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EP1994304A1 - Frein à disque avec accumulateur de force - Google Patents

Frein à disque avec accumulateur de force

Info

Publication number
EP1994304A1
EP1994304A1 EP07711755A EP07711755A EP1994304A1 EP 1994304 A1 EP1994304 A1 EP 1994304A1 EP 07711755 A EP07711755 A EP 07711755A EP 07711755 A EP07711755 A EP 07711755A EP 1994304 A1 EP1994304 A1 EP 1994304A1
Authority
EP
European Patent Office
Prior art keywords
brake
force
disc brake
bearing
caliper
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Withdrawn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
EP07711755A
Other languages
German (de)
English (en)
Inventor
Alfred Utzt
Karlheinz Heidl
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.)
Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH
Original Assignee
Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Knorr Bremse Systeme fuer Schienenfahrzeuge 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 Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH, Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH filed Critical Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Publication of EP1994304A1 publication Critical patent/EP1994304A1/fr
Withdrawn legal-status Critical Current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
    • F16D65/14—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
    • 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
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/58—Mechanical mechanisms transmitting linear movement
    • F16D2125/64—Levers
    • F16D2125/645—Levers with variable leverage, e.g. movable fulcrum

Definitions

  • the invention relates to a disc brake according to the preamble of claim 1.
  • a Sp Schwarzkeilvorraum is known in which a wedge element, on the wedge surfaces on both sides of the drive points of the brake shoes are arranged is moved between them and so transmits a braking force to the brake shoes by being spread apart.
  • the expanding wedge is driven by an external brake cylinder, for example pneumatically or hydraulically.
  • the object of the invention over the prior art is to provide an improved disc brake, which no longer has the disadvantages mentioned above and offers further advantages.
  • a permanent force is generated by a force storage element, for example by a preloaded spring, wherein its action on the brake pads and thus on the brake disc with the lowest possible energy is controllable.
  • the deflection device for deflecting the force flow of the energy storage element for applying at least one brake pad in a transverse direction of a brake disc is designed to be controllable.
  • the deflecting device has the advantage that the disc brake has a compact construction, and, on the other hand, it is equipped with this deflecting device in a tax-deductible manner. ren execution possible to influence the power flow of the energy storage element in a simple manner continuously for deflection as a braking force in an equally adjustable manner.
  • the at least one energy storage element is arranged in the brake caliper of the disc brake that its power flow direction in a longitudinal direction parallel to the brake disc of the disc brake and perpendicular to the transverse direction, resulting in a particularly space-saving design.
  • the wedge angle is according to a variant, a pivoting angle of a brake lever about a fixed axis in the caliper pivot axis.
  • a brake lever is at its opposite end of the pivot axis with a deflection in cooperation, which is connected to the energy storage element and a brake pad.
  • the deflecting element between the caliper and the opposite end of the pivot axis of the brake lever is arranged, wherein the brake lever has at its opposite end of the pivot axis a wedge bearing, which is guided in the course of Verschwenkwegs of the brake lever on a guide cam of the deflection ,
  • the deflection element is acted upon by the force storage element with its force and transmits this force via its guide track on the brake lever, which initiates this force in the brake caliper when the brake lever in a release position ment stands.
  • the brake lever is pivotable about this point of introduction in the brake caliper, with its other end being guided on the guide track of the deflection element.
  • the pivot angle of the brake lever forms the wedge angle of the deflection.
  • the power flow is now divided in the pivoted position of the brake lever, so that a force flow component is generated in the direction of the brake pads, which is dependent on the pivoting angle.
  • the axis of rotation is coupled with an adjusting device for adjustment in the transverse direction with wear of the brake linings. Due to the fact that the operating force of the brake lever changes according to wear of the brake pads, it is provided in a further preferred embodiment, that the adjusting device is in operative connection with a measuring device for measuring the operating force of the brake lever.
  • the deflection device is formed from two substantially wedge-shaped in cross-section rotary wedge elements, which are arranged with their straight surfaces opposite to the axis of rotation pivotable and mutually displaceable in a recess of the caliper.
  • the rotary wedge elements are arranged in the recess of the brake caliper, that the first rotary wedge member is slidably disposed, wherein the second rotary wedge member is in communication with a brake actuator.
  • a simple wedge gear with adjustable wedge angle is created that easily and continuously for adjusting the braking force for the disc brake can be used. It is also compact and can be integrated into the caliper.
  • the rotary wedge elements in the recess of the brake satteis in the longitudinal direction with a force input bearing and a transverse bearing and in the transverse direction with a longitudinal bearing and a power output bearing in operative connection are provided.
  • the friction loss is particularly low, which provides a further advantage for reducing the operating force.
  • the longitudinal bearing and the transverse bearing are mounted on fixed axes of rotation in the caliper, and that the force introduction bearing rotatably adjustable in a first guide in the longitudinal direction and the power output bearing rotatably arranged in a second guide in the transverse direction, wherein the force input bearing with the force storage element and the power output bearing with the brake pad is in cooperation.
  • the caliper and the brake pads are elastic to a certain extent and also generate here by the acting braking forces a restoring force for the deflection device.
  • the outer contour of the first rotary wedge member each having an eccentric portion of an input cam having a first nose and an eccentric portion of an output cam having a second nose.
  • the input curve of the first rotary wedge element projecting toward the first nose and the output curve towards the second nose project radially outward.
  • the opposing surfaces of the rotary wedge members may be eccentric.
  • the input cam of the first rotary wedge member is in operative connection with the power input bearing and the output cam of the first rotary wedge member is operatively connected to the power output bearing.
  • the curve shape allows unwinding, with a low frictional resistance which keeps the actuating forces low.
  • the power flow of the power storage element is introduced in the release position of the disc brake via the force input bearing via the first and second rotary wedge member and the transverse bearing in the brake caliper, wherein in a different from the release position pivoting position of the rotary wedge elements in Depending on their Verschwenkwin- kel the size of the power flow of the energy storage element is set in the transverse direction of the brake pad on the power output bearing.
  • the power flow can be divided by this deflection and even amplified at certain wedge angles.
  • Another great advantage is that the force for controlling the controllable deflection device is substantially lower than the force generated by the force storage element, and thus space-saving operating units such as pneumatic and / or hydraulic cylinders or electromotive actuators can be used. This significantly reduces the high energy transfer losses of the prior art.
  • the force storage element is a spring, a pneumatic cylinder or a preloaded casting or a combination of these, since thus built into the caliper of the disc brake permanent or rechargeable power storage is created, whereby the transmission of high energy to the disc brakes can be omitted in a vehicle according to the prior art.
  • a disc brake described above has an electromotive actuator for brake actuation.
  • a parking brake is made possible by a special shape of the input-output curves.
  • Figure 1 is a schematic diagram of a wedge gear with different wedge angles
  • Figure 2 is a schematic representation of a disc brake in a release position
  • Figure 3 is a schematic representation of the disc brake of Figure 2 in a first braking position
  • Figure 4 is a schematic representation of the disc brake of Figure 2 in a second braking position
  • Figure 5 is a schematic representation of an exemplary embodiment of the disc brake according to the invention in a release position
  • Figure 6 is a schematic representation of the disc brake of Figure 5 in a first braking position
  • Figure 7 is a schematic representation of the disc brake of Figure 5 in a second braking position.
  • FIG. 8 shows a section of a further variant of the disc brake from FIGS. 5 to 7.
  • the same reference numbers apply to parts having the same or similar function.
  • a coordinate system x, y, z is shown for orientation, which indicates x a longitudinal direction parallel to a brake disc 2 of the disc brake 1, y a transverse direction perpendicular to the longitudinal direction x and z a direction perpendicular to the plane of the drawing.
  • the transverse direction y runs parallel to the wheel axis of the disc brake 1.
  • a wedge gear as a deflection device 20 for an input force F E in an output force F A is shown schematically.
  • the input force F E acts on a first wedge element 21, which is guided laterally on a longitudinal guide in the longitudinal direction x. It is connected to a second wedge element 22 via an oblique parting line 25, 26, 27 in connection, wherein the three parting lines 25, 26, 27 represent three different wedge angle ⁇ , which is drawn only at the parting line 27 between this and the vertical or longitudinal direction x is.
  • the second wedge element 22 is guided by a transverse guide 24 in the transverse direction y.
  • the wedge angle ⁇ is shown here by the three different parting lines 25, 26, 27 in three different sizes.
  • the wedge angle ⁇ is 63 ° from the parting line 25 to the longitudinal direction x or 27 ° from the parting line 25 to the transverse direction y.
  • this wedge angle or deflection angle ⁇ must be infinitely adjustable.
  • FIG. 2 shows a disc brake 1 with a disc 2, which is only partially shown.
  • the first brake pad 3 is connected to a leg of the caliper 5.
  • the caliper 5 is extended to the right side of the figure out and between the this side leg and the second brake pad 4, a deflection element 30 is arranged, which is guided in the longitudinal direction x of the right leg of the caliper 5.
  • the right leg forms the longitudinal guide 23 (see FIG. 1).
  • the deflecting element 30 is connected on its left side to the second brake pad 4, wherein it has a recess 6 which surrounds a rotation axis 42.
  • This rotation axis 42 is fixedly connected to the caliper 5 in this example.
  • On her a bearing 31 is attached to which a brake lever 33 is pivotally mounted.
  • the brake lever 33 has at its end opposite the fixed bearing 31 a wedge bearing 32, which is felt on a guide rail 34 of the deflecting element 30 and in principle forms the longitudinal guide 23 and the transverse guide 24 of FIG. 1 for the deflecting element 30 during operation.
  • the deflection element 30 is connected on its upper side with a force storage element 10, in this example a prestressed spiral spring, which is supported on the caliper 5, wherein the force direction of the energy storage element 10 in the longitudinal direction x acts on the deflection element 30. 2, the disc brake 1 is shown in a so-called release position.
  • the force of the energy storage element 10 presses the deflecting element 30 to the wedge bearing 32.
  • the power flow of the energy storage element 10 acts directly in the longitudinal direction x and is received by the wedge bearing 32 on the guide rail 34 of the deflecting element 30 and the brake lever 33 in the fixed bearing 31 and thus in passed the caliper 5.
  • a force component in the transverse direction y does not occur, thus no application force is exerted on the brake lining 4.
  • the deflection element 30 and the brake lever 33 form the deflection device 20 according to FIG. 1, wherein in this case the release position in FIG. 2 is the wedge angle ⁇ 90 °.
  • the force component in the direction y corresponds to the force of the energy storage element 10.
  • the deflection element 30 is displaced in the transverse direction y onto the brake disk 2.
  • the recess 6 serves as a free space for the fixed bearing 31.
  • the movement of the deflection element 30 in the transverse direction y is compensated by the force storage element 10 by expanding.
  • ⁇ is about 27 °.
  • This position of the brake lever 33 is provided for braking with high braking force.
  • the position of the brake lever increases the force of the energy storage element 10th
  • the caliper 5 When applying the application force in the transverse direction y, the caliper 5 is stretched elastically. This generates a restoring force for the deflecting element 30 as soon as the brake lever 33 is moved again in the direction of the release position (see FIG. 2).
  • the guideway 34 of the deflection element 30 is designed so that the smallest possible extent in the longitudinal direction x takes place and the deflection element 30 moves mainly in the transverse direction y perpendicular to the brake disc 2.
  • the movement of the brake lever 33 advantageously requires only low energy, in a design of the wedge bearing 32 as a rolling bearing mainly the bearing pressure, which acts against the force of the energy storage element 10.
  • the brake control device for all embodiments, in particular also the rotary wedge elements of Fig. 5 ff is electrically, pneumatically, hydraulically and purely mechanically interpretable and it is an operation with low actuation force possible.
  • a coil spring as a force storage element 10
  • a leaf spring instead of a coil spring as a force storage element 10, a leaf spring, a pneumatic cylinder or a combination of which is conceivable.
  • a prestressed casting is possible, which corresponds to the brake caliper 5 in its elasticity.
  • the pneumatic cylinder can be provided with check valves, that is, a single filling this would suffice as a force storage , They would only be refilled if there was a leak. Since the parking brake springs inevitably co-operate with each braking, both these and the pneumatic cylinder can be dimensioned correspondingly small.
  • the operation of the brake lever 33 is possible by means of a separate pneumatic cylinder, since the brake lever 33 only controls the braking force. Thus, it requires relatively little pressure and volume, thereby advantageously contributing to a substantial reduction of the necessary air procurement on each vehicle.
  • the movement of the brake lever 33 requires the same force for applying as for releasing the brake.
  • the wedge bearing 32 leaves its ideal path on the guideway 34 of the deflection element 30. This results in different forces on the brake lever 33 during application and release.
  • This can be measured in a further embodiment, which can also be regarded as an independent invention, for example via measuring devices such as strain gauges, wherein an electrical adjusting device is provided, which adjusts the fixed bearing 31 in the transverse direction y on the brake disk 2 until the actuation forces are the same again on the brake lever 33.
  • FIGS. 5 to 7 show a second exemplary embodiment of the disk brake 1 according to the invention in various positions.
  • the right portion of the caliper 5 has a circular recess 6, in which two rotary wedge elements 40, 41 are arranged pivotable about the axis of rotation 42.
  • the rotary wedge elements 40, 41 each have a substantially semicircular cross-section and are arranged with their straight surfaces opposite one another, wherein these surfaces can slide on each other or by means of suitable rollers are mutually displaceable.
  • the rotary wedge elements 40, 41 are mounted in different rollers 11, 43, 44, 45, each of which encloses the rotary wedge elements 40, 41 as a deflection device 20 in the longitudinal direction x and transverse direction y.
  • a force input bearing 11 is slidably disposed in a first guide 12 in the caliper 5, wherein the power input bearing 11 is disposed between the power storage element 10 and the first rotary wedge member 40, in which it initiates the force of the energy storage element 10.
  • the straight bottom surface of the upper, first rotary wedge member 40 then transfers the force to the straight upper surface of the lower second rotary wedge member 41, which in turn is supported on the transverse bearing 44 (see designation 24 in Fig. 1) ,
  • the transverse bearing 44 initiates the force thus transmitted of the force storage element 10 in the caliper 5 in the longitudinal direction x.
  • a force component in the transverse direction y is not generated in this position.
  • both rotary wedge elements 40, 41 are mounted in the transverse direction y by a longitudinal bearing 43 (see designation 23 in FIG. 1) and by a force output bearing 45.
  • the power output bearing 45 is rotatably and slidably disposed in a second guide 46, wherein it is connected to the brake pad 4.
  • the first rotary wedge member 40 has portions 47, 48 on its outer surface, referred to as input cam 47 and output cam 48. In this case, these curves 47 and 48 are eccentric and expand radially on lugs 50 and 51 to the outside. Their function will be described further below.
  • the lower rotary wedge member 41 has a semicircular outer contour and is driven by an actuator for braking such that it is pivoted for applying the brake pad in a counterclockwise direction about the axis of rotation. The pivoting angle is the wedge angle ⁇ .
  • Fig. 6 shows, similar to Fig. 3 shows a position of the disc brake 1 for a mean braking force.
  • the force of the force storage element 10 via the Force input bearing 11, which rolls on the input cam 47, the upper rotary wedge member 40 is moved to the left, the power output bearing 45 rolls on the output curve 48 and deliver the brake pad 4 in the transverse direction y to the brake disc 2 through the second guide 12.
  • the underside of the first rotary wedge member 40 slides or rolls on the non-displaceable, opposite upper side of the second rotary wedge member 41 with a relative movement from its central position, which he had in the release position (see Fig. 5).
  • Fig. 7 the minimum deflection angle ⁇ is now shown, wherein the first Drehkeil- dement 40 is further shifted relative to the second rotary wedge member 41.
  • the tension of the brake caliper 2 is exaggeratedly large with an angle ß indicated.
  • the eccentric raceways or curves 47, 48 on the outside of the first rotary wedge member 40 must be designed in this execution, since they keep the bearings 45 and 11 at each angular position of ⁇ at the outermost point of the track perpendicular to the axis of rotation 42.
  • a relatively easy pivoting of the two rotary wedge elements 40, 41 can be advantageously achieved as a controllable deflection device 20.
  • the rotary wedge member 40 is moved in the Z-axis in the direction of decreasing radius, this can be done by a separate drive or by coupling to the wear adjuster, as this anyway the dwindling covering strength reacts.
  • an electro-mechanical brake system with integrated parking brake (spring storage as energy storage element 10) can be executed, which has an advantageously low energy consumption, since the actuation force for the inventive disc brake 1, the braking force of the energy storage element 10 only controls.
  • the braking force is deflected by the deflecting device 20 controlled thereby and adjusted in accordance with the deflection angle ⁇ in a corresponding size.
  • the rotary wedge elements 40, 41 and also the deflecting element 30 can be installed in parallel in a larger number.
  • the force storage elements 10 are arranged several times, whereby combinations of different types are also possible.
  • the opposite surfaces of the rotary wedge elements 40, 41 are curved sliding surfaces or roller tracks, wherein the outer contours are semicircular.

Landscapes

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

Abstract

Frein à disque (1) pourvu d'au moins un élément accumulateur de force (10) et d'un dispositif de changement de direction (20, 34), caractérisé en ce que ledit dispositif (20, 34) destiné à changer la direction du flux de force de l'élément d'accumulation de force (10) pour le serrage d'au moins une garniture de frein (3, 4) dans le sens transversal (y) d'un disque de frein (2) est conçu de manière à pouvoir être commandé.
EP07711755A 2006-03-06 2007-03-02 Frein à disque avec accumulateur de force Withdrawn EP1994304A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006010216A DE102006010216B3 (de) 2006-03-06 2006-03-06 Scheibenbremse mit Kraftspeicher
PCT/EP2007/001796 WO2007101614A1 (fr) 2006-03-06 2007-03-02 Frein à disque avec accumulateur de force

Publications (1)

Publication Number Publication Date
EP1994304A1 true EP1994304A1 (fr) 2008-11-26

Family

ID=38234483

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07711755A Withdrawn EP1994304A1 (fr) 2006-03-06 2007-03-02 Frein à disque avec accumulateur de force

Country Status (4)

Country Link
US (1) US20100025165A1 (fr)
EP (1) EP1994304A1 (fr)
DE (1) DE102006010216B3 (fr)
WO (1) WO2007101614A1 (fr)

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Publication number Priority date Publication date Assignee Title
DE102007048363A1 (de) * 2007-10-09 2009-04-23 Federal-Mogul Friction Products Gmbh Bremsbelagsatz mit unterschiedlicher Kompressibilität
DE102007057264A1 (de) * 2007-11-26 2009-05-28 Siemens Ag Vorrichtung und Verfahren zum Abbremsen eines sich in eine Bewegungsrichtung bewegenden Elements
AT513989A1 (de) * 2013-03-11 2014-09-15 Ve Vienna Engineering Forschungs Und Entwicklungs Gmbh Elektrisch betätigte Reibungsbremse
US9933033B2 (en) * 2013-06-06 2018-04-03 Freni Brembo S.P.A. Pad replacement kit, caliper body, pad and insert assembly and method of exerting a modified braking action
US9616875B2 (en) 2014-09-11 2017-04-11 Westinghouse Air Brake Technologies Corporation Piston stroke sensor arrangement for a brake unit
US10119873B2 (en) 2014-09-15 2018-11-06 Westinghouse Air Brake Technologies Corporation Brake force sensor arrangement for a brake unit
DE102016103187A1 (de) * 2016-02-24 2017-08-24 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Scheibenbremse mit einer Schnellanlegevorrichtung
DE102018212031A1 (de) 2018-07-19 2020-01-23 Robert Bosch Gmbh Verfahren zum Betreiben eines Kraftfahrzeugs, Steuergerät und Kraftfahrzeug

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DE3717072A1 (de) * 1987-05-21 1988-12-08 Knorr Bremse Ag Zuspannvorrichtung fuer bremsen
CN1211691A (zh) * 1997-09-12 1999-03-24 陈坤 机械盘式制动器和离合器
DE29901831U1 (de) * 1999-02-03 1999-05-06 Quenstedt, Jan, Dipl.-Ing., 52152 Simmerath Backenbremse mit Servoeffekt
DE10046177A1 (de) * 2000-09-19 2002-04-04 Bosch Gmbh Robert Scheibenbremse
DE10046981A1 (de) * 2000-09-22 2002-04-25 Bosch Gmbh Robert Radbremsvorrichtung
DE10140076A1 (de) * 2001-08-16 2003-02-27 Wabco Gmbh & Co Ohg Zuspanneinrichtung für Scheibenbremsen
FR2838694B1 (fr) * 2002-04-18 2004-07-09 Bosch Gmbh Robert Dispositif de freinage pour vehicule automobile et systeme de freinage comportant un tel dispositif
US6932198B2 (en) * 2002-08-07 2005-08-23 Ford Global Technologies, Llc Brake assembly and a method for braking a vehicle or another selectively movable assembly
DE10324424A1 (de) * 2003-05-30 2004-12-16 Robert Bosch Gmbh Reibungsbremse mit mechanischer Selbstverstärkung und Verfahren zu ihrer Betätigung
DE102005027916B4 (de) * 2005-06-16 2013-04-11 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Fahrzeugbremse in selbstverstärkender Bauart

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Also Published As

Publication number Publication date
WO2007101614A1 (fr) 2007-09-13
US20100025165A1 (en) 2010-02-04
DE102006010216B3 (de) 2007-10-25

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