed down by the 2nd planetary gear mechanism PG0 according to the reduction ratio of regulation by tooth rest C0
To the sun gear S1 of the 1st planetary gear mechanism PG1.The power inputted is by the state after the 1st planetary gear mechanism PG1 speed change
Under, differential mechanism 4 is delivered to by the 2nd pinion gear P2 and the 2nd sun gear S2.The power transmitted distributes to a left side by differential mechanism 4
Right drive shaft SL, SR, and it is delivered to the driving wheel of left and right.Hereinafter, the gear shifting operation to speed change gear 1 is said in detail
It is bright.
Firstly, be that single pinion type and its gear ring R0 are fixed on shell CA based on the 2nd planetary gear mechanism PG0,
And using sun gear S0 as input, using tooth rest C0 as exporting, thus the number of teeth of usable gear ring R0 and sun gear S0
ZR0, ZS0, the reduction ratio based on the 2nd planetary gear mechanism PG0 is showed by following formula (1), and (hereinafter referred to as " S0-S1 slows down
Than ") RS01.
RS01=(ZR0/ZS0)+1 (1)
If ZR0, ZS0 on the right substitutes into the numerical value of Fig. 3, S0-S1 reduction ratio RS01 are as follows:
RS01=(147/36)+1=5.083.
In addition, being the 2nd small of double-pinion type and the 1st planetary gear mechanism PG1 based on the 1st planetary gear mechanism PG1
Gear P2 is engaged with the 2nd sun gear S2 of the input gear as differential mechanism 4, thus can be come for example as the alignment chart of Fig. 5
Show the relationship of the revolving speed between the rotary element of speed change gear 1.That is, by sun gear S1 (tooth rest C0), gear ring R1, tooth rest C1
4 rotary elements, and the conllinear pass of the revolving speed arrangement of this 4 rotary elements point-blank are constituted with the 2nd sun gear S2
It is tied to form vertical.
In addition, the λ 1 and λ 2 of the figure be respectively between tooth rest C1- gear ring R1 on the basis of (=1), tooth rest C1- too
Speed ratio (hereinafter referred to as " the 1st lever ratio ") between sun wheel S1 and the speed ratio between the 2nd sun gear S2 of tooth rest C1- are (following
Referred to as " the 2nd lever ratio "), they can be showed by following formula (2), (3).
λ 1=(ZR1/ZS1) (2)
λ 2=(ZR1/ZS2) (3)
In the speed change gear 1 of above structure, advance high speed (Hi) mode, advance low speed are set with as action mode
(Low) mode and retrogressing (RVS) mode, are also set with the mode of cutting off.Hereinafter, referring to the action schedule of Fig. 4, according to every kind of movement mould
Formula illustrates the movement of speed change gear 1.
[Hi mode]
As shown in figure 4, in the state of defined direction drive motor 2 marched forward, making the 1st under the Hi mode
Brake B1 stops, and the 2nd brake B2 is made to work, and gear ring R1 is braked and fixed.Rotary element at this time
Between the relationship of revolving speed show as shown in Figure 5, the revolving speed of gear ring R1 is 0, and the power of sun gear S1 is being inverted and is slowing down
In the state of pass to the 2nd sun gear S2.
The relationship of 1st and the 2nd lever ratio λ 1, λ 2 according to figure 5 can be showed under the Hi mode by following formula (4)
The 2nd sun gear S2 of sun gear S1- between reduction ratio (hereinafter referred to as " Hi mode reduction ratio ") RS12 (Hi).
RS12 (Hi)=(λ 1-1)/(λ 2+1)
=[(ZR1/ZS1) -1]/[(ZR1/ZS2)+1] (4)
If ZR1, ZS1, ZS2 on the right substitutes into the numerical value of Fig. 3, Hi mode reduction ratio RS12 (Hi) are as follows:
RS12 (Hi)=[(147/36) -1]/[(147/93)+1]=1.195.
In addition, the total reduction ratio between motor 2- differential mechanism 4 under Hi mode can pass through the S0-S1 reduction ratio of the formula (1)
The product of RS01 (=5.083) and Hi mode reduction ratio RS12 (Hi) (=1.195) shows, and is 5.083 × 1.195=6.074.
[Low mode]
Under the Low mode, in the state of defined direction drive motor 2 marched forward, make the 1st and the 2nd braking
Device B1, B2 stop.In this state, tooth rest C1 and gear ring R1 idle running, so that tooth rest C1 is intended to identical with sun gear S1
Even if the direction that direction, drive shaft SL, SR retreat rotates, therefore the one-way clutch OWC set as described above works.
As a result, being connected between shell CA and tooth rest C1, tooth rest C1 is fixed to rotate.Rotation at this time is wanted
The relationship of revolving speed between element can show as shown in Figure 6, and the revolving speed of tooth rest C1 is 0, also, the power of sun gear S1 to invert and
State than more substantially slowing down when Hi mode is delivered to the 2nd sun gear S2.
The relationship of 1st and the 2nd lever ratio λ 1 according to figure 6, λ 2, can be showed under the Low mode by following formula (5)
The 2nd sun gear S2 of sun gear S1- between reduction ratio (hereinafter referred to as " Low mode reduction ratio ") RS12 (Low),
1/ λ 2 of RS12 (Low)=λ
=(ZR1/ZS1)/(ZR1/ZS2) (5)
If ZR1, ZS1, ZS2 on the right substitutes into the numerical value of Fig. 3, Low mode reduction ratio RS12 (Low) are as follows:
RS12 (Low)=(147/36)/(147/93)=2.583, can obtain than Hi mode reduction ratio RS12 (Hi) (=
1.195) bigger reduction ratio.
In addition, total reduction ratio between motor 2- differential mechanism 4 under Low mode can by S0-S1 reduction ratio RS01 (=
5.083) it is showed with the product of Low mode reduction ratio RS12 (Low) (=2.583), is 5.083 × 2.583=13.129.
[RVS mode]
Under the RVS mode, in the state of the opposite contrary direction drive motor 2 with above-mentioned advance, make
1st brake B1 works, and tooth rest C1 is braked and fixed, and stops the 2nd brake B2, allows gear ring R1
Rotation.About the relationship of the revolving speed between rotary element at this time, as shown in fig. 7, with above-mentioned Low mode the case where positive negative
Instead, sun gear S1 is rotated to the direction opposite with when Low mode, and the revolving speed of tooth rest C1 is 0.In addition, the power of sun gear S1
Be delivered to the 2nd sun gear S2 in the state of after reversion and according to Low mode when identical reduction ratio are slowed down, thus come into
Row retreats traveling.
[cutting off mode]
It is carrying out selection when cutting off operating of the transmitting cutting of the power between motor 2 and driving wheel cutting off mode.?
This cuts off under mode, stops the 1st and the 2nd brake B1, B2 in the state of stopping motor 2.As shown in fig. 7, in the state
Under, the power of driving wheel is passed by differential mechanism 4, thus tooth rest C1 and gear ring R1 rotation, however they only carry out sky
Turn, therefore without the power transmitting between motor 2 and driving wheel.
The movement of speed change gear 1 more than induction and conclusion then as shown in Figure 7 passes through the movement and to motor 2
The work and stopping of 1 and the 2nd brake B1, B2 is controlled, thereby executing 2 grades of the advance changes based on Low mode and Hi mode
Speed and based on RVS mode and cut off the movement of mode.
In addition, in the present embodiment, as described above, carrying out the gear under Low mode by one-way clutch OWC
The fixation of frame C1 relatively carries out the fixation of the tooth rest C1 under RVS mode by the 1st brake B1.This point is to be based on
Following reason.That is, biggish braking torque is needed in order to fix tooth rest C1 under Low mode, and under RVS mode,
Since the torque of motor 2 at this time is suppressed to necessary degree needed for the commodity of vehicle, so as to pass through lesser system
Dynamic torque fixes tooth rest C1.Based on this relationship, by distinguished as described above using the 1st brake B1 and unidirectionally from
Clutch OWC, to realize the reduction of the clutch capacity of the 1st brake B1.
As described above, the deceleration device 1 of motor according to the present embodiment, by switching the 1st and the 2nd brake
The work and stopping of B1, B2 so as to make the power of motor 2 carry out speed change in a manner of 2 grades of speed changes, and can pass through difference
The power is distributed to drive shaft SL, SR of left and right by fast device 4.In addition, the power of motor 2 is subtracted by the 2nd planetary gear mechanism PG0
Speed, therefore the available bigger reduction ratio of entire speed change gear.
In addition, by the base portion P2B of the 2nd pinion gear P2 from the 1st planetary gear mechanism PG1 as double-pinion type to
The extension portion P2E and the 1st brake B1 and one-way clutch OWC that the opposite side of motor 2 extends mark off space on the inside of it,
The major part of differential mechanism 4 is accommodated in the inner space.Axis is arranged in relative to gear with differential mechanism as a result,
Situation on direction is compared, and can shorten axis direction length, it can be achieved that entire including speed change gear 1 and differential mechanism 4
The miniaturization of device.In addition, using structure more simple poorer than the planetary gear mechanism of double-pinion type as differential attachment
Fast device 4, therefore can realize the simplification of the structure of device entirety and cost effective.Moreover, the 1st and the 2nd brake B1, B2 and list
The peripheral wall portion in shell CA is configured to clutch OWC, therefore is arranged in axis side with relative to planetary gear mechanism etc.
Upward existing situation is compared, and axis direction length can be shortened, and can further realize the miniaturization of whole device.
Moreover, carrying out requiring the tooth rest C1's under the Low mode of biggish braking torque by one-way clutch OWC
It is fixed, and do not required by the 1st brake B1 consolidating for tooth rest C1 under the RVS mode of biggish braking torque
It is fixed, therefore can realize the reduction of the clutch capacity of the 1st brake B1.
In the following, referring to Fig. 8 etc., to the motor of the 2nd embodiment of the invention with speed change gear (hereinafter, appropriate be referred to as
" speed change gear ") it 51 is illustrated.The speed change gear 51 compared with the speed change gear 1 of the 1st embodiment above-mentioned, it is main not
Be with place: the 2nd pinion gear P2 of the 1st planetary gear mechanism PG1 is made of duplex pinion gear；It has added and the small tooth of the duplex
2nd gear ring R2 of an engagement in wheel and the 3rd brake B3 that the 2nd gear ring R2 is braked.In addition, in change below
In the explanation of speed variator 51, assign same label to the constituent element identical or same with speed change gear 1, with speed change gear 1
It is illustrated centered on different parts.
As shown in figure 8, the 2nd pinion gear P2 of the 1st planetary gear mechanism PG1 by have the gear wheel P21 that is mutually integrated and
The duplex pinion gear of pinion gear P22 is constituted.Gear wheel P21 has base portion P21B and extends from base portion P21B to 4 side of differential mechanism
Extension portion P21E, engaged at base portion P21B with the 1st pinion gear P1 and gear ring R1, at extension portion P21E with differential mechanism 4
2nd sun gear S2 engagement.Pinion gear P22 configuration than extension portion P21E by 4 side of differential mechanism position at, and with the 2nd gear ring
R2 engagement, the 2nd gear ring R2 and the 3rd brake B3 link.
Fig. 9 shows the setting example of the number of teeth of the main rotary element of present embodiment.According to compared with Fig. 3 it is found that with
The tooth number Z of the rotary elements such as the sun gear S0 that the 1st embodiment equally uses is set to value identical with the 1st embodiment.
In addition, the tooth number Z P22 of the pinion gear P22 of the 2nd additional pinion gear P2 is less than the number of teeth of gear wheel P21 in the present embodiment
ZP21, correspondingly, the tooth number Z R2 of the 2nd gear ring R2 are less than the tooth number Z R1 of gear ring R1.
In addition, according to Fig. 3 it is found that the 1st brake B1 and one-way clutch OWC are relative to the 2nd brake compared with Fig. 8
The opposite side (4 side of differential mechanism) that B2 configured in the 1st embodiment in motor 2, and then configure in the present embodiment in motor 2
Side.As a result, the extension portion P21E of the gear wheel 21 of the 2nd pinion gear P2 and configuration its extend side pinion gear P22 inside,
Space longer and bigger in the axial direction when marking off than 1 embodiment, it is entire poor to be accommodated in the inner space
Fast device 4.
In addition, the 3rd brake B3 is set to the peripheral wall portion of shell CA, there is structure same as the 1st and the 2nd brake B1, B2
At internal component 15a, external component 15b and actuator (not shown), internal component 15a and the 2nd gear ring R2 link, external structure
Part 15b is arranged on shell CA in a manner of it can move in the axial direction and is not revolvable.Therefore, stop in the actuator
In the state of, the 2nd gear ring R2 is unlatched and is allowed to rotate, and when actuator work, the 2nd gear ring R2 is braked, and is fixed
For that cannot rotate.
In the speed change gear 51 of above structure, be carried out similarly speed change gear 1 above-mentioned based on the 2nd planetary gear
The speed-down action of mechanism PG0 and gear shifting operation (Hi mode, Low mode, RVS mode based on the 1st planetary gear mechanism PG1 etc.
With cut off mode).In addition, the tooth number Z of the rotary element of the 1st and the 2nd planetary gear mechanism PG1, PG0 etc. and the 1st embodiment
It is identical, thus S0-S1 reduction ratio RS01, Hi mode reduction ratio RS12 (Hi) and Low mode as obtained from their movement
Reduction ratio RS12 (Low) is also identical as the 1st embodiment.
Other than above movement, in the speed change gear 51, carried out also as described below based on advance middling speed
(Mid) gear shifting operation of mode.Firstly, since the 2nd pinion gear P2 of the 1st planetary gear mechanism PG1 of double-pinion type is by double
Join pinion gear to constitute, pinion gear P22 is engaged with the 2nd gear ring R2, and the 2nd gear ring R2 and the 3rd brake B3 link, therefore speed change fills
The relationship for setting the revolving speed between 51 rotary element can for example be showed like that by the alignment chart of Figure 11.That is, by sun gear S1 (tooth rest
C0), gear ring R1, the 2nd gear ring R2, tooth rest C1 and the 2nd sun gear S2 5 rotary elements of composition, and this 5 rotary elements
The collinear relationship of revolving speed arrangement point-blank is set up.
In addition, the λ 3 of the figure be between tooth rest C1- gear ring R1 on the basis of, speed between the 2nd gear ring R2 of tooth rest C1-
Than (hereinafter referred to as " the 3rd lever ratio "), can be showed by following formula (6).
λ 3=(ZR1/ZR2) (ZP22/ZP21) (6)
As shown in Figure 10, under Mid mode, in the state of defined direction drive motor 2 marched forward, make the 1st
Stop with the 2nd brake B1, B2, allow the rotation of tooth rest C1 and gear ring R1, and the 3rd brake B3 is made to work, it is right
2nd gear ring R2 is braked and is fixed.About the relationship of the revolving speed between rotary element at this time, can show as shown in Figure 11, the 2nd
The revolving speed of gear ring R2 is 0, and the power of sun gear S1 is delivered to the 2nd sun gear S2 in the state of inverting and being decelerated.
The relationship of the 1st~the 3rd 1~λ of lever ratio λ 3 according to shown in Figure 11 can show the Mid mode by following formula (7)
Under the 2nd sun gear S2 of sun gear S1- between reduction ratio (hereinafter referred to as " Mid mode reduction ratio ") RS12 (Mid).
RS12(Mid)
=(λ 1- λ 3)/(λ 2+ λ 3)
=[(ZR1/ZS1)-(ZR1/ZR2) (ZP22/ZP21)]
/[(ZR1/ZS2)+(ZR1/ZR2)·(ZP22/ZP21)]···(7)
If ZR1, ZS1, ZS2, ZP21 and ZP22 on the right substitutes into the numerical value of Fig. 9, Mid mode reduction ratio RS12
(Mid) are as follows:
RS12(Mid)
=[(147/36)-(147/141) (20/26)]
/ [(147/93)+(147/141) (20/26)]=1.377,
Hi mode reduction ratio RS12 (Hi) (=1.195) and Low mode reduction ratio RS12 (Low) (=2.583) can be obtained
Between reduction ratio.
In addition, the total reduction ratio between motor 2- differential mechanism 4 under Mid mode can pass through the S0-S1 reduction ratio of formula (1)
The product of RS01 (=5.083) and Mid mode reduction ratio RS12 (Mid) (=1.377) shows, and is 5.083 × 1.377=
6.999。
The movement of speed change gear 51 more than induction and conclusion passes through the movement and the 1st to motor 2 as shown in Figure 12
The work and stopping of~the 3 brake B1~B3 is controlled, before based on Low mode, Mid mode and Hi mode
Into 3 grades of speed changes and based on RVS mode and cut off the movement of mode.
As described above, the deceleration device 51 of motor according to the present embodiment, by switching the 1st~the 3rd brake
The work and stopping of B1~B3 can make the power of motor 2 carry out speed change in the way of 3 grades of speed changes, and can pass through difference
The power is distributed to drive shaft SL, SR and driving wheel of left and right by fast device 4.
In addition, the 2nd pinion gear P2 of the 1st planetary gear mechanism PG1 is by being provided integrally with gear wheel P21 and pinion gear P22
Duplex pinion gear constitute, by the extension portion P2E of gear wheel P21 and extend pinion gear P22 that side extends to it and mark off ratio
1st embodiment longer bigger inner space in the axial direction.It is entire poor thereby, it is possible to be stored in the inner space
Fast device 4.Moreover, the 3rd brake B3 is also disposed in the peripheral wall portion of shell CA, therefore in the same manner as the 1st and the 2nd brake B1, B2
Axis direction length can be shortened, it can be achieved that whole device miniaturization.
In addition, can implement in various ways the present invention is not limited to illustrated embodiment.For example, differential mechanism 4 is not
It is limited to the general structure illustrated in embodiments, it can also be using other any type of structures.In addition, in embodiment
In, multi-plate friction clutch is used as the 1st~the 3rd brake B1~B3, as long as however can be to as object
Rotary element braked, then the brake of other appropriate types also can be used.
In addition, in embodiments, in order to reduce the clutch capacity of the 1st brake B1, and be respectively provided with unidirectionally from
Clutch OWC, is used for the fixation of the tooth rest C1 under Low mode, however also can be omitted one-way clutch OWC, passes through the 1st
Brake B1 carries out the fixation of tooth rest C1.
Moreover, embodiment is the example being used for speed change gear 1 and 51 in the motor 2 of the power source as vehicle, so
And the invention is not limited thereto, can also be widely used in the motor for other purposes being used together with differential attachment.Furthermore, it is possible to
The structure of specific part is suitably changed in the range of the purport of the present invention.
Claims (5)
1. a kind of motor speed change gear carries out speed change to the power of motor, and passes through differential attachment for the power
2 output shafts are distributed to, which is characterized in that,
The motor has the planetary gear mechanism with the double-pinion type of the output shaft arranged coaxial with speed change gear,
The planetary gear mechanism includes
Sun gear, the power of the motor are input into the sun gear；
Tooth rest engages more respectively by multiple 1st pinion gears engaged with the sun gear and with multiple 1st pinion gear
A 2nd pinion gear rotatably supports；And
Gear ring is engaged with the multiple 2nd pinion gear,
The motor is also included with speed change gear
1st brake is used to brake the tooth rest；And
2nd brake is used to brake the gear ring,
The multiple 2nd pinion gear respectively includes the base portion engaged with the 1st pinion gear and the gear ring；And from the base
The extension portion that portion extends to the opposite side of the motor,
The differential attachment is made of differential mechanism, which has the 2nd engaged with the extension portion of the 2nd pinion gear
Sun gear is as input gear, and the differential attachment is configured in by the extension portion of the multiple 2nd pinion gear
In the inner space marked off.
2. motor speed change gear according to claim 1, which is characterized in that
The multiple each free duplex pinion gear of 2nd pinion gear is constituted, which is provided integrally with: gear wheel, tool
There are the base portion and the extension portion；And pinion gear, the number of teeth of the gear ratio gear wheel is few,
The motor is also included with speed change gear
2nd gear ring is engaged with the pinion gear；And
3rd brake is used to brake the 2nd gear ring.
3. motor speed change gear according to claim 2, which is characterized in that
The pinion gear of 2nd pinion gear configures the opposite side in the motor, the difference relative to the gear wheel
Fast device configuration is in the inner space marked off by the extension portion and the pinion gear of the gear wheel.
4. motor speed change gear according to claim 2 or 3, which is characterized in that
The motor, the planetary gear mechanism and the differential mechanism are incorporated in shell, the 1st brake, described
2nd brake and the 3rd brake are configured at the peripheral wall portion of the shell.
5. according to claim 1 to motor speed change gear described in any one in 4, which is characterized in that
The motor speed change gear also has the 2nd planetary gear mechanism of single pinion type, the 2nd planetary gear mechanism with
The output shaft is coaxially arranged between the motor and the planetary gear mechanism,
2nd planetary gear mechanism includes
Sun gear links with the motor；
Not revolvable gear ring；And
Tooth rest rotatably supports the pinion gear engaged with the sun gear and the gear ring, and with the row
The sun gear of star gear mechanism links.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2018009337A JP6546300B1 (en) | 2018-01-24 | 2018-01-24 | Transmission for motor |
| JP2018-009337 | 2018-04-26 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN110067836A true CN110067836A (en) | 2019-07-30 |
Family
ID=67297535
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201811638566.1A Pending CN110067836A (en) | 2018-01-24 | 2018-12-29 | Motor speed change gear |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP6546300B1 (en) |
| CN (1) | CN110067836A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110784065A (en) * | 2019-09-26 | 2020-02-11 | 曾浩文 | Electric drive device |
| CN111934488A (en) * | 2020-08-07 | 2020-11-13 | 江苏川钿明椿电气机械有限公司 | A gear motor aluminum wire motor for stereo garage |
| CN114506206A (en) * | 2020-11-17 | 2022-05-17 | 丰田自动车株式会社 | Drive device for hybrid vehicle |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH05332408A (en) * | 1992-05-25 | 1993-12-14 | Toyota Motor Corp | Electric automobile transmission |
| JPH05332405A (en) * | 1992-05-25 | 1993-12-14 | Toyota Motor Corp | Electric automobile reduction gear |
| CN101988562A (en) * | 2009-07-31 | 2011-03-23 | 加特可株式会社 | Automatic transmission |
| US20110203898A1 (en) * | 2010-02-25 | 2011-08-25 | Terasu Harashima | Vehicle power transmission device |
| CN102616134A (en) * | 2012-04-16 | 2012-08-01 | 中国汽车技术研究中心 | Integrated driving device for pure electric vehicle |
| CN102691758A (en) * | 2011-03-24 | 2012-09-26 | 加特可株式会社 | Automatic transmission |
| CN105408148A (en) * | 2013-07-02 | 2016-03-16 | 大众汽车有限公司 | Electric drive |
| WO2016142446A1 (en) * | 2015-03-11 | 2016-09-15 | Gkn Driveline International Gmbh | Gearing assembly and electric drive having a gearing assembly of this type |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4980786B2 (en) * | 2007-05-15 | 2012-07-18 | 富士重工業株式会社 | Vehicle differential device |
-
2018
- 2018-01-24 JP JP2018009337A patent/JP6546300B1/en not_active Expired - Fee Related
- 2018-12-29 CN CN201811638566.1A patent/CN110067836A/en active Pending
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH05332408A (en) * | 1992-05-25 | 1993-12-14 | Toyota Motor Corp | Electric automobile transmission |
| JPH05332405A (en) * | 1992-05-25 | 1993-12-14 | Toyota Motor Corp | Electric automobile reduction gear |
| CN101988562A (en) * | 2009-07-31 | 2011-03-23 | 加特可株式会社 | Automatic transmission |
| US20110203898A1 (en) * | 2010-02-25 | 2011-08-25 | Terasu Harashima | Vehicle power transmission device |
| CN102691758A (en) * | 2011-03-24 | 2012-09-26 | 加特可株式会社 | Automatic transmission |
| CN102616134A (en) * | 2012-04-16 | 2012-08-01 | 中国汽车技术研究中心 | Integrated driving device for pure electric vehicle |
| CN105408148A (en) * | 2013-07-02 | 2016-03-16 | 大众汽车有限公司 | Electric drive |
| WO2016142446A1 (en) * | 2015-03-11 | 2016-09-15 | Gkn Driveline International Gmbh | Gearing assembly and electric drive having a gearing assembly of this type |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110784065A (en) * | 2019-09-26 | 2020-02-11 | 曾浩文 | Electric drive device |
| CN111934488A (en) * | 2020-08-07 | 2020-11-13 | 江苏川钿明椿电气机械有限公司 | A gear motor aluminum wire motor for stereo garage |
| CN114506206A (en) * | 2020-11-17 | 2022-05-17 | 丰田自动车株式会社 | Drive device for hybrid vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| JP6546300B1 (en) | 2019-07-17 |
| JP2019127981A (en) | 2019-08-01 |
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