CN104141708B - clutch actuator - Google Patents
clutch actuator Download PDFInfo
- Publication number
- CN104141708B CN104141708B CN201410188300.7A CN201410188300A CN104141708B CN 104141708 B CN104141708 B CN 104141708B CN 201410188300 A CN201410188300 A CN 201410188300A CN 104141708 B CN104141708 B CN 104141708B
- Authority
- CN
- China
- Prior art keywords
- gear
- clutch
- actuating mechanism
- transmission device
- gear stage
- 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
- 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
- F16D21/00—Systems comprising a plurality of actuated clutches
- F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
- F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
-
- 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
-
- 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
- F16D21/00—Systems comprising a plurality of actuated clutches
- F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
- F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
- F16D2021/0607—Double clutch with torque input plate in-between the two clutches, i.e. having a central input plate
- F16D2021/0615—Double clutch with torque input plate in-between the two clutches, i.e. having a central input plate the central input plate is supported by bearings in-between the two 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
- F16D21/00—Systems comprising a plurality of actuated clutches
- F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
- F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
- F16D2021/0646—Electrically actuated clutch with two clutch plates
-
- 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
- F16D21/00—Systems comprising a plurality of actuated clutches
- F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
- F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
- F16D2021/0692—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric with two clutches arranged axially without radial overlap
-
- 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
- F16D2023/123—Clutch actuation by cams, ramps or ball-screw mechanisms
-
- 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
-
- 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
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/46—Systems consisting of a plurality of gear trains each with orbital gears, i.e. systems having three or more central gears
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Retarders (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
The invention relates to a clutch actuator for actuating a friction clutch arranged about a rotational axis by means of an actuator mechanism which is driven by a servomotor arranged substantially perpendicularly to the rotational axis with respect to a rotor axis and displaces a lever element of the friction clutch axially along an actuation path relative to the rotational axis. In order to achieve a high reduction ratio of the servomotor with a small installation space, a planetary gear set is arranged coaxially with the rotor shaft, which reduces the rotational speed of the rotor, and the actuator mechanism comprises a rotary lever, which is driven in rotation by the planetary gear set and axially displaces the actuating sleeve.
Description
Technical field
The present invention relates to a kind of clutch actuating mechanism, the clutch actuating mechanism is used for by means of executing agency's machinery
Device manipulates the friction clutch being arranged around pivot center, and executing agency's mechanical device is by basic about rotor axis
On perpendicular to pivot center setting servo motor driven and by the lever element of friction clutch relative to pivot center axial direction
Ground is shifted along path is manipulated.
Background technology
Clutch actuating mechanism is used to manipulate the friction clutch in the powertrain of motor vehicles.Here, according to rubbing
The composition for wiping clutch manipulates the friction clutch being arranged around pivot center by means of the axially displaced of lever element.By
It herein can be in dish type in the friction clutch for being configured to the lever element of disc spring in the state of no manipulation and being closed
The friction clutch that spring taper with coaxial pulls out or pushes open, and opened in the state of no manipulation for example by means of
The lever taper for helping arm spring is compressed or is tensed.Two such friction clutches can be combined into double clutch,
So that two clutch actuating mechanisms that are individual or being assembled into structural unit manipulate friction clutch respectively.
This clutch actuating mechanism is driven by electric servomotor, and the electric servomotor is controlled by control device
System so that the desired torque to be transmitted can be controlled rapidly and reproducibly.For example, the clutch equipped with electric servomotor
Executing agency is known from document DE102008013054A1 and DE102004009832A1.Here, the armature spindle of servo motor
Line is arranged substantially perpendicular to the pivot center of friction clutch respectively.In order to which the rotational motion of the rotor of servo motor is turned
It changes linear motion into and is equipped with corresponding transmission device respectively.Here, according to clutch on the manipulation path of friction clutch
Position uses different power so that servo motor must be designed for maximum power.In addition, servo motor is in required work(
It is configured to the slow-speed of revolution in the case of rate relatively large so that use the servo horse of high-speed rotation in conjunction with speed reduction gearing when necessary
It reaches.
Invention content
Therefore, the purpose of the present invention is to be constituted clutch execution in a manner of saving space and have big transmission ratio
Mechanism.
The purpose is realized by a kind of clutch actuating mechanism according to the present invention.Hereafter provide advantageous implementation again
Example.
Itd is proposed for manipulates around pivot center setting friction clutch clutch actuating mechanism comprising about
Rotor axis is substantially perpendicular to the servo motor of pivot center setting.The servo motor is by means of executing agency's mechanical device
The lever element of friction clutch is set to shift axially along path is manipulated relative to pivot center, for example, such as friction clutch
Disc spring and arm spring lever element.Lever element shifts in which can press or pull.As a result, with friction clutch
Composition relatively, can forcibly close or open friction clutch.Here, the reduction ratio that the rotating speed of servo motor is slack-off
It is realized by means of the planet gear transmission device for the reduction rotor speed being coaxially disposed with armature spindle.Executing agency's mechanical device
Including by the rotating lever axially displaced by sleeve is manipulated of planet gear transmission device rotation driving.
It is particularly favourable that two clutch actuating mechanisms can be combined to manipulate the friction clutch of double clutch,
Middle rotating lever and the manipulation sleeve shifted by it can be nested with one another so that in larger one friction clutch of diametrically manipulation
Device and in smaller another friction clutch of diametrically manipulation.Here, for example identical clutch actuating mechanism in addition
Rotation direction is different, and by this way, a friction clutch manipulates with capable of being pulled and another friction clutch
It manipulates with capable of being pressed.
Planet gear transmission device is preferably configured as the planet gear transmission device of three-level.Here, the first and second planets
Gear stage can be configured to double-shaft transmission device and third planet gear stage can be configured to three-axle gear.Preferably,
Second double-shaft transmission device and three-axle gear form the positive drive device (Plusgetriebe) with high reduction ratio.Example
Such as, the electro-motor of high-speed rotation can for example be equipped with relatively small power, and the electro-motor is by means of positive drive device phase
Slow down with answering.In this regard, propose the slack-off transmission ratio of motor rotary speed, i.e. from 100 to 600 transmission ratio, preferably approximately 300.Here,
The modulus of teeth portion is preferably defined as being equal to or less than 1, enabling is equipped with small structure space for transmission device.Have confirmed for
Advantageously, modulus determine at so that electro-motor and planet gear transmission device outer diameter substantially having the same so that row
Star gear assembly can be directly connected on rotor with flange or input shaft or the planet gear transmission device in
Sun gear can be constituted one-piece.Here, structural unit can be equipped with unified outer diameter.
According to an advantageous form of implementation, the first and second epicyclic gear stages have common, antitorque setting, for example
The integrated gear ring with the shell or electro-motor of planet gear transmission device and the common shell of planet gear transmission device.
In addition, the first and second epicyclic gear stages can have common pinion frame and be distributed in the circumferential and
And the planetary gear engaged with the gear ring of second and third planet gear stage.Here, the sun gear of the first epicyclic gear stage can
It is torsionally connected with armature spindle and pinion frame can be antitorque with the common sun gear of second and third planet gear stage
Ground connects.
In addition, it has already been proven that be advantageously, being set respectively between the planetary gear and sun gear of three epicyclic gear stages
Fixed identical teeth portion.In order to constitute high reduction ratio, in particular, the quantity of the tooth of the gear ring of the first epicyclic gear stage with second and
Difference between the quantity of the tooth of the common gear ring of third planet gear stage can at most be equivalent to second and third planet gear
The planetary quantity of grade.
In another advantageous form of implementation of planet gear transmission device, the gear ring of third planet gear stage can have
There is the common gear ring of positive displacement and the first and second epicyclic gear stages that there can be negative displacement.
Generally, the present invention relates to a kind of axis settings perpendicular to the friction clutch to be manipulated in rotating lever
The clutch actuating mechanism of the form of actuator, the wherein torque of rotating lever are via electro-motor and the intermediate planet tooth accessed
Driver is taken turns to provide.Planetary transmissions (Umlaufgetriebe), such as planet gear transmission device pass through more herein
The design scheme of grade has the resultant gear ratio between 100 and 600, wherein especially advantageous deformation scheme is with about 300
Transmission ratio.The modulus of teeth portion is less than 1 herein, so as to realize structure space as compact as possible.Therefore, rotating lever executes
The size of device can be constrained to the diameter less than 50mm.The structure length of planetary gear mechanism can be less than 30mm.
Description of the drawings
The present invention is elaborated according to the embodiment shown in Fig. 1 to 5.It is shown here：
Fig. 1 shows the portion of the double clutch of the clutch actuating mechanism with the friction clutch for manipulating double clutch
Divide section,
Fig. 2 shows the tool of the double clutch of Fig. 1 there are two clutch actuating mechanism manipulation device schematic diagram,
Fig. 3 shows the transmission device schematic diagram of the planet gear transmission device of the clutch actuating mechanism of Fig. 1 and 2,
Fig. 4 shows scheming according to the 3D of open transmission device for the form of implementation of the planet gear transmission device of Fig. 3, and
Fig. 5 shows the sectional view of the planet gear transmission device of Fig. 4.
Specific implementation mode
Fig. 1 shows the upper of the double clutch 100 with the friction clutch 101 tensed and the friction clutch 102 of compression
Half portion sectional view.Friction clutch 101,102 is manipulated by means respectively of the axially displaced of lever element 103,104, wherein respectively
One connector 107,108 by means of manipulating the disengaging of bearing 105,106 is by clutch actuating mechanism 1 axially along double clutches
The pivot center d displacements of device 100.In this regard, its rotor axis d (r) perpendicular to double clutch 100 pivot center d setting from
1 rotation driving mechanism mechanical device 113 of clutch executing agency.Executing agency's mechanical device includes from visible turn of detail D
Dynamic lever 109 so that when the drive shaft 2 of clutch actuating mechanism 1 rotates, connector 107 is moved along sleeve part 110 is axial
Position.Clutch actuating mechanism 1 is rotatably received in by means of bearing 111 in load bearing component 112.Load bearing component 112 for example with
The connection of transmission device wall portion is for example spirally connected.Clutch actuating mechanism 1 for example by electro-motor 3 and is arranged in the electro-motor
Planet gear transmission device 4 between drive shaft 2 is constituted.
Fig. 2 shows clutch actuating mechanism 1, the 3D schematic diagrames of 1a, the clutch actuating mechanism by means of bearing 111,
111a is rotatably supported at its drive shaft 2,2a on load bearing component 112.Electro-motor 3,3a are by means of being arranged described
Planet gear transmission device 4 that big degree between electro-motor and drive shaft 2,2a is slowed down, 4a drive drive shaft 2,2a,
Rotating lever 109,109a are fixed in the drive shaft.Rotating lever 109,109a make being not shown, embedding to each other with diameter
Cover and in terms of movement mode independent of each other the different connectors being diametrically contained in sleeve part 110 axially
Displacement.
Fig. 3 shows that the transmission device for the planet gear transmission device 4 being integrated into the clutch actuating mechanism 1 of Fig. 2,1a shows
It is intended to.Planet gear transmission device 4 is made of epicyclic gear stage I, II, III.On the whole, planet gear transmission device 4 with electricity
Input shaft 5 that is that the armature spindle (Fig. 1) of dynamic motor 3 coaxially connects or constituting one-piece and for driving rotating lever 109
Drive shaft 2 (Fig. 1 and 2) between formed preferably 300 slack-off transmission ratio.Here, by small input torque Min, for example
0.1Nm drives input shaft 5.Due to the characteristic of the torque transfer of planet gear transmission device 4, presence on the driving shaft is about
The output torque M of 30Nmout。
First epicyclic gear stage I forms double-shaft transmission device, wherein the sun gear 7 driven by input shaft 5 drives rotatably
Ground is arranged the planetary gear 9 on pinion frame 8, the planetary gear 9 simultaneously be arranged to and the fixed gear ring of shell 10
Engagement.Epicyclic gear stage II equally constitutes as double-shaft transmission device.Sun gear 11 is driven by the pinion frame 8 of epicyclic gear stage I
It moves and is engaged with the planetary gear 13 being contained on pinion frame 12.Planetary gear 13 and it is arranged to and the fixed tooth of shell
10 engagement of circle, the gear ring are configured to the common gear ring of epicyclic gear stage I, II.Epicyclic gear stage III is configured to the transmission of three axis
Device, the three-axle gear share sun gear 11, pinion frame 12 and planetary gear 13 with epicyclic gear stage II.Planet
Gear 13 is engaged with gear ring 10 and the gear ring being connect with drive shaft 2 14 simultaneously.The number of teeth of gear ring 10,14 is only slight different, at most
The quantity of the planetary gear 13 of difference distribution in the circumferential.Thereby, it is possible to realize to have from input shaft 5 to the slack-off of drive shaft 2
Especially high transmission ratio, that is to say, that there is the positive drive device of high reduction ratio when Low-torque is converted into high torque.
Figure 4 and 5 show being opened in shell 15 for the form of implementation constituted in the structure of the planet gear transmission device 4 of Fig. 3
When view (Fig. 4) and sectional view (Fig. 5).Epicyclic gear stage I has input teeth portion 16 identical with sun gear 7, described defeated
Enter to be connected with the rotor of electro-motor with flange in teeth portion.Disc-shaped part 17 forms pinion frame 8 and can turn on side
Planetary gear 9 is accommodated dynamicly.The other side of planetary gear 9 is made of the flange components 18 of sun gear 11.It can on sun gear 11
Rotationally bearing, such as slidably supported disc-shaped part 19.The disc-shaped part 19 forms pinion frame 12 with disc-shaped part 20
For accommodating the planetary gear 13 of epicyclic gear stage II, III.The gear ring 10 of epicyclic gear stage I, II are integrated by its interior teeth portion
Into shell 15.The gear ring 14 of epicyclic gear stage III is located axially adjacent to 15 ground of shell setting and for example straight by means of convex block 21
Ground connection or the sleeve part by means of being not shown or the flange components axially widened and drive shaft are in a manner of being rotatably assorted
Connection.Small outer diameter D (a) less than 50mm can be realized by the compact structure of planet gear transmission device 4 and is less than
The short axial length l of 30mm.
Reference numerals list：
1 clutch actuating mechanism
1a clutch actuating mechanisms
2 drive shafts
2a drive shafts
3 electro-motors
3a electro-motors
4 planet gear transmission devices
4a planet gear transmission devices
5 input shafts
7 sun gears
8 pinion frames
9 planetary gears
10 gear rings
11 sun gears
12 pinion frames
13 planetary gears
14 gear rings
15 shells
16 input teeth
17 disc-shaped parts
18 flange components
19 disc-shaped parts
20 disc-shaped parts
21 convex blocks
100 double clutches
101 friction clutches
102 friction clutches
103 lever elements
104 lever elements
105 manipulate bearing
106 manipulate bearing
107 connectors
108 connectors
109 rotating levers
109a rotating levers
110 sleeve parts
111 bearings
111a bearings
112 load bearing components
113 executing agency's mechanical devices
D details
D (a) overall diameters
D pivot centers
D (r) rotor axis
L length
MinInput torque
MoutOutput torque
I epicyclic gear stages
II epicyclic gear stages
III epicyclic gear stages.
Claims (10)
1. a kind of clutch actuating mechanism (1,1a), the clutch actuating mechanism is used for by means of executing agency's mechanical device
(113) friction clutch being arranged around pivot center (d) is manipulated, executing agency's mechanical device is by rotor axis (d
(r)) be substantially perpendicular to the pivot center (d) setting electro-motor (3,3a) driving and by friction clutch (101,
102) lever element (103,104) exists relative to the pivot center (d) axially along path displacement, feature is manipulated
In, the planet gear transmission device (4,4a) with the rotor axis (d (r)) coaxially equipped with reduction rotor speed, and institute
It includes by the planet gear transmission device (4,4a) rotation driving, by connector to state executing agency's mechanical device (113)
(107,108) axially displaced rotating lever (109,109a), wherein the friction clutch is to include two sub- clutches
The double clutch of (101,102), the rotating lever (109,109a) and the manipulation sleeve by its displacement can be nested with one another, and be made
It obtains and diametrically manipulates a sub- clutch and in smaller another sub- clutch of diametrically manipulation in larger.
2. clutch actuating mechanism (1,1a) according to claim 1, which is characterized in that the planet gear transmission device
(4,4a) are configured to the planet gear transmission device of three-level.
3. clutch actuating mechanism (1,1a) according to claim 2, which is characterized in that the first epicyclic gear stage (I) and
Second epicyclic gear stage (II) is configured to double-shaft transmission device and third planet gear stage (III) is configured to three axis transmission dress
It sets.
4. clutch actuating mechanism (1,1a) according to claim 3, which is characterized in that the second double-shaft transmission device and institute
It states three-axle gear and forms the positive drive device with high reduction ratio.
5. clutch actuating mechanism (1,1a) according to claim 3 or 4, which is characterized in that first planetary gear
Transmission device (I) and second planet gear transmission device (II) have the gear ring (10) of common, antitorque setting.
6. clutch actuating mechanism (1,1a) according to claim 3 or 4, which is characterized in that second planetary gear
Grade (II) and the third planet gear stage (III) with common pinion frame (12) and be distributed in the circumferential and
With the planetary gear of the gear ring (10,14) of second epicyclic gear stage (II) and the third planet gear stage (III) engagement
(13)。
7. clutch actuating mechanism (1,1a) according to claim 6, which is characterized in that first epicyclic gear stage
(I) sun gear (7) is torsionally connected with armature spindle, and pinion frame (8) and second epicyclic gear stage (II) and
The common sun gear (11) of the third planet gear stage (III) is torsionally connected.
8. clutch actuating mechanism (1,1a) according to claim 3 or 4, which is characterized in that in three planet teeth
Identical teeth portion is set separately between the sun gear (7,11) and planetary gear (9,13) of wheel grade (I, II, III).
9. clutch actuating mechanism (1,1a) according to claim 5, which is characterized in that first epicyclic gear stage
(I) quantity of the tooth of gear ring (10) and second epicyclic gear stage (II) and third planet gear stage (III's) is total to
The difference of the quantity of the tooth of same gear ring (14) is at most equivalent to second epicyclic gear stage (II) and the third planet gear
The quantity of the planetary gear (13) of grade (III).
10. clutch actuating mechanism (1,1a) according to claim 3 or 4, which is characterized in that the third planet gear
The gear ring (14) of grade (III) can be with positive displacement and first epicyclic gear stage (I) and second planetary gear
The common gear ring (10) of grade (II) can have negative displacement.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102013208323 | 2013-05-07 | ||
| DE102013208323.8 | 2013-05-07 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104141708A CN104141708A (en) | 2014-11-12 |
| CN104141708B true CN104141708B (en) | 2018-10-12 |
Family
ID=51787727
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410188300.7A Active CN104141708B (en) | 2013-05-07 | 2014-05-06 | clutch actuator |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN104141708B (en) |
| DE (1) | DE102014207080A1 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| ITUB20154031A1 (en) * | 2015-09-30 | 2017-03-30 | Freni Brembo Spa | MOTORCYCLE CLUTCH ACTUATOR |
| DE102016215596A1 (en) * | 2016-08-19 | 2018-02-22 | Schaeffler Technologies AG & Co. KG | friction clutch |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2161237B (en) * | 1984-05-28 | 1987-11-25 | Valeo | Power actuator for a machine element such as a clutch brake or change speed gearing |
| CN1198133A (en) * | 1995-07-12 | 1998-11-04 | 卢克驱动系统有限公司 | Clutch and gear actuation device |
| US6099430A (en) * | 1999-08-06 | 2000-08-08 | New Venture Gear, Inc. | Clutching actuator for clutch control system in a drive line apparatus |
| DE102004009832A1 (en) * | 2003-03-03 | 2004-09-16 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Disengaging system for a motor vehicle coupling or brake has lever with support point which is displaceable to adjust the operating force on the coupling |
| CN101581341A (en) * | 2008-03-06 | 2009-11-18 | 格特拉格传动机构和齿轮工厂赫尔曼·哈根迈尔有限公司&两合公司 | Adjustment mechanism for inserting and extracting a separation coupling with rotating curve segment |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3309427A1 (en) * | 1982-03-18 | 1983-10-06 | Valeo | ACTUATING DEVICE FOR A CLUTCH, A REGULAR GEARBOX, A BRAKE, OR SIMILAR |
-
2014
- 2014-04-14 DE DE102014207080.5A patent/DE102014207080A1/en active Granted
- 2014-05-06 CN CN201410188300.7A patent/CN104141708B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2161237B (en) * | 1984-05-28 | 1987-11-25 | Valeo | Power actuator for a machine element such as a clutch brake or change speed gearing |
| CN1198133A (en) * | 1995-07-12 | 1998-11-04 | 卢克驱动系统有限公司 | Clutch and gear actuation device |
| US6099430A (en) * | 1999-08-06 | 2000-08-08 | New Venture Gear, Inc. | Clutching actuator for clutch control system in a drive line apparatus |
| DE102004009832A1 (en) * | 2003-03-03 | 2004-09-16 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Disengaging system for a motor vehicle coupling or brake has lever with support point which is displaceable to adjust the operating force on the coupling |
| CN101581341A (en) * | 2008-03-06 | 2009-11-18 | 格特拉格传动机构和齿轮工厂赫尔曼·哈根迈尔有限公司&两合公司 | Adjustment mechanism for inserting and extracting a separation coupling with rotating curve segment |
Non-Patent Citations (1)
| Title |
|---|
| NGWN(Ⅱ)型行星减速器基于Matlab的优化设计;朱思东等;《机电一体化》;20110810;第17卷(第3期);第95-98页 * |
Also Published As
| Publication number | Publication date |
|---|---|
| CN104141708A (en) | 2014-11-12 |
| DE102014207080A1 (en) | 2014-11-13 |
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