CN101065596B - Self-energising disk brake and control method for a self-energising brake - Google Patents
Self-energising disk brake and control method for a self-energising brake Download PDFInfo
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- CN101065596B CN101065596B CN2005800404413A CN200580040441A CN101065596B CN 101065596 B CN101065596 B CN 101065596B CN 2005800404413 A CN2005800404413 A CN 2005800404413A CN 200580040441 A CN200580040441 A CN 200580040441A CN 101065596 B CN101065596 B CN 101065596B
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Abstract
A portable gas grill for cooking food, consists of a substantially vertical housing; a substantially horizontal burner within the housing; a gas supply; a control valve connecting the gas supply to the burner; an igniter; and a substantially vertically oriented food retaining unit insertable into and removable from the housing above the burner.
Description
Technical field
The present invention relates to a kind of by the disk type braker of the structural type of reinforcement voluntarily.
Background technique
The break of reinforcement is known in diverse structure voluntarily.The structural type of the classics of the break of reinforcement is drum brake voluntarily, is provided with at this brake slipper with rising, makes that the frictional force between brake lining and drum is supported impacting force.
The opposite past, people were from following in disk type braker, promptly just in time embody the basic advantage of brake structural form, only perpendicular to around the brake lining of brake disc interlocking in do not produce the effect of reinforcement voluntarily, only an Effector that is parallel to the effect of brake disc axis is used on the described brake lining with the masterpiece of such orientation.This disk type braker for heavy more commerial vehicle is suitable more, handles in described commerial vehicle and preferably hydraulically or pneumatically carries out.
If but the disk type braker of the Effector with electronic promotion will be installed also in heavier commerial vehicle, the disk type braker of reinforcement becomes preferably so voluntarily, because it shows such possibility, promptly because the design of electrical motor of reinforcement voluntarily of break must be less than situation possible in the disk type braker of non-reinforcement voluntarily.
The disk type braker of reinforcement is known in diverse form of implementation voluntarily.But most of solution of describing is described such action principle, though described action principle allows reinforcement voluntarily, this action principle is usually owing to lack and be fit to actual conditions and because loaded down with trivial details structure is not suitable for realization for that produce, that can make the economically in batch disk type braker of reaching of heavy commerial vehicle and therefore often do not surmount the stage of theoretical consideration.
Summary of the invention
Before this background, the objective of the invention is to realize a kind of disk type braker of the dynamo-electric reinforcement voluntarily that moves, this disk type braker can made in simple structure at an easy rate.This disk type braker should also preferably provide advantage, and promptly because effective reinforcement voluntarily, the power demand of electronic drive unit is also minimum in the compass of coefficient of friction of brake linings with respect to the break of comparable direct electro-mechanical manipulation.
The present invention proposes a kind of by the disk type braker of the structural type of reinforcement voluntarily, the actuator that comprises electricity, wherein the steering force that is applied by actuator is strengthened by means of a step-up system voluntarily that is arranged between actuator and the brake lining, has following feature: a compressing unit, this compressing unit be used for carry out brake lining under the situation that compresses motion of brake disc at least one brake lining of brake disc one side compression, this compresses motion can resolve at least one component motion that is parallel to the brake disc spin axis and at least one component motion that tangentially extends with respect to the brake disc spin axis; At least one electronic drive unit is used to handle compressing unit as actuator; It is characterized in that: compressing unit designs like this, makes it compress between moving period a kind of motion that the same rotation of the output shaft of electronic drive unit is converted to brake lining, and this motion component motion on tangential direction at least is non-linear; Motor directly or by at least one or a plurality of driving mechanism rotates a crank as electronic drive unit, this crank has a crank pin, this crank pin is used to make the brake lining unit to be tangential to brake disc and promptly is parallel to brake disc friction surface ground motion, and crank pin is parallel to brake disc axis ground and extends and be embedded in the opening of the corresponding orientation in pressing plate.
The present invention realizes the design of compressing unit like this, make this compressing unit compress between moving period a kind of motion that the same rotation of the output shaft of electronic drive unit is converted to brake lining, this motion component motion on tangential direction (direction U) at least is non-linear.
Not only reduce manufacturing price by the present invention for the braking equipment of commerial vehicle, and because effective reinforcement voluntarily, the power demand of dynamo-electric drive unit also significantly reduces in the compass of coefficient of friction of brake linings with respect to the break of comparable direct electro-mechanical manipulation.Even can obviously reduce power demand with respect to the design of non-reinforcement voluntarily by especially favourable deformation program.
Also possible at this is relatively to satisfy identical power requirements with the compressed air brake in modern times and also make identical predetermined installation conditions and weight setting value become reasonable.
Also can utilize adjustable ramp system, so that realize a reliably and also self-adjusting Parking Brake in the friction piece that shrinks owing to cooling.Therefore another main advantage of the present invention is, also realizes the parking braking of reliable action under the situation of not additional essential control member by the disk type braker of suggestion.
Must determine like this in this ramp angle, make that reinforcement is also still possible voluntarily when the minimum lining mu of considering with maximum reinforcement voluntarily.
Thereby in the break of inserting, obtain the only maintenance effect of machinery of break.When brake lining and/or brake disc shrink or during stop phase, occur carrying out the automatic adjustment of break and carrying out the adjustment of the reinforcement voluntarily of break when friction factor descends, static so that vehicle keeps.
Preferred electronic drive unit is connected with a control gear and/or controlling device, and this control gear and/or controlling device are designed for control or regulate the position of adjusting element or brake lining.In this position according to the set point adjustment brake lining unit of higher level unit (for example controller).
Control gear and/or controlling device are preferably as follows operation:
The preferred basis of regulating design is that vehicle braked is regulated or lagged behind and regulates, and is adjusted in the vehicle that current EBS with pneumatic braking equipment regulates as this and uses always.
Driver or the predetermined braking expectation of Vehicular system automatically or the brake expectation or the expectation that lags behind in this braking equipment, this expectation is converted into the signal of " braking ", this signal is by the EBS system handles and convert the control corresponding of wheel braking actuator (pneumatic linear actuator or motor) to, and this causes a corresponding braking maneuver.
In the disk type braker of air-operated control, carry out the simple pressure control of the manipulation cylinder of corresponding break usually, because retardation pressure=＞cylinder power=＞tension force=＞it is accurate or confirmable and reproducible that the pass of frictional force ties up in the enough narrow boundary.
Adjusting accuracy enough between parameter and the frictional force at actuator in the break of the electro-mechanical manipulation of reinforcement voluntarily no longer provides usually.
Often adopt motor current as this electromechanical voluntarily the actuator of the break of reinforcement adjust parameter.But by for example also disperseing (Streuung) to obtain the like this big error of obtainable braking action with friction factor that the efficient and the last efficient of reinforcement machinery voluntarily of the moyor of temperature correlation, reduction gearing mechanism combine brake lining, the control of feasible braking action by motor current seems impossible.
Advised directly determining and regulated frictional force (WO 03/100282 or later break EP 0 953 785 B1) for known reinforcement voluntarily with wedge-type Effector.
Problem is in this method, finds the measure that is fit to that is used for determining frictional force.Obtain such difficulty in addition, promptly frictional force with very strong degree by break vibration and unsteadiness of wheels is affected and from but the adjusting parameter that may be difficult to control.
Therefore should find for the regulating method of the break of reinforcement voluntarily, this method also is fit to be subjected to the disk type braker of load especially well and avoids regulating relevant problem with frictional force.
In a word in order to solve described purpose, the present invention realizes a kind of method of the break of reinforcement voluntarily that is used to control, one of them is strengthened by means of a step-up system voluntarily that is provided with between actuator and brake lining by the steering force that actuator applies, wherein actuator is connected with a control gear or controlling device, this control gear or controlling device are designed for controlling actuator, so that regulate the position of brake lining unit, it is characterized in that: when regulating, determine and compensation under the situation of the wheel drag of regulating by braking system by the braking force that error causes poor (be called the 3rd and regulate parameter).
The present invention also realizes a kind of method that is used to carry out parking braking, comprise a kind of by break of the present invention, wherein only compress by means of spool with simple mode break when the parking braking, make the liner unit move on the dish up to rolling element, therefore acting under the situation that does not have cranker of reinforcement adopted voluntarily always.
Adopt that as far as possible existed and reliable and verified sensed system at this in order to be identified for regulating required signal.
First kind of deformation program at first is discussed
Solution was regulated parameter in 1: the three
The solution that describes below is set a braking system, regulate parameter " braking or lag behind " and actuator at vehicle and adjust and introduce one the 3rd between the parameter " electric current or actuator position " and regulate parameter in this braking system, the 3rd regulates parameter, and to be identified for compensating the braking force that is caused by error basically under the situation of the wheel drag of being regulated by braking system poor.
Compare for definite individually the 3rd adjusting parameter of each wheel and with the value of on other wheel, determining.
It is for the setting value (motor current or actuator position) of each break modifying factor that correspondingly superposes, poor when the setting value with the EBS system has unallowed deviation with the braking force that this modifying factor compensation exists.
This adaptation procedure is undertaken by a plurality of braking maneuvers with smaller step size in case of necessity.
Regulate the wheel slip that parametric optimization is analyzed corresponding wheel as the 3rd.
In this method, unexpectedly needn't be created in the accurate relation between wheel slip and the braking force, but the wheel slip special parameter that obtains only is adapted to the setting rating value of determining (Sollwertvorgabe) of EBS system on each wheel.Especially the wheel slip special parameter that as far as possible accurately adapts to the break of each at this.The coordinated with each other of the wheel slip special parameter of each carried out under the situation of consideration for the different in case of necessity setting value of the braking system of each in second step.
The tension force that also can determine selectively to act on break is as the 3rd adjusting parameter.Tension force fix on really break load member for example on the brake calipers measurement by deformation stroke or component stress be possible.Can be arranged on brake inside and be integrated in case of necessity in the control electronic equipment that is arranged in the break at this required sensor.
Solution 2: the control by means of actuator position or motor current combines with error compensation
Second solution is based upon on the basis of adjusting algorithm of existence of current EBS system, and wherein only actuator is adjusted pressure value and adjusted parameter by another system specific (systemspezifisch) and replace.Especially provide actuator position and motor current as the specific adjustment parameter of system.
Mentioned bigger error dispersion in the comment of prior art, this error disperses to make the application of this method to become difficult.So must be breaking at the error effect that exists in the effect chain to a great extent.
This preferably uses the measure effect below one or more:
● the air clearance overcomes by regulating device before the manipulation of brake actuator, makes the air clearance not be re-used as error source when the real braking feed movement by brake actuator begins and exists.
● the influence of the brake lining compression that state of wear is different with state of temperature compensates to the setting rating value of braking system by modifying factor.Accurately determine the state of wear of two brake lining for each break at this.Same by analyzing break energy balance (Energiebilanz) thus determine the enthalpy of this break and also definite brake lining temperature.The analysis of energy balance can be carried out by electric brake system or by electric control device integrated in break.
● the relation of tension force-pincers expansion disperse when break assembles, to compensate because of break different (bremsenindividuell) by calibration process.The actuator adjustment stroke that for example on assembly line, loads and determine in the expansion of this generation or need directly to determine for this reason with the power of determining during final inspection at this brake calipers.The power of determining applies preferably carries out like this, make in brake calipers, for example replace brake disc and adopt the load device and then control be used to produce the actuator of predetermined tension force.The relation of determining like this of tension force-actuator position can for example be kept in the electronic equipment integrated in break now.
● when adopting motor current to adjust parameter as actuator, described error compensation is used in an identical manner.The pass of tension force-motor current ties up to and determines in the calibration process and preservation as described above then.In calibration process, also eliminate and be used for the driving mechanism of room temperature condition and the error effect of motor at least.On the motor for example the temperature effect on the permanent magnet at this motor can compensate by means of above-mentioned heat Balance Calculation again.Really the normal force that causes of fixed position is relevant with many factors for step-up system voluntarily, as:
● current air clearance
● perpendicular to the rigidity of the break (pincers) of friction surface
● the variable rigidity of liner especially, described rigidity depends on:
Zero liner position
Zero state of wear, i.e. residual thickness
Zero temperature
Development (Vorgeschichte) (to compressible influence) before zero
Zero hygroscopicity
● the temperature of the variation of pincers and dish during braking
● the friction factor between brake lining and brake disc (thereby to reinforcement effect voluntarily and to normal force promptly also to the influence of frictional force).This also depends on itself:
Zero temperature
Zero speed
If give no thought to the influence of described parameter, instruction so according to the present invention is used to realize that the control targetedly of the slope position of the impacting force determined almost is impossible.
On the contrary becoming possible by the present invention in simple mode is, by step-up system or brake lining voluntarily follow the tracks of targetedly control can realize the liner impacting force of an expectation and can abandon frictional force from the rating value to the actual value can the difficult compensation that realizes, perhaps but the rating value/actual value by liner impacting force or frictional force relatively allow a control in advance targetedly for break.
By this following realization of the present invention, promptly interference volume compensates by the parameter of considering to be correlated with, the coherence of this interference volume influence between slope position or liner position and liner impacting force.
Determine characteristic curve at this, this characteristic curve is determined corresponding impacting force by step-up system (for example slope) voluntarily or by the position of the predetermined adjustment stroke of actuator.
This characteristic curve preferably continues realization, so that for example can consider the influence as temperature and speed.
Brake lining for example reclining a little on brake disc determined by means of the electric current of the actuator of electricity or by the calculating of current air clearance and slope geometrical shape.
The characteristic gradient and slope position or liner position adapt to relatively:
A) perpendicular to the rigidity of the break (pincers) of friction surface
Can be by experiment or by calculating definite and almost being constant.
B) the variable rigidity of liner especially, this rigidity depends on:
Zero liner position
Perhaps the explanation by in tolerable scope or by when liner is changed
Input/the selection of the relevant parameter in the sub-controller.
Zero state of wear, i.e. residual thickness
Sensing (prior art) continuously
Zero temperature
Perhaps by measure or by calculated example as by means of energy integral, cooling power etc.
Development (to compressible influence) before zero
The record of brake lining history (wearing out) is for example by means of energy integral, maximum temperature etc.Can by experience determine liner rigidity and aging between relation.
C) temperature of the variation of pincers and dish during braking
Perhaps calculate by measuring (for example thermoelement) or passing through.
D) friction factor between brake lining and brake disc (thereby to reinforcement effect voluntarily and to normal force promptly also to the influence of frictional force).
This itself depends on as inferior:
Zero temperature
Zero speed
The determining by experience of coherence.
Selectively or additionally, break also can be regulated by determining the normal force that acts between liner and the dish.This normal force for example can be determined by the sensing that pincers strut.If the actual normal force and the normal force of expectation depart from, this normal force can be adaptive by means of displacement-Li-characteristic curve of describing so.
Compressing unit or compress the slope and can constitute pressure ramp, pulling force slope or tension and compression slope definitely by an angle.Especially advantageously select self-locking system as drive unit under the situation on tension and compression slope, promptly a higher power that causes by a high/low unusually friction factor on steering can not cause the out of contior of slope to move.
Described disturbance variable compensation also can be for the system applies of direct manipulation (control surface=supporting surface)
As deformation program independently and also set as further scheme of the present invention, motor directly or by at least one or a plurality of driving mechanism rotates a crank, this crank has a crank pin as drive element, this crank pin is used to make the brake lining unit motion, and wherein crank pin is parallel to the brake disc axis orientation.This layout constitutes compactly and can realize simple in structurely.
Have a driven shaft at this preferred motor, this driven shaft is parallel to directed and this driven shaft in brake disc axis ground directly or the transmission component rotary crank by connecting in the middle of other, and this crank affacts on the brake lining unit.
If each pressure side of at least two or the changeable spool of more a plurality of preferred axial lengths own is being provided with a groove with slope shape profile on the side of brake lining unit, rolling element is corresponding to be embedded in this groove, this rolling element is bearing on the slope shape profile of pressure side of spool on the one hand and is bearing on the other hand on the brake lining unit, and the break of reinforcement can be used especially many-sidedly and regulate reliably so voluntarily.Suitablely at this be that described at least one the electronic drive unit or another the electronic drive unit that are used to handle compressing unit are designed to be used in addition drive spool, are used to change the axial length of spool at least.
In addition according to another deformation program independently of the present invention, compressing unit have at least one especially two or even more a plurality of spool (adjustment piston), described spool be parallel to the directed and described spool in brake disc axis BA ground the one end be bearing in by a bearing device on the brake calipers or one with member that brake calipers is connected on, this bearing device correspondingly allows at least one parts of spool to rotate around the longitudinal axis of this spool.
Advantage below obtaining in a word (respectively for itself and also in combination):
● the simple circumference by crank is handled
The driver element of coaxial setting
Preferred integrated control electronic equipment
● the simple combination that screw-operated and crank are handled
The force-stroke of the function that reclines by screw mandrel-by crank
By screw mandrel recline and the crank of adaptive brake-when high loading is braked is handled
Parking braking function by screw mandrel
● reliable and uncomplicated parking braking function
By screw mandrel pretension-by boosting system in the tensioning more automatically that does not have under the crank manipulation situation
The additional tensioning of handling by crank more in case of necessity
Connect the ramp angle of high reinforcement
● utilize common drive unit
Convertible distribution driving mechanism
Automatically the conversion function that reclines of screw mandrel (only by)
Outside connect (by the parking braking function and the partial load braking function of screw mandrel)
● variable reinforcement voluntarily
Multistage, convertible
Stepless, adaptive and/or external control automatically
● the in check self-locking of spool
By being locked into the in check of no self-locking operation and the automatic conversion under error condition certainly
A) connection of the prime of the screw mandrel of self-locking and a no self-locking (collapsible slope, ball formula slope etc.)
B) screw mandrel of no self-locking and a connection that produces the prime (gear stage of self-locking etc.) of self-locking
● gapless drive unit
Be used for getting rid of until the Path of Force Transfer of liner pressing plate the measure in gap from drive motor.
Description of drawings
Describe the present invention below with reference to accompanying drawing in detail by means of embodiment.Wherein:
Fig. 1-3 shows corresponding sketch, and each sketch is pressed the theory structure of the formal description of sectional view by the different distortion scheme of disk type braker of the present invention,
Fig. 4 shows another sketch of the principle function of the disk type braker be used to describe Fig. 1 to 3,
Fig. 5 shows that another presses the sketch as sectional view of disk type braker of the present invention,
Fig. 6 shows the different view of the part area of pressure plunger, has the pressure elements that is used to abut on the brake lining unit in Fig. 6 a.
Embodiment
Shown conception plans is described below with its key character.
At first describe the principle of work and power of Fig. 1 in detail, be included in the nonadjustable ramp slope on the pressure side 5,6 of spool.
Fig. 3 shows that a kind of deformation program with ramp rate that can stepless adjustment and Fig. 2 show a kind of deformation program that the ramp slope that level adjusts can be arranged that has then.Fig. 4 combines with Fig. 1 and describes the fundamental function principle.
Preferably be contemplated that the basis with fixing jaw type by disk type braker of the present invention, the brake calipers 1 (being also referred to as brake casing) of one of them single-piece or multi-part type is not fixed on the wheel shaft with respect to a brake disc 2 with not moving.The basis of the design that describes below is a fixedly caliper brake with wearing and tearing regulating device outside electro-mechanical manipulation and electrical adjustment to a certain extent.Action principle and described feature in principle for other brake structural form for example slide caliper brake or the swing caliper brake also be adoptable.Only the compressing unit of the electromechanics of reinforcement replaces the binding clip that comprises brake control device of the basic break of machinery/air-operated control by having voluntarily.The fixedly caliper brake of the hold down gag of an air-operated control with this mode for example shows in DE 36 10569 A1, DE 37 16 202 A1 or EP 0 688 404 A1.Fixedly caliper brake with electric adjusting apparatus shows in WO 02,/14 708 A1.The suggestion embodiment in (if desired) this electric adjusting apparatus can be set on the reaction side respectively.
Brake calipers 1 is only represented in it compresses the zone of side in Fig. 1.In fact the preferred frame shape of this brake calipers ground surrounds the top circumferential area of brake disc and is fixed on one on this sightless shaft flange.
Brake calipers 1 is at its spool 5,6 (is two at this) that has one or more preferred two openings 3,4 and have a respective amount on the side of the brake disc 2 with a brake disc spin axis, and it is directed that described spool is parallel to brake disc axis BA ground.
According to Fig. 1 to 4 two spools parallel to each other 5,6 are set respectively.
Two spools 5,6 or adjust piston respectively directly or the element (is Sliding bush 9,10 at this) by middle connection be bearing on the rear wall that deviates from brake disc 11 of brake calipers.Preferred spheres 7,8 is used as bearing device with Sliding bush 9.
Bearing device designs like this, makes them allow spool 5,6 or adjustment piston to rotate around the longitudinal axis L A of himself.
In spool 5,6 and in brake calipers, constitute (domed) groove of ball section shape respectively at this, wherein Sliding bush 9,10 is presented in one of them groove (in this is presented to groove in the brake calipers), makes ball 7,8 to rotate with respect to Sliding bush.
Replace ball and groove, (not the describing at this) such as supportings of the sliding bearing on plane or annular also can be considered.
Spool 5,6 has one respectively and is provided with externally threaded screw mandrel 12, and a nut 13 with sleeve shape of corresponding internal thread rotatably is set on this screw mandrel.That described screw thread can constitute non-self-locking according to the different situations of design or self-locking.
Entire mechanism is towards the pressing plate tensioning selectively.
According to Fig. 1 to 4, the nut 13 of each spool 5,6 is arranged on the side of brake disc and screw mandrel 12 is arranged on the side of brake calipers inside.Opposite configuration also is (not the describing at this) that can consider.
Can adjust axial length of each spool 5,6 that constitutes like this by nutting 13 on screw mandrel 12, for example be used to compensate brake pad wear and under liner clings to situation on the brake disc 2.
Spool 5,6 (is nut 13 at this) promptly is respectively equipped with the groove or the profile 14 of a slope shape on the side of brake disc at it on its pressure side, its deepest point is preferably placed in the scope of longitudinal axis of spool.
This especially preferably in Fig. 6 as seen.According to Fig. 6, two each other " tracks " or profile 14a, the 14b of half-twist be arranged in the nut 13 of spool 5,6, described profile has angular aperture α 1, the α 2 with respect to the different sizes of longitudinal axis L A respectively.When break compresses, with 90 ° of rotations, can utilize one or another profile 14a, 14b by spool 5,6 (being nut 13 perhaps) around its longitudinal axis at this, this causes the different characteristic (following also description in more detail) of break.
Groove or tracks 14 constitute with constant angular aperture or the ramp angle α with respect to longitudinal axis L A conically, but perhaps for example preferably press for example form formation of elliptic cone profile of changeable conical surface profile according to a kind of especially preferred deformation program, its ramp angle α with respect to the longitudinal axis L A of spool 5,6 for example has level ground (Fig. 6) or changes continuously on circumferencial direction (with respect to the longitudinal axis L A of spool).
In groove 14, embed rolling element 16 respectively, in preferred construction, constitute ball 16 at this this rolling element.
Selectively according to a kind of selectable form of implementation, for example columniform or can consider with the rolling element (for example bucket) that other mode forms, they for example roll on the groove of the flute profile in spool then.But therefore as below becoming apparent may not be all forms of implementation that in Fig. 1 to 3, provides of the present invention be attainable.But the embodiment who has a groove in pressure side according to the form of Fig. 1 is attainable.
Rolling element 16 rabbet on it deviates from the side of brake disc that different situations according to the structure of rolling element 16 constitute at this in the domed Sliding bush 17, described Sliding bush is inserted in the groove of the corresponding moulding in pressing plate 18, this pressing plate abuts on the support plate 19 of the brake lining that compresses side 20 with brake lining material 21, this brake lining in brake calipers 1, be parallel to brake disc spin axis BA and on circumferencial direction U (perhaps tangential or be parallel to tangential) be provided with movingly with respect to brake disc 2.
Under making the situation of pressing plate 18 at pretension, the fastening spring 22 between pressing plate 18 and the nut 13 remains on the nut 13.Can consider also that selectively pressing plate is otherwise for example in upward tensioning of housing (pincers).
The drive motor 23 of electricity is used to drive break, a preferred reduction gearing mechanism 24 is arranged on this drive motor back, and the driven shaft 25 of this reduction gearing mechanism affacts another driving mechanism that is arranged on the center between the screw mandrel 26 especially on the planetary gear mechanism.
At the sun gear 27 of these driven shaft 25 driving planetary gear mechanisms 26, this sun gear drives planet wheel 28.Planet wheel 28 (not describing in detail) and sun gear 27 and a ring internal tooth and external tooth 29 engagements at this.According to the different situations (convertibility is not described in detail at this) of transition status, this planet wheel make planet type star polygon work (Planetenstern) 33 or encircle 29 the rotation.Ring 29 is with its outer toothed portion and gear 30 engagements, and described gear 30 is installed on the screw mandrel 12 or is molded on the described screw mandrel.
For conversion driving device (for example motor) automatically, a ball seat loop mechanism (not describing at this) that is subjected to spring load can be set.Transfer process also can otherwise realize (for example electromagnetism).
Being provided with one on the axially-extending line of the star type star polygon work 33 of being expert at is cylindrical formation and crank 34 that be parallel to the setting of brake disc axis at this, that this crank constitutes by an Off center ground (prejudicially) on the side of brake disc 2 at it, be parallel to the directed abreast crank pin 35 of brake disc axis BA equally and be embedded in the corresponding opening 36 in the brake lining unit, its split shed 36 has for example corresponding with the cross section of crank pin 35 cross section, but perhaps chute shape ground long hole shape ground formation (at this for example perpendicular to plan) especially for example.
Changeable adjustment piston of length or spool 5,6 constitute in order to wear and tear adjustment by two for Effector or compressing unit in the embodiment in figure 1, they have groove 14 by the form of ramp profile on the pressure side of brake disc 2 at it, rolling element 16 moves on described groove, and this rolling element will be delivered on the brake lining unit by the impacting force that break produces or be delivered on the pressing plate that is positioned on the brake lining.
Rolling element 16 holds by the slope profile (not describing at this) that constitutes on the contrary in the pressure side of brake lining unit or pressing plate 18, perhaps (preferred, because rolling element guides especially reliably, in this description) in sliding bearing bed (Sliding bush 17), hold.
The brake lining unit so flexibly presses against spool and adjusts on the piston 5,6, this brake lining unit constitutes at this single-piece or multi-part type by brake lining 20 and pressing plate 18, makes the rolling element 16 that is provided with between them flexibly be clamped between brake lining unit and the spool.
The manipulation of break is parallel on the sense of rotation of friction surface at this brake disc of brake disc after brake lining 20 clings to the process that reclines on the brake disc or mobile the carrying out on the circumferencial direction together with brake lining 20 by pressing plate.
This move preferably produces by crank mechanism 35,36, and this crank mechanism compresses in the housing (brake calipers) 1 roughly to be bearing at pressing plate 18 effects of brake lining unit 18,20 and the spin axis that is parallel to brake disc at the center with crank pin 35 from untie-sell and at this.
The motor 23 that the drive unit of the manipulation of crank mechanism by electricity for example has rearmounted driving mechanism 24 carries out.
Fig. 1 is characterised in that a constant ramp angle α.Therefore realize an especially simple structure, the characteristics of this structure are firm structure, good safety in operation and lower manufacturing price.Can adopt the motor 23 of minimum output power especially.Provide ball 16 as cheap rolling element at this, this rolling element itself is directed on ramped surfaces to a certain extent.Also can in the raceway groove that is fit to, move in order to improve the bearing capacity ball.
A kind of deformation program that has as the roller of rolling element 16 has an especially little hysteresis (not describing at this) on the contrary.
The difference of the deformation program of Fig. 2 and Fig. 1 at first is, the ramp angle of groove 14 be not constant on the circumferencial direction of the longitudinal axis of adjusting nut or brake piston 5,6, but transformable, make that there are different steep ramp angle α in the different situations according to the rotation of nut 13.Be provided with the different gradients at this for different rotation situation ball tracks.
Compressing characteristic at this changes in simple mode, because nut 13 for example rotates by the adjustment actuator 39 (for example another less motor) of an independent preferred electromechanical structure form, this adjustment actuator is by driven shaft 40 swivel nuts 13 with gear 41, for example should adjust at this that actuator for example drives this nut on the outer toothed portion of the flange of a nut 13 therein by follower 41 and another nut 13 drives by belt drive unit 42, this belt drive unit twines two nuts 13.
The obtainable degree of reinforcement voluntarily of Fig. 1 to 2 also can improve in the compass of friction factor.But conversion only can be carried out under releasing orientation, because nut 13 can not rotate during the compressing of break.
According to Fig. 3, ramp angle tangentially changes continuously around the longitudinal axis L A of spool 5,6.It is adaptive that this is used for automatic angle.
Be connected between the crank 34 and first planetary gear mechanism 26 on the one hand and be arranged on center between the spool again at this second other planetary gear mechanism 37 that axially staggers in first planetary gear mechanism 26, this second planetary gear mechanism has a driven torus 38 that is driven by planet wheel 43, this driven torus drives the nut 13 of external tooth, and the planet type star polygon work 44 of this planetary gear mechanism drives crank again or makes this crank around its longitudinal axis rotation on the contrary.
In this operation below when braking compresses is possible:
This braking compresses resolved into the next stage:
1. overcome the air clearance,
2. set up braking force,
3. release brake,
4. adjusting air clearance.
Stage 1: overcome the air clearance
Initial situation is as follows before braking.
Crank 34 on zero-bit (Fig. 1) at first, this crank for example keeps (not describing at this) by means of the ball seat circle that is subjected to spring load on this zero-bit.
Adjust nut 13 and load by means of pressure spring 32 usefulness friction torque or holding torque in this case, it is all the time greater than the screw mandrel friction torque.
Drive motor 23 rotary screw 12 on the sense of rotation of feeding at first.Block at this journey star type star polygon work 33 crank by stop in follower 26.Ring 29 external gear or internal tooth and external tooth rotates on direction of feed adjusts screw mandrel 12, abuts on the brake disc 2 up to brake lining 21.
Adjust nut 13 at this and prevent rotation by sufficiently high holding torque.
Adjust screw mandrel by the reaction force of setting up then or spool 5,6 is blocking on preferred (but whether indispensable) movable brake disc 2 (but axial motion under the situation in fixation clamps), this brake disc abuts on the liner of reaction side (not describing at this).
Stage 2: set up braking force
Because the adjustment screw mandrel 12 that blocks, the driving moment on crank 34 rise now so greatly, make this crank be unclamped by stop position.
The component motion of this brake lining (be parallel to the brake disc friction surface) in a circumferential direction or tangentially go up or the tangential U that is parallel to crank pin show as nonlinear because on the circular track of crank pin at first in a circumferential direction than the motion time per unit in the past of crank pin 35 on its circular track through bigger stroke.Driving mechanism with crank mechanism designs like this, makes be not the linear motion that converts brake lining on the motor with in the angular motion in a circumferential direction from untie-sell, but converts the motion of hysteresis to.
Now three kinds of situations are distinguished.
Situation 1
Current coefficient of friction of brake linings enough accurately is equivalent in groove 14 or the tangent at the inclination angle, slope in the pressure side of adjusting nut 13.
Preposition expends realization by only less adjustment power in this case.
Current coefficient of friction of brake linings is obviously greater than in groove 14 or the tangent at the inclination angle, slope in adjusting the pressure side of nut 13.
By excessive reinforcement voluntarily, brake lining 20 rotatablely moves than stronger under the situation corresponding to the precalculated position and driven further by brake disc.
Applying a rotating force to crank 34 by brake lining on the moving direction of brake disc 2.
Because the drive motor 23 of electricity makes the sun gear 27 of the planetary gear mechanism 26 and second planetary gear mechanism 37 remain on the nominal position, so thereby thereby the rotation of the continuation of the planet type star polygon work 44 of the crank 34 and second driving mechanism 37 produces external gear or outer shroud 38 internal tooth and external tooth and two rotations of adjusting nut 13 of second driving mechanism 37.
Overcome two holding torques of adjusting nut 13 at this.
By adjusting the rotation of nut 13, the slope inclination alpha that works changes on the direction of the reinforcement voluntarily that reduces, up to the friction factor of the enough accurately adaptive current brake lining of the reinforcement voluntarily that works.
If current coefficient of friction of brake linings is significantly less than the tangent of the slope inclination alpha in the groove 14 on adjusting the pressure side of nut 13, brake lining is driven deficiently by less reinforcement voluntarily so.Therefore a higher relatively driving moment needs that become on crank 34 are so that brake lining 20 is moved.
Because the reaction running torque that works on the hollow wheels of driving mechanism 24 is adjusted screw mandrel 5,6 and is rotated on the direction of the raising of reinforcement process voluntarily, enough accurately coordinates with coefficient of friction of brake linings again up to the tangent of the slope inclination alpha that works.
Stage 3: release brake
For release brake, thereby crank 34 and brake lining 20 are got back on the stop position by the drive motor of electricity.
Power demand essential for this reason on crank is less because voluntarily reinforcement in braking process before by adaptive.
When snapping onto on the stop position, crank 34 produces a torque sudden change.
By analyzing service data (for example rotating speed, the power consumption) arrival of stop position as can be known of electric drive motor.
Stage 4: the adjusting of air clearance and control thereof
Because crank 34 force-closed ground stop now, driving mechanism 26 is activated again when the upside-down motion of the continuation of the drive motor 23 of electricity, adjust screw mandrel 12, the air clearance that is used for release brake and is used to produce the amount of determining by the rotation back now of this driving mechanism.
Cling on the brake disc 2 by brake lining in the phase I 20, realize the control of air clearance, and by realize the adjusting of air clearance from the reversion of determining of this position.
The analysis of the position signal of the drive motor by electricity after the air clearance is regulated attrition value determine the possibility that becomes.
Explain the given possibility that when reversion, is used to brake below tout court.
Braking when reversion:
By the measure that is fit to for example the corresponding analysis of the rotation signal by wheel speed sensor (for example abs sensor) on the break/interior advance and reversion distinguishing on this controller of not describing or on the controller a higher level of braking system at one, this controller is connected with motor and/or controls this motor.
Be controlled at stage 1 end by braking and on corresponding to the sense of rotation of brake disc sense of rotation, control crank 34 afterwards.Observe the present invention from other directions below.
Go through the basic principle of the Fig. 1 with nonadjustable ramp slope at first again.In order to realize that this form of implementation at first has a groove 14 of slope form in spool 5,6 realization is necessary.
It is rotatably mounted in liner pressing plate 18 to constitute a corresponding slope or (better) rolling element 16 accordingly in liner pressing plate 18, and perhaps the slope constitutes in liner pressing plate 18 and rolling element bearing (is not described at this) in spool.
For rolling element 16 in the starting of the groove of the nut 13 of spool 5,6 and in order to make brake lining 20 move towards brake disc, essential is, liner pressing plate and brake lining in a circumferential direction move preferably by one coaxial in the brake disc longitudinal axis and be parallel to the adjustment element (is crank 34 at this) that this brake disc longitudinal axis is provided with and realize.Nut 13 does not preferably rotate during real braking process.
Two-way slope profile in spool 5,6 (on the circumferencial direction U and opposite with this circumferencial direction) on two direction of travel, allow boosting function voluntarily at this.
Preferably crank mechanism 14 drives by the motor 23 with rearmounted driving mechanism 24,26.
What can consider is an independent drive unit that is used for spool to be set, perhaps but feasible adjustment drive unit and crank driving device combine (Fig. 1 and Fig. 2).The latter has advantage, promptly only needs a unique drive motor that is used for two kinds of functions.
Also can consider at this, carry out overcome (stage 1 of functional description) of air clearance by independent adjustment drive unit.
Carrying out the air clearance by means of especially " steep slope " by crank driving device when moving beginning equally overcomes and can consider.
Two-way slope profile (groove 14) in spool 5,6 allows boosting function voluntarily at this on two direction of travel.The control relevant with the wheel sense of rotation that liner moves is attainable.
According to Fig. 3, groove 14 or the slope in spool constitute the hollow body of similar truncated cone.Rolling element is bearing in again in the pressing plate 18.Therefore the adaptive rotation by spool 5,6 of ramp slope and lining mu is possible.The rotation of spool 5,6 by an independent drive unit 39 or automatically the driving mechanism 26 by a branch carry out, this driving mechanism make in driven rotatablely moving by rotatablely moving of producing of drive motor 23 can be delivered on the crank 34 and the whirligig 12 of spool 5,6 on.
The driving mechanism 26 of branch is a planetary gear mechanism preferably.One the locomotivity that works of becoming on the crank pin 35 (during at too small reinforcement voluntarily the brake lining unit by crank 34 move or during at excessive reinforcement voluntarily crank 34 by the pulling of brake lining unit) cause the moment of reaction in the driving mechanism 26 in branch, this moment of reaction is made every effort to, and rotatablely moves producing on the input shaft and/or on spool 5,6.If on input shaft, apply a sufficiently high confining force (for example by drive motor, this drive motor keeps the position of input shaft by its electronic control) now, on spool 5,6, be rotated so.
When the sense of rotation of adjusting piston 5,6 adapts to the direction that affacts the power on the crank pin suitably, ramp slope (the liner unit spurs on crank pin) when excessive reinforcement voluntarily rotates through steep ramp angle, and (crank pin moves the liner unit) adjusted smooth ramp angle when too small reinforcement voluntarily, promptly on the direction that reinforcement increases voluntarily.
In the scheme that has the ramp slope that the level adjustment can be arranged, be provided with the slope track of at least two different gradient that are provided with angledly.This rolling element again sliding bearing on liner pressing plate 18.
The adaptive of ramp slope and lining mu undertaken by spool 5,6 being transformed into after braking process before on the better adaptive ramp slope, the necessity of conversion wherein occurs.
The rotation of spool 5,6 is by an independent drive unit or automatically for example be similar to above-mentioned carrying out suchly.
Transfer process just activates after end of braking, wherein by driving mechanism affact adjustment on the spool rotatablely move flexibly be stored in the transmitting element and when the release brake because the rotation that reduces again then of spool hinders just carries out.
Hinder rotation can by because braking force affacts that frictional force on the screw mandrel produces or since confining force produce, described confining force by electricity drive motor or the coupling device of a connection for example the coupling device of an electromagnetism be applied to spool originally on one's body or be applied on the element of transfer unit or described confining force preferably by ball or rolling element and by means of the braking force of transmitting by spool, the bearing of the shape sealing in slope track (raceway groove) and the holding torque of position generation that is eccentric in the existence at spool center, described ball or rolling element are positioned in the track of slope outside the center of spool in braking process.
The structure of the raceway groove of slope track is carried out with such form aptly, makes in the scope of less impacting force to be that groove depth is less and realizes a bigger groove depth that is used to obtain than high bearing capacity towards the direction of the outer diameter of spool in the scope of less eccentricity of ball or rolling element.
Possibility is in this scheme, and it still is possible directly changing during braking process in less braking force scope.Ball or rolling element just have such position in the raceway groove of slope when higher braking force occurring, and the conversion during braking on this position no longer is possible.
Preferably adopt a crank mechanism in order to drive the brake lining unit.Replacing other clamping element of crank mechanism also is to consider as eccentric etc., if they cause the nonlinear motion in a circumferential direction of brake lining unit.
The control of dynamo-electric break is respectively by means of carrying out at the computing unit on the break or for example carry out by means of the computer of the higher level who is used for one or more breaks on vehicle, and each computing unit is networked in case of necessity.
Selectively, the drive unit of a linearity similarly can be considered in the structure to a great extent.Replace crank pin and be installed on the live axle at this gear segment, this gear segment is embedded in the tooth bar in the portion of the liner back side (not describing at this).
But preferably adopt nonlinear drive unit.
Fig. 5 shows that this disk type braker is equivalent to the embodiment of Fig. 1 to a great extent by another deformation program of the disk type braker of reinforcement voluntarily of the present invention.
As in the embodiment in figure 1, changeable adjustment piston of length or spool 5,6 constitute in order to wear and tear adjustment by two for Effector or compressing unit, they have groove 14 by the form of ramp profile on the pressure side of brake disc 2 at it, rolling element 16 moves on described groove, and described rolling element will be delivered on the brake lining unit by the impacting force that break produces or be delivered on the pressing plate that is positioned on the brake lining.
A convertible coupling device additionally is set, at this for example is a magnetic coupling device 46, especially the coupling device that has the regulating magnet of bistable effect, this coupling device constitutes like this, but makes that for example in the radial teeth portion 48 of axial motion crank 34 being transformed into the Transmitted chains neutralization breaks from Transmitted chains.For example for parking braking at first or even can only brake by spool 5,6, but perhaps for example can be only the change of axial length of rotation by spool 5,6 or spool carry out less adaptive brake.If introduce one " normally " operation braking on the contrary, change coupling device so and brake by crank 34.
As a supplement, be provided with a conversion equipment 47 that is used for the rotation brake plunger, turn to other tracks 14b by tracks 14a at this nut according to Fig. 5.Conversion equipment 47 can constitute independent motor or but constitute conversion magnet etc., it for example by tooth bar etc. with one of them nut 13 half-twist, another nut 13 for example drives by gear ring.Passable in a kind of such device.
Also be noted that the also especially advantageously classification aspect its control characteristic of current brake structural.
If for example carrying out normal force regulates, this normal force is regulated and is not thought available by prior art as unique adjusting, so advantageously effect is, for example be bearing on the brake calipers normal force and can very accurately determine (power that is parallel to the longitudinal axis of spool) by spool because for example corresponding sensor is arranged on the spool and/or the element of adjacency on.
Reference numerals list
1 caliper
2 brake discs
3,4 openings
5,6 spools
7,8 fulcrum balls
9,10 Sliding bushes
11 rear walls
12 screw mandrels
13 nuts
The groove of 14 slope shapes
15 grooves
16 rolling elements
17 Sliding bushes
18 pressing plates
19 support plates
20 brake lining
21 brake lining materials
22 fastening springs
23 drive motors
24 reduction gearing mechanisms
25 driven shafts
26 driving mechanisms
27 sun gears
28 planet wheels
29 rings
30 gears
31 flanges
32 pressure springs
33 planet type star polygon work
34 cranks
35 crank pins
36 openings
37 driving mechanisms
38 rings
39 adjust actuator
40 driven shafts
41 gears
42 belt drive units
43 planet wheels
44 planet type star polygon work
45 gear rings
46 magnetic coupling devices
47 conversion equipments
The α ramp angle
The LA longitudinal axis
The U circumferencial direction
BA brake disc axis
Claims (39)
1. press the disk type braker of the structural type of reinforcement voluntarily for one kind, comprise the actuator of electricity, wherein the steering force that is applied by actuator is strengthened by means of a step-up system voluntarily that is arranged between actuator and the brake lining, has following feature:
A) compressing unit, this compressing unit be used for carry out brake lining (20) under the situation that compresses motion of brake disc (2) in brake disc (2) one at least one brake lining of side compression (20), this compresses motion can resolve at least one component motion that is parallel to brake disc spin axis (BA) and at least one component motion that tangentially extends with respect to brake disc spin axis (BA);
B) at least one electronic drive unit is used to handle compressing unit as actuator;
It is characterized in that:
C) compressing unit designs like this, makes it compress between moving period a kind of motion that the same rotation of the output shaft of electronic drive unit is converted to brake lining (20), and this motion component motion on tangential direction (U) at least is non-linear;
D) motor (23) directly or by at least one driving mechanism (24,26,37) rotates a crank (34) as electronic drive unit, this crank has a crank pin (35), this crank pin is used to make the brake lining unit to be tangential to brake disc and promptly is parallel to brake disc friction surface ground motion, and crank pin (35) is parallel to the brake disc axis and extends (BA) and be embedded in the corresponding directed opening in pressing plate (18).
2. by the described disk type braker of claim 1, it is characterized in that: compressing unit designs like this, makes it compress between moving period the motion of a kind of hysteresis on tangential direction (U) at least that the rotation of the output shaft of electronic drive unit (23) is converted to brake lining (20).
3. by claim 1 or 2 described disk type brakers, it is characterized in that: compressing unit has at least one spool (5,6) in addition, described spool be parallel to directed (BA) and the described spool of brake disc axis at the one end by a bearing device (7,8; 9,10) be bearing in brake calipers (1) go up or be bearing in one with member that brake calipers (1) is connected on, at least one parts of this bearing device permission spool rotate around the longitudinal axis (LA) of this spool.
4. by the described disk type braker of claim 3, it is characterized in that: spool (5,6) is provided with a pressure side at it on the side of brake lining unit, this pressure side has a groove (14) that has the slope shape profile, and rolling element (16) is corresponding to be embedded in this groove.
5. by the described disk type braker of claim 4, it is characterized in that: rolling element (16) is embedded into respectively in the corresponding groove in addition, promptly is embedded in the groove with corresponding geometrical shape in brake lining unit (18,20,21).
6. by the described disk type braker of claim 3, it is characterized in that: rolling element (16) is embedded into respectively in the ramp profile in brake lining unit (18,20,21), and rolling element bearing is in spool.
7. by the described disk type braker of claim 4, it is characterized in that: rolling element constitutes ball (16) and groove (14) cone-shaped ground constitutes.
8. by the described disk type braker of claim 4, it is characterized in that: rolling element constitutes ball (16) and groove constitutes tracks.
9. by the described disk type braker of claim 4, it is characterized in that: rolling element (16) constitutes roller and groove (14) slope shape or wedge shape ground and constitutes.
10. by the described disk type braker of claim 4, it is characterized in that: groove (14) two-way wedge shape ground or cone-shaped ground constitute.
11. by the described disk type braker of claim 10, it is characterized in that: the groove of cone-shaped (14) has a constant angular aperture (α) with respect to spool longitudinal axis (LA) on the circumferencial direction of spool longitudinal axis (LA).
12. by the described disk type braker of claim 10, it is characterized in that: the groove of cone-shaped (14) has an angular aperture (α) with respect to the variation of spool longitudinal axis (LA) on the circumferencial direction of spool longitudinal axis (LA).
13. by the described disk type braker of claim 10, it is characterized in that: the groove of cone-shaped (14) has an angular aperture (α) that level ground is arranged or change continuously with respect to spool longitudinal axis (LA) on the circumferencial direction of spool longitudinal axis (LA).
14. by the described disk type braker of claim 5, it is characterized in that: Sliding bush (17) is presented in the groove in the pressing plate (18) of brake lining unit (18,20).
15. by the described disk type braker of claim 3, it is characterized in that: two spools (5,6) deviate from the inside that is bearing in brake calipers (1) on the end of brake disc (2) by the bearing device of brake calipers at it respectively.
16. by the described disk type braker of claim 3, it is characterized in that: spool (5,6) has one respectively and is provided with externally threaded screw mandrel (12), and nut (13) can be rotatably set on this screw mandrel with the internal thread of correspondence.
17. by the described disk type braker of claim 16, it is characterized in that: each nut (13) pass respectively one in the shut in brake calipers or on brake calipers opening (3,4) and on it deviates from the side of brake disc, have a flange (31), wherein between the inwall of flange (31) and brake calipers (1), pressure spring (32) is set respectively.
18. by the described disk type braker of claim 3, it is characterized in that: compressing unit has two spools (5,6).
19. by claim 1 or 2 described disk type brakers, it is characterized in that: the brake lining unit has described pressing plate (18), this pressing plate abuts on the brake lining support plate (19) of brake lining (20).
20. by the described disk type braker of claim 15, it is characterized in that: described bearing device is the sliding bearing device on fulcrum ball (7,8) or plane, annular guided bearing device.
21. by the described disk type braker of claim 3, it is characterized in that: the opening (36) in pressing plate (18) is arranged on the center between two spools (5,6).
22. by claim 1 or 2 described disk type brakers, it is characterized in that: opening (36) the chute-type ground in pressing plate (18) constitutes.
23., it is characterized in that: be provided with another drive unit or another adjustment actuator (39), be used to drive the screw mandrel (12) or the nut (13) of spool (5,6) by the described disk type braker of claim 16.
24. by claim 1 or 2 described disk type brakers, it is characterized in that: be provided with spring (32), described spring by nut towards brake lining unitary elasticity ground pretension brake calipers.
25. by the described disk type braker of claim 16, it is characterized in that: be provided with a convertible driving mechanism (26), this driving mechanism is used for changing motor (23) between in order to the position that drives crank (34) and the position in order to the screw mandrel (12) of rotation brake plunger (5,6).
26., it is characterized in that: be provided with a ball seat loop mechanism that is subjected to spring load that is used for automatically changing motor by the described disk type braker of claim 25.
27. by the described disk type braker of claim 25, it is characterized in that: driving mechanism (26) is a planetary gear mechanism.
28. by the described disk type braker of claim 12, it is characterized in that: be provided with such device, this device is used for being provided with the automatic spin orientation of the spool (5,6) at transformable tapered opening angle (α) in groove (14).
29. by the described disk type braker of claim 28, it is characterized in that: the device that is used for the orientation of spool constitutes other driving mechanism.
30. by the described disk type braker of claim 28, it is characterized in that: the self-orientating device that is used for spool constitutes the other drive unit with motor.
31. by claim 1 or 2 described disk type brakers, it is characterized in that: the brake calipers of disk type braker is a fixation clamps.
32. by claim 1 or 2 described disk type brakers, it is characterized in that: independent regulating device is set with compressing on the opposed side, side at brake disc.
33. by claim 1 or 2 described disk type brakers, it is characterized in that: the brake calipers of disk type braker is swing pincers or sliding clamp.
34. by claim 1 or 2 described disk type brakers, it is characterized in that: electronic drive unit is connected with a control gear and/or controlling device as actuator, thereby this control gear and/or controlling device are designed to control or regulate the position of adjusting element and the position of controlling or regulate brake lining.
35. by the described disk type braker of claim 3, it is characterized in that: the opening (36) in pressing plate (18) constitutes slotted hole, this slotted hole extends perpendicular to a plane by two spools (5,6).
36. by the described disk type braker of claim 23, it is characterized in that: it is another motor that described another drive unit or another are adjusted actuator (39).
37. by each described disk type braker of claim 28 to 30, it is characterized in that: the device that is used for the automatic spin orientation of spool (5,6) is used for the spin orientation of the nut (13) of spool.
38. by the described disk type braker of claim 28, it is characterized in that: described automatic spin orientation and friction factor are realized relatively.
39. by the described disk type braker of claim 29, it is characterized in that: described other driving mechanism constitutes other planetary gear mechanism.
Applications Claiming Priority (7)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102004050065 | 2004-10-13 | ||
| DE102004050065.7 | 2004-10-13 | ||
| DE102005015408.5 | 2005-04-04 | ||
| DE102005015408 | 2005-04-04 | ||
| DE102005030617A DE102005030617A1 (en) | 2004-10-13 | 2005-06-30 | Disc brake in self-reinforcing design and control method for a self-energizing brake |
| DE102005030617.9 | 2005-06-30 | ||
| PCT/EP2005/010447 WO2006042620A1 (en) | 2004-10-13 | 2005-09-28 | Self-energising disk brake and control method for a self-energising brake |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101065596A CN101065596A (en) | 2007-10-31 |
| CN101065596B true CN101065596B (en) | 2010-09-22 |
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ID=38965709
Family Applications (4)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2005800404413A Expired - Fee Related CN101065596B (en) | 2004-10-13 | 2005-09-28 | Self-energising disk brake and control method for a self-energising brake |
| CNB2005800404428A Expired - Fee Related CN100561004C (en) | 2004-10-13 | 2005-09-28 | Press the disk type braker of the structural type of reinforcement voluntarily |
| CN2005800405030A Expired - Fee Related CN101065598B (en) | 2004-10-13 | 2005-09-28 | Self-energising disk brake and control method for a self-energising brake |
| CN2005800405026A Expired - Fee Related CN101065597B (en) | 2004-10-13 | 2005-09-28 | Self-energising disk brake and control method for a self-energising brake |
Family Applications After (3)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005800404428A Expired - Fee Related CN100561004C (en) | 2004-10-13 | 2005-09-28 | Press the disk type braker of the structural type of reinforcement voluntarily |
| CN2005800405030A Expired - Fee Related CN101065598B (en) | 2004-10-13 | 2005-09-28 | Self-energising disk brake and control method for a self-energising brake |
| CN2005800405026A Expired - Fee Related CN101065597B (en) | 2004-10-13 | 2005-09-28 | Self-energising disk brake and control method for a self-energising brake |
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| Country | Link |
|---|---|
| CN (4) | CN101065596B (en) |
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| EP2327902B2 (en) * | 2008-07-04 | 2019-06-26 | KNORR-BREMSE Systeme für Nutzfahrzeuge GmbH | Brake pad for a self-energising disc brake |
| CN102454728B (en) * | 2010-10-25 | 2013-08-21 | 赵宝瀛 | Brake device |
| GB201105236D0 (en) * | 2011-03-29 | 2011-05-11 | Meritor Heavy Vehicle Braking | A brake adjuster mechanism |
| JP2012237408A (en) * | 2011-05-12 | 2012-12-06 | Tbk:Kk | Disk brake device |
| DE102015211409B4 (en) * | 2015-06-22 | 2023-02-02 | Robert Bosch Gmbh | parking brake in a vehicle |
| JP6490309B2 (en) * | 2016-05-30 | 2019-03-27 | 三菱電機株式会社 | Brake device automatic stroke adjustment mechanism |
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| CN107299947A (en) * | 2017-06-28 | 2017-10-27 | 无锡英捷汽车科技有限公司 | It is a kind of to increase Cheng Zhusai certainly |
| WO2019198272A1 (en) * | 2018-04-11 | 2019-10-17 | 日立オートモティブシステムズ株式会社 | Disc brake and planetary gear deceleration mechanism |
| IT201800006685A1 (en) * | 2018-06-26 | 2019-12-26 | Vehicle brake | |
| CN109058327B (en) * | 2018-10-08 | 2024-01-26 | 山东云宇机械集团有限公司 | Brake half shaft device for engineering machinery drive axle |
| DE102019112005A1 (en) * | 2019-05-08 | 2020-11-12 | Stabilus Gmbh | Braking device, method for controlling the braking device |
| DE102019113139A1 (en) * | 2019-05-17 | 2020-11-19 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Device and method for current control of an actuator |
| CN110206836B (en) * | 2019-06-18 | 2021-05-25 | 天津瑞源电气有限公司 | Spring-loaded brake wear detection system and detection method thereof |
| CN112145582B (en) * | 2019-06-28 | 2021-11-12 | 比亚迪股份有限公司 | Disc brake, brake-by-wire system and vehicle |
| KR102644871B1 (en) * | 2019-07-16 | 2024-03-07 | 현대모비스 주식회사 | Parking brake apparatus for vehicle |
| JP7268658B2 (en) * | 2020-07-29 | 2023-05-08 | トヨタ自動車株式会社 | Wear amount estimating device, wear amount estimating method, and wear amount estimating program |
| CN113320507B (en) * | 2021-06-01 | 2022-09-23 | 华为数字能源技术有限公司 | Braking device and automobile |
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| EP0153265A1 (en) * | 1984-02-10 | 1985-08-28 | Goodyear Aerospace Corporation | Electrically actuated aircraft brakes |
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| DE50313257D1 (en) * | 2002-05-28 | 2010-12-23 | Estop Gmbh | ERROR SAFETY CONCEPT FOR A SELF-REINFORCED ELECTROMECHANICAL BRAKE |
| DE10226035A1 (en) * | 2002-06-12 | 2003-12-24 | Bosch Gmbh Robert | Brake, especially disc brake |
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2005
- 2005-09-28 CN CN2005800404413A patent/CN101065596B/en not_active Expired - Fee Related
- 2005-09-28 CN CNB2005800404428A patent/CN100561004C/en not_active Expired - Fee Related
- 2005-09-28 CN CN2005800405030A patent/CN101065598B/en not_active Expired - Fee Related
- 2005-09-28 CN CN2005800405026A patent/CN101065597B/en not_active Expired - Fee Related
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0153265A1 (en) * | 1984-02-10 | 1985-08-28 | Goodyear Aerospace Corporation | Electrically actuated aircraft brakes |
| CN86101461A (en) * | 1985-03-09 | 1986-10-29 | 鲁卡斯工业公共有限公司 | The improvement of self-energising disc brakes |
| US6008604A (en) * | 1995-07-21 | 1999-12-28 | Robert Bosch Gmbh | Electric motor wheel brake for vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| CN101065597B (en) | 2011-03-30 |
| CN101175930A (en) | 2008-05-07 |
| CN101065597A (en) | 2007-10-31 |
| CN101065598A (en) | 2007-10-31 |
| CN100561004C (en) | 2009-11-18 |
| CN101065598B (en) | 2010-12-08 |
| CN101065596A (en) | 2007-10-31 |
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