EP1623138A1 - Frein automobile hydraulique - Google Patents

Frein automobile hydraulique

Info

Publication number
EP1623138A1
EP1623138A1 EP04731179A EP04731179A EP1623138A1 EP 1623138 A1 EP1623138 A1 EP 1623138A1 EP 04731179 A EP04731179 A EP 04731179A EP 04731179 A EP04731179 A EP 04731179A EP 1623138 A1 EP1623138 A1 EP 1623138A1
Authority
EP
European Patent Office
Prior art keywords
brake
housing
brake piston
piston
fluid chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP04731179A
Other languages
German (de)
English (en)
Inventor
Leo Gilles
Marcus Janson
Ralf Leiter
Gregor Poertzgen
Ralf Erben
Karl-Heinz Schaust
Manfred Meyer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ZF Active Safety GmbH
Original Assignee
Lucas Automotive GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Lucas Automotive GmbH filed Critical Lucas Automotive GmbH
Publication of EP1623138A1 publication Critical patent/EP1623138A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T7/00—Brake-action initiating means
    • B60T7/02—Brake-action initiating means for personal initiation
    • B60T7/08—Brake-action initiating means for personal initiation hand actuated
    • B60T7/10—Disposition of hand control
    • B60T7/107—Disposition of hand control with electrical power assistance
    • 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
    • F16D65/00—Parts or details
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
    • F16D65/18—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes
    • 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
    • F16D2121/00—Type of actuator operation force
    • F16D2121/02—Fluid pressure
    • 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
    • F16D2121/00—Type of actuator operation force
    • F16D2121/14—Mechanical
    • 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
    • F16D2123/00—Multiple operation forces
    • 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
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/20—Mechanical mechanisms converting rotation to linear movement or vice versa
    • F16D2125/34—Mechanical mechanisms converting rotation to linear movement or vice versa acting in the direction of the axis of rotation
    • F16D2125/36—Helical cams, Ball-rotating ramps

Definitions

  • the present invention relates to a hydraulically actuated vehicle brake with a housing, a brake piston accommodated in the housing, to which a brake lining is attached, a blocking device for locking the brake piston within the housing and an actuating device for controlling the blocking device, the brake piston being connected to the housing fluid chamber limited, which is chargeable with hydraulic fluid, so that the brake piston for actuating the vehicle brake hydraulic within the housing along a Kolbenlteils- axis publisher ⁇ e ⁇ bar is, wherein the blocking means comprises at least a ramp assembly and relative to the housing displaceable blocking element, and wherein by means of the Actuating device, the blocking element can be displaced in interaction with the ramp arrangement for locking the brake piston within the housing and can be coupled to the brake piston.
  • Such a vehicle brake is already known.
  • the generic European patent EP 0 403 635 B1 shows a vehicle brake of this type.
  • the brake piston in an operating braking situation, the brake piston is displaced within the housing by charging the fluid chamber with hydraulic fluid, and the brake lining is thereby pressed onto a rotating brake disc in order to brake it.
  • hydraulic fluid is discharged from the fluid chamber, so that the brake piston with the brake lining attached can move back into its starting position.
  • a lever provided on the blocking device is pivoted by means of a Bowden cable which can be displaced via a hand lever or a pedal.
  • the pivoting of the lever has the effect that the ramp arrangement spreads within the housing and thus executes a lifting movement in the direction of the piston longitudinal axis.
  • This lifting movement is transmitted to the blocking element, which then presses against the action of a return spring on the brake piston and axially displaces it.
  • the lever of the blocking device is again brought into its starting position, whereupon the ramp arrangement shifts back from its spread position to its starting position. Under the action of the return spring, the blocking element also moves together with the brake piston into its initial position, so that the brake lining releases the brake disc.
  • Actuating forces applied to the pedal must be relatively large if a reliable parking brake effect is to be ensured. In addition, from today's point of view, it is uncomfortable for a driver to apply the forces required to activate the parking brake effect purely mechanically by means of a hand lever or a pedal.
  • EP 0 551 397 B1 shows a hydraulically actuable vehicle brake in which, in order to activate the parking brake function, the brake piston is first displaced hydraulically and then a blocking rod is driven by an electric motor until it contacts the brake piston.
  • the blocking rod is provided with an external thread which engages with an internal thread provided in the housing.
  • the interlocking threads are self-locking, so that mutual rotation between the blocking rod and the housing is prevented when an axial force acts on the blocking rod.
  • the hydraulic fluid is drained out of the chamber again.
  • the brake piston tries to move back to its starting position, which he does but is hindered by the locking rod attached to it.
  • the brake is in its parking brake position.
  • the fluid chamber is again supplied with hydraulic fluid, so that the blocking rod is released by the brake pistons. Then it can be moved back to its starting position via the electric motor. The hydraulic fluid can then be drained out of the fluid chamber again, so that the brake piston can move back into its starting position which is free from braking.
  • a vehicle brake is known from US Pat. No. 6,505,714 Bl, in which the parking brake function can be activated by a motor, a spring element being introduced into the clamping force path, which can compensate for changes in the clamping path.
  • a vehicle brake of the type described at the outset in which the actuating device has a motor drive which is coupled in terms of drive to the ramp arrangement in such a way that the blocking element, when the motor drive is activated, locks and releases the brake piston within the housing relocated.
  • the vehicle brake is therefore equipped with a motor-driven actuation device which makes it unnecessary for the driver to apply the clamping force required to activate the parking brake function in a purely mechanical manner in an uncomfortable manner.
  • the parking brake function can be activated electronically, ie at the push of a button or on the basis of an automatic operating situation detection.
  • the invented Vehicle brake according to the invention that the actual displacement of the brake piston with its brake lining also takes place hydraulically when the parking brake function is activated and - if necessary - the actuating device merely causes an increase in the clamping force in addition to the hydraulically generated clamping force.
  • the blocking device also has the function of locking the brake piston in its axial position achieved by the hydraulic displacement, so that a sufficiently high clamping force can be maintained which ensures a reliable parking brake function even in the case of elastic and thermal dimensional changes in the components incorporated in the tensioning path.
  • the motor drive it can be provided that it is designed as a rotary drive, for example a conventional rotary electric motor can be used.
  • the actuating device has an eccentric arrangement, by means of which the motor drive is coupled to the ramp arrangement.
  • the eccentric arrangement can have an eccentric disc coupled to the motor drive and a swivel lever coupled to the ramp arrangement, the swivel lever sliding on the eccentric disc when the motor drive is activated and thereby pivoting.
  • a suitable choice of the shape of the eccentric disk and the outer contour of the pivoting lever can achieve a desired course of the clamping force.
  • the outer contour of the eccentric disc and the swivel lever to have contour sections which lock the eccentric disc and swivel lever with respect to one another, so that an unintentional release of the parking brake function is blocked.
  • the motor drive can also be designed as a linear drive. This can be achieved, for example, in that a rotary drive is coupled to a screw drive which converts the rotary movement into a linear movement.
  • a development of the invention provides that the actuating device has a lever arrangement, by means of which the motor drive is coupled to the ramp arrangement.
  • the motor drive can comprise an electric motor.
  • the motor drive it is possible for the motor drive to comprise a solenoid if it is designed as a linear drive.
  • the design of the motor drive in the form of a hydraulic motor, in particular in the form of a hydraulically controllable piston-cylinder arrangement, is also possible within the scope of the invention.
  • the ramp arrangement has at least one first ramp surface which is attached to the housing or is coupled to it in a rotationally fixed manner, and has at least one second ramp surface which is formed on a ramp component which is displaceable relative to the housing and is coupled to the blocking element is, when the motor drive is activated, the two ramp surfaces slide against one another to displace the blocking element.
  • the invention provides that rolling elements are provided between the at least one first ramp surface and the at least one second ramp surface, by means of which the at least one first ramp surface is in contact with the at least one second ramp surface.
  • Such a ramp arrangement behaves in such a way that the second ramp surface, which can be displaced relative to the housing, executes an axial movement with respect to the housing.
  • This axial movement can be used to displace the brake piston in the direction of its longitudinal piston axis and thus apply it to a brake disc.
  • a plurality of complementary ramp surfaces preferably cooperate, which are each designed in a complementary manner on the housing and on the ramp component. Balls or rollers, for example, are suitable as rolling elements.
  • the brake piston in a service brake situation the brake piston can be displaced within the housing by charging and emptying the fluid chamber with hydraulic fluid and that in a parking brake situation the brake piston is first displaced within the housing by charging the fluid chamber with hydraulic fluid, then the Actuating device for locking the brake piston is actuated, the blocking element being advanced to the brake piston and finally hydraulic fluid being discharged from the fluid chamber for reducing the pressure in the fluid chamber.
  • the fluid chamber is supplied with hydraulic fluid until the blocking element is released from the brake piston, then the blocking element is removed from the brake piston via the blocking device and finally for a pressure reduction in the fluid chamber Hydraulic fluid is discharged from the fluid chamber.
  • the clamping force applied via a hydraulic actuation and displacement of the brake piston can be used to apply and apply the brake lining to the brake disc.
  • the clamping force applied via the actuating device can be additively superimposed on the hydraulically applied clamping force.
  • axial force component that is mechanically exerted on the brake piston in addition to the hydraulically generated axial force component is greater in magnitude or equal to a minimum axial force by which the component to be braked by the brake piston applied axial force is reduced after the brake piston locks and the hydraulic fluid is discharged from the fluid chamber. After hydraulic fluid has been removed from the fluid chamber, the clamping force is still large enough to ensure a reliable parking brake effect.
  • the clamping force applied according to the invention is still large enough. to ensure a reliable parking brake effect.
  • the invention further relates to a method for actuating a vehicle brake of the type described above, wherein in a service braking situation the brake piston is displaced within the housing by the fact that hydraulic fluid is supplied to or removed from the fluid chamber, and that in a parking brake situation the brake piston is first loaded by the Fluid chamber with hydraulic fluid is displaced within the housing, then the actuating device for locking the brake piston is actuated, the blocking element being delivered to and pressing on the brake piston, and finally hydraulic fluid being discharged from the fluid chamber for pressure reduction in the fluid chamber.
  • the axial force component that is mechanically exerted is selected in such a way that its magnitude is greater than or equal to a minimum axial force by which the brake piston brakes on one
  • the axial force exerted on the component is reduced after the brake piston has locked and the hydraulic fluid has been removed from the fluid chamber.
  • the minimum taxi force can be calculated, for example, from the difference between the
  • Elasticity modules of the components involved in the hydraulic displacement of the brake piston and of the components involved in the mechanical actuation of the actuating device are determined.
  • the fluid chamber is supplied with hydraulic fluid until the blocking element is at least partially relieved or released by the brake piston, then the blocking element is removed from the brake piston via the blocking device and, finally, hydraulic fluid is removed from the fluid chamber for pressure reduction in the fluid chamber.
  • FIG. 1 shows a three-dimensional view of a first exemplary embodiment of a vehicle brake according to the invention
  • FIG. 2 shows a longitudinal section through the vehicle brake according to FIG. 1;
  • Fig. 3 is a front view of the vehicle brake shown in Fig. 1;
  • FIG. 4 shows a graph which shows the course of the hydraulic pressure in the fluid chamber and the course of the clamping force for an exemplary activation of the parking brake function
  • FIG. 5 shows a graph corresponding to FIG. 4 with a different activation of the parking brake function
  • FIG. 6 shows a three-dimensional view of a second exemplary embodiment
  • FIGS. 6 and 7 shows a longitudinal section of the embodiment according to FIGS. 6 and
  • FIG. 8 is a front view of the embodiment of FIG. 6.
  • a vehicle brake according to the invention is generally designated 10. This is carried out with a housing 12 in which a brake piston 14 is received.
  • the brake piston 14 is mechanically coupled at its right end in FIG. 2 to a brake lining carrier 16, to which a brake lining 18 is attached.
  • Another brake pad 20 is located opposite the brake pad 18 and is attached to a corresponding brake pad carrier 22.
  • the brake pad carriers 16 and 22 are accommodated in the housing 12 in a conventional manner according to the floating caliper principle. This means that when the brake pad carrier 16 is displaced along the piston longitudinal axis A in FIG. 2 to the right, there is a complementary displacement of the brake caliper carrier 22 along the piston longitudinal axis A in the direction in FIG.
  • the vehicle brake 10 further comprises a blocking device 24, by means of which the brake piston 14 can be locked in different axial positions on the longitudinal axis A of the piston.
  • the blocking device 24 comprises a ramp arrangement 26 with a ramp disk 28, which is fixed to the housing 12 by means of a bolt 30. On the ramp disk 28 fixed to the housing, three trough-like ramps are formed which are elongated in the circumferential direction and each receive a spherical expansion body 34.
  • the spreading bodies 34 cooperate with a respective ramp of a ramp component 32.
  • This ramp component 32 has a shaft section 36, at the end of which a polygonal or multi-groove profile 38 is formed.
  • a pivot lever 40 of an actuating device 42 is positively placed on this polygonal or multi-groove profile 38 and mechanically secured with a lock nut 44.
  • the pivot lever 40 is - as shown in FIGS. 1 and 3 - curved and has a pitch curve 46. Via the pitch curve, the pivot lever 40 comes into contact with an eccentric disk 48, which is mounted on a motor shaft 50 of an electric motor which is formed with the housing 12 and can be controlled via the electrical connections 52. More specifically, the eccentric disk arrangement 48 has two plates 54 and 56, between which an end face 58 runs, which defines the eccentric path with respect to the motor shaft 50, on which the rolling curve 46 of the pivoting lever 40 rolls.
  • the ramp component 32 At its end facing away from the pivot lever 40, the ramp component 32 has a head 60 which contacts an axial pressure bearing 62.
  • the thrust bearing 62 is designed as a plain bearing, but can equally be designed as a roller bearing, for example as an axial needle bearing.
  • the ramp component 32 is supported in the axial direction against the pressure formed by the expansion bodies 26 via the thrust bearing 62 on an abutment 64 which is formed like a head on one end of a threaded bolt 66.
  • the threaded bolt 66 is screwed to a threaded bushing 70 by means of a steep thread pairing 68, which is self-locking and which has a precisely defined thread play, and together with this forms a strut arranged coaxially with the piston 14 and the bolt 30, the effective length of which corresponds to the gradually progressing one Pad wear of the brake pads 18 and 20 can be increased.
  • the threaded bushing 70 is designed as an auxiliary piston and is displaceably guided in a corresponding auxiliary cylinder bore 72 in the piston 14. The end of the threaded bushing 70 facing one end of the piston 14 is sealed by a base plate 74.
  • the part of the auxiliary cylinder bore 72 bounded by this base plate 74 and the end face of the piston 14 is connected to an outer groove 78 of the piston 14 by a radial relief channel 76 so that it always remains depressurized.
  • One end of a bellows 80 is received in the groove 78 and connects the end of the piston 14 protruding from the housing 12 to the housing 12 and thereby protects the inside of the housing 12 from contamination.
  • a spring washer arrangement 86 with axial pretension is arranged within the piston 14 between the flange 82 and a locking ring 88 which is locked in the piston 14.
  • the spring washer assembly 86 normally holds the flange 82 in contact with the inner cone 84 and thereby prevents the threaded bushing 70 from rotating with respect to the piston 14.
  • the piston 14 in turn is normally prevented from doing so by conventional means, for example by its interaction with the brake lining carrier 16 to turn.
  • a sleeve-like or cage-like insert 92 is arranged within the housing 12 in a fluid chamber 90 enclosed by the housing 12 and the piston 14 and is fastened to the housing 12 against axial displacement and against rotation.
  • the insert 92 is designed, for example as a deep-drawn part made of sheet metal, in such a way that the threaded bolt 66 is secured against rotation by the insert 92 without being prevented from axial displacements.
  • the insert 92 has a plurality of longitudinal grooves 94, in each of which a radial projection 96 of the abutment 62 engages.
  • a return spring 98 in the example shown a helical wire spring, is supported with one end; its other end is supported on the inside of the insert 12 fixed to the housing.
  • the return spring 98 is pretensioned with a certain force of, for example, 50 kp, so that it strives to hold the ramp component 32 in its position closest to the housing-fixed ramp disk 28, the rest position.
  • the vehicle brake 10 functions as follows: In a service braking situation in which a rotating brake disk which is present between the brake linings 18 and 20 but is not shown in the figures is to be braked, the fluid chamber 90 is charged with hydraulic fluid and the brake piston 14 is thereby displaced within the housing 12. As long as this displacement is not greater than the thread play existing in the high-helix pair 68 between the threaded bolt 66 and the threaded bushing 70 and which corresponds to the intended brake-air play, the threaded bushing 70 completely carries out the displacement of the brake piston 14; the spring washer arrangement 86 does not yet yield.
  • the pressure in the fluid chamber 90 also acts on the threaded bushing 70 designed as an auxiliary piston.
  • the axial forces exerted by the spring washer arrangement 86 and by the hydraulic pressure on the threaded bushing 70 are overall greater than the force which the return spring 98 applies the abutment 64 formed on the threaded bolt 66 exercises.
  • the return spring 98 is therefore no longer able to hold the threaded bushing 70 in place.
  • the flange 82 cannot lift off the inner cone 84.
  • the threaded bushing 70 is thus prevented from rotating, the brake application therefore takes place without readjustment. Only when the hydraulic pressure has dropped below the above-mentioned threshold value of 20 bar, for example, can an adjustment be made up if this has become necessary due to advanced wear of the brake pads 18 and 20.
  • the threaded bolt 66 is displaced to the right in FIG. 2 while the return spring 98 is deformed.
  • the force transmitted in this case is transmitted to the threaded bushing 70 via the high-pitch thread pairing 68.
  • the hydraulically generated force component F 3 and the force component generated via the ramp arrangement are additively superimposed, so that a clamping force Fi results at time t 2 .
  • the pressure of the value pi is reduced again by discharging hydraulic fluid from the fluid chamber 90 until finally the hydraulic pressure in the fluid chamber 90 again assumes the value po.
  • the assembly - formed from threaded bushing 70, threaded bolt 66, ramp component 32 and expansion body 26 - blocks a return movement of the piston 14 and thus largely holds it in its axial position.
  • the parking brake function is thus activated.
  • the clamping force F decreases from the value Fi to the value F 2 .
  • the brake piston 14 presses in this state with the clamping force F 2 on the brake disc, not shown, and holds it against rotation.
  • the drop in force from the force value Fi to the force value F 2 can be explained by the fact that after reducing the hydraulic pressure within the fluid chamber 90, the system relaxes slightly elastically and that the brake piston 14 thereby moves slightly back towards its starting position. However, this restoring movement is so small and the clamping force Fi is large enough to be able to maintain a clamping force F 2 which is sufficient to prevent the brake disc from being inadvertently pressed even after the hydraulic pressure in the fluid chamber 90 has been completely reduced to the value p 0 Secure rotation.
  • the spreading of the ramp arrangement 26 is canceled at time t4 by actuating the actuating device 42 with an adequately powerful electric motor, as shown in FIG. 4, so that the threaded bolt 66 together with the threaded bushing 70 are displaced back into their starting positions.
  • the brake piston 14 can move back into its starting position according to FIG. 2 until it finally reaches it at the time t 5 .
  • the clamping force F decreases continuously between the times t 4 and ts.
  • the clamping force F is thus based on the The value F of 12 kN, which is generated by the hydraulic pressure within the fluid chamber 90 of approximately 120 bar, is increased to a value Fi of 14 kN. At time t 3 , the pressure p is then reduced to 0 bar. The clamping force also drops to the value F 2 of 7.7 kN, which means that the clamping force decreases by 6.3 kN.
  • the hydraulic pressure can be increased again at time t 4 to release the parking brake until it reaches the value pi.
  • the clamping force then increases further until it finally reaches the clamping force value F 3 , in which the flange 82 does not press as much against the inner cone 84, so that the threaded bushing 70 is relative to the piston 14 can turn.
  • the electric motor is then actuated so that the actuating device 42 can turn the bolt 36 back into its starting position according to FIG. 2.
  • the head 60 approaches the ramp disk 28 fixed to the housing while the spreading state is canceled, until the ramp component 32 again assumes its position shown in FIG. 2.
  • the threaded bolt 66 can thus move back into its starting position shown in FIG. 2 and with it the threaded bushing 70.
  • the hydraulic pressure in the fluid chamber 90 is then reduced until it reaches the value p 0 . In this state, the vehicle brake 10 has returned to its non-braking position shown in FIG. 2.
  • FIG. 5 shows a similar diagram, in which the force component additionally applied by the ramp arrangement 26 is twice as large as in the tensioning process according to FIG. 4. This means that the additional clamping force is 4 kN.
  • the clamping force curve corresponds in any case qualitatively to the clamping force curve described in FIG. 4 at the corresponding times and was accordingly provided with the same reference numerals, but with an apostrophe.
  • the clamping force is increased by spreading the ramp arrangement 26 from 12 kN to 16 kN and falls back to 11.8 kN after reducing the hydraulic pressure p to the value 0 bar, with which the brake disc is then held in the parking brake situation against unintentional blocking.
  • the exemplary embodiment according to FIGS. 6 to 8 differs from the first exemplary embodiment according to FIGS. 1 to 3 only in the configuration of the actuating device 42.
  • an electric motor which is integrated in the housing 12 and has a motor shaft 50
  • its longitudinal axis essentially 6 to 8 has an electric motor 102a, which is attached to the housing 12 via a bracket 104a in such a way that it can shift about a pivot axis S, which essentially runs parallel to the piston longitudinal axis A.
  • a motor longitudinal axis B runs orthogonally to the pivot axis S and to the piston longitudinal axis A, along which extends a threaded spindle 106 which can be rotated by the electric motor 102a in both directions of rotation about the motor longitudinal axis B.
  • a pin 108 is screwed onto the threaded spindle 106 and is mounted in the lever 40a so that it can pivot about the pivot axis T.
  • the lever 40a is attached to the bolt 36a in a manner analogous to the first exemplary embodiment according to FIGS. 1 to 3.
  • the service brake function of the second exemplary embodiment according to FIGS. 6 to 8 is similar to the first exemplary embodiment according to FIGS. 1 to 3.
  • the motor 102a is energized to activate the parking brake function.
  • the threaded spindle 106a rotates so that the pin 108a with an internally threaded bore is displaced along the longitudinal axis B of the motor on the threaded spindle 106a. With such a displacement, the motor 102a pivots about the pivot axis S.
  • the pin 108a pivots about the pivot axis T. Due to the displacement of the pin 108a, the lever 40a pivots about the longitudinal axis A.
  • lever 40a in Fig. 8 can be pivoted clockwise or counterclockwise.
  • a pivoting of the lever 40a has the same consequence as the pivoting of the lever 40 according to the first exemplary embodiment according to FIGS. 1 to 3, namely an actuation of the ramp arrangement 26a and thereby an activation or deactivation of the parking brake function.
  • FIGS. 1 to 8 show a vehicle brake in which the hydraulic actuation of the service brake function can be used to activate the parking brake function in order to be able to achieve high parking clamping forces.
  • the actuating device for Activation of the parking brake function is designed such that the clamping force component caused by the hydraulic actuation can be superimposed on a clamping force component generated by the actuating device.
  • clamping forces can be achieved by the driver without mandatory mechanical effort, which ensure a reliable parking brake effect in every operating state.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Braking Arrangements (AREA)

Abstract

L'invention concerne un frein automobile (10) comportant un piston de frein (14) disposé dans un boîtier (12), un dispositif de blocage destiné à bloquer le piston de frein (14) à l'intérieur du boîtier (12), et un dispositif d'actionnement (42) destiné à commander le dispositif de blocage (42). Selon l'invention, le piston de frein (14) et le boîtier (12) délimitent une chambre fluidique (90) pouvant recevoir un fluide hydraulique, de telle manière que le piston de frein (14) puisse être déplacé hydrauliquement dans le boîtier (12), le long d'un axe longitudinal de piston (A), pour l'actionnement du frein automobile (10). Par ailleurs, le dispositif de blocage (14) comporte un système de rampe (26) et un élément de blocage (70) pouvant se déplacer par rapport au boîtier (12), et le dispositif d'actionnement permet de déplacer l'élément de blocage (70), par interaction avec le dispositif de rampe (26), afin de bloquer le piston de frein à l'intérieur du boîtier (12), et de coupler l'élément de blocage au piston de frein. Le dispositif d'actionnement (42) comporte en outre un entraînement à moteur couplé en entraînement au dispositif de rampe (26), l'élément de blocage (70) se déplaçant lors de l'actionnement de l'entraînement à moteur afin de bloquer et libérer le piston de frein (14) à l'intérieur du boîtier (12).
EP04731179A 2003-05-09 2004-05-05 Frein automobile hydraulique Withdrawn EP1623138A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10320906A DE10320906B4 (de) 2003-05-09 2003-05-09 Hydraulisch betätigbare Fahrzeugbremse
PCT/EP2004/004771 WO2004099645A1 (fr) 2003-05-09 2004-05-05 Frein automobile hydraulique

Publications (1)

Publication Number Publication Date
EP1623138A1 true EP1623138A1 (fr) 2006-02-08

Family

ID=33426723

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04731179A Withdrawn EP1623138A1 (fr) 2003-05-09 2004-05-05 Frein automobile hydraulique

Country Status (4)

Country Link
US (1) US7370735B2 (fr)
EP (1) EP1623138A1 (fr)
DE (1) DE10320906B4 (fr)
WO (1) WO2004099645A1 (fr)

Families Citing this family (17)

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DE102005055084B4 (de) * 2005-09-29 2017-02-09 Robert Bosch Gmbh Kombinierte Betriebs- und Feststellbremseinrichtung
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US7370735B2 (en) 2008-05-13
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DE10320906B4 (de) 2007-12-27
WO2004099645A1 (fr) 2004-11-18

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