CN107435693A - For the device for the clutch for manipulating vehicle - Google Patents
For the device for the clutch for manipulating vehicle Download PDFInfo
- Publication number
- CN107435693A CN107435693A CN201710288611.4A CN201710288611A CN107435693A CN 107435693 A CN107435693 A CN 107435693A CN 201710288611 A CN201710288611 A CN 201710288611A CN 107435693 A CN107435693 A CN 107435693A
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- rotation
- section
- cam disc
- anglec
- clutch
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- 230000008878 coupling Effects 0.000 claims abstract description 31
- 238000010168 coupling process Methods 0.000 claims abstract description 31
- 238000005859 coupling reaction Methods 0.000 claims abstract description 31
- 230000033001 locomotion Effects 0.000 claims abstract description 26
- 230000003068 static effect Effects 0.000 claims description 40
- 230000008859 change Effects 0.000 claims description 7
- 230000005540 biological transmission Effects 0.000 description 13
- 238000000034 method Methods 0.000 description 11
- 238000000926 separation method Methods 0.000 description 11
- 230000002829 reductive effect Effects 0.000 description 9
- 238000010586 diagram Methods 0.000 description 7
- 230000006870 function Effects 0.000 description 5
- 230000007246 mechanism Effects 0.000 description 5
- 238000006243 chemical reaction Methods 0.000 description 4
- 238000006073 displacement reaction Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 3
- 230000002441 reversible effect Effects 0.000 description 3
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- 238000007906 compression Methods 0.000 description 2
- 230000009977 dual effect Effects 0.000 description 2
- 230000005611 electricity Effects 0.000 description 2
- 230000002349 favourable effect Effects 0.000 description 2
- 239000010720 hydraulic oil Substances 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000035939 shock Effects 0.000 description 2
- 230000007704 transition Effects 0.000 description 2
- 230000006978 adaptation Effects 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000019771 cognition Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000005662 electromechanics Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
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- 238000013021 overheating Methods 0.000 description 1
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K23/00—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for
- B60K23/02—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for for main transmission clutches
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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
- 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
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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
- 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
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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
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
The present invention relates to the device for manipulating vehicular clutch,Including the cam disc that can be rotated around an axis,Push rod,Wherein,Push rod couples in a Coupling point with cam disc,So that the linear motion of push rod is caused by the rotation of cam disc and linear motion is passed into clutch,Cam disc has the first radius in first anglec of rotation,To cause the closed mode of clutch,There is the second radius in second anglec of rotation,To cause the open mode of clutch,Cam disc has the first section and the second section between first anglec of rotation and second anglec of rotation,To be rotated in order that clutch is transformed into open mode cam disc from closed mode along the first direction of rotation,To be rotated in order that clutch is transformed into closed mode cam disc from open mode along the second direction of rotation,The radius of cam disc has constant first slope in the first section,There is the second constant slope in the radius of the second section convexity wheel disc,First slope is more than the second slope.
Description
Technical field
It is used to manipulate the device of vehicular clutch actuator in other words the present invention relates to a kind of.The invention further relates to one kind to use
In the cam disc of the device actuator in other words for the clutch for manipulating vehicle.
Background technology
It is used to manipulate the device of vehicular clutch actuator in other words by known in the art.Recently taste more and more
Examination, using following clutch, wherein, clutch process is caused by the actuator of electromechanics.In automatic driver it is also known that this
The clutch that kind activates electromechanically.This clutch in other words be used for manipulate vehicular clutch device be alternatively referred to as " it is automatically controlled from
Clutch " is referred to as " e-Clutch ".
It is often necessary to motor in this electrically controlled clutch system in the actuator of electrically controlled clutch system in other words
It is coupled to the convert rotational motion linear movement of the transmission mechanism on motor, to manipulate hydraulic cylinder.The hydraulic cylinder can then be grasped
Another hydraulic cylinder is indulged, the clutch disk coupled with another hydraulic cylinder is separated by (open mode) by another hydraulic cylinder, with
Just the torque transmission between clutch disk and Flywheel disc is interrupted.Flywheel disc is connected with the drivetrain of vehicle herein.The actuator
The counter rotational movement of the motor of device then causes reverse linear movement in other words, and the reverse linear movement manipulates hydraulic cylinder
And thereby another hydraulic cylinder is also manipulated, so as to cause clutch disk to be engaged relative to Flywheel disc.(closed in clutch engagement
State) when realize torque transmission between Flywheel disc and clutch disk.
In order to realize convert rotational motion linear movement, cam disc (Kurvenscheibe) and convex with this can be used
The push rod of wheel disc coupling.Here, the cam disc is permanently connected with transmission mechanism, and transmission mechanism itself is connected with motor.It is logical
Crossing which and being rotated by motor makes cam disc spins by transmission mechanism.By changing the half of cam disc according to the anglec of rotation
Footpath (such as passing through cam disc profile) can obtain the linear movement of push rod in a known way.Push rod is herein by guiding system (example
Such as bearing or slide) guiding so that the push rod is only capable of implementing linear movement.
This conventional embodiment for being used to manipulate the device of the clutch of vehicle is set, in cam disc cam used
Radius R linearly increases relative to anglec of rotation φ.In other words, the linear speed and cam of the speed of push rod stroke push rod in other words
Angular speed is proportional in other words for the rotating speed of disk.When angular speed keeps constant to the rotating speed of cam disc in other words, push rod linear movement
The speed of push rod stroke is thus constant in other words.
The content of the invention
The present invention is from following cognition：When using this cam disc, typically, cam disc highest is available in the presence of 360 °
Rotation angle range, clutch is moved into released state from engagement state.
It is relevant with cam disc slope for the motor torque needed for the rotation of cam disc.The slope of cam disc is defined herein as convex
First derivatives of the radius R of wheel disc on anglec of rotation φ, i.e. m=dR/d φ.Furthermore, it is necessary to motor torque with treating by pushing away
The power that bar passes to clutch is relevant, and the power is used to clutch being displaced to desired position in other words for clutch to be protected
Hold in desired position.Thus the lever arm in the direction transverse to the extension of pushrod movement direction is typically resulted in.The lever arm is made
Vertical interval for rotation axis to the Coupling point of cam disc obtains.Especially when clutch is opened, to pass through motor torque gram
Strong spring force is taken, thus very big opposing torque is applied to cam disc by push rod.Even in the so-called semi-linkage of clutch
(wherein, the Flywheel disc of clutch trackslips relative to clutch disk and only occurred between two disks small in the region of state
Torque transmission), it is also desirable to certain torque of motor.It is determined that transport condition in, such as when being travelled in congestion, Chang Li
Toggled between separation (opening) state of clutch and the semi-linkage state of clutch.For keep released state in other words be
Motor torque required for switching between semi-linkage state and released state is bigger, then motor dimension must calmly it is bigger.It is larger
Torque mean higher power consumption, such as the power consumption in terms of electric energy simultaneously, the power consumption can make automobile electric
Net is loaded and can caused the premature abrasion for manipulating the component of electronic unit due to high current drain.
Therefore following demand be present, there is provided it is a kind of to be used to manipulate the device of vehicular clutch actuator in other words, wherein, it is
Torque required for controlled clutch, acting the motor driven is as small as possible, while between the engagement and separation of clutch
Switching time it is as short as possible and ideally cam disc is rotated up to for clutch is displaced into released state from engagement state
355°.The demand to the device of the clutch for manipulating vehicle actuator in other words is particularly there may be, described device is in other words
The actuator is when clutch is displaced to semi-linkage state from engagement state and when being maintained at released state in switching time
The motor torque needed while short is as small as possible.
A kind of device for manipulating vehicular clutch actuator in other words is proposed according to the first aspect of the invention.It is described
Actuator includes that the cam disc of axis rotation can be surrounded and including push rod device in other words.Described device actuator example in other words
Can such as have motor, for making cam disc spins.The push rod has first end, in the first end upper push-rod in Coupling point
Being coupled in the following manner with cam disc can couple in other words：So that being caused by cam disc around axis rotation can draw in other words
The linear motion of push rod is played, the linear motion is passed into clutch.The radius R of cam disc is defined herein as from axis to coupling
The spacing of chalaza.Cam disc has the first radius R1 in the case of the first anglec of rotation φ 1, for causing the closing of clutch
State C engagement state C in other words.Cam disc has the second radius R2 in the case of the second anglec of rotation φ 2, for cause from
The open mode O of clutch released state O in other words.Cam disc has between the first anglec of rotation φ 1 and the second anglec of rotation φ 2
There are at least one first section S1 and the second section S2.Described device is configured to：In order that clutch is transformed into from closed mode C
Open mode O, cam disc will rotate along the first direction of rotation and can be rotated in other words along the first direction of rotation, wherein, the coupling
Put the first section S1 and then second section S2 that passes by that passes by first；In order to which clutch is transformed into closed mode from open mode O
C, cam disc can will rotate along second direction of rotation in other words along the second direction of rotation rotation opposite with the first direction of rotation,
Wherein, the Coupling point is passed by first the second section S2 and then passes by the first section S1.Here, in the first section S1 convexity wheel discs
Radius R there is the first slope m1 of substantial constant on anglec of rotation φ.Here, the half of the second section S2 convexity wheel discs
Footpath R has the second slope m2 of substantial constant on anglec of rotation φ.Here, first slope m1 is more than the second slope m2.It is special
Not advantageously, first slope m1 is at least the big twice of the second slope m2.
By using following cam disc：The slope of the cam disc is all linear not in gamut, it may be advantageous to
On the one hand by the motor torque of needs and thereby power consumption is reduced, at the same can by between engagement state and released state or
Person says the anglec of rotation between engagement state and semi-linkage state and thereby reduces adjustment time therebetween.Thus can will be from drive
The torque of dynamic system and Flywheel disc to clutch disk transmits rapidly to reduce to be interrupted in other words.
It is the motor torque required for rotation cam disc with slope (slope is bigger, then the torque needed is bigger) and from pushing away
The power (power is bigger, then the torque needed is bigger) of bar clutch in other words is relevant.As long as clutch is also in engagement state or close
Engagement state is that is, for example small in the radius small stroke of the push rod in other words hour of cam disc, the power that cam disc is acted on from push rod.Cause
And in the scope, such as in the first section, slope is selected larger because can by this way using motor torque come
Push rod is subjected to linear displacement with speed as high as possible.In other words, it is supplied to the torque of motor can be with small originally herein
The anglec of rotation makes push rod pass by linear section as big as possible.This reduces the rotation angle range for for example realizing semi-linkage state,
So as to reduce the switching time for realizing semi-linkage state.As long as clutch is resisted spring force with can feeling and is opened, then via push rod
Act on that the power of cam disc is significantly higher, it is also significantly higher so as to act on the opposing torque of cam disc from push rod.In order in example
The motor power consumption of needs is reduced when being travelled such as in congestion in conventional scope, slope can be reduced herein.Thus can example
Such as reduce the lever arm between Coupling point and axis, the opposing torque decline of cam disc is thus acted on from push rod can protect in other words
Hold constant.In other words：The torque of motor is enough to compensate the opposite force for acting on push rod changed with other gearratios.Even if thus
The opposing torque applied by push rod can be also overcome with available motor power, even if being the linear distance section of restriction of push rod for this
Required anglec of rotation distance is also such when increasing.In the second section with second slope smaller than first slope because
And it can advantageously avoid the overheat of motor or the power electronic component for operating the motor.It can alternatively construct than when second is oblique
Small motor when rate extends as first slope.It can thus adjusted while using the motor with little power consumption
Enough torques are provided in whole sections of journey while can reduce adjustment time.By constructing with the oblique of substantial constant
The first section and the second section of rate can also cause especially uniform and low noise adjustment process, because preventing push rod uneven
Even speed and thereby anti-throw-out lever lift (generation noise) from cam disc and are stuck in other words in cam disc.In addition prevent from being applied to
Hydraulic pressure impact on push rod.Finally can advantageously extremely simple, manufacture safety, there is small franchise and cost-effectively make
Into with the cam disc of lower curtate, slope is linear in the section.
Concept " slope of substantial constant " is understood to the slope (such as in the first section in other words in the secondth area
Section in) change be no more than 3%.
Push rod herein can for example by one or more bearings or guiding, slide be supported is guided in other words so that favourable
Ground suppresses institute of the vertical interval between the axial direction and cam disk axis of linear motion deviation and push rod in cam disc
All it is constant in the case of having the anglec of rotation.
Clutch is alternatively referred to as the separation of clutch from off state to the conversion of open mode.Push rod separates herein.Instead
Come over, conversion of the clutch from open mode to closed mode can be described as the engagement of clutch.Push rod engages herein, and thereby with
Axis of its first end close to cam disc.Closed mode is defined herein as following state, in a state clutch not by
Power loads and thereby maximum closing.Open mode is defined as following state, in a state between Flywheel disc and clutch disk not
Generation torque transmission.It is possible that clutch exceedes the state just opened and further separated.
As having shown that above, slope m is defined herein as first derivatives of the radius R on anglec of rotation φ：M=
dR/dφ.Here, anglec of rotation φ increases when being rotated along the first direction of rotation.In other words, rotation angle value is from clutch
Closed mode increases to the open mode of clutch.
Such as it is settable, described device is configured to, and cam disc is only capable of in initial rotation angle φ A and final anglec of rotation φ
Rotated between E.Here, initial rotation angle φ A can be equivalent to 0 ° the anglec of rotation.Final anglec of rotation φ E can be equivalent to phase
Be less than 355 ° of anglec of rotation φ for initial rotation angle φ A, advantageously, final anglec of rotation φ E can equivalent to relative to
Initial rotation angle φ is less than 340 ° of anglec of rotation φ.Thus advantageously prevent the transition of cam disc from rotating, when cam disc from
Second anglec of rotation φ 2 is further rotated up to initial rotation angle from final anglec of rotation φ E along the first direction of rotation in other words
φ A are spent in other words when the first anglec of rotation φ 1, i.e., when being rotated by 360 ° altogether, transition rotation can cause the prominent of clutch
So engagement.
In addition it is for example settable：Cam disc is configured to prevent cam disc from further rotating more than the final anglec of rotation (φ E).
This can for example realize that the jam device prevents from rotating along the first direction of rotation to be exceeded in other words more than stop member by jam device
The final anglec of rotation.Merely illustratively, this jam device can by cam disc or in stop member formed or by convex
Chute in wheel disc is formed, and key is coupled in the chute.This jam device also may be configured to by the collective effect with push rod
To prevent from further rotating more than the final anglec of rotation.This can for example be risen by the step of cam disc radius causes.
In other words, initial rotation angle can only pass through cam disc from the anglec of rotation for being more than initial rotation angle
Back rotation is realized again.With the push rod of cam disc coupling thus in engagement with separating when pass by identical function of radius R=F
(φ), only it is merely in the opposite direction.
It can be set herein, in the case of the first anglec of rotation φ 1, the first radius R1 is equivalent to cam disc entirely can be real
Least radius in existing rotation angle range, in the rotation angle range, push rod can form Coupling point with cam disc.From
Thus in maximum closing, push rod is in maximum engagement state to engagement state to clutch in other words in other words.In addition can be set,
In the case of second anglec of rotation φ 2, the second radius R2 is equivalent to cam disc in whole achievable rotation angle range
Maximum radius, push rod can form Coupling point with cam disc in the rotation angle range.Clutch is thus opened in maximum
Push rod is in greatest separation to released state to state in other words in other words.Here, clutch can be before greatest separation
Just it is in open mode (i.e.：Torque transmission no longer occurs).
Settable, the first radius R1 is less than the second radius R2.
Such as settable, the radius on terminals of the radius R less than the second section S2 on the first section S1 terminal.Thus
Advantageously make it possible to realize the especially uniform especially uniform linear movement for separating push rod in other words of clutch.
It is settable, radius dull increase between first anglec of rotation and second anglec of rotation.It is particularly advantageous
Ground can be set, and radius increases from the starting point of the first section up to the terminal of the second section is dull.Particularly advantageously, radius is from first
The starting point of section is until the terminal strictly monotone of the second section increases.Thus the especially uniform linear fortune of push rod is advantageously caused
It is dynamic.This causes especially small noise to generate, because push rod lifts or be stuck in the risk in the sliding groove structure of cam disc from cam disc
Reduce.In addition can prevent due to load unnecessary caused by the compression shock from the hydraulic cylinder coupled with push rod.Thus most
Realize uniform maneuvering performance in the whole service life of the device for controlled clutch eventually, and with residing environment temperature
It is old unrelated with the use of the part of installation in a device.
Here, for example settable, radius R on anglec of rotation φ function R=F φ in the first section S1 and the second section
Second Order Continuous can be micro- between S2, especially can be micro- in each point Second Order Continuous.In other words, function of radius does not have bending.Thus
Especially small noise is advantageously caused to generate.Push rod lift or thus blocking for push rod equally can advantageously be avoided by.
Can be set in expansion scheme, cam disc has the end face being radially outward directed, wherein, the first end of push rod exists
One, which reclines, a little abuts on end face.Here, it is a little the Coupling point to recline.Push rod is, for example, that this can be configured with its first end
Pulley, the pulley roll on the end face of cam disc.Thus, device can run advantageously special low friction and low noise and
Make the risk minimization blocked.
It can be set in an expansion scheme, the anglec of rotation that the second section S2 starting point and the first section S1 terminal is spaced
Spend to be maximum 25 °.Particularly advantageously, the anglec of rotation that the second section S2 starting point and the first section S1 terminal are spaced is
Maximum 15 °, particularly advantageously the anglec of rotation is maximum 10 ° completely.Thus the first rotation of cam disc can particularly efficiently be utilized
Rotation angle range between gyration and second anglec of rotation and until reaching the switching time of semi-linkage state can keep
It is especially small.
It can be set in an expansion scheme, the first section S1 starting point is in first anglec of rotation on the first direction of rotation
The anglec of rotation φ 1 of φ 1 and first are added in the rotation angle range between 30 °.Thus advantageously cause, until reaching the secondth area
The switching time of section is especially short and available rotation angle range between first anglec of rotation and second anglec of rotation is special
Do not utilize efficiently.Unwanted cam disc " idle running " is thus advantageously avoided.
Alternatively or additionally it can be set, the second slope m2 is more than zero.Thus avoid reaching clutch push rod in other words
Semi-linkage state and until reach released state switching time delay.Because slope is zero to be parked in its position equivalent to push rod
Put motionless and slope is less than the zero direction displacement equivalent to push rod edge towards cam disc.
It can be set in expansion scheme, the first section S1 and the second section S2 each extend over the anglec of rotation by least 5 °
Scope, particularly advantageously pass through at least 10 ° of rotation angle range.Thus the especially uniform motion of push rod is advantageously caused.
Because in the case of cam disc constant angular speed, both push rod linear movement was in other words in the first section or in the second section
Push rod stroke is carried out with constant speed.Thus the risk that push rod blocks advantageously is also reduced, such as is stuck on bearing, or is subtracted
The small compression shock caused by push rod is acted on hydraulic cylinder.In addition make it possible to realize the operation of special low noise, because
Occur without push rod lifting or blocking relative to cam disc.
Alternatively or additionally it can be set, the first section S1 extends past at least 15 ° of rotation angle range.It is particularly advantageous
Ground, the first section extend past at least 30 ° of rotation angle range.Thus switching time is particularly efficiently reduced, because
The distance passed by one section per anglec of rotation distance by push rod is especially big.The rotation angle range of first section is bigger, then cuts
It is smaller to change the time.
Alternatively or additionally it can be set, the second section S2 extends past at least 120 ° of rotation angle range.Especially have
Sharp ground, the second section extend past at least 140 ° of rotation angle range.Thus can be particularly efficiently by the power consumption of motor
Keeping small can keep especially small by the motor torque of needs in other words.The secondth area can be passed through when big spring-force driven dual is in push rod
Slope flat Duan Zhonggeng causes push rod further to separate in the case of fractional motor torque.Because such as reduced by smaller slope
Lever arm of the push rod to cam disk axis.Longer switching time required for this can be by sufficiently long and provided with enough
The first section compensation of big first slope.The overheat of motor or the power electronic component for manipulating motor thus can be advantageously
It is avoided by.
It can be set in expansion scheme, cam disc has the between the first anglec of rotation φ 1 and the second anglec of rotation φ 2
Three section S3, wherein, there is the 3rd oblique of substantial constant on anglec of rotation φ in the radius R of the 3rd section S3 convexity wheel discs
Rate m3.Here, the second section S2 is arranged between the first section S1 and the 3rd section S3 on anglec of rotation φ.Here, second
Slope m2 is more than the 3rd slope m3.Thus, in the spring force for acting on push rod, (spring force is for example alternatively non-linear class
Type) it is big in the case of, can further reduce the power consumption of motor can overcome this by the relatively small torque of motor in other words
Kind spring force.The distance needed and slightly longer switching duration are added in 3rd section can pass through the phase of the first and second sections
Answer slope and the section length compensation of ground adaptation.Thus device with compact motor can be provided on the whole.
3rd section S3 for example may extend past at least 5 °, preferably at least 10 ° of rotation angle range.
Alternatively or additionally, the 3rd section S3 starting point and the second section S2 terminal can be spaced maximum 15 ° rotation
Angle, it can particularly advantageously be spaced the maximum 10 ° anglec of rotation.Thus first anglec of rotation that the push rod of cam disc can be engaged
Available rotation angle range between second anglec of rotation of push rod separation particularly efficiently utilizes, also, until reaches
The switching time of open mode semi-linkage state in other words can keep especially small.
Settable, the 3rd slope m3 is more than zero.Thus avoid reach clutch in other words the semi-linkage state of push rod and
Until reach the delay of the switching time of released state.Because slope be zero stopped at corresponding to push rod it is motionless and oblique on its position
Rate is less than zero and shifted equivalent to push rod along the direction towards cam disc.
In addition the 4th section can be set, the 4th section is seen in the first rotational direction to be arranged in after the 3rd section, its
In, there is on anglec of rotation φ the 4th slope m4 of substantial constant in the radius R of the 4th section convexity wheel disc.4th slope
The 3rd slope can be more than herein.The switching time for the push rod for reaching separation can further be shortened by this way.
It can be set in expansion scheme, there is cam disc the 3rd radius R3 to cause the semi-linkage state K of clutch.
This, the 3rd radius R3 is associated with the anglec of rotation φ S of cam disc, and the anglec of rotation is in the second section S2 or in the 3rd area
In section S3.Thus advantageously cause, often must conversion between the clutch and semi-linkage state K in engagement (such as in congestion
Traveling) transport condition in, can keep small by the torque of needs and thereby by the power consumption of motor.It can avoid by this way
Motor in other words drive motor control electronic unit overheat.
Semi-linkage state is understood to the following state of clutch, and clutch did not both have (complete) to beat in a state
Opening does not have (complete) close yet.Exactly, in semi-linkage state, clutch disk mechanically abuts in the Flywheel disc of motor-side
On so that the force closure between clutch disk and Flywheel disc is also not enough to prevent Flywheel disc " trackslipping " relative to clutch disk.
In other words：Whole torques clutch disk is not delivered to from Flywheel disc like that just like in the case of clutch closed mode.
For example, semi-linkage state may be defined as, 1.5Nm to 6Nm, such as 3Nm torque are passed into clutch disk from Flywheel disc.
Can be set in expansion scheme, cam disc has static section (SR), wherein, the starting point of static section (SR) is the
Start during three anglecs of rotation (φ 3).3rd anglec of rotation (φ 3) is more than or equal to second anglec of rotation (φ 2).Cam disc is quiet
Only there is static radius (RR) to cause the open mode of clutch in section (SR).Here, radius (R) is on the anglec of rotation
The first derivative of (φ) substantial constant and equal to zero in static section (SR).Thus advantageously cause, for push rod
Released state and thereby for clutch released state need not provide or need only provide for minimum motor torque.Even in
In the case of the vibration worked transverse to the direction of linear motion of push rod, push rod may remain in static section.Thus, example
Such as travelled or in red light in congestion, i.e., when clutch must resist the spring force to work of clutch in longer time
Stay open when separating in other words, required power consumption declines.Here, static section (SR) is seen along the first direction of rotation
It is arranged in after the minus section of slope.Undesirable engagement particularly effectively can be occurred by anti-throw-out lever by the measure.
Alternatively, radius (R) is less than zero on the first derivative of the anglec of rotation (φ) in static section (SR).Single order is led
Number may also be constant herein.The stop part for push rod can be set in the destination county of static section.Thus, even if described device
Clutch is particularly securely avoided to be not intended to connect in the case where only being loaded by motor with small torque in other words in motor power-off
Close.Because in order to engage clutch push rod in other words, motor must be such that cam disc is moved on the contrary with the first direction of rotation first
And the additional spring force for acting on push rod is overcome herein.
Alternatively, radius (R) has from less than zero on the first derivative of the anglec of rotation (φ) in static section (SR)
Value to more than zero value sign conversion.In other words, small hole (Kuhle) is configured with cam disc, wherein push rod
Can metastable state it couple.By the expansion scheme, as long as Coupling point is in static section (SR), then push rod is particularly securely prevented
The only unintentional engagement of clutch, even if being also such when motor does not provide torque or only provides small torque.
It is that the anglec of rotation is from the closed mode in the case of the first anglec of rotation φ 1 for derivative precondition in this
Towards the open mode increase in the case of the second anglec of rotation φ 2, in other words, anglec of rotation φ increases along the first direction of rotation.
In other words, it is first in static section when sign of the first derivative from minus value to the value more than zero converts
Radius R reduction is first set and the increase of radius is then set with the anglec of rotation φ further increased along the first direction of rotation.
On the whole can be by setting resting position to prevent motor overheat and the power consumption of automobile electrical network can be reduced.
It can be set in expansion scheme, static section (SR) extends past at least 30 ° of rotation angle range, particularly advantageous
Ground extends past at least 40 ° of rotation angle range.Thus can especially safely and reliably anti-throw-out lever inadvertently engages.
The convex of the device actuator in other words for the clutch for being used to manipulate vehicle is provided with according to the second aspect of the invention
Wheel disc.Cam disc can rotate around an axis herein.The radius R of cam disc is defined as the spacing from axis to Coupling point, and push rod can
Coupled in the Coupling point with cam disc.There is cam disc the first radius R1 to be used to cause clutch in the first anglec of rotation φ 1
The closed mode C of device.There is cam disc the second radius R2 to be used for the open mode for causing clutch in the second anglec of rotation φ 2
O.Cam disc has at least one first section S1 and the second section S2.Here, cam disc is configured to, in order to which clutch is from closing
State C is transformed into open mode O cam discs and rotated along the first direction of rotation can rotate along the first direction of rotation in other words, its
In, Coupling point is passed by first the first section S1 and then passes by the second section S2；And in order to which clutch is transformed into from open mode O
Closed mode C, cam disc will rotate along the second direction of rotation opposite with the first direction of rotation in other words can be along the second rotation side
To rotation, wherein, Coupling point is passed by first the second section S2 and then passes by the first section S1.In the first section S1 convexity wheel discs
Radius R has the first slope m1 of substantial constant on anglec of rotation φ.The second section S2 convexity wheel discs radius R on
Anglec of rotation φ has the second slope m2 of substantial constant.First slope m1 is more than the second slope m2 herein.Here, can be special
Advantageously first slope is at least the big twice of the second slope m2, and completely particularly advantageously, first slope m1 can be second oblique
Rate m2 at least three times are big.
By using following cam disc：The slope of the cam disc not on gamut be all it is linear, can be favourable
On the one hand ground reduces the motor torque needed and thereby reduces power consumption, at the same can reduce engagement state and semi-linkage state it
Between state between the anglec of rotation and adjustment time.Thus interrupted in other words from vehicle motor it is possible that rapidly reducing
To the torque transmission of clutch disk.
Thus can be while the power consumption of the motor used be relatively small in all sections for separating clutch
Enough torques are provided while adjustment time can be reduced.In addition can advantageously particularly simply, in manufacture reliably, have
Small franchise and cost-effectively manufacture cam disc, its have with lower curtate, slope is linear in the section.
Concept " slope of substantial constant " is understood to, slope (such as in the first section in other words in the second section
In) change be no more than 3%.
Brief description of the drawings
Those skilled in the art can by later in reference to description of the accompanying drawing to illustrative embodiments obtain the present invention its
His feature and advantage, but the illustrative embodiments are not construed as limitation of the present invention.
Accompanying drawing is shown：
Fig. 1 a：The schematic diagram of the electrically-energized clutch system of energy；
Fig. 1 b：The diagram of the device for the clutch that the electrically-energized actuator of energy is used in controlled clutch system in other words；
Fig. 1 c：From the three-dimensional cutaway view of the actuator in Fig. 1 b in terms of the line of vision different from Fig. 1 b；
Fig. 2 a-2c：Schematic diagram in different conditions of cam disc and push rod and affiliated clutch state (engagement state,
Semi-linkage state and released state)；
Fig. 3 a：The schematic diagram of the cam disc concured with push rod；
Fig. 3 b：Curve map, the relation between the radius of Fig. 3 a cam disc and the anglec of rotation is shown；
Fig. 3 c：Curve map, be shown as separate clutch required for motor torque and the cam disc in Fig. 3 a the anglec of rotation
Relation between degree；
Fig. 4 a：Curve map, the half of Fig. 3 a cam disc is shown compared with the cam disc of the radius increased with Strict linear
Relation between footpath and the anglec of rotation；
Fig. 4 b：Curve map, it is shown as separating clutch compared with the cam disc of Fig. 4 a radius with Strict linear increase
Relation between torque required for device and the anglec of rotation of the cam disc in Fig. 3 a；
Fig. 5：Curve map, the relation between the radius of another embodiment of cam disc and the anglec of rotation is shown.
Fig. 6 a-6c：Curve map, the relation tool between the radius of the other embodiment of cam disc and the anglec of rotation is shown
Have and be configured to different static sections；
Embodiment
Fig. 1 shows the electrically-energized clutch system 1 of the energy of automobile-use.Pedal 3 can resist the ground pressure of spring 5 by driver
It is low.Asked for herein by sensor 7 and be delivered to controller 9 in the current location of pedal 3.Based on the signal of sensor 7,
Controller 9 controls the motor 11 of the device 13 in other words of actuator 13 for controlled clutch.Motor 11 can be for example electricity
The Brushless DC motor of sub- rectification or traditional motor.Motor 11 is steered, with by the suitable (example of force transfering device 15
Such as in the form of transmission mechanism 15) piston 17 is moved in active cylinder 19, the active cylinder forms the one of clutch adjuster 14
Part.Herein, hydraulic oil can be extruded in slave cylinder 23 by pipeline 21.Piston 25 and clutch 27 in slave cylinder 23
In mechanical connection and clutch can separate in the case where being manipulated by slave cylinder 23.It is arranged on answering on clutch 27
Position spring 29 is used herein to provide the corresponding buffer brake acted on slave cylinder 23 so that is weakening the behaviour to pedal 3
Actuator 13 vertical and that correspondingly (reverse) is manipulated for manipulating vehicular clutch 27 in other words will be from the case of device 13
Clutch 27 engages again.Air vent 18 is provided with the Background Region of active cylinder 19 of clutch adjuster 14 is formed.When piston 17
When being moved rearwards far enough more than air vent 18, hydraulic oil can be supplemented by container 16 and flowed in active cylinder 19.27, clutch
Such as by can be formed by clutch disk that described device is driven and with the drivetrain Flywheel disc that vehicle motor couples in other words.
Clutch disk is mechanically separated from Flywheel disc when separating clutch 27 so that no longer occur from Flywheel disc to clutch disk
Torque transmission.
In accompanying drawing below, identical reference is provided with the element identical in Fig. 1 or function identical element.
Fig. 1 b show the diagram of actuator 13 for controlled clutch 27 device 13 in other words.Motor 11 passes through herein
The driving cam disk 50 of force transfering device 15.Force transfering device 15 by worm gear 15a and engages in the illustrated embodiment
Gear 15b is formed.The ground of axis 51 is eccentric on the gear 15b rotated around axis 51 and is disposed with taking in small pin-shaped formula
Part 15c.
Cam disc 50 is disposed with gear 15b, the cam disc has breach 56, and carrying piece 15c is received in the breach 56
In.By this way, cam disc 50 couples with gear 15b.When motor 11 rotates gear 15b by force transfering device 15
When, cam disc 50 can rotate around axis 51 as gear 15b or rotate around axis 51 or be rotated around axis 51.
In principle it is also possible that motor 11 driving cam disk 50 and makes in the case where no force transfering device 15 is connected on centre
It rotates around axis 51.For the actuator 13 that manipulates vehicular clutch 27, device 13 has push rod 40 in addition in other words.Push away
Bar 40 has first end 46, and the first end couples with cam disc 50 so that is rotated by cam disc 50 around axis 51 to draw
Play the linear motion of push rod 40.The linear motion of push rod 40 can then pass to the work of active cylinder 19 as described for Fig. 1 a
Plug 17.In the embodiment as shown, the first end 46 of push rod 40 has a roller 42, and the roller can be radially outward directed
Rolled on end face 54 (Fig. 1 c), to reduce friction.Push rod 40 couples in Coupling point 53 with cam disc 50.Coupling point 53 is for example such as
In the illustrated embodiment like that by the first end 46 of the push rod 40 in other words of roller 42 on the end face 54 of cam disc 50
Recline and a little 52 formed.
In principle, push rod 40 also can be by chute guider (chute in cam disc 50) or flange guide means
(Kragenf ü hrung) is coupled on cam disc 50.Coupling point 53 this then by cam disc 50 or on chute and push rod
The coefficient point of 40 first end 46 passes through the common of the flange on cam disc 50 and the first end 46 of push rod 40
The point of effect is formed.
Cam disc 50 has the first radius R1 in the case of the first anglec of rotation φ 1.Push rod 40 is with cam disc first
Collective effect in the case of the anglec of rotation causes the closed mode C of clutch 27 herein.Cam disc 50 is also in second anglec of rotation
There is the second radius R2 in the case of degree φ 2.Push rod 40 and common work of the cam disc 50 in the case of the second anglec of rotation φ 2
With the open mode O for causing clutch 27 herein.The radius R of cam disc 50 is defined as pasting in other words from axis 51 to Coupling point 53
By the spacing of point 52.Because cam disc 50 does not have circular outline chute in other words, in the opening position a little that reclines
Radius R changes according to anglec of rotation φ.First radius R1 and the second radius R2 is thus mutually different and thereby causes push rod 40
Different linear positions.
For example, the second radius R2 is more than the first radius R1.Thus, push rod 40 in the first anglec of rotation φ 1 (such as Fig. 1 b institutes
Show) in the case of engage, i.e., shifted in other words towards axis 51 towards cam disc 50 on its linear movement.If cam disc 50 is being schemed
Along the first direction of rotation 91 (along clockwise in figure) motion in 1b, then radius R also increase with anglec of rotation φ increase and
Push rod 40 to the right, i.e., shifts with leaving from the axis 51 of cam disc 50 in Figure 1b.Push rod 40 separates.Similar to the fortune of push rod 40
Dynamic, clutch 27 is in engagement state, i.e. closed mode C in the case of the first anglec of rotation φ 1, and in second anglec of rotation
Open mode O is in the case of φ 2, the open mode is equivalent to released state O.In order to be beaten in other words from released state O again
Open state O returns to engagement state C closed mode C in other words, it is desirable that, the direction of rotation 91 of cam disc 50 and first is on the contrary
Along the second direction of rotation 92 (herein：Counterclockwise) toward revolution.Here, push rod 40 is passed by separation, cam disc 50 is same
Profile, but in opposite direction.
Fig. 1 c show the three-dimensional cutaway view from the actuator in Fig. 1 b in terms of the different lines of vision from Fig. 1 b.In this view
It can be seen that the second end 48 of push rod 40, the second end couples with the piston 17 of active cylinder 19.Push rod is guided by bearing 44,
So that push rod is only capable of implementing linearly to move along a straight line in other words.It can be seen that roller 42, the roller 42 on the first end 46 of push rod
A little 52 coupled reclining with the end face 54 of cam disc.
Coefficient schematic diagram in different conditions of cam disc 50 and push rod 40 and affiliated is shown respectively in Fig. 2 a-2c
The state of clutch 27 (engagement state, semi-linkage state and released state).
Fig. 2 a show the cam disc in the case of the first anglec of rotation φ 1, and first anglec of rotation is alternatively initial rotation
Angle.Initial rotation angle can for example be attached to 0 ° of rotation angle value to first anglec of rotation φ 1 in other words.In first rotation
The first radius R1 is provided in the case of angle φ 1, first radius is for example equivalent to the least radius of cam disc 50.The first half
The spacing of the first end 46 of push rod 40 to axis 51 is especially small in the case of footpath.Engagement is in the clutch 27 shown in right side
State.Therefore, Flywheel disc and clutch disk are mechanically interconnected so that can realize that the maximum from Flywheel disc to clutch disk turns
Square transmission.Back-moving spring 29 is in unloading position so that is that push rod 40 is maintained in bonding station from motor need not to turn
Square is applied to cam disc or only needs to be applied to cam disc 50 from motor 11 by very small torque.
Fig. 2 b show the cam disc in the case of semi-linkage anglec of rotation φ S, and the semi-linkage anglec of rotation is more than first
Anglec of rotation φ 1.Semi-linkage anglec of rotation φ S for example can be relative to the first anglec of rotation φ 1 in other words relative to initial rotation
Angle φ be in 140 ° to 220 ° between and along the first direction of rotation 91 (herein：It is rotated clockwise)
After reach.In the case of semi-linkage anglec of rotation φ S, cam disc 50 has the 3rd radius R3, and the 3rd radius is greater than
First radius R1 and less than the second radius R2.Clutch 27 is in semi-linkage state K.Clutch disk is not complete in a state
Released from the Flywheel disc of clutch 27.The small torque occurred, which is transmitted, to be in the range of such as 1Nm to 10Nm, is preferably in
1.5Nm is between 6Nm, for example, 3Nm.In other words：Flywheel disc trackslips relative to clutch disk in semi-linkage state K.In order to
Reach semi-linkage state K, it is necessary to overcome the spring force of back-moving spring 29.It will thus be determined by clutch 27 by back-moving spring 29
Power pass to push rod 40.Actuator 13 for controlled clutch 27 in other words device 13 motor 11 thus necessary for from
Engagement state C, which sets out, to be realized the state and uses torque bigger compared with the engagement state C of clutch 27.In order to keep half
Linkage status K, it is also desirable to the bigger torque compared with engagement state C, because otherwise the push rod 40 loaded by spring force just makes
Cam disc 50 back rotates against the first direction of rotation 91.
Fig. 2 c show the cam disc in the case of final anglec of rotation φ E.The final anglec of rotation is equivalent to cam disc 50
Maximum possible the anglec of rotation.It is maximum 340 ° in other words that final anglec of rotation φ E, which for example can be maximum 355 °, is, for example,
330°.Final anglec of rotation φ E can be more than the second anglec of rotation φ 2, and clutch 27 has been in the case of second anglec of rotation
In released state O in other words open mode O.Clutch 27 can also be in opening in the case of final anglec of rotation φ E
In state O.Push rod 40 is in the case of the second anglec of rotation φ 2 and in the case of final anglec of rotation φ E with joining half
Dynamic state K compares farther every obtaining with axis 51 in the case of the semi-linkage anglec of rotation and initial rotation angle φ A in other words.For
Need motor 11 torque that applies as small as possible under the open mode O of clutch 27, cam disc 50, which can be directed to, is more than second
Anglec of rotation φ 2 anglec of rotation φ has static section SR.Static section SR is for example more than the of the second anglec of rotation φ 2
Start during three anglec of rotation φ 3.Static radius RR can be set in static section, the static radius is permanent on the second radius R2
It is fixed or even with respect to the second radius R2 reduce.Maximum radius thus may be provided at the second anglec of rotation φ 2 and the 3rd rotation
Between angle φ 3.
Fig. 3 a show cam disc 50 and 40 coefficient schematic diagram of push rod.Solid line is shown in which the radius of cam disc.
In possible embodiment, the line is approximately equivalent to the end face 54 of cam disc (assuming that a little 52 Coupling points in other words that recline
53 is constant).Alternatively, the line can show in cam disc 50 or on chute or flange profile.
In an embodiment of cam disc 50, push rod 40 rolls on the end face 54 of cam disc 50, preferably
In, push rod 40 a little 52 is abutted on the end face 54 of cam disc 50 with reclining.
Show such as the curve map of the cam disc in Fig. 3 a, to draw radius on the y axis, rotation is drawn in X-axis in fig 3b
Angle.In figure 3 c, drawn with profile example：In the case of the anglec of rotation of the determination according to Fig. 3 b of cam disc 50
The great torque of motor 11 must be applied.
Push rod 40 is seen (herein along the first direction of rotation 91 when rotated on cam disc 50：Rotate clockwise) slave phase
Set out the first section S1 for passing by first on cam disc 50 when in 0 ° of the first anglec of rotation φ 1, from the first section S1 starting point
71 until the first section S1 terminal 72.When cam disc 50 further rotates, push rod 40 passes through the secondth area on cam disc 50
Section S2, second section have the second section S2 starting point 73 and terminal 74.Here, cam disc 50 has in the first section S1
The first slope m1 of substantial constant, the first slope is equivalent to first derivative of the radius on anglec of rotation φ.In other words：
Radius linearly increases substantially as anglec of rotation φ in first section S1.
It can be seen that, cam disc 50 has the second slope m2 of substantial constant in the second section S2 in fig 3b.Second
Slope m2 is more than zero in the illustrated embodiment.First slope m1 is more than the second slope m2.It is preferred that first slope m1 is at least
Two slope m2's is big twice.Particularly preferably, first slope m1 be at least the second slope m2 three times it is big.Thus, push rod 40 is convex
Wheel disc 50 reverses the straight line distance that edge is passed by relatively large from the direction that axis 51 leaves in the first relatively small section S1, by
This, the switching time separated for clutch 27 is shortened.Such as when existing bigger spring-force driven dual is in the push rod, push rod
40 reach in the second section S2, and in second section, the torque T of motor 11 can then pass through less second slope m2 and first
Slope m1 is smaller compared to holding along the situation that whole cam disc 50 is applicable.
Semi-linkage state K realizes that the semi-linkage anglec of rotation corresponds to the 3rd in the case of semi-linkage anglec of rotation φ S
Radius R3 and thereby the push rod stroke for corresponding to restriction.The semi-linkage anglec of rotation is for example attached to the second section S2.Thus can be
The torque of motor 11 is kept small when clutch must often be maintained at semi-linkage state K congestion traveling.
To be seen along the first direction of rotation 91, clutch is in released state O in the case of the second anglec of rotation φ 2,
No longer exist torque and be delivered to clutch disk from Flywheel disc.Cam disc 50 can still further rotate, until push rod 40 is in the 3rd rotation
The static section SR on cam disc 50 is reached in the case of gyration φ 3.In the static section SR, cam disc 50 has static
Radius RR.Static radius is, for example, constant, i.e., the slope in static section SR is zero.Thus for keep push rod stroke and no longer
The torque T of motor 11 is needed, thus when clutch 27 opens the opening completely to the full extent of clutch 27 in other words, automobile electricity
Net is not loaded and avoids motor 11 from overheating.
First section S1 starting point for example can be along the first direction of rotation (i.e. along the opening direction edge in other words of clutch 27
The detaching direction of push rod 40) 0 ° to 30 ° of rotation angle range is in, wherein, here, initial rotation angle should attach troops to a unit 0 °
Value.Radius-the anglec of rotation-the function shown in fig 3b is preferably at least from the first section S1 starting point 71 up to the second section S2
The Second Order Continuous of terminal 74 can be micro-, so as to low noise as far as possible and equably shift push rod 40 and minimize abrasion.
Second section S2 starting point 73 can for example be spaced 25 ° of maximum with the first section S1 terminal 72 herein, particularly preferably
Maximum 15 ° and completely particularly preferred 10 ° of maximum.
First section S1 and the second section S2 may be configured to them and each extend over by least 5 °, preferably each extend over by
At least 10 ° are passed through at least 15 ° with completely particularly preferred.
First section S1 also may extend past at least 20 ° of rotation angle range or even past at least 30 °.Pass through
Which, push rod 40 can pass through available motor torque T king-sized sections of linear displacement in a short time.
Second section S2 may extend past at least 100 ° of rotation angle range, preferably extend past at least 120 ° and complete
Particularly preferably extend past at least 140 ° entirely.
Static section SR for example may extend past at least 30 °, preferably at least 40 ° of rotation angle range.
Fig. 4 a show the comparison of traditional cam disc and Fig. 3 b embodiment in the radius-anglec of rotation-curve map.Pass
The radius of the cam disc of the system-anglec of rotation-change procedure (chain-dotted line) linearly increases in whole rotation angle range herein.It is real
Line shows Fig. 3 b radius-anglec of rotation-change procedure.When in same push rod stroke, i.e., the same point of Y- axles is (in the 3rd radius
In the case of R3) when reaching semi-linkage state K, point is compared with the cam disc 50 in Fig. 3 a and 3b described in traditional cam disc
Realized in the case of the bigger anglec of rotation (in the accompanying drawings in φ s ').This causes longer in the case of traditional cam disc
Switching time.
Fig. 4 b show cam disc, the category of the conventional cam disk with Fig. 3 a and 3b with fairly linear slope (chain-dotted line)
In Fig. 4 a torque-anglec of rotation-change procedure.Traditional cam disc connects compared with Fig. 3 a and 3b cam disc from clutch 27
First anglec of rotation for closing push rod engagement in other words is set out the torque T of motor 11 or only is not needed on bigger rotation angle range
Need the torque T of motor 11 of very little.But as long as the spring force that push rod 40 is acted on by the back-moving spring 29 of clutch 27 increases,
Will occur the strong unexpected raising of torque request due to bigger slope compared with the second slope m2.In order to by cam
Disk is fully rotating until the second anglec of rotation φ 2, it is also necessary to bigger peak value-torque compared with Fig. 3 a and 3b cam disc.Tool
There is the actuator 13 for controlled clutch 27 of Fig. 3 a and 3b cam disc 50 device 13 thus can realize and have in other words
The actuator of the cam disc of the radius of continuously linear increase compares smaller motor 11.In addition, in shorter switching time
Semi-linkage state K is inside realized in the case of the less anglec of rotation in other words.On the whole, motor 11 is from initial rotation angle
Until more uniformly loaded on the whole rotation angle range of the final anglec of rotation.Pass through the cam disc 50 in Fig. 3 a and 3b
In the case of the static section SR that sets, the torque T of motor 11 is approximately zero Nm when clutch opens that push rod 40 separates in other words.
But it must also use very big torque all the time when clutch 27 is opened when using the cam disc conventional without static section
(such as a quarter of the torque of maximum demand), to prevent cam disc from back being rotated due to being loaded with the push rod 40 of power.
Fig. 5 shows the radius-anglec of rotation-change procedure of another embodiment of cam disc 50.In this embodiment,
Cam disc 50 has the 3rd section S3, and the 3rd section has the 3rd slope m3 of substantial constant.3rd slope m3 herein may be used
It is greater than zero.3rd slope m3 is less than the second slope m2 herein.Second section S2 sees cloth along the first direction of rotation 91 herein
Put between the first section S1 and the 3rd section S3.Push rod 40 is passed by first when cam disc 50 rotates along the first direction of rotation 91
The terminal 76 of the starting point 75 of 3rd section and then the 3rd section S3 that passes by.3rd section S3 starting point and the second section S2 terminal
74 interval is preferably smaller than 25 °, particularly preferably less than 15 ° and completely particularly preferably less than 10 °.Second section S2 and the 3rd section
The coextensive angular ranges for passing through at least 120 ° of S3, preferably extend past at least 140 ° of angular range.Semi-linkage state K exists
Realized in the case of semi-linkage anglec of rotation φ S, the semi-linkage anglec of rotation φ S are attached to the 3rd section S3.Therefore, with half
Linkage status K compares with the second slope m2 or the section realization with first slope m1, can be to motor 11
Torque request causes clutch 27 to be maintained in semi-linkage state K in the case of further reducing.Thus example can preferably be prevented
The overheat of motor 11 such as when congestion travels.
It is connected with the 4th section S4 of starting point 77 and terminal 78 to the 3rd section, the 4th section and for example extends up to second
Anglec of rotation φ 2.4th section S4 can for example have the slope m4 of substantial constant.4th slope m4 can be more than the 3rd slope
M3, to realize that clutch 27 is kept completely separate state to push rod 40 in other words as quickly as possible.4th slope is such as may be configured to
In the second slope m2.
Schematical radius-the anglec of rotation-curve map is shown in Fig. 6 a-6c, these curves illustrate cam disc quiet
The only possible embodiment in section SR.Change procedure especially in the first section S1 and the second section S2 is only illustrated herein
Show to property.In principle can be up to reaching static section SR and in the presence of the change procedure such as Fig. 3 a or Fig. 5.
Fig. 6 a show the radius-anglec of rotation-change procedure of an embodiment of cam disc 50, wherein, realizing push rod
40 in other words after the maximum separation position of cam disc 50, the feelings that the radius R of cam disc 50 further increases in anglec of rotation φ
The first direction of rotation of condition lower edge 91 somewhat reduces first.Then static section SR is reached in the case of the 3rd anglec of rotation φ 3
Starting point 81, it is zero that slope is constant in static section.
Fig. 6 b show the radius-anglec of rotation-change procedure of another embodiment of cam disc 50, wherein, pushed away in arrival
Bar 40 is in other words after the maximum separation position of cam disc 50, the radius R of cam disc 50 edge when the anglec of rotation further increases
First direction of rotation 91 is continuously reduced.Radius R reducing in static section SR can be carried out with constant slope.In order to avoid pushing away
Bar 40 at stagnant zone SR terminal 82 from cam disc 50 " skidding off " (terminal for example can be rotation angle range terminal),
Settable stop part 58.The unexpected, approximate of radius R can be alternatively or additionally set to hang down on the terminal of rotation angle range
Straight increase so that anti-throw-out lever 40 skids off from cam disc 50.
Fig. 6 c show the radius-anglec of rotation-change procedure of an embodiment of cam disc 50, wherein, reaching push rod
40 in other words after the maximum separation position of cam disc 50, the radius R of cam disc 50 edge when anglec of rotation φ further increases
First direction of rotation 91 somewhat reduces (slope thus less than zero) subsequent increase again first (slope is more than zero).I.e. in static section
Sign of the slope from minus value to the value more than zero occurs in SR to change.Thus there is for example metastable state, quilt
Loading can keep only keeping with the small torque T of motor 11 in other words with the push rod 40 of power in the case of no torque T of motor 11
In the metastable state state.Cam disc 50 unintentionally back rotation thus even if also approximation is excluded in the case of vibrations.
By the cam disc 50 of proposition likely, there is provided for manipulating the clutch of vehicle (such as car, lorry etc.)
Device 13 in other words of actuator 13, it can make clutch 27 from connecing by the motor compactly constructed in short adjustment time
Conjunction state C be transformed into semi-linkage state K and there keep and its even in longer be maintained at semi-linkage state K's
In the case of it is only hot.Additionally can be by setting static section SR to avoid motor 11 in the open mode O of clutch 27
Overheat.
Claims (10)
1. a kind of device for being used to manipulate vehicular clutch, including
- the cam disc (50) that can be rotated around an axis (51),
- push rod (40),
Wherein, the push rod (40) has first end (46), on the first end push rod a Coupling point (53) place with
The cam disc (40) couples in the following manner so that is caused by rotation of the cam disc (50) around the axis (51)
The linear motion of the push rod (40), the linear motion is passed into the clutch (27),
Wherein, the radius (R) of the cam disc (50) is defined as the spacing from the axis (51) to the Coupling point (53),
Wherein, the cam disc (50) has the first radius (R1) in the case of first anglec of rotation (φ 1), described to cause
The closed mode (C) of clutch (27),
Wherein, the cam disc (50) has the second radius (R2) in the case of second anglec of rotation (φ 2), described to cause
The open mode (O) of clutch (27),
Wherein, the cam disc (50) has between first anglec of rotation (φ 1) and second anglec of rotation (φ 2)
At least one first section (S1) and the second section (S2),
Wherein, described device (13) is configured to：
- in order that the clutch (27) is transformed into the open mode (O), the cam disc from the closed mode (C)
(50) to be rotated along the first direction of rotation (91), wherein, the Coupling point (53) passes by first section (S1) then first
Pass by second section (S2), and
- in order that the clutch (27) is transformed into the closed mode (C), the cam disc from the open mode (O)
(50) to be rotated along second direction of rotation (92) opposite with first direction of rotation (91), wherein, the Coupling point (53)
Pass by first second section (S2) and then first section (S1) of passing by,
Wherein, in first section (S1), the radius (R) of the cam disc (50) has substantially on the anglec of rotation (φ)
Upper constant first slope (m1),
Wherein, in second section (S2), the radius (R) of the cam disc (50) has substantially on the anglec of rotation (φ)
Upper constant the second slope (m2),
Wherein, the first slope (ml) is more than second slope (m2), is especially at least second slope (m2)
It is big twice.
2. device according to claim 1,
Wherein, the cam disc (50) has the end face (54) being radially outward directed,
Wherein, the first end (46) of the push rod (40) is abutted on the end face (54) in the point (52) that reclines,
Wherein, the point (52) that reclines is the Coupling point (53).
3. according to the device of one of preceding claims,
Wherein, the starting point (73) of second section (S2) and 25 ° of terminal (72) the interval maximum of first section (S1)
The anglec of rotation, the especially maximum 15 ° anglec of rotation in interval.
4. according to the device of one of preceding claims,
Wherein, the starting point (71) of first section (S1) is in first anglec of rotation on first direction of rotation (91)
(φ 1) and first anglec of rotation (φ 1) are added in the rotation angle range between 30 °, and/or
Wherein, second slope (m2) is more than zero.
5. according to the device of one of preceding claims,
Wherein, first section (S1) and second section (S2) each extend over the rotation angle range by least 5 °,
The rotation angle range by least 10 ° is especially each extended over,
And/or
Wherein, first section (S1) extends past at least 15 ° of rotation angle range, especially extends past at least 30 °
Rotation angle range, and/or
Wherein, second section (S2) extends past at least 120 ° of rotation angle range, especially extends past at least 140 °
Rotation angle range.
6. according to the device of one of preceding claims,
Wherein, the cam disc (50) has between first anglec of rotation (φ 1) and second anglec of rotation (φ 2)
3rd section (S3),
Wherein, in the 3rd section (S3), the radius (R) of the cam disc (50) has substantially on the anglec of rotation (φ)
Upper the 3rd constant slope (m3),
Wherein, second section (S2) is arranged in first section (S1) and the 3rd section on the anglec of rotation (φ)
(S3) between,
Wherein, second slope (m2) is more than the 3rd slope (m3),
Wherein, the 3rd section (S3) especially extends past at least 5 ° of rotation angle range,
And/or
Wherein, in particular, the starting point (75) of the 3rd section (S3) and the terminal (74) of second section (S2) are spaced most
Big 15 ° of the anglec of rotation, the especially maximum 10 ° anglec of rotation in interval.
7. according to the device of one of preceding claims,
Wherein, the cam disc (50) has the 3rd radius (R3), to cause the semi-linkage state (K) of the clutch (27),
Wherein, the 3rd radius (R3) is attached to the following anglec of rotation (φ S) of the cam disc (50), the anglec of rotation
In second section (S2) or in the 3rd section (S3).
8. according to the device of one of preceding claims,
Wherein, the cam disc (50) has static section (SR),
Wherein, the starting point (81) of the static section (SR) starts in the case of the 3rd anglec of rotation (φ 3),
Wherein, the 3rd anglec of rotation (φ 3) is more than or equal to second anglec of rotation (φ 2),
Wherein, the cam disc (50) has static radius (RR) in the static section (SR), to cause the clutch
(27) open mode,
- wherein, radius (R) on the anglec of rotation (φ) first derivative in the static section (SR) substantial constant and
Equal to zero,
Or
- wherein, radius (R) is less than zero on the first derivative of the anglec of rotation (φ) in the static section (SR),
Or
- wherein, radius (R) has from minus on the first derivative of the anglec of rotation (φ) in the static section (SR)
It is worth the sign change of the value more than zero.
9. according to the device of one of preceding claims,
Wherein, the static section (SR) extends past at least 30 ° of rotation angle ranges, especially extends past at least 40 ° of rotation
Gyration scope.
10. a kind of cam disc for being used to manipulate the device of vehicular clutch, wherein, the cam disc can exist around an axis (51)
Rotated between initial rotation angle (φ A) and the final anglec of rotation (φ E),
Wherein, the radius (R) of the cam disc (50) is defined as the spacing from the axis (51) to Coupling point (53), described
A push rod (40) can couple with the cam disc (50) at Coupling point,
Wherein, the cam disc (50) has the first radius (R1) in the case of first anglec of rotation (φ 1), described to cause
The closed mode (C) of clutch (27),
Wherein, the cam disc (50) has the second radius (R2) in the case of second anglec of rotation (φ 2), described to cause
The open mode (O) of clutch (27),
Wherein, the cam disc (50) has at least one first section (S1) and the second section (S2),
Wherein, the cam disc (50) is configured to
- in order that the clutch (27) is transformed into the open mode (O), the cam disc from the closed mode (C)
(50) to be rotated along the first direction of rotation (91), wherein, the Coupling point (53) passes by first section (S1) then first
Pass by second section (S2), also,
- in order that the clutch (27) is transformed into the closed mode (C), the cam disc from the open mode (O)
(50) to be rotated along second direction of rotation (92) opposite with first direction of rotation (91), wherein, the Coupling point (53)
Pass by first second section (S2) and then first section (S1) of passing by,
Wherein, in first section (S1), the radius (R) of the cam disc (50) has substantially on the anglec of rotation (φ)
Upper constant first slope (m1),
Wherein, in second section (S2), the radius (R) of the cam disc (50) has substantially on the anglec of rotation (φ)
Upper constant the second slope (m2),
Wherein, the first slope (m1) is more than second slope (m2), and the two of particularly at least described second slope (m2)
It is big again.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102016207253.6A DE102016207253A1 (en) | 2016-04-28 | 2016-04-28 | Device for actuating a clutch of a vehicle |
| DE102016207253.6 | 2016-04-28 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN107435693A true CN107435693A (en) | 2017-12-05 |
Family
ID=60081885
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710288611.4A Pending CN107435693A (en) | 2016-04-28 | 2017-04-27 | For the device for the clutch for manipulating vehicle |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN107435693A (en) |
| DE (1) | DE102016207253A1 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102019122088A1 (en) * | 2019-08-16 | 2021-02-18 | Wabco Europe Bvba | Electromechanical brake actuator |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102007034568A1 (en) * | 2007-07-25 | 2009-01-29 | Bayerische Motoren Werke Aktiengesellschaft | Vehicle with a transmission and a clutch assembly |
| DE102013225009A1 (en) * | 2013-12-05 | 2015-06-11 | Robert Bosch Gmbh | In the maximum position latching actuator for actuating a hydraulic clutch actuator and electrically actuated clutch system |
-
2016
- 2016-04-28 DE DE102016207253.6A patent/DE102016207253A1/en not_active Withdrawn
-
2017
- 2017-04-27 CN CN201710288611.4A patent/CN107435693A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| DE102016207253A1 (en) | 2017-11-02 |
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| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| WD01 | Invention patent application deemed withdrawn after publication | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20171205 |