CN109667848A - Automobile and electric clutch executing agency - Google Patents
Automobile and electric clutch executing agency Download PDFInfo
- Publication number
- CN109667848A CN109667848A CN201710957775.1A CN201710957775A CN109667848A CN 109667848 A CN109667848 A CN 109667848A CN 201710957775 A CN201710957775 A CN 201710957775A CN 109667848 A CN109667848 A CN 109667848A
- Authority
- CN
- China
- Prior art keywords
- executing agency
- transmission shaft
- electric clutch
- force
- disengaging yoke
- 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
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D28/00—Electrically-actuated clutches
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
- F16D23/14—Clutch-actuating sleeves or bearings; Actuating members directly connected to clutch-actuating sleeves or bearings
- F16D2023/141—Clutch-actuating sleeves or bearings; Actuating members directly connected to clutch-actuating sleeves or bearings characterised by using a fork; Details of forks
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
A kind of automobile and electric clutch executing agency, wherein electric clutch executing agency includes: actuator, is used for output torque；Disengaging yoke axis；Transmission mechanism connects the actuator and disengaging yoke axis, for transmitting the output torque of the actuator to disengaging yoke axis to drive the disengaging yoke axis to rotate around own central axis line；Compensation section, for providing balancing force in clutch separation, to compensate the output torque of the disengaging yoke axis.By means of compensation section, the electric clutch executing agency of the technical program is capable of providing enough clutch separation forces, and clutch is promoted to efficiently separate.
Description
Technical field
The present invention relates to automobile technical field, in particular to a kind of automobile and electric clutch executing agency.
Background technique
Currently, automatic transmission clutch executing agency includes hydraulic and electronic two ways.Hydraulic clutch executes machine
Structure can provide larger motive force, but it has the disadvantages of structure is complicated, difficulty of processing is big, higher cost when practical application.
Therefore, the prior art develops electric clutch executing agency, and electric clutch executing agency provides clutch using motor
Torque needed for separating, and compared to hydraulic clutch executing agency, the structure of electric clutch executing agency is simple, difficult processing
Degree is little.But electric clutch executing agency requires motor to provide larger rated moment, to provide sufficiently large clutch point
From power, this undoubtedly will increase the volume and power of motor, this is a big difficulty for cost control and space layout.
Summary of the invention
Problems solved by the invention is, how under the premise of not increasing motor volume and power, effectively promoted it is electronic from
The torque that clutch executing agency can be provided during clutch separation.
To solve the above problems, the present invention provides a kind of electric clutch executing agency.Electric clutch executing agency packet
Include: actuator is used for output torque；
Disengaging yoke axis；
Transmission mechanism connects the actuator and disengaging yoke axis, and the output torque for transmitting the actuator is extremely divided
From shift fork axle to drive the disengaging yoke axis to rotate around own central axis line；
Compensation section, for providing balancing force in clutch separation, to compensate the output torque of the disengaging yoke axis.
Optionally, the compensation section and the disengaging yoke axis are hinged, and hinge joint is suitable for synchronous with the disengaging yoke axis
Rotation, and the balancing force is suitable for compensating the force of periphery needed for the disengaging yoke axis rotates by the hinge joint.
Optionally, the transmission mechanism includes: the transmission shaft for transmitting torque；
The compensation section and the transmission shaft are hinged, and hinge joint is suitable for rotating synchronously with the disengaging yoke axis, and described
Balancing force is suitable for compensating the force of periphery needed for the transmission shaft rotates by the hinge joint.
Optionally, the outer peripheral surface of the transmission shaft is equipped with protruding portion, and the transmission shaft passes through the protruding portion and the benefit
It is hinged to repay portion.
Optionally, the hinge joint be suitable for the clutch separation process successively from initial position, through middle position to
Final position rotation；
In the middle position, the compensation section is to the position of the transmission shaft applied force by the transmission shaft
Axis；
From the initial position to middle position, the transmission shaft is suitable for overcoming by the actuator output torque described
The barrier force that compensation section applies；
From the middle position to the final position, the compensation section is adapted to provide for the balancing force.
Optionally, electric clutch executing agency further include: locating part is suitable in the initial position and the hinge joint
It keeps out, to stop the transmission shaft to be rotated by the barrier force.
Optionally, the compensation section is helical spring, and from the initial position to middle position, the helical spring is in pressure
Contracting state and provide the elastic force to generate the barrier force；
From the middle position to the final position, the compressive deformation of the helical spring is discharged to provide the compensation
Power.
Optionally, the transmission mechanism further includes at least one level deceleration mechanism, and every grade of deceleration mechanism includes input unit
And output section, and the output revolving speed of the output section is lower than the input speed of the input unit.
Optionally, the deceleration mechanism includes at least two-stage, the upper level speed reducer in deceleration mechanism described in adjacent two-stage
The output section of structure and the input unit of next stage deceleration mechanism are connected to same axis.
Optionally, the same axis is as the transmission shaft.
Optionally, the input unit is worm screw, and the output section is worm gear, and the worm gear and worm screw engagement are to form worm gear
Worm mechanism.
Optionally, the input unit is first gear and the output section is second gear, the first gear and second
Gear is engaged to form gear drive.
Optionally, the compensation section includes: helical spring, for discharging elastic force by compressive state in clutch separation,
Using as the balancing force.
Optionally, the compensation section includes: hydraulic mechanism or air pressure mechanism, comprising:
Cylinder body limits pressure chamber；
Piston is located in the pressure chamber；
Push rod is connect positioned at the axial side of the piston, and with the piston；
The compensation section is used for: the piston is mentioned backwards to the liquid medium or gas medium of the pressure chamber portions of push rod side
For hydraulic or air pressure using as the balancing force.
The present invention also provides a kind of automobiles.The automobile includes: any of the above-described electric clutch executing agency.
Compared with prior art, technical solution of the present invention has the advantage that
In clutch separation process, actuator output torque finally to drive disengaging yoke axis to rotate to clutch separation,
Driving force needed for disengaging yoke axis rotates derives from actuator.In this course, compensation section provides and driving force benefit in the same direction
Power is repaid, this can compensate the output torque of disengaging yoke axis, realize the effect of significant torque increase.Therefore, by means of compensation section, this skill
The electric clutch executing agency of art scheme is capable of providing enough clutch separation forces, and clutch is promoted to efficiently separate.
Detailed description of the invention
Fig. 1 is the structural schematic diagram of the electric clutch executing agency of the specific embodiment of the invention；
Fig. 2 is effect picture of the electric clutch executing agency in the course of work of the specific embodiment of the invention.
Specific embodiment
To make the above purposes, features and advantages of the invention more obvious and understandable, with reference to the accompanying drawing to the present invention
Specific embodiment be described in detail.
In the car, including electric clutch executing agency.Referring to Figures 1 and 2, the technical program provide it is a kind of it is electronic from
Clutch executing agency 1, electric clutch executing agency 1 may include:
Actuator 2 is used for output torque；
Disengaging yoke axis 3 connects disengaging yoke 4；
Transmission mechanism 5 connects actuator 2 and disengaging yoke axis 3, and output torque to the separation for transmitting actuator 2 is dialled
Fork shaft 3 is to drive the disengaging yoke axis 3 to rotate around own central axis line.
During clutch separation, disengaging yoke axis 3 drives 4 synchronous rotary of disengaging yoke, and disengaging yoke 4 is rotating
When, it pushes thrust bearing and diaphragm spring to be axially moved, (or pulling) clutch friction plate is pushed to separate with rubbing surface.Therefore,
The output torque when rotated of disengaging yoke axis 3, to drive clutch separation.
Wherein, transmission mechanism 5 includes: the transmission shaft 50 for transmitting torque, is exported as torque input shaft or torque
Axis.Electric clutch executing agency 1 further include: compensation section 6, for providing balancing force in clutch separation.Compensation section 6 and biography
Moving axis 50 is hinged, and hinge joint A is suitable for rotating synchronously with disengaging yoke axis 3, and balancing force is suitable for compensating transmission shaft 50 by hinge joint A
The force of periphery needed for rotating.Increase since transmission shaft 50 rotates the required force of periphery, from transmission shaft 50 to the defeated of disengaging yoke axis 3
Torque enhances out, and clutch separation force increases, and clutch is promoted to efficiently separate.
It should be noted that actuator 2 can invert the rotation (as counterclockwise) in clutch from being separated in cohesive process
Turn, disengaging yoke axis 3 and disengaging yoke 4 is driven to invert, until clutch engages.
In the present embodiment, a transmission shaft 50 in compensation section 6 and transmission mechanism 5 carries out hingedly, and balancing force is directly made
For transmission shaft 50.In addition to this, in a kind of variation, compensation section can be hinged with disengaging yoke axis, hinge joint be suitable for
Disengaging yoke axis rotates synchronously, and balancing force is suitable for compensating the force of periphery needed for disengaging yoke axis rotates by hinge joint.At this point, mending
The balancing force for repaying portion's application directly acts on disengaging yoke axis, eliminates intermediate transfer structure.
Wherein, compensation section 6 may include: helical spring 60, for discharging elastic force by compressive state in clutch separation,
Using as balancing force.
Wherein, motion profile of hinge joint A during clutch separation can be set as: hinge joint A is suitable in clutch
Device separation process is successively from initial position a, through middle position b position c rotation to terminal, wherein middle position b is located at initial bit
It sets between a and final position c, initial position a leans on close over close to lower section, final position c.
In middle position b, compensation section 6 passes through the central axes of transmission shaft 50 to the position of 50 applied force of transmission shaft, such as
The central axes of helical spring 60 are intersected with transmission shaft 50, and helical spring 60 applies the position of elastic force by transmission to transmission shaft 50
The central axes of axis 50.At this point, compensation section 6 does not provide compensation effect to the rotation of transmission shaft 50.
From initial position a to middle position b, transmission shaft 50 is suitable for overcoming compensation section 6 to apply by 2 output torque of actuator
Barrier force.In this course, helical spring 60 provides elastic force in compressive state to generate the barrier force, the barrier force
It is contrary that the required force of periphery is rotated with transmission shaft 50, therefore in clutch separation process, transmission shaft 50 will overcome barrier force to revolve
Go to middle position b.From initial position a to middle position b, hinge joint A gradually rotates upwards, and moves closer to helical spring 60
Side, therefore helical spring 60 is squeezed by continued compression, and elastic force is accumulated.
Initial position a why is defined, is when clutch is in engagement state, helical spring 50 is still in compression shape
State inhibits transmission shaft 50 to rotate, and keeps the positional stability of transmission shaft 50, and then keep disengaging yoke axis 3 and disengaging yoke 4
Stability, to effectively maintain the engagement state of clutch.
From middle position b to final position c, the compressive deformation of helical spring 60 is discharged to provide balancing force, is compensated at this time
Power is the component of elastic force along a tangential direction, and transmission shaft 50 can effectively be driven to rotate.The output torque and spiral bullet of actuator 2
The balancing force that spring 60 provides drives transmission shaft 50 to rotate jointly,
Wherein, the outer peripheral surface of transmission shaft 50 is equipped with protruding portion 53, and transmission shaft 50 is hinged by protruding portion 53 and compensation section 6,
Compensation section 6 is hinged by helical spring 60 and protruding portion 53 simultaneously.On the one hand, protruding portion 53 provides hinged mounting portion.Another party
Face, when transmission shaft 50 rotates, can be relatively rotated between protruding portion 53 and helical spring 60 by hinged, avoid spiral shell
The spring wire of rotation spring 60 is distorted deformation.
Wherein, electric clutch executing agency 1 further include: locating part 7, suitable for being kept out in initial position a and hinge joint A,
To stop transmission shaft 50 to be blocked power rotation.Initial position a can correspond to clutched state, as previously mentioned, initial
Position a, compensation section 6 are that transmission shaft 50 provides barrier force, this makes transmission shaft 50 have the trend rotated counterclockwise.At this point, limit
Position part 7 and hinge joint A is kept out, and the rotating tendency of transmission shaft 50 can be stopped to be converted into effective rotation, this may be implemented preferably
Mechanical self-latching function guarantees that larger shaking will not occur under external force in electric clutch executing agency 1.
Compensation section 6 further includes positioning region 61 (Fig. 1 is not shown), and positioning region 61 is fixed in one end of helical spring 60, positioning
Portion 61 is used to fix helical spring 60.
Wherein, actuator 2 includes first rotating shaft 20.Transmission mechanism 5 further include: first order deceleration mechanism 51 and the second level subtract
Fast mechanism 52, every first class reducer structure includes input unit and output section, and the output revolving speed of output section is defeated lower than input unit
Enter revolving speed.
Wherein, first order deceleration mechanism 51 includes as the first input unit 511 of input unit and as the first of output section
Output section 512.First input unit 511 and first rotating shaft 20 are coaxially connected, and the first output section 512 and transmission shaft 50 are coaxially connected,
First output section, 512 output torque and revolving speed are to transmission shaft 50.Also, shape between the first input unit 511 and the first output section 512
Cooperate at slowing down, so that the output revolving speed of the first output section 512 is lower than the input speed of the first input unit 511.
Second level deceleration mechanism 52 includes: the second input unit 521 as input unit and the second output as output section
Portion 522.Second input unit 521 and transmission shaft 50 are coaxially connected, and the second input unit 521 is from 50 input torque of transmission shaft and revolving speed.
Second output section 522 and disengaging yoke axis 3 are coaxially connected, and the second output section 522 is to 3 output torque of disengaging yoke axis and revolving speed.
Also, the output revolving speed of the second output section 522 is lower than the input speed of the first input unit 511.
It is equal to the product of torque and revolving speed, the output of first order deceleration mechanism 51 and second level deceleration mechanism 52 according to power
Revolving speed reduces, but output torque increases, therefore transmission mechanism 5 plays the role of deceleration torque increase.
In a kind of variation, transmission mechanism may include at least one level deceleration mechanism, be not limited to double reduction mechanism.This
When, wherein at least the input unit in primary speed-down mechanism or output section and transmission shaft are coaxially connected.
In the present embodiment, first order deceleration mechanism 51 be second level deceleration mechanism 52 upper level deceleration mechanism, second
Grade deceleration mechanism 52 is the next stage deceleration mechanism of first order deceleration mechanism 51, wherein the first output section 512 and the second input unit
521 are connected to transmission shaft 50.
In a kind of variation, deceleration mechanism includes at least two-stage, and the upper level in deceleration mechanism described in adjacent two-stage subtracts
The output section of fast mechanism and the input unit of next stage deceleration mechanism are connected to same axis, and the structure that transmission mechanism can be enhanced in this is tight
Degree of gathering.Meanwhile the same axis can be used as transmission shaft, be connected to compensation section.
In first order deceleration mechanism 51, the first input unit 511 is worm screw, and the first output section 512 is worm gear, worm gear and snail
Bar is engaged to form worm gear mechanism, and the worm gear mechanism is as first order deceleration mechanism 51.The biography of Worm Wheel System
Dynamic the ratio between the number of teeth and the helical rack number of worm screw than being equal to worm gear, is 1 in the helical rack number of worm screw, and the number of teeth of worm gear is
Several, transmission ratio is integer, therefore the revolving speed of worm gear is less than the revolving speed of worm screw, realizes first order deceleration torque increase effect.Wherein,
Worm screw is coaxially connected in first rotating shaft 20, and worm gear fixing sleeve is on transmission shaft 50.
Wherein, worm gear is sector gear, and cost is relatively low.
In second level deceleration mechanism 52, the second input unit 521 is first gear and the second output section 522 is the second tooth
Wheel, first gear and second gear engagement are to form gear drive.The reduction ratio of gear drive is equal to first gear
Radius and the ratio between the radius of second gear may be implemented second when the radius of first gear is less than the radius of second gear
The effect of 52 deceleration torque increase of grade deceleration mechanism.
Wherein, first gear fixing sleeve is on transmission shaft 50 and second gear fixing sleeve is on disengaging yoke axis 3.Second tooth
Wheel is sector gear.
Other than compensation section 6 can choose helical spring 60, in a kind of variation, compensation section may include: hydraulic press
Structure or air pressure mechanism, comprising: cylinder body limits pressure chamber；Piston is located in the pressure chamber；Push rod, positioned at the axis of the piston
It is connect to side, and with the piston.The compensation section is used for: liquid medium of the piston backwards to the pressure chamber portions of push rod side
Or gas medium provides hydraulic or air pressure using as the balancing force.During clutch separation, it can be broken through in hinge joint
When middle position, start to provide air pressure or hydraulic to generate balancing force, to compensate the output torque of actuator.It is engaged in clutch
State can provide air pressure or hydraulic to generate barrier force, realize mechanical self-latching in initial position.
Although present disclosure is as above, present invention is not limited to this.Anyone skilled in the art are not departing from this
It in the spirit and scope of invention, can make various changes or modifications, therefore protection scope of the present invention should be with claim institute
Subject to the range of restriction.
Claims (12)
1. a kind of electric clutch executing agency characterized by comprising
Actuator is used for output torque；
Disengaging yoke axis；
Transmission mechanism connects the actuator and disengaging yoke axis, and output torque to the separation for transmitting the actuator is dialled
Fork shaft is to drive the disengaging yoke axis to rotate around own central axis line；
Compensation section, for providing balancing force in clutch separation, to compensate the output torque of the disengaging yoke axis；
The transmission mechanism includes: the transmission shaft for transmitting torque；The compensation section and the transmission shaft are hinged, and hinge joint is suitable
It is rotated synchronously in the disengaging yoke axis, and the balancing force is suitable for compensating transmission shaft rotation institute by the hinge joint
Need the force of periphery；
The hinge joint is suitable in the clutch separation process successively from initial position, through middle position position rotation to terminal
Turn；
In the middle position, the compensation section passes through the axis of the transmission shaft to the position of the transmission shaft applied force
Line；
From the initial position to middle position, the transmission shaft is suitable for overcoming the compensation by the actuator output torque
The barrier force that portion applies；
From the middle position to the final position, the compensation section is adapted to provide for the balancing force；
Further include: locating part, suitable for being kept out in the initial position and the hinge joint, to stop the transmission shaft by the resistance
Keep off power rotation.
2. electric clutch executing agency as described in claim 1, which is characterized in that the compensation section and the disengaging yoke
Axis is hinged, and hinge joint is suitable for rotating synchronously with the disengaging yoke axis, and the balancing force is suitable for compensating by the hinge joint
The force of periphery needed for the disengaging yoke axis rotates.
3. electric clutch executing agency as described in claim 1, which is characterized in that the outer peripheral surface of the transmission shaft is equipped with prominent
Portion out, the transmission shaft are hinged by the protruding portion and the compensation section.
4. electric clutch executing agency as described in claim 1, which is characterized in that the compensation section is helical spring, from
For the initial position to middle position, the helical spring provides the elastic force in compressive state to generate the barrier force；
From the middle position to the final position, the compressive deformation of the helical spring is discharged to provide the balancing force.
5. electric clutch executing agency as described in claim 1, which is characterized in that the transmission mechanism further includes at least one
Grade deceleration mechanism, every grade of deceleration mechanism includes input unit and output section, and the output revolving speed of the output section is lower than described
The input speed of input unit.
6. electric clutch executing agency as claimed in claim 5, which is characterized in that the deceleration mechanism includes at least two
Grade, the output section of the upper level deceleration mechanism in deceleration mechanism described in adjacent two-stage is connected with the input unit of next stage deceleration mechanism
In same axis.
7. electric clutch executing agency as claimed in claim 6, which is characterized in that the same axis is as the transmission
Axis.
8. electric clutch executing agency as claimed in claim 5, which is characterized in that the input unit is worm screw, described defeated
Portion is worm gear out, and the worm gear and worm screw engagement are to form worm gear mechanism.
9. electric clutch executing agency as claimed in claim 5, which is characterized in that the input unit is first gear and institute
Stating output section is second gear, and the first gear and second gear engagement are to form gear drive.
10. electric clutch executing agency as described in claim 1, which is characterized in that the compensation section includes:
Helical spring, for discharging elastic force by compressive state in clutch separation, using as the balancing force.
11. electric clutch executing agency as described in claim 1, which is characterized in that the compensation section includes:
Hydraulic mechanism or air pressure mechanism, comprising:
Cylinder body limits pressure chamber；
Piston is located in the pressure chamber；
Push rod is connect positioned at the axial side of the piston, and with the piston；
The compensation section is used for: the piston provides liquid backwards to the liquid medium or gas medium of the pressure chamber portions of push rod side
Pressure or air pressure are using as the balancing force.
12. a kind of automobile characterized by comprising the described in any item electric clutch executing agencies of claim 1-11.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710957775.1A CN109667848B (en) | 2017-10-13 | 2017-10-13 | Automobile and electric clutch actuating mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710957775.1A CN109667848B (en) | 2017-10-13 | 2017-10-13 | Automobile and electric clutch actuating mechanism |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109667848A true CN109667848A (en) | 2019-04-23 |
| CN109667848B CN109667848B (en) | 2021-05-28 |
Family
ID=66139042
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710957775.1A Active CN109667848B (en) | 2017-10-13 | 2017-10-13 | Automobile and electric clutch actuating mechanism |
Country Status (1)
| Country | Link |
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| CN (1) | CN109667848B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110985561A (en) * | 2019-12-27 | 2020-04-10 | 株洲齿轮有限责任公司 | Clutch actuating mechanism, clutch and automobile |
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| CN1786501A (en) * | 2004-12-09 | 2006-06-14 | 财团法人工业技术研究所 | The actuator structure of the electromechanical control clutch |
| JP2008121714A (en) * | 2006-11-08 | 2008-05-29 | Aisin Seiki Co Ltd | Clutch actuator |
| EP2060817A1 (en) * | 2007-11-15 | 2009-05-20 | Yamaha Hatsudoki Kabushiki Kaisha | Clutch drive device and vehicle equipped therewith |
| CN202545647U (en) * | 2012-04-23 | 2012-11-21 | 东风汽车公司 | Clutch automatic control mechanism |
| CN105351393A (en) * | 2015-11-30 | 2016-02-24 | 重庆科鑫三佳车辆技术有限公司 | Automatic clutch actuator |
| CN105570452A (en) * | 2016-01-25 | 2016-05-11 | 上海易巴汽车动力系统有限公司 | AMT (automated mechanical transmission) clutch mechanism for commercial vehicle |
-
2017
- 2017-10-13 CN CN201710957775.1A patent/CN109667848B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1786501A (en) * | 2004-12-09 | 2006-06-14 | 财团法人工业技术研究所 | The actuator structure of the electromechanical control clutch |
| JP2008121714A (en) * | 2006-11-08 | 2008-05-29 | Aisin Seiki Co Ltd | Clutch actuator |
| EP2060817A1 (en) * | 2007-11-15 | 2009-05-20 | Yamaha Hatsudoki Kabushiki Kaisha | Clutch drive device and vehicle equipped therewith |
| CN202545647U (en) * | 2012-04-23 | 2012-11-21 | 东风汽车公司 | Clutch automatic control mechanism |
| CN105351393A (en) * | 2015-11-30 | 2016-02-24 | 重庆科鑫三佳车辆技术有限公司 | Automatic clutch actuator |
| CN105570452A (en) * | 2016-01-25 | 2016-05-11 | 上海易巴汽车动力系统有限公司 | AMT (automated mechanical transmission) clutch mechanism for commercial vehicle |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN110985561A (en) * | 2019-12-27 | 2020-04-10 | 株洲齿轮有限责任公司 | Clutch actuating mechanism, clutch and automobile |
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| Publication number | Publication date |
|---|---|
| CN109667848B (en) | 2021-05-28 |
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Effective date of registration: 20210114 Address after: No. 203, Shanghai Songjiang Road, No. 201563, Pudong New Area Applicant after: SAIC Motor Corp.,Ltd. Address before: 201203 Room 509, Building No. 1, 563 Songtao Road, Zhangjiang High-tech Park, Pudong New Area, Shanghai Applicant before: SAIC Motor Corp.,Ltd. |
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