CN108869564A - For manipulating the actuator of vehicular clutch - Google Patents
For manipulating the actuator of vehicular clutch Download PDFInfo
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- CN108869564A CN108869564A CN201710338946.2A CN201710338946A CN108869564A CN 108869564 A CN108869564 A CN 108869564A CN 201710338946 A CN201710338946 A CN 201710338946A CN 108869564 A CN108869564 A CN 108869564A
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- Prior art keywords
- cam disc
- push rod
- rotation angle
- clutch
- rotation
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- 230000004913 activation Effects 0.000 description 1
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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
- F16D13/00—Friction clutches
- F16D13/22—Friction clutches with axially-movable clutching members
-
- 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
- F16D13/00—Friction clutches
- F16D13/58—Details
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
The present invention relates to a kind of for manipulating the actuator of vehicular clutch.The actuator includes the push rod with longitudinal axis that can be supported around the cam disc that rotation axis rotates and in axial supporting arrangement.Here, axial supporting arrangement includes at least one supporting member.Push rod has first end, and push rod couples at Coupling point with cam disc on the first end, so that causing push rod along the linear motion of its longitudinal axis around the rotation of rotation axis by cam disc, which is passed to clutch.Actuator is configured to：In order to which clutch is transformed into opening state from closed state, cam disc will rotate along the first direction of rotation.Axial supporting arrangement is arranged to relative to rotation axis, longitudinal axis and is parallel to paralleling to the axis for longitudinal axis and is separated spacing, wherein is paralleled to the axis and jante et perpendiculaire.
Description
Technical field
The present invention relates to a kind of for manipulating the actuator of vehicular clutch.
Background technique
It is known from the state of the art the device or actuator for manipulating vehicular clutch.Always try to now using below from
Clutch, wherein clutch process is caused by electromechanical actuator.It is also known that the clutch of this electromechanical activation in automatic transmission
Device.This clutch is used to manipulate the device alternatively referred to as so-called " electric control clutch " of vehicular clutch or is referred to as in other words
“eClutch”。
In this electrically controlled clutch system, often by motor or this need to be coupled in the actuator of electrically controlled clutch system
The rotary motion of transmission mechanism on motor changes linear movement, to manipulate hydraulic cylinder.The hydraulic cylinder can then manipulate another
The clutch disk coupled with another hydraulic cylinder can be separated (opening state) by another hydraulic cylinder, to interrupt by hydraulic cylinder
Torque transfer between clutch disk and Flywheel disc.Flywheel disc is connect with the driving system of vehicle herein.The actuator is in other words
The reverse rotation motion of the motor of device then leads to reversed linear movement, which manipulates the hydraulic cylinder simultaneously
To manipulate another hydraulic cylinder, and clutch disk is caused to engage relative to Flywheel disc.(closed state) is engaged in clutch
In the case where carry out torque transfer between Flywheel disc and clutch disk.
Linear movement is converted rotary motion into order to realize, cam disc and the push rod coupled with the cam disc can be used.
Here, cam disc is fixedly connected with transmission mechanism, and transmission mechanism itself is connect with motor.Motor can be passed through by this way
Rotation makes cam disc spins by transmission mechanism.Radius by changing cam disc according to rotation angle (such as passes through cam
Plate wheel is wide) linear movement of push rod can be obtained in a known way.Push rod can be guided at this in axial supporting arrangement, so that should
Push rod is only capable of implementing linear movement.
Summary of the invention
The present invention is not only obtained when the power of cam disc passes to push rod along push rod longitudinal axis from following cognition
Axial force.But carry out transmission force also by the collective effect of cam disc and push rod, which has point perpendicular to axial force component
Amount, i.e., so-called radial force.Radial force must be born by axial bearing.Radial force causes friction in supporting member and pushes away
Friction on bar.It causes to wear by the friction, which can lead to the use of actuator electrically controlled clutch system in other words
Service life shortens or makes its functional deterioration.It is also possible to issue bigger noise due to the friction.
Thus there are following demands：There is provided the actuator for manipulating the clutch of vehicle, wherein act on axial bearing
The noise that the radial force of device is dropped as small as possible and/or issued drops as small as possible.Exist simultaneously following demand：In axial branch
Push rod is lubricated in bearing member, so that the required maintenance to push rod is as few as possible.In addition, acting the motor driven and being
Torque needed for controlled clutch should drop as small as possible, also, the switching time between the engagement and separation of clutch should drop
It obtains as short as possible.
It proposes according to the first aspect of the invention a kind of for manipulating the actuator of vehicular clutch.The actuator includes energy
Cam disc around rotation axis rotation and the push rod being supported in axial supporting arrangement, the push rod is with longitudinal axis.Axial branch
Bearing apparatus includes at least one supporting member.Here, push rod have first end, the first end upper push-rod Coupling point with
Cam disc couples in the following manner, so that causing the straight line of push rod line along its longitudinal axis around the rotation of rotation axis by cam disc
Movement, will move along a straight line and pass to clutch.Here, actuator is configured to, in order to which clutch to be transformed into from closed state
Opening state cam disc will be rotated along the first direction of rotation or can be rotated along the first direction of rotation.Here, axial supporting arrangement phase
Rotation axis is disposed so as the longitudinal axis and is parallel to paralleling to the axis for the longitudinal axis to separate spacing, wherein institute
It states and parallels to the axis and the jante et perpendiculaire.
In other words, described parallel to the axis with the longitudinal axis is mutually different axis.
It separates spacing by longitudinal axis and can advantageously be obtained on the entire rotation angle range of cam disc with paralleling to the axis
Especially small contribution to the maximum radial force for acting on axial supporting arrangement.Thus be advantageously used be configured to it is especially small simultaneously
And the axial supporting arrangement of cost advantages.Abrasion also advantageously reduces.Can also advantageously it cause to the special of axial supporting arrangement
Efficient lubrication, so that maintenance needed for actuator is especially few.It alternatively or additionally can be by being greater than zero or minus
Make the noise issued especially small away from D.
Settable in expansion scheme, cam disc has the end face being radially outward directed, wherein the first end of push rod exists
It reclines and a little sticks on end face.Here, reclining is a little Coupling point.Thus especially small and noise can advantageously be rubbed especially smallly
It runs described device and the risk blocked is minimized.Push rod can in order to further decrease friction and for example in its first end
On be configured with sliding roller idler wheel in other words, idler wheel rolls the sliding roller on the end face of cam disc in other words.
In principle, the coupling of push rod and cam disc can also for example pass through chute guide device or flange guide device
(Kragenf ü hrung) (flange on sliding slot or cam disc in cam disc) carries out.
Settable in expansion scheme, the radius (R) of cam disc is limited to the spacing of rotation axis and Coupling point.Here,
Cam disc can have the first radius (R1) in the case where the first rotation angle (φ 1), to cause the closed state of clutch
(C), also, cam disc can have the second radius (R2) in the case where the second rotation angle (φ 2), to cause beating for clutch
Open state (O).Cam disc can first rotation angle (φ 1) and second rotation angle (φ 2) between at least one first
Section (S1) and the second section (S2), wherein the radius (R) of cam disc is about rotation angle (φ) tool in the first section (S1)
There is substantially constant first slope (m1).The radius (R) of cam disc can be about rotation angle (φ) in the second section (S2)
With substantially constant second slope (m2).First slope (m1) can be greater than the second slope (m2), especially the second slope
(m2) at least twice is big.
By using following cam disc：The slope of the cam disc is linear not in entire scope, it may be advantageous to one
Aspect reduces required motor torque and thereby reduces power consumption, and at the same time can reduce between engagement state and discrete state
Or rotation angle and adjustment time between engagement state and semi-linkage state.Thus it is possible that quickly reduce or in
The disconnected torque transfer from driving system and Flywheel disc to clutch disk.In such an implementation, by longitudinal axis and paralleling to the axis
Between spacing can especially reduce maximum radial force by force.
For motor torque needed for making cam disc spins and slope (slope is bigger, then the torque needed is bigger) and with come
It is related from the power (power is bigger, then the torque needed is bigger) of push rod or clutch.
As long as clutch is also in engagement state or close to engagement state, i.e., for example in the small push rod in other words of the radius of cam disc
Stroke hour, the power for acting on cam disc from push rod are small.Thus in the range, such as in the first section, slope is selected
Must be larger, because linear displacement can be carried out with speed as high as possible for push rod using motor torque by this way.Change speech
It, the torque for being supplied to motor originally herein can make push rod pass by linear section as big as possible with small rotation angle.This
Reduce the rotation angle range for for example realizing semi-linkage state, to reduce the switching time for reaching semi-linkage state.
As long as clutch can resist spring force and be opened with feeling, the power for acting on cam disc via push rod is significantly higher,
To which the opposing torque for acting on cam disc from push rod is also significant higher.In order in the common range when driving for example in congestion
It is middle to reduce the motor power consumption needed, slope can be reduced herein.Thus the thick stick between Coupling point and axis can for example be reduced
Thus lever arm can be kept constant in other words from the opposing torque decline that push rod acts on cam disc.In other words：The torque foot of motor
To compensate the opposite force for acting on push rod changed with other transmission ratios.Thus even if with available motor power can also overcome by
The opposing torque that push rod applies, even if increase thus for rotation angle distance required for the linear distance section of restriction of push rod
It is also such.
With second slope smaller than first slope the second section in thus can advantageously avoid motor or for grasping
Control the overheat of the power electronic component of the motor.It can alternatively construct smaller than when the second slope extends as first slope
Motor.Thus enough turn can be provided in whole sections of adjustment process while using the motor with little power consumption
Square is and at the same time can reduce adjustment time.May be used also by constructing the first section with substantially constant slope and the second section
Cause especially uniform and low noise adjustment process, because preventing the non-uniform speed of push rod and thereby anti-throw-out lever is from convex
Wheel disc lifts and (generates noise) or is stuck in cam disc.Furthermore prevent the hydraulic pressure being applied on push rod from impacting.Can finally have
Sharply extremely simple, manufacture safety with small franchise and is cost-effectively made and has with the cam disc of lower curtate, described
Slope is linear in section.
Concept " substantially constant slope " 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%.
Clutch is alternatively referred to as the separation of clutch from off state to the conversion of opening state.Push rod separates herein.Instead
Come over, conversion of the clutch from opening state to closed state 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 state may be defined as following state herein, and clutch does not have in this state
By power load and thereby maximum closing.Opening state is defined as following state, in this state between Flywheel disc and clutch disk
Torque transfer does not occur.It is possible that clutch is more than the state just opened and further separates.
Slope m is defined herein as first derivative of the radius R about rotation angle φ:M=dR/d φ.Here, here, rotation
Angle φ increases when rotating along the first direction of rotation.In other words, rotation angle value is from the closed state of clutch to clutch
Opening state increase.
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 rotation angle φ
It is rotated between E.Here, initial rotation angle φ A can be equivalent to 0 ° of rotation angle.Final rotation angle φ E can be equivalent to phase
Rotation angle φ for initial rotation angle φ A less than 355 °, advantageously, it is final rotate angle φ E can be equivalent to relative to
Rotation angle φ of the initial rotation angle φ A less than 340 °.Thus advantageously prevent the transition of cam disc from rotating, when cam disc from
Second rotation angle φ 2 is further rotated along the first direction of rotation from final rotation angle φ E up to initial rotation angle in other words
φ A is spent in other words until when being rotated by 360 ° in total, transition rotation will lead to the prominent of clutch when first rotates angle φ 1
So engagement.
Furthermore for example settable：Cam disc is configured to prevent cam disc from further rotating to be more than final rotation angle (φ E).
This can for example realize that the card resistance device prevents from rotating along the first direction of rotation is more than in other words more than stop member by card resistance device
Final rotation angle.Merely illustratively, this card resistance device can by cam disc or in stop member formed or by convex
Sliding slot in wheel disc is formed, and tenon is cooperated in the sliding slot.This card resistance device also may be configured to through the collective effect with push rod
It is more than final rotation angle to prevent from further rotating.This can for example be risen by the step of cam disc radius causes.
In other words, the rotation angle that initial rotation angle can be greater than initial rotation angle from one, only passes through cam disc
Back rotation is realized again.With cam disc coupling push rod thus engagement when with the identical function of radius R=F that passes by when separating
(φ) is only merely in the opposite direction.
Settable herein, in the case where the first rotation angle 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
Clutch is thus in maximum closing, and push rod is in maximum engagement state to engagement state in other words in other words.Furthermore settable,
In the case where second rotation angle φ 2, the second radius R2 is equivalent to cam disc in entire achievable rotation angle range
Maximum radius, push rod can form Coupling point with cam disc in the rotation angle range.Clutch is thus in maximum opening
Push rod is in greatest separation to discrete state to state in other words in other words.Here, clutch can be before greatest separation
Just it is in the open state (i.e.：Torque transfer no longer occurs).
Settable, the first radius R1 is less than the second radius R2.
Such as settable, the radius on terminal of the radius R less than the second section S2 on the terminal of the first section S1.Thus
Advantageously make the especially uniform especially uniform linear movement for separating push rod in other words for being able to achieve clutch.
Settable, radius is dull between the first rotation angle and the second rotation angle to be increased.It is particularly advantageous
Ground is settable, and radius is from the starting point of the first section up to the terminal dullness of the second section increases.Particularly advantageously, radius is from first
The starting point of section is until the terminal strictly monotone of the second section increases.Thus advantageously cause the especially uniform linear fortune of push rod
It is dynamic.This causes especially small noise to generate, because push rod is from the risk in the sliding groove structure that cam disc lifted or be stuck in cam disc
Reduce.Furthermore the unnecessary load as caused by the compression shock from the hydraulic cylinder coupled with push rod can be prevented.Thus most
Realize uniform maneuvering performance on the service life for the device of controlled clutch eventually, and with locating environment temperature and peace
Dress component in a device with old unrelated.
Here, for example settable, radius R about rotation angle φ function R=F (φ) in the first section S1 and the secondth area
Section S2 between Second Order Continuous can be micro-, especially each point Second Order Continuous can be micro-.In other words, function of radius does not have bending.By
This advantageously causes especially small noise to generate.Push rod lift or thus blocking for push rod equally can advantageously be avoided by.
It is settable in expansion scheme, it is being supported along the first direction of rotation (91) observation in rotation axis (51) and axially
Longitudinal axis (LA) is arranged in when the section extended between device (30) parallel to the axis (PA) before.This space D is referred to hereinbelow as
" positive spacing ", which " is greater than 0 " according to the present invention (D>0).Thus maximum delivered can numerically be reduced especially bigly
To the radial force of axial supporting arrangement.Thus advantageously reduce abrasion, noise emission and can by axial bearing or bearing member
Part is configured to smaller and more cost advantages.Can also it is extremely simple, efficiently and regularly cause push rod in axial bearing or branch
Hold the lubrication in element.Especially when in axial supporting arrangement or axially be spaced from each other spacing two supporting members it
Between be equipped with lubricant locker room when.
It is settable in expansion scheme, it is being observed along the first direction of rotation between rotation axis and axial supporting arrangement
Longitudinal axis (LA) is arranged in when the section of extension parallel to the axis (PA) after.This space D is hereinafter referred to as " negative spacing ", should
Negative spacing (the D " less than 0 " according to the present invention<0).Thus when radial force is acted in same direction always and is not zero always
When, it may be advantageous to cause particularly simple axial supporting arrangement.Thus the noise of sending can also be reduced.
Settable in expansion scheme, at least one described supporting member is made up of sliding bearing.Advantageously, it supports
Element can extremely simple by this way and abnormal cost be advantageously carried out.The sliding bearing for example can be by polytetrafluoroethylene (PTFE)
Or it is made of the other materials compared with push rod with especially small coefficient of friction.
Settable in expansion scheme, at least one described supporting member is constituted by having at least one slotted track,
At least one described track is, for example, linear, wherein be disposed at least one induction element on push rod, it is described at least one
Induction element is guided in slot.The induction element can for example be configured to tenon.Thus particularly reliable axial direction can be favorably provided
Supporting arrangement.
Here, Ball support device (Kugellagerung) can be arranged in the track.It can be realized by this way to pushing away
The especially small guidance of especially small and noise that rubs of bar.
Settable in expansion scheme, push rod has idler wheel, which has a diameter (D1), wherein the spacing (D)
Numerical value be in the range of the 5% to 30% of the diameter (D1).It can be advantageously by cam disc and push rod by setting idler wheel
Between frictionally hold especially small.Thus the abrasion and noise for reducing actuator issue.By selecting the spacing in institute
State the 3% to 35% of the diameter of idler wheel, it, can be special in the range of preferably 5% to 30% and completely particularly preferred 8% to 22%
The earth reduces maximum radial force.Furthermore the noise of sending thus for example can also especially be reduced by force.It finally can also be by axial bearing
The supporting member can be configured to that extremely simple, especially small and abnormal cost is advantageous by part in other words.The range provided relates to herein
And the numerical value of spacing, i.e., the described spacing can be positive value or negative value.
Settable in expansion scheme, cam disc has static section (SR), wherein the starting point of static section (SR) is the
Start when three rotation angle (φ 3).Third rotates angle (φ 3) and is greater than or equal to the second rotation angle (φ 2).Cam disc is quiet
Only cause the opening state of clutch in section (SR) with static radius (RR).Here, radius (R) is about rotation angle
The first derivative of (φ) is substantial constant in static section (SR) and is equal to zero.Thus advantageously cause, for push rod
Discrete state and thereby the smallest motor torque is needed not be provided or must only provided for the discrete state of clutch.Even if in transverse direction
In the case where the vibration that the direction of linear motion of push rod works, push rod can still keep stablizing in static section.Example as a result,
Such as in congestion traveling or in red light, i.e., when clutch must resist the spring force of clutch to work in longer time
It stays open when separating in other words, required power consumption decline.Here, static section (SR) is seen along the first direction of rotation
It is arranged in after the minus section of slope.Particularly effectively undesirable engagement can occur by anti-throw-out lever by the measure.
Alternatively, radius (R) about rotation angle (φ) first derivative in static section (SR) less than zero.The single order
Derivative can also be constant herein.In the settable stop part for push rod of the terminal point of static section.As a result, described device or
Even if the actuator is powered off in motor and is particularly securely avoided in the case where only passing through motor and being loaded with small torque in other words
Clutch is not intended to engage.Because in order to engage clutch push rod in other words, motor must be such that cam disc and first rotates first
It moves in the opposite direction and overcomes the additional spring force for acting on push rod herein.
Alternatively, radius (R) has in static section (SR) from less than zero about the first derivative of rotation angle (φ)
Value to greater than zero value sign transformation.In other words, small hole (Kuhle) is configured in cam disc, wherein push rod
It can couple to metastable state.By the expansion scheme, as long as Coupling point is in static section (SR), 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 to rotate angle from the closed state in the case of the first rotation angle φ 1 for derivative precondition in this
Increase towards the opening state in the case of the second rotation angle φ 2, in other words, rotation angle φ increases along the first direction of rotation.
In other words, it is first in static section when the sign in first derivative from minus value to the value greater than zero converts
The reduction of radius R is first set and then with the increasing of the rotation angle φ setting radius further increased along the first direction of rotation
Greatly.
It can prevent the power consumption that motor overheats and can reduce automobile electrical network by setting resting position on the whole.
Settable 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.It thus can especially safely and reliably anti-throw-out lever unintentionally engages.
Rotation angle settable in an expansion scheme, that the terminal of the starting point of the second section S2 and the first section S1 are spaced
Degree is 25 ° maximum.Particularly advantageously, the rotation angle that the terminal of the starting point of the second section S2 and the first section S1 are spaced is
15 ° maximum, particularly advantageously the rotation angle is 10 ° maximum completely.Thus the first rotation of cam disc can particularly efficiently be utilized
Between gyration and the second rotation angle available rotation angle range and until reach switching time of semi-linkage state can
It keeps especially small.
Settable in an expansion scheme, the starting point of the first section S1 is in the first rotation angle about the first direction of rotation
The rotation angle φ 1 of φ 1 and first is plus in the rotation angle range between 30 °.Thus advantageously cause, until reaching the secondth area
Section switching time it is especially short and first rotation angle and second rotation angle between available rotation angle range it is special
It does not utilize efficiently.Unwanted cam disc " idle running " is thus advantageously avoided.
Alternatively or additionally settable, the second slope m2 is greater than zero.Thus it avoids reaching clutch push rod in other words
Semi-linkage state and until reach discrete state switching time delay.Because slope is zero to be equivalent to push rod and be parked in its position
It sets motionless and slope is equivalent to push rod edge less than zero towards the displacement of the direction of cam disc.
Settable in expansion scheme, the first section S1 and the second section S2 each extend over the rotation angle by least 5 °
Range, particularly advantageously passes through at least 10 ° of rotation angle range, especially advantageously passes through at least 15 ° of rotation angle range.
Thus advantageously cause the especially uniform movement of push rod.Because in the case where cam disc constant angular speed, both in the firstth area
Also push rod stroke is carried out in other words with constant speed for push rod linear movement in the second section in section.Thus advantageously also reduce
The risk that push rod blocks, such as block on the bearer, or reduce acted on hydraulic cylinder due to push rod caused by pressure rush
It hits.Furthermore make the operation for being able to achieve special low noise, because not occurring push rod lifting or blocking relative to cam disc.
Alternatively or additionally settable, the first section S1 extends past at least 20 ° of rotation angle range.It is particularly advantageous
Ground, the first section extend past at least 30 ° of rotation angle range.Thus particularly efficiently reduce switching time, because
The distance that every rotation angle distance is passed by by push rod in one section is especially big.The rotation angle range of first section is bigger, then cuts
It is smaller to change the time.
Alternatively or additionally settable, 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.It thus can be particularly efficiently by the power consumption of motor
Keeping small can keep especially small for 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
Duan Zhonggeng flat slope causes push rod further to separate in the case where fractional motor torque.Because such as being subtracted by smaller slope
Lever arm of the small push rod to cam disk axis.Thus required for longer switching time can by it is sufficiently long and be equipped with foot
The first section compensation of enough big first slopes.The overheat of motor or the power electronic component for manipulating motor thus can be advantageous
Ground is avoided by.
Settable in expansion scheme, cam disc has the between the first rotation angle φ 1 and the second rotation angle φ 2
Three section S3, wherein the radius R of cam disc has substantially constant third oblique about rotation angle φ in third section S3
Rate m3.Here, the second section S2 is arranged between the first section S1 and third section S3 about rotation angle φ.Here, second
Slope m2 is greater than third slope m3.In the spring force for acting on push rod, (spring force for example can also be non-linear class as a result,
Type) it is big in the case where, the power consumption that can further decrease 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 third section can pass through the phase of the first and second sections
Slope and the section length compensation being adapted to answering.Thus device with compact motor can be provided on the whole.
Third section S3 for example may extend past at least 5 °, preferably at least 10 ° of rotation angle range.
Alternatively or additionally, the terminal of the starting point of third section S3 and the second section S2 can be spaced maximum 15 ° of rotation
Angle can particularly advantageously be spaced maximum 10 ° of rotation angle.Thus the first rotation angle that the push rod of cam disc can be engaged
Available rotation angle range between the second rotation angle of push rod separation particularly efficiently utilizes, also, until reaches
The switching time of opening state semi-linkage state in other words can keep especially small.
Settable, third slope m3 is greater than zero.Thus avoid reach clutch in other words the semi-linkage state of push rod and
Until reaching the delay of the switching time of discrete state.Because slope be zero corresponding to push rod stop at it is motionless and oblique on its position
Rate is equivalent to push rod less than zero and shifts along the direction towards cam disc.
Furthermore settable 4th section, the 4th section is seen in the first rotational direction to be arranged in after third section,
In, the radius R of cam disc has substantially constant 4th slope m4 about rotation angle φ in the 4th section.4th slope
Third slope can be greater than herein.The switching time for reaching push rod separation can further be shortened by this way.
Settable in expansion scheme, cam disc has third radius R3 to cause the semi-linkage state K of clutch.?
This, third radius R3 is associated with the rotation angle φ S of cam disc, which is in the second section S2 or in third area
In section S3.Thus advantageously cause, must often converted between the clutch and semi-linkage state K of engagement (such as in congestion
Traveling) driving status in, can by the torque of needs and thereby by the power consumption of motor keep it is small.It can avoid by this way
Motor in other words drive motor control electronic component overheat.
Semi-linkage state is understood to the following state of clutch, and clutch did not both have (complete) to beat in this state
Opening does not have (complete) close yet.Exactly, in semi-linkage state, clutch disk mechanically sticks on the flywheel that driving is side
On disk, so that the force closure between clutch disk and Flywheel disc is also not enough to prevent Flywheel disc relative to the " sliding of clutch disk
Turn ".In other words：Whole torques clutch is not transmitted to from Flywheel disc like that just like in the case where clutch closed state
Disk.For example, semi-linkage state may be defined as, the torque of 1.5Nm to 6Nm, such as 3Nm are passed into clutch disk from Flywheel disc.
Those skilled in the art can be by obtaining of the invention its to the description of illustrative embodiments later in reference to attached drawing
His feature and advantage, but the illustrative embodiments are not construed as limitation of the present invention.
Detailed description of the invention
Attached drawing is shown：
Fig. 1 a：The schematic diagram of the electrically-energized clutch system of energy；
Fig. 1 b：The electrically-energized actuator of energy is used for the diagram of the device of the clutch in controlled clutch system in other words；
Fig. 1 c：From the three-dimensional cutaway view of the actuator in terms of the visual direction different from Fig. 1 b in 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 discrete state)；
Fig. 3 a:The perspective view of embodiment of the axial supporting arrangement as slide support or as rail support；
Fig. 3 b:Another perspective view of the axial supporting arrangement of Fig. 3 a；
Fig. 4 a:The schematic diagram of cam disc, the cam disc are concured with push rod guided in axial supporting arrangement,
The longitudinal axis of the push rod is greater than zero with the space D to parallel to the axis；
Fig. 4 b:Curve graph shows the relationship between the radius of the cam disc of Fig. 4 a and rotation angle；
Fig. 4 c:Curve graph shows and acts on being associated between the radial force of axial supporting arrangement and rotation angle, as
The actuator of Fig. 4 a and following actuator are compared, longitudinal axis is consistent with paralleling to the axis in the actuator；
Fig. 5 a:The schematic diagram of cam disc, cam disc are concured with push rod guided in axial supporting arrangement, should
The longitudinal axis of push rod and the space D to parallel to the axis are less than zero；
Fig. 5 b:Curve graph, the curve illustrate the rotation of the cam disc of the radial force and Fig. 5 a that act on axial supporting arrangement
Association between gyration.
Specific embodiment
Fig. 1 shows the electrically-energized clutch system 1 of energy of automobile-use.Foot pedal 3 can resist 5 ground pressure of spring by driver
It is low.It is sought herein by sensor 7 and is delivered to controller 9 in the current location of foot pedal 3.Based on the signal of sensor 7,
Motor 11 of the manipulation of controller 9 for the device 13 in other words of actuator 13 of controlled clutch.Motor 11 can be for example electricity
The Brushless DC motor or traditional motor of son rectification.Motor 11 is steered, by suitable 15 (example of force transfering device
Such as in the form of transmission mechanism 15) move piston 17 in active cylinder 19, which 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 be separated in the case where being manipulated by slave cylinder 23.Answering on clutch 27 is set
Position spring 29 is used herein to provide the corresponding buffer brake for acting on slave cylinder 23, so that weakening the manipulation to foot pedal 3
And correspondingly (reversed) manipulation is for manipulating the actuator 13 of vehicular clutch 27 in other words in the case where device 13 by clutch
Device 27 engages again.Air vent 18 is equipped in the Background Region of active cylinder 19 for forming clutch adjuster 14.When 17 foot of piston
When enough far moving backward more than air vent 18, hydraulic oil can be supplemented by container 16 and be flowed in active cylinder 19.Clutch 27 is for example
It can vehicle motor couples in other words by the clutch disk that can be driven by described device 13 or actuator 13 and with driving system
Flywheel disc is formed.Clutch disk is mechanically separated from Flywheel disc when separating clutch 27, so that no longer occurring from Flywheel disc
To the torque transfer of clutch disk.
In attached drawing below, the identical element of or function identical with the element in Fig. 1 is equipped with identical appended drawing reference.
Fig. 1 b shows the diagram of the device 13 in other words of actuator 13 for controlled clutch 27.Motor 11 passes through herein
Force transfering device 15 drives cam disc 50.Force transfering device 15 by worm gear 15a and engages in the illustrated embodiment
Gear 15b is formed.Taking in small pin-shaped formula is disposed with being eccentric in 51 ground of axis on the gear 15b that axis 51 rotates
Part 15c.
Cam disc 50 is disposed on gear 15b, which has notch 56, and carrying piece 15c is received in the notch 56
In.By this way, cam disc 50 is coupled with gear 15b.When motor 11 rotates gear 15b by force transfering device 15
When, cam disc 50 around the rotation of axis 51 or around the rotation of axis 51 or can will surround the rotation of axis 51 as gear 15b.
In principle it is also possible that motor 11 drives cam disc 50 in the case where no force transfering device 15 connects in centre and makes
It is rotated around axis 51.In other words furthermore device 13 has push rod 40 to actuator 13 for manipulating vehicular clutch 27.It pushes away
Bar 40 has first end 46, which couples with cam disc 50, so that being drawn by cam disc 50 around the rotation of axis 51
Play the linear motion of push rod 40.The linear motion is carried out along the longitudinal axis L A of push rod 40 herein.The linear motion of push rod 40 is then
The piston 17 of active cylinder 19 can be passed to as Fig. 1 a description.In the embodiment as shown, the first of push rod 40
End 46 has idler wheel 42, which can roll on the end face 54 (Fig. 1 c) being radially outward directed, to reduce friction.The rolling
Wheel 42 has diameter D1.Push rod 40 is coupled in Coupling point 53 with cam disc 50.Coupling point 53 is for example as in the illustrated embodiment
Reclining a little 52 formation like that by the first end 46 of the push rod 40 in other words of idler wheel 42 on the end face of cam disc 50 54.
Push rod 40 is implemented as elongated element.Push rod passes through axial supporting arrangement 30 (Fig. 1 c) and is guided, so that push rod is only
It is only capable of moving along a straight line in other words along its longitudinal axis L A implementation linear movement.Axial supporting arrangement 30 is herein relative to rotation axis
51, which are disposed so as longitudinal axis L A, separates space D with the PA that parallels to the axis for being parallel to longitudinal axis L A.Here, the PA that parallels to the axis
Intersect with rotation axis 51.In other words, the longitudinal axis L A of push rod 40 is arranged to be eccentric in or be staggered in rotation axis 51.Longitudinal axis
LA is not extended on the rotation axis 51 of cam disc thus, but is extended by rotation axis 51.
In principle, push rod 40 can also be coupled by chute guide device (sliding slot in cam disc 50) or flange guide device
Onto cam disc 50.Coupling point 53 this then pass through in cam disc 50 or on sliding slot and the first end 46 of push rod 40 it is common
The point of effect is formed by the coefficient point of flange and the first end 46 of push rod 40 on cam disc 50.
Cam disc 50 has the first radius R1 in the case where the first rotation angle φ 1.Push rod 40 and cam disc are first
Collective effect in the case where rotation angle causes the closed state C of clutch 27 herein.Cam disc 50 is also in the second rotation angle
There is the second radius R2 in the case where spending φ 2.The common work of push rod 40 and cam disc 50 in the case where the second rotation angle φ 2
With the opening state 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 outer profile sliding slot in other words, at the position to recline a little
Radius R changes according to rotation angle φ.First radius R1 and the second radius R2 is thus mutually different and thereby leads to push rod 40
Different linear positions.
For example, the second radius R2 is greater than the first radius R1.Push rod 40 is in the first rotation angle φ 1 (such as Fig. 1 b institute as a result,
Show) in the case where engage, i.e., in terms of its linear movement towards cam disc 50 in other words towards axis 51 shift.If cam disc 50 exists
91 (along clockwise in figure) movement along the first direction of rotation in Fig. 1 b, then radius R also increases simultaneously with the increase of rotation angle φ
And push rod 40 is in Figure 1b to the right, i.e., shifts with leaving from the rotation axis 51 of cam disc 50.Push rod 40 separates.Similar to push rod
40 movement, clutch 27 is in engagement state, i.e. closed state C in the case where the first rotation angle φ 1, and revolves second
O in the open state in the case where gyration φ 2, the opening state are equivalent to discrete state O.In order to again from discrete state O or
Person says that opening state O returns to engagement state C closed state C in other words, it is desirable that, cam disc 50 and the first direction of rotation 91
On the contrary (herein along the second direction of rotation 92：Counterclockwise) toward revolution.The cam disc 50 here, push rod 40 is passed by separation
Same profile, but in opposite direction.
Fig. 1 c shows the three-dimensional cutaway view from the actuator in terms of the different visual directions from Fig. 1 b in Fig. 1 b.In this view
It can be seen that the second end 48 of push rod 40, the second end are coupled with the piston 17 of active cylinder 19.
In the embodiment provided, axial supporting arrangement 30 has in the direction of the second end 48 away from first end 46
There are two supporting members 31.The first supporting member 31a towards cam disc 50 and by comparison with cam disc 50 every it is farther away
Second supporting member 31b can receive the radial force of push rod 40.Concept " radial power " is understood in other words " radial force "
It is substantially perpendicular to the axial direction (power to work along longitudinal axis L A).First supporting member 31a can be configured to sliding branch
Bearing member 34a.Similarly, the second supporting member 31b can be configured to sliding bearing 34b.First supporting member 31a, 34a and/or
Second supporting member 31b, 34b for example can constitute or be configured to linear ball axis by the material of polytetrafluoroethylene (PTFE) or other low frictions
It holds.Lubricant locker room can be arranged between two supporting members 31a, 31b.Thus can in a long time non-maintainingly, friction
Push rod 40 is guided smallly.
In principle it is also possible that axial supporting arrangement 30 only includes only one supporting member 31.Alternatively, axial branch
Bearing apparatus may also comprise has more than two supporting member 31 in other words.
As that the description of Figure 4 and 5, can arranged further below by the way that push rod 40 is eccentric in cam disc 50, to reduce
The noise that actuator 13 issues when running.When being equipped with lubricant locker room along the longitudinal axis L A of push rod 40, also visual space D
Design depending on improve supplemental lubrication characteristic.Finally it can also reduce maximum effect according to space D in supporting member 31 in other words
Act on supporting member 31a, the radial force of 31b.
It can be seen that idler wheel 42 on the first end 46 of push rod, the idler wheel recline a little 52 and cam disc 54 coupling of end face
It closes.Idler wheel 42 rotates around another rotation axis 41 and has diameter D1.
Fig. 2 a-2c be shown respectively cam disc 50 and push rod 40 in different conditions coefficient schematic diagram and it is affiliated from
27 state of clutch (engagement state, semi-linkage state and discrete state).Merely illustratively, the axial supporting arrangement 30 of push rod 40
The first supporting member 31a and the second supporting member 31b are respectively provided with similar to the embodiment in Fig. 1 c.
Fig. 2 a shows the cam disc at the first rotation angle φ 1, which can also be initial rotation
Angle φA.First rotates the initial rotation angle φ in other words of angle φ 1A0 ° of rotation angle value can be for example attached to.This
The first radius R1 is provided in the case where one rotation angle φ 1, which is for example equivalent to the least radius of cam disc 50.?
The spacing of the first end 46 of push rod 40 to rotation axis 51 is especially small in the case where first radius.In the clutch shown in right side
27 are in engagement state.Therefore, Flywheel disc and clutch disk are mechanically interconnected, so that being able to achieve from Flywheel disc to clutch
The torque capacity of disk is transmitted.Reset spring 29 is in unloading position, so that not needing for push rod 40 to be maintained in bonding station
Torque is applied to cam disc from motor 11 or only needs to be applied to cam disc 50 from motor 11 by very small torque.
Fig. 2 b shows the cam disc in the case where semi-linkage rotates angle φ S, which rotates angle and be greater than first
Rotate angle φ 1.Semi-linkage rotates angle φ S for example can be relative to the first rotation angle φ 1 in other words relative to initial rotation
Angle φ A be in 140 ° to 220 ° between and along the first direction of rotation 91 (herein：It rotates clockwise)
Reach later.In the case where semi-linkage rotates angle φ S, cam disc 50 has third radius R3, and the third radius is for example big
In the first radius R1 and less than the second radius R2.Clutch 27 is in semi-linkage state K.Clutch disk is not complete in this state
It is loosened entirely from the Flywheel disc of clutch 27.The small torque transfer occurred is in the range of such as 1Nm to 10Nm, is preferably located
In 1.5Nm between 6Nm, for example, 3Nm.In other words：Flywheel disc trackslips relative to clutch disk in semi-linkage state K.For
Reach semi-linkage state K, it is necessary to overcome the spring force of reset spring 29.It will thus be determined by reset spring 29 by clutch 27
Fixed power passes to push rod 40.Actuator 13 for controlled clutch 27 in other words device 13 motor 11 thus necessary for
The state is realized from engagement state C and uses torque bigger compared in 27 engagement state C of clutch.In order to keep
Semi-linkage state K, it is also desirable to the bigger torque compared with engagement state C, because the push rod 40 loaded by spring force is otherwise
Rotate cam disc 50 back against the first direction of rotation 91.
Fig. 2 c shows cam disc in the case where finally rotation angle φ E.Final rotation angle φ E is equivalent to cam disc
The rotation angle of 50 maximum possible.Final rotation angle φ E may be, for example, maximum 355 ° in other words to be 340 ° maximum, for example,
330°.Final rotation angle φ E can be greater than the second rotation angle φ 2, and clutch 27 has been in the case where the second rotation angle
In discrete state O in other words opening state O.Clutch 27 can also be in opening in the case where finally rotation angle φ E
In state O.Push rod 40 joins in the case where the second rotation angle φ 2 and in the case where finally rotation angle φ E with half
Dynamic state K rotates angle φ in semi-linkage in other wordsSCompared in the case where initial rotation angle φ A with axis 51 every more
Far.In order to which 11 torque of motor for needing to apply at the opening state O of clutch 27 is as small as possible, cam disc 50, which can be directed to, to be greater than
The rotation angle φ of second rotation angle φ 2 has static section SR.Static section SR is for example being greater than the second rotation angle φ 2
Third rotate angle φ 3 when start.The settable static radius RR in static section, the static radius is about the second radius R2
It is constant or even with respect to the second radius R2 reduction.Maximum radius thus may be provided at the second rotation angle φ 2 and third
It rotates between angle φ 3.
Fig. 3 a and Fig. 3 b show axial supporting arrangement 30 as slide support and are used as in other words the implementation of rail support
Two different perspective views of mode.Here, axial supporting arrangement 30 is respectively provided in the opposite longitudinal direction side of push rod 40
One track 32 is used as supporting member 31.Each track 32 has the slot 33 towards push rod 40.Be disposed on push rod 40 towards
Two induction elements 38 of two tracks 32, described two induction elements are scarfed to respectively in a slot 33.Induction element 38 can
It is configured to the tenon outwardly protruded or is configured to the element longitudinally extended along longitudinal axis outwardly protruded.By in slot 33
Induction element 38 is received, the freedom of motion of push rod 40 is confined to the extending direction along track 32 within small franchise
Linear motion.In the illustrated embodiment, track 32 linearly constructs, so that push rod only implementable linear motion.
It can also arrange that track can be configured to linear ball to ball bearings in other words in track 32 in principle in order to reduce friction
Bearing.
Fig. 4 a shows the schematic diagram of the illustrative embodiments of cam disc 50, the cam disc and push rod 40 in other words with arrangement
Idler wheel 42 on the first end 46 of push rod 40 concurs.The radius of cam disc 50 is shown here in solid line.In cam
In one embodiment of disk 50, push rod 40 rolls on the end face of cam disc 50 54, and in this embodiment, push rod 40 is with its rolling
Reclining for wheel 42 a little 52 sticks on the end face 54 of cam disc 50.The axial supporting arrangement 30 of push rod 40 schematically passes through two
Supporting member 31, the first supporting member 31a and the second supporting member 31b are shown, and described two supporting members are for example embodied as sliding
Dynamic supporting member 34a, 34b.
Push rod 40 is directed toward to the right from the rotation axis 51s of the cam disc 50 of Fig. 4 a.Make to push away by the first direction of rotation 91
Bar 40 separates, i.e., shifts the first end 46 of push rod 40 with leaving from rotation axis 51 by it, which exists
It is provided in Fig. 4 a by (dextrorotation) clockwise.In fig.4 along the first direction of rotation 91 observation rotation axis 51 with
When the section extended between axial supporting arrangement 30, longitudinal axis L A is arranged in parallel to the axis PA before.In other words, the longitudinal axis of push rod
Line extends in the top that parallels to the axis in fig.4 and thereby extends above the intersection point of rotation axis 51 and plan.It constructs in this way
Space D " offset (Offset) " D is positioned as space D in the sense of the present invention in other words>0 (D is greater than zero).The regulation is logical
Cross the coordinate system foundation of Fig. 4 a.In XY coordinate system, the rotation axis 51 of cam disc is located at point (0；0).Longitudinal axis L A
It is parallel to X-axis with the PA that parallels to the axis to extend, wherein the PA that parallels to the axis extends past origin (0；0).Longitudinal axis L A exists in the figure
Value greater than zero intersects with Y-axis.
Reclining between idler wheel 42 and cam disc 50 a little 52 itself can be eccentric in longitudinal axis L A.Normal force FNTowards idler wheel 42
The direction of another rotation axis 41 a little 52 acts on idler wheel 42 from reclining.Normal force FNWork perpendicular to longitudinal axis L A
Component cause to act on the radial force of axial supporting arrangement 30.Here, reclining for marking a little 52 will be in figure downwards (along negative
Y-direction) be directed toward the first radial force FR1Act on the first supporting member 31a.In the design shown and in the rotation angle shown
In the case where spending φ, the second radial force FR2Act on the second supporting member 31b, second radial force herein along positive Y-direction (i.e.
In figure upwards) work.Apparent rotation angle φ, the direction towards cam disc 50 from clutch 27 act on the anti-of push rod 40
At Xiang Li and the position present rotation angel degree φ depending on slope (dR/d φ) of the radius R about rotation angle, recline a little 52 in its position
It is changeable to set aspect.Thus different normal force F is obtained depending on apparent rotation angle φNWith different radial force FR1And FR2.Especially
It is when radius R changes about the slope of rotation angle φ, reclining a little 52 can be changed, so that reclining a little has about longitudinal axis L A
Different eccentricity deviates spacing in other words in other words.
It, can be by actuator design at can be individually by purposefully adjusting longitudinal axis L A and the space D of PA of paralleling to the axis
Or it can simultaneously realize different purposes.Such as it thus can be minimum by the radial force for maximally acting on axial supporting arrangement 30
Change.It simultaneously or additionally can for example reduce noise being issued, for example being formed due to supporting member gap.
Curve graph for the cam disc of Fig. 4 a shown in fig. 4b, draws radius in Y-axis and draws rotation angle in X-axis
Degree.
Push rod 40 91 is seen (herein along the first direction of rotation when rotated on cam disc 50：Rotate clockwise) from phase
When the first rotation angle φ 1 in 0 ° sets out the first section S1 to be passed by cam disc 50 first, from the starting point of the first section S1
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 starting point 73 and terminal 74 of the second section S2.Here, cam disc 50 has in the first section S1
Substantially constant first slope m1, the first slope are equivalent to first derivative of the radius about rotation angle φ.In other words：?
Radius linearly increases substantially as rotation angle φ in first section S1.
It can be seen that, cam disc 50 has substantially constant second slope m2 in the second section S2 in fig. 4b.Second
Slope m2 is greater than zero in the illustrated embodiment.First slope m1 is greater than the second slope m2.It is preferred that first slope m1 is at least
Twice of two slope m2 is big.Particularly preferably, first slope m1 be at least the second slope m2 three times it is big.Push rod 40 is convex as a result,
The straight line distance that edge is passed by relatively large from the direction that rotation axis 51 leaves in the first relatively small section S1 of the torsion of wheel disc 50,
The switching time isolated for clutch 27 is shortened as a result,.Such as it is pushed away when the push rod in existing bigger spring-force driven dual
Bar 40 reaches in the second section S2, and in second section, the torque T of motor 11 can then pass through lesser second slope m2 and the
One slope m1 is smaller compared to holding along the situation that entire cam disc 50 is applicable in.
Semi-linkage state K realizes that the semi-linkage rotates angle and corresponds to third in the case where semi-linkage rotates angle φ S
Radius R3 and thereby the push rod stroke for corresponding to restriction.Semi-linkage rotation angle is for example attached to the second section S2.It thus can be
The torque of motor 11 is kept small when driving by the congestion that clutch 27 must often be maintained at semi-linkage state K.
It is seen along the first direction of rotation 91, clutch 27 is in discrete state O in the case where the second rotation angle φ 2
In, no longer exist torque from Flywheel disc and is transmitted to clutch disk.Cam disc 50 can still further rotate, until push rod 40 is in third
The static section SR on cam disc 50 is reached in the case where rotating angle φ 3.In the static section SR, cam disc 50 has quiet
Only radius RR.Static radius RR be, for example, it is constant, i.e., the slope mR in static section SR is zero.It thus is holding push rod stroke
And the torque T of motor 11 is no longer needed, thus when clutch 27 fully opens the opening of clutch 27 to the full extent in other words,
Automobile electrical network is not loaded and motor 11 is avoided to overheat.
The starting point of first section S1 for example can be along the first direction of rotation (i.e. along the opening direction of clutch 27 edge in other words
The detaching direction of push rod 40) it is in 0 ° to 30 ° of rotation angle range, wherein here, initial rotation angle φ A can attach 0 °
Value.The radius shown in fig 3b-rotation angle function is preferably at least from the starting point 71 of the first section S1 up to the second section
74 Second Order Continuous of terminal of S2 can be micro-, so as to low noise as far as possible and equably shifts push rod 40 and minimizes abrasion.
The starting point 73 of second section S2 can for example be spaced 25 ° of maximum with the terminal 72 of the first section S1 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 the king-sized section of linear displacement in a short time available motor torque T.
Second section S2 may extend past at least 100 ° of rotation angle range, preferably extend past at least 120 ° and complete
At least 140 ° are particularly preferably extended past entirely.
Static section SR for example may extend past the rotation angle range of at least 30 °, preferably at least 40 °.
Fig. 4 c shows curve graph, shows on the first supporting member 31a acted on axial supporting arrangement 30
One radial force FR1Or the second radial force F on the second supporting member 31bR2Association between rotation angle φ, as Fig. 4 a
Actuator (space D>0) it compared with following actuator 13, longitudinal axis L A and parallels to the axis in the case where actuator 13
PA is consistent (space D=0).Cam disc 50 forms in the same manner in both cases herein.For the actuator of space D=0, first
Radial force FR1, D=0It is shown as curve 61 (solid line) and the second radial force FR2, D=0It is shown as curve 62 (solid line).For Fig. 4 a's
Cam disc-push-rod assembly, the first radial force FR1, D>0It is shown as curve 63 (chain-dotted line) and the second radial force FR2, D>0It is shown as song
Line 64 (chain-dotted line).In the example shown, when roller diameter D1 is 20mm, space D is 2mm (D=2mm).Generally, space D
Such as can be at idler wheel 42 diameter D1 3% to 35% in the range of, in the range of preferably 5% to 30% and completely especially
It is preferably in the range of 8% to 22%.
Obviously it can be seen that maximum effect is in supporting member 31a, the radial force of 31b is greater than zero (D in space D>0) when
Considerably smaller than space D is equal to the case where zero (D=0).In the example shown, each supporting member 31a, the maximum, force of 31b
It is more that numerical value reduces half herein.Thus supporting member 31a, the abrasion of 31b are reduced.Also size can be used to determine to obtain lesser bearing
Element 31a, 31b, so as to more cost-effectively manufacture actuator and be made to smaller.
It can also be seen that the numerical value of cam disc-push-rod assembly radial force of the spacing equal to zero (D=0) is up to about 285 °
Rotation angle φ is both greater than space D greater than zero (D>0) numerical value of cam disc-push-rod assembly radial force is (respectively by curve 61
Compared with curve 63 and by curve 62 compared with curve 64).In the design of the cam disc shown in Fig. 4 a and 4b, angle φ is rotated
=285 ° of terminals for being approximately equivalent to the second section S2, slightly before in static section SR in other words in the transition to static section SR.
From reaching the static section SR that slope used herein is zero (mR=0), subtract for the radial force that space D is zero (D=0)
It is small to be approximately equal to zero or be equal to zero.
Finally, it is greater than zero (D in space D>0) the first radial force of cam disc-push-rod assembly FR1(curve 63) and second
Radial force FR2In the trend of (curve 64), it can be seen that the variation in power direction in the region for reaching static section SR.It means that
The first radial force F in static section SR after direction change on the first supporting member 31a in fig.4R1Along positive Y-direction
Be directed toward and the second supporting member 31b on the second radial force FR2It is directed toward along negative Y-direction.By being installed by push rod 40 in axial branch
It sets and slightly reverses bring radial force direction change in 30, be conducive to the excellent of the axial supporting arrangement 30 in other words of axial bearing 30
Change lubrication.If being equipped with lubricant locker room between 31b in supporting member 31a, then can will be moistened by the variation in radial force direction
Lubrication prescription, such as rouge or oil, are evenly distributed in supporting member 31a, and 31b and push rod 40 are arranged in the guidance on the push rod in other words
On contact surface between element.
Shown in radial force trend want to go to understand merely illustratively.In other cam disc geometries or selected other
The trend of different radial forces can be obtained in the case where space D.
Fig. 5 a shows the schematic diagram of cam disc 50, the cam disc in axial supporting arrangement 30 guided push rod 40 it is total
With working, the spacing of the longitudinal axis L A of the push rod and PA that parallels to the axis is D, and the spacing similar to Fig. 4 a the case where observing
Under less than zero (D<0).Thus prolonging between rotation axis 51 and axial supporting arrangement 30 along the observation of the first direction of rotation 91
Longitudinal axis L A is arranged in when the section stretched parallel to the axis PA after, i.e., in fig 5 a below the PA that parallels to the axis.Show shown in
In example, space D is then negative 2mm.Push rod 40, idler wheel 42 and cam disc 50 are consistent with Fig. 4 a in terms of remaining.
The first radial force F on first supporting member 31a is shown in figure 5bR1, D<0As curve 65 and show second
The second radial force F on supporting member 31bR2, D<0As curve 66.Two radial force FR1, D<0And FR2, D<0Sd is herein in its effect
In entire rotation angle range φ (from φ in terms of directionA=0 ° to φE=330 °) on it is mutually opposite and respectively its numerically
Greater than zero.In other words, push rod 40 is greater than always with numerical value on each supporting member 31a, 31b on entire rotation angle range
Zero radial force is extruded in the same direction.Thus can particularly simply constructing axial bearing 30, axial branch installs in other words
Set 30.Because only by each supporting member 31a, the respective side loaded by radial force 31b is designed to can receive radial force.It is horizontal
Make to be able to achieve supporting member 31a in other words to seeing side opposed respectively in longitudinal axis L A in principle and can cancel, 31b is described
The size of very little on side.Thus in fig 5 a in the case where the first supporting member 31a the first supporting member 31a in figure
As supporting member, just upside has been just enough enough and in the case where the second supporting member 31b for underlying side.
Pass through：Radial force FR1, FR2It is all not zero in entire rotation angle range, push rod 40 is in rotation angle range
On any position all will not loose ground in axial bearing 30, do not occur the variation in power direction yet.Even if thus in operation
Cam disc 50 91 and is usually moved along the second direction of rotation 92 and is still prevented in the case where quickly moving along the first direction of rotation
" the tumbling " of the push rod 40 and noise for thus advantageously reducing sending.Thus sending noise keep it is small while can be used compared with
Big manufacturing tolerance.
Pass through the cam disc-in the actuator 13 of the clutch for manipulating vehicle (such as car, lorry etc.) of proposition
Push-rod assembly can provide actuator 13, occur in the axial supporting arrangement of push rod in the case where the actuator especially small most
Big radial force.Abrasion and noise sending be reduced and actuator can abnormal cost advantageously manufacture and be made to small.
Claims (10)
1. it is a kind of for manipulating the actuator of vehicular clutch, including
-- the cam disc (50) that can be rotated around rotation axis (51),
-- it is supported on the push rod (40) in axial supporting arrangement (30), which has longitudinal axis (LA),
-- wherein, the axial direction supporting arrangement (30) includes at least one supporting member (31,31a, 31b), wherein the push rod
(40) there are first end (46), which couples at Coupling point (53) with the cam disc (40) on the first end,
So that causing the push rod (40) along the vertical of the push rod around the rotation of the rotation axis (51) by the cam disc (50)
The linear motion is passed to the clutch (27) by the linear motion of axis (LA),
Wherein, the actuator (13) is configured to：In order to which the clutch (27) is transformed into opening state from closed state (C)
(O), the cam disc (50) (91) will rotate along the first direction of rotation,
Wherein, the axial supporting arrangement (30) is arranged to relative to the rotation axis (51)：The longitudinal axis (LA) and flat
Row separates spacing (D) in parallel to the axis (PA) of the longitudinal axis (LA), wherein (PA) and the rotation axis of paralleling to the axis
(51) intersect.
2. actuator 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) sticks on the end face (54) in the point (52) that reclines,
Wherein, the point (52) that reclines is the Coupling point (53).
3. actuator according to claim 1 or 2,
Wherein, the radius (R) of the cam disc (50) is defined as from the rotation axis (51) to the Coupling point (53)
Away from,
Wherein, the cam disc (50) has the first radius (R1) in the case where the first rotation angle (φ 1), described to cause
The closed state (C) of clutch (27),
Wherein, the cam disc (50) has the second radius (R2) in the case where the second rotation angle (φ 2), described to cause
The opening state (O) of clutch (27),
Wherein, the cam disc (50) has between first rotation angle (φ 1) and second rotation angle (φ 2)
At least one first section (S1) and the second section (S2),
Wherein, the radius (R) of the cam disc (50) described in first section (S1) has basic about rotation angle (φ)
Upper constant first slope (m1),
Wherein, the radius (R) of the cam disc (50) described in second section (S2) has basic about rotation angle (φ)
Upper constant the second slope (m2),
Wherein, the first slope (m1) be greater than second slope (m2), at least the two of especially described second slope (m2)
It is big again.
4. according to claim 1 to one of 3 actuator,
Wherein, along first direction of rotation (91) in the rotation axis (51) and the axial supporting arrangement (30)
Between the section that extends when being observed, the longitudinal axis (LA) is arranged in described parallel to the axis before (PA).
5. according to claim 1 to one of 3 actuator,
Wherein, along first direction of rotation (91) in the rotation axis (51) and the axial supporting arrangement (30)
Between the section that extends when being observed, the longitudinal axis (LA) is arranged in described parallel to the axis after (PA).
6. according to the actuator of one of preceding claims,
Wherein, at least one described supporting member (31a, 31b) is made up of sliding bearing (34a, 34b).
7. according to the actuator of one of preceding claims,
Wherein, at least one described supporting member (31a, 31b) is made up of at least one track (32), and the track has slot
(33), the track is especially linear,
Wherein, at least one induction element (38) is disposed on the push rod (40), the induction element is in the slot (33)
In be guided,
Wherein, ball bearing device is especially equipped in the track (32).
8. according to the actuator of one of preceding claims,
Wherein, the push rod (40) has idler wheel (42), which has diameter (D1),
Wherein, the numerical value of the spacing (D) is between the 5% to 30% of the diameter (D1).
9. 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) rotates angle (φ in third3) at start,
Wherein, which rotates angle (φ3) it is greater than or equal to the second rotation angle (φ 2),
Wherein, the cam disc (50) has static radius (RR) in the static section (SR), to cause the clutch
(27) opening state (O),
Wherein, radius (R) about rotation angle (φ) first derivative in the static section (SR) it is substantial constant and
Equal to zero, or
Wherein, radius (R) about rotation angle (φ) first derivative in the static section (SR) less than zero, or
Wherein, radius (R) has in the static section (SR) from minus about the first derivative of rotation angle (φ)
It is worth the sign variation of the value greater than zero.
10. device according to claim 9,
Wherein, the static section (SR) extends past at least 30 ° of rotation angle range, especially extends past at least 40 °
Rotation angle range.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710338946.2A CN108869564A (en) | 2017-05-15 | 2017-05-15 | For manipulating the actuator of vehicular clutch |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710338946.2A CN108869564A (en) | 2017-05-15 | 2017-05-15 | For manipulating the actuator of vehicular clutch |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN108869564A true CN108869564A (en) | 2018-11-23 |
Family
ID=64320213
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710338946.2A Pending CN108869564A (en) | 2017-05-15 | 2017-05-15 | For manipulating the actuator of vehicular clutch |
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| Country | Link |
|---|---|
| CN (1) | CN108869564A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114728649A (en) * | 2019-12-05 | 2022-07-08 | 采埃孚商用车***欧洲有限公司 | Brake actuator, in particular electromechanical brake actuator for commercial vehicles |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102012200464A1 (en) * | 2011-02-25 | 2012-08-30 | Honda Motor Co., Ltd. | Control device for clutch drive mechanism |
| CN102939228A (en) * | 2010-03-16 | 2013-02-20 | 罗伯特·博世有限公司 | Brake booster |
| CN202971661U (en) * | 2009-11-19 | 2013-06-05 | 爱信精机株式会社 | Clutch actuator |
| WO2016188732A1 (en) * | 2015-05-26 | 2016-12-01 | Robert Bosch Gmbh | Torque and speed converter having a cam disc and a tappet, positioned to minimise transverse force, for actuating a clutch |
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2017
- 2017-05-15 CN CN201710338946.2A patent/CN108869564A/en active Pending
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN202971661U (en) * | 2009-11-19 | 2013-06-05 | 爱信精机株式会社 | Clutch actuator |
| CN102939228A (en) * | 2010-03-16 | 2013-02-20 | 罗伯特·博世有限公司 | Brake booster |
| DE102012200464A1 (en) * | 2011-02-25 | 2012-08-30 | Honda Motor Co., Ltd. | Control device for clutch drive mechanism |
| WO2016188732A1 (en) * | 2015-05-26 | 2016-12-01 | Robert Bosch Gmbh | Torque and speed converter having a cam disc and a tappet, positioned to minimise transverse force, for actuating a clutch |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114728649A (en) * | 2019-12-05 | 2022-07-08 | 采埃孚商用车***欧洲有限公司 | Brake actuator, in particular electromechanical brake actuator for commercial vehicles |
| CN114728649B (en) * | 2019-12-05 | 2023-11-17 | 采埃孚商用车***欧洲有限公司 | Brake actuator, in particular electromechanical brake actuator for commercial vehicles |
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Application publication date: 20181123 |