WO2000008352A1 - Etrier combine avec dispositif electrique de reglage et de blocage - Google Patents

Etrier combine avec dispositif electrique de reglage et de blocage Download PDF

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Publication number
WO2000008352A1
WO2000008352A1 PCT/EP1999/003674 EP9903674W WO0008352A1 WO 2000008352 A1 WO2000008352 A1 WO 2000008352A1 EP 9903674 W EP9903674 W EP 9903674W WO 0008352 A1 WO0008352 A1 WO 0008352A1
Authority
WO
WIPO (PCT)
Prior art keywords
brake
nut
piston
spindle
brake piston
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.)
Ceased
Application number
PCT/EP1999/003674
Other languages
German (de)
English (en)
Inventor
Rudolf Thiel
Hans-Georg Keferstein
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.)
Continental Teves AG and Co OHG
Original Assignee
Continental Teves AG and Co OHG
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 Continental Teves AG and Co OHG filed Critical Continental Teves AG and Co OHG
Publication of WO2000008352A1 publication Critical patent/WO2000008352A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
    • F16D65/56—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut
    • F16D65/567—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut for mounting on a disc brake
    • 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
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • F16D65/095—Pivots or supporting members therefor
    • F16D65/097—Resilient means interposed between pads and supporting members or other brake parts
    • F16D65/0971—Resilient means interposed between pads and supporting members or other brake parts transmitting brake actuation force, e.g. elements interposed between brake piston and pad
    • 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
    • F16D65/00—Parts or details
    • F16D65/38—Slack adjusters
    • F16D2065/386—Slack adjusters driven electrically
    • 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
    • F16D66/00—Arrangements for monitoring working conditions, e.g. wear, temperature
    • F16D2066/003—Position, angle or speed
    • 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
    • F16D2121/18—Electric or magnetic
    • F16D2121/24—Electric or magnetic using motors
    • 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
    • F16D2125/40—Screw-and-nut
    • 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
    • F16D2125/44—Mechanical mechanisms transmitting rotation
    • F16D2125/46—Rotating members in mutual engagement

Definitions

  • the invention relates to a brake device, in particular a motor vehicle disc brake device, with a brake housing, a brake piston which can be moved hydraulically / mechanically axially in the brake housing, furthermore with a hydraulic actuation device and with a mechanical actuation device, with a rotatable spindle and one axially due to the rotation of the spindle Slidable nut, wherein the brake piston can be acted upon hydraulically by means of the hydraulic actuation device and / or mechanically by means of the mechanical actuation device, and wherein the brake piston is supported on the nut during mechanical actuation.
  • a braking device of the construction described in the introduction has become known from German laid-open specification 195 21 634.
  • a conventional combination caliper with a service and parking brake function has been implemented, which additionally has an adjustment device in order to compensate for brake pad wear.
  • the adjusting device works automatically, as it were, using a coupling element which is non-rotatably connected to the nut and has a conical friction surface.
  • the disc brake is actuated mechanically, this friction surface can be pressed against a friction surface formed on the brake piston in order to prevent the nut from rotating.
  • the brake is actuated hydraulically, the axially movable brake piston disengages from the coupling element, so that the nut on the associated spindle can be rotated to readjust the adjusting device.
  • the aforementioned adjustment is carried out the hydraulic pressure does not exceed a predetermined (relatively low) value.
  • the described prevention of the adjustment at high hydraulic pressure has its purpose in that it generates large clamping forces. Since the brake housing has a certain elasticity and bends somewhat with large application forces, B with unchanged effectiveness of the adjusting device B would come to a blocking of the disc brake after the hydraulic actuation had ended, since the brake housing deforms elastically without the brake piston being able to perform a corresponding return movement . B For this reason, the previously known braking device, in particular a motor vehicle disk brake, has a relatively complicated structure and, as far as the aforementioned functional interruption of the adjusting device is concerned, is not always free of malfunctions. Ultimately, the work here is purely mechanical, so that aging effects, temperature-related canting and jamming and similar effects cannot be ruled out with absolute certainty. This is where the invention comes in.
  • the invention has for its object to develop such a braking device so that a perfect function of both the hydraulic and the mechanical actuating device is given, regardless of temperature and aging effects.
  • the invention proposes in a brake device of the construction described at the outset that at least one sensor is provided, the mechanical actuating device correspondingly tracking the brake piston as a function of the brake lining wear determined by the sensor, and the mechanical actuating device when the sensor detects hydraulic made determination of an associated brake fixed the brake piston.
  • Two or more sensors are regularly provided, specifically an adjustment sensor for determining, for example, the brake piston travel during service braking or the number of braking operations, and a parking sensor for detecting the achievement of the required parking force for the brake.
  • the two aforementioned sensors can be connected to an evaluation unit which also acts on the aforementioned electric motor.
  • the spindle is preferably connected to a drive shaft of the electric motor via a self-locking movement thread and is therefore designed to be rotatable accordingly.
  • the translation of the rotational movement of the spindle into a translational movement of the nut is accomplished via a screw thread or likewise (self-locking) movement thread between the spindle and nut, the screw thread having a predetermined pitch.
  • a ball screw thread can also be realized, which connects the spindle and nut with each other.
  • the brake piston is usually a hollow cylinder with a spindle and nut arranged in its interior.
  • the nut has at least one anti-rotation device, which is in an associated anti-rotation device on the inside wall side of the hollow cylinder engages.
  • the nut has at least one anti-rotation device, which is in an associated anti-rotation device on the inside wall side of the hollow cylinder engages.
  • the nut on the piston head side can have a projection or an elastically compressible intermediate layer, for example one or more disc springs, between the nut and the piston head.
  • this compressible intermediate layer, or the disc springs it can be achieved with a fixed brake piston and thus locked brake that a loss of clamping force is compensated for by the spring accumulator which is thereby practically realized.
  • Such a decrease in the application force can be caused, for example, by cooling a previously hot brake disc. Because in the course of cooling, the thickness of the brake disc also decreases, so that the locking function could be impaired if the clamping force is not tracked. The same naturally also applies in the event that the brake pads slowly cool down after heating.
  • the brake piston can have an inner wall-side ring and the nut can have at least one pressure segment enclosed by the ring, the ring and the pressure segment being designed to be displaceable relative to one another on a common contact surface.
  • the pressure segment or the nut is acted on, so that the ring and thus the brake piston are axially displaced.
  • both an automatic adjustment of the brake piston for brake pad wear compensation and a determination of an associated brake or brake disc are essentially implemented by a mechanical actuation device, which is moved by an electric motor (and an evaluation unit) depending on sensor values. Since a mechanically triggered readjustment and determination or fixing is fundamentally dispensed with, elaborate mechanisms - as are absolutely necessary according to the prior art (compare DE-OS 195 21 634) - can be dispensed with.
  • the mechanical actuation device is rather triggered as a function of signals from the adjuster sensor and / or the parking sensor.
  • the adjustment sensor detects the path of the brake piston, for example.
  • the evaluation unit connected to the adjustment sensor recognizes this fact as increasing brake lining wear. Consequently, the electric motor is triggered in such a way that the nut and thus the base or the stop (i.e. ultimately the contact surface) for the brake piston is axially displaced in the direction of the brake or disc brake. Accordingly, brake pad wear compensation takes place.
  • the readjustment sensor it is also possible for the readjustment sensor to determine the number of braking operations and to draw conclusions about the expected wear and to take appropriate countermeasures via the evaluation unit.
  • the generation of the required application force on the brake for the locking process takes place hydraulically, specifically via the hydraulic actuating device, which usually pressurizes the brake piston via a motor / pump unit. According to its piston surface, this generates the clamping force required to lock the vehicle or block the (disc) brake. So- As soon as the parking sensor detects that the required parking force for the brake has been reached, the electric motor is actuated to rotate the spindle. Accordingly, the nut moves towards the brake piston and fixes it. In this way, an electric parking brake is implemented. The previously applied hydraulic pressure can consequently be released or can escape via ventilation bores, since a reliable mechanical blockage of the brake has been achieved via the mechanical actuation device. As a result, long-term locking of the brake or disc brake is possible, which could not be achieved with hydraulic locking (if only because the hydraulic pressure slowly drops when the engine is switched off).
  • FIG. 1 shows a first embodiment of the invention
  • FIG. 2 shows a simplified modified embodiment
  • FIG. 3 shows a further embodiment of the invention
  • FIGS. 4a, 4b and 4c further modifications of the invention.
  • a brake device according to the embodiment, a motor vehicle disc brake device is shown.
  • this has a brake housing 1 (brake caliper 1) which overlaps a brake disk (not shown) and brake shoes arranged on both sides of the brake disk.
  • the brake shoes are also not shown.
  • the brake pad carrier 2 of the brake shoes can only be seen.
  • An axially displaceable brake piston 3 is arranged in the brake housing 1 and can be moved hydraulically / mechanically.
  • a hydraulic actuation device 4 is used, which acts on the brake piston 3 with a hydraulic pressure medium via a motor / pump unit, which is not explicitly shown.
  • a mechanical actuation device 5 is realized, which in its basic structure has a rotatable spindle 6 with an associated nut 7 which can be axially displaced by the spindle rotation.
  • the aforementioned brake piston 3 can also be moved mechanically by means of the mechanical actuation device 5.
  • the spindle 6 has an electric motor 8 connected at the end.
  • This electric motor 8 sets the spindle 6 in rotation by means of a drive shaft 9.
  • the electric motor 8 can be arranged in the longitudinal extension of the spindle 6 together with the drive shaft 9 or in any other angular position with respect to the axis of the drive shaft 9 (e.g. right angle, see FIG. 3). It should be noted here that, for example, by interposing a suitable gear (e.g. worm gear), secure power transmission from the electric motor 8 to the drive shaft is ensured at every angular position of the electric motor 8.
  • a suitable gear e.g. worm gear
  • a preferably self-locking movement thread 10 is realized, which connects the spindle 6 to the drive shaft.
  • a sealing ring 11 seals the hydraulic part of the brake housing 1 or brake caliper 1 against the electric motor 8.
  • the nut 7, which is displaceable on the rotatable spindle 6, has at least one anti-rotation lock 12 which engages in an associated anti-rotation lock receptacle 12 'on the inside wall side of the brake piston 3.
  • the brake piston is constructed as a hollow cylinder 3 with 'arranged in its interior the spindle 6 and nut. 7
  • the brake piston 3 or hollow cylinder has an inner wall-side ring 13 which is fixedly connected to the brake piston 3.
  • the nut 7 has at least one pressure segment 14 enclosed by the ring 13.
  • two pressure segments 14 are realized.
  • three or more pressure segments 14 can also be provided.
  • a sleeve 15 is realized, which is supported against the piston crown 17 via a compression spring 16. Due to the force of the compression spring 16, the or the pressure segments 14 are pressed against the nut 7 via the sleeve 15.
  • the adjusting motor 19, 19 'and the connected evaluation unit 20 apply the electric motor 8 in such a way that it rotates the spindle 6.
  • This rotation means that the nut 7, which is axially displaceable on the spindle 6, is moved in the direction of the brake piston 3, so that the associated contact surface 21 between the ring 13 and the pressure segments 14 also shifts to the left in FIG. 1.
  • the contact surface 21 is conical. Accordingly, the ring 13 has an inner cone and the pressure segments 14 have an associated outer cone.
  • the contact surface 21 represents, as it were, the base or the stop of the brake piston 3 on the mechanical actuating device 5.
  • the locking process is carried out hydraulically in such a way that the pressure medium is passed onto the brake piston 3 via the bore 18. In accordance with the inner surface of the brake piston 3 relevant for the axial application direction, this generates the application force required to fix the motor vehicle.
  • a parking sensor 22 or force sensor 22 on the brake lining carrier 2 detects that the required parking force for the brake has been reached, the spindle 6 is again acted upon by the electric motor 8.
  • the pressure segments 14 are consequently brought into engagement with the ring 13. In this position, the brake piston 3 is supported by the ring 13, the pressure segments 14, the sleeve 15, the nut 7, the spindle 6 and the drive shaft 9 on the brake housing 1 from.
  • a collar 23 is provided on the drive shaft 9.
  • a bearing 24 for the drive shaft 9 can be provided between the collar 23 and the brake housing 1.
  • the elastic deformation of the brake housing 1 generates a reaction force of the brake piston 3, which is supported on the brake housing 1 in the aforementioned manner.
  • the locking process is now complete.
  • the torque occurring between the brake or brake disc and brake piston 3 can be absorbed by a positive connection 25 between the brake piston 3 and the brake pad carrier 2 or by a frictional connection between the brake piston 3 and the sealing ring 26.
  • FIG. 2 corresponds essentially to the configuration of FIG. 1, so that the same parts are identified by the same reference numerals.
  • a contact surface 21 working as it were on impact is realized here.
  • FIG. 3 shows a modification such that the drive shaft 9 has a so-called sliding seat 27, via this sliding seat 27 the drive shaft 9 is coupled to the spindle 6 in a longitudinally displaceable and rotationally fixed manner.
  • the brake piston 3 has in the area of its piston crown 17 a seal 28 for sealing the pressure chamber to which the hydraulic pressure medium can be applied.
  • a bore 29 ensures that a differential pressure can take effect.
  • a cylindrical section 30 is realized, which together with the nut 7 forms a pressure chamber.
  • bearing 24 is provided to support the reaction force of brake piston 3 with respect to brake housing 1.
  • the brake piston 3 moves back and forth as part of the ventilation play.
  • the compressible intermediate layer 30 is therefore relaxed.
  • the nut 7 moves together with the spindle 6 and the brake piston 3 back and forth.
  • the resulting movement between the spindle 6 and the drive shaft 9 is compensated for by the sliding seat 27.
  • the locking process takes place hydraulically, with a pressure medium being let into the brake housing 1 via the bore 18 to act upon the brake piston 3 via a motor / pump unit (not shown).
  • the nut 7 is moved in the direction of the piston head 17 of the brake piston 3 in order to fix the hydraulically carried out determination and compresses the elastically compressible intermediate layer 31.
  • a corresponding rotation becomes as long made until the spindle 6 comes to rest on a stop surface 32 of the drive shaft 9.
  • the position of the brake piston 3 is fixed with respect to the brake housing 1 via the self-locking movement thread G and the previously hydraulically applied force is mechanically supported. In conjunction with the compressible intermediate layer 31, the force required to lock the motor vehicle is applied.
  • a loss of clamping force caused by the cooling of a clamped brake disc is compensated for by the correspondingly expanding intermediate layer 31. That is, the intermediate layer 31 acts like a spring accumulator.
  • FIGS. 4a, 4b and 4c show simplified variants with a particularly small-sized electric motor 8.
  • the brake piston 3 has an anti-rotation lock receptacle 12 'on the inside wall, which, for. B. is designed as a hexagon.
  • any other suitable profiling for securing against rotation can also be used at this point.
  • the nut 6 engages in this anti-rotation or hexagon receptacle 12 ′ with a corresponding outer profile or the anti-rotation device 12.
  • the nut 7 and the spindle 6 are equipped with a ball screw thread 33, which significantly increases the efficiency of the self-locking movement thread G otherwise provided at this point.
  • a locking ring 34 is provided which fixes the spindle 6 in the axial position.
  • the nut 7 has a projection 35 on the piston bottom side, which receives the contact surface 21.

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

Abstract

L'invention concerne un système de freinage, notamment un système de freinage de véhicule. Ce système comporte un carter de frein (1), un piston de freinage (3) pouvant être déplacé hydrauliquement/mécaniquement dans le sens axial à l'intérieur du carter (1), une unité d'actionnement hydraulique (4) et une unité d'actionnement mécanique (5). Il est en outre prévu au moins un détecteur (19, 19', 22).
PCT/EP1999/003674 1998-08-06 1999-05-27 Etrier combine avec dispositif electrique de reglage et de blocage Ceased WO2000008352A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19835550.5 1998-08-06
DE1998135550 DE19835550A1 (de) 1998-08-06 1998-08-06 Kombisattel mit elektrischer Nach- und Feststellung

Publications (1)

Publication Number Publication Date
WO2000008352A1 true WO2000008352A1 (fr) 2000-02-17

Family

ID=7876662

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1999/003674 Ceased WO2000008352A1 (fr) 1998-08-06 1999-05-27 Etrier combine avec dispositif electrique de reglage et de blocage

Country Status (2)

Country Link
DE (1) DE19835550A1 (fr)
WO (1) WO2000008352A1 (fr)

Cited By (3)

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DE102005001234A1 (de) * 2005-01-11 2006-07-20 Wabco Gmbh & Co.Ohg Bremszylinder mit Parkbremsfunktion
US10295004B2 (en) 2017-02-16 2019-05-21 Akebono Brake Industry Co., Ltd. Hydraulically-adjustable rotary to linear stage mechanism
US10428888B2 (en) 2017-10-30 2019-10-01 Akebono Brake Industry Co., Ltd. Brake system

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DE10148480A1 (de) 2001-10-01 2003-04-17 Knorr Bremse Systeme Feststellbremsvorrichtung und Verfahren zum Ansteuern der Feststellbremse
DE10152248B4 (de) * 2001-10-23 2006-03-16 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Scheibenbremse mit elektromotorisch betätigtem Nachstellsystem
DE10152423C2 (de) * 2001-10-24 2003-08-21 Lucas Automotive Gmbh Scheibenbremse
DE10228115B4 (de) * 2002-06-24 2004-05-13 Lucas Automotive Gmbh Elektrisch betätigbare Fahrzeugbremse und Verfahren zur Steuerung einer elektrisch betätigbaren Fahrzeugbremse
ES2255630T3 (es) 2001-11-23 2006-07-01 Lucas Automotive Gmbh Funcionamiento de un sistema de frenado de un vehiculo en funcion de las temperaturas de las superficies de frenado.
DE10163144B4 (de) * 2001-12-20 2008-04-24 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Feststellbremsvorrichtung und Steuerverfahren
WO2003080415A1 (fr) * 2002-03-21 2003-10-02 Lucas Automotive Gmbh Frein automobile electrique et procede de commande d'un frein automobile electrique
DE10214669B4 (de) 2002-04-03 2014-01-23 Knorr-Bremse Systeme für Schienenfahrzeuge GmbH Verfahren und Vorrichtung zur Ansteuerung einer elektrisch betätigten Verschleißnachstelleinrichtung
DE10261969B4 (de) * 2002-06-24 2011-01-05 Lucas Automotive Gmbh Elektrisch betätigbare Fahrzeugbremse und Verfahren zur Steuerung einer elektrisch betätigbaren Fahrzeugbremse
DE10232961B4 (de) * 2002-07-19 2007-06-14 Wabco Perrot Bremsen Gmbh Scheibenbremse, insbesondere für Landfahrzeuge
FR2860850B1 (fr) * 2003-10-08 2007-03-02 Bosch Gmbh Robert Dispositif de feinage de vehicule automobile comportant des moyens elastiques de stockage d'energie de serrage
DE102004004992B4 (de) 2004-01-30 2008-03-13 Lucas Automotive Gmbh Verfahren zum Betreiben der Bremsausrüstung eines Fahrzeugs
DE102005015726B4 (de) 2005-04-06 2019-03-14 Robert Bosch Gmbh Kfz-Festellbremse mit Positionssensor
DE102005022400B4 (de) * 2005-05-13 2016-08-18 Robert Bosch Gmbh Hydraulische Fahrzeugbremse mit Feststelleinrichtung und Verfahren zur Funktionsüberprüfung der Feststellbremse
DE102005023362B4 (de) * 2005-05-20 2016-04-28 Robert Bosch Gmbh Fahrzeugbremse mit integrierter Feststelleinrichtung sowie Verfahren zum Betreiben einer Feststelleinrichtung
DE102007046953A1 (de) 2007-10-01 2009-04-02 Lucas Automotive Gmbh Kugelgewindetrieb für eine Kraftfahrzeugbremse und Kraftfahrzeugbremse
DE102007046952B4 (de) * 2007-10-01 2026-02-05 Zf Active Safety Gmbh Kraftfahrzeugbremse, insbesondere elektromechanisch betätigbare Kraftfahrzeugbremse, und Fahrzeugbremsanlage mit einer derartigen Kraftfahrzeugbremse
DE102008042778B4 (de) * 2008-10-13 2020-01-23 Robert Bosch Gmbh Ansteuerbare elektromechanische Einrichtung zur Feststellung eines Kolbens in einem Zylinder und damit ausgestattete Fahrzeugbremsanlage
US10316944B2 (en) 2016-06-28 2019-06-11 Akebono Brake Industry Co., Ltd Linear motion mechanism
DE102018132260A1 (de) * 2018-12-14 2020-06-18 Zf Active Safety Gmbh Aktuatorvorrichtung für eine Feststellbremse, Feststellbremse und Feststellbremsanlage
DE102019203605B4 (de) * 2019-03-18 2024-09-05 Continental Automotive Technologies GmbH Kombinierte Fahrzeugbremse
DE102021108111A1 (de) 2021-03-30 2022-10-06 Zf Active Safety Gmbh Elektrische Parkbremse sowie Verfahren zur Herstellung
FR3151363A1 (fr) * 2023-07-19 2025-01-24 Hitachi Astemo France Dispositif de freinage comprenant un mécanisme d’entraînement de piston pourvu d’une couronne de renfort

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US5148894A (en) * 1990-10-11 1992-09-22 Allied-Signal Inc. Disk brake/parking brake with threaded piston rod and motor
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US8944527B2 (en) 2005-01-11 2015-02-03 Wabco Gmbh Brake cylinder with parking brake function
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