EP2847485A1 - Frein à disques - Google Patents

Frein à disques

Info

Publication number
EP2847485A1
EP2847485A1 EP13721760.0A EP13721760A EP2847485A1 EP 2847485 A1 EP2847485 A1 EP 2847485A1 EP 13721760 A EP13721760 A EP 13721760A EP 2847485 A1 EP2847485 A1 EP 2847485A1
Authority
EP
European Patent Office
Prior art keywords
blocking
disc brake
threaded tube
rotary lever
brake
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Withdrawn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
EP13721760.0A
Other languages
German (de)
English (en)
Inventor
Alexander Asen
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
Original Assignee
Knorr Bremse Systeme fuer Nutzfahrzeuge 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 filed Critical Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Publication of EP2847485A1 publication Critical patent/EP2847485A1/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Withdrawn legal-status Critical Current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
    • F16D65/38—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
    • F16D65/568—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut for mounting on a disc brake for synchronous adjustment of actuators arranged in parallel
    • 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
    • F16D2127/00—Auxiliary mechanisms
    • F16D2127/06—Locking mechanisms, e.g. acting on actuators, on release mechanisms or on force transmission mechanisms

Definitions

  • the invention relates to a disc brake, in particular for a motor vehicle, according to the preamble of claim 1.
  • Such disc brakes are usually pneumatically operated and equipped with automatically acting, mechanical Verschl constitunachstellvorraumen.
  • These wear adjusting devices have a very reliable effect and reduce the clearance that has become too large. They are known in different designs, such as e.g. mechanical adjuster with automatic adjustment of a friction point.
  • the adjusting device e.g. by a feed element of a brake disk application device, activated.
  • an automatic readjustment of the pads by means of the pad wear adjuster e.g. by an adjustment of variable-length pressure punches.
  • a drive rotational movement is e.g. from a torque limiting device, for example with a ball ramp, via a continuously acting clutch (slip clutch) to an adjusting spindle, e.g. a threaded pipe, a printing stamp forwarded.
  • a continuously acting clutch slip clutch
  • the threaded tubes can twist and reduce the clearance, for example, whereby brake pads can grind on the brake discs.
  • the fuel consumption of the vehicle can thereby increase.
  • a Lsymmetricspielveriererung energy consumption can be increased because a larger clearance must be run through to the brake application.
  • the energy consumption can be eg an increased compressed air consumption.
  • the object of the present invention is to provide an improved disc brake.
  • a disc brake which has a blocking device with which a rotation of a threaded tube is blocked in a blocking position.
  • the blocking device can be adjusted in a release position. In this case, this blockage is reversed and released a rotation of the threaded tube, so that readjustment due to wear of the brake lining is possible by a wear adjustment.
  • the blocking device can be returned from the release position back to the blocking position.
  • a disc brake according to the invention in particular for a motor vehicle, comprises a clamping device, preferably with a rotary lever, at least one spindle unit with a threaded tube, and at least one wear adjusting device, which can be coupled to the application device, preferably to the rotary lever, and to the at least one spindle unit interacts.
  • the disc brake has at least one blocking device which can be adjusted from a blocking position, in which the blocking device blocks a rotation of the threaded tube of the at least one spindle unit, into a release position, in which the blocking device releases a rotation of the threaded tube of the at least one spindle unit, and back is.
  • the threaded tube In the blocking position, the threaded tube is blocked against twisting. This results in a safeguard against vibrations, shaking and the like. caused clearance changes. Due to the adjustability of the blocking device in the release position, the blocking position is canceled and a rotation of the threaded tube, e.g. for the purpose of wear adjustment, it is still possible.
  • the blocking device assumes the blocking position when the disc brake is released, and the release position assumes when the disc brake is applied. This allows a coupling of the blocking device with the application device, so that the blocking device is actuated by the application device.
  • the at least one blocking device comprises at least one blocking element, which engages in the blocking position with the threaded tube and is in the blocking position out of engagement with the threaded tube. The blocking element is thus engaged with the threaded tube, for example by pressure, that the threaded tube is fixed.
  • the at least one blocking element is connected to the clamping device, preferably to the rotary lever. This results in a compact design.
  • the at least one blocking element is attached to an end face of the rotary lever. It can be made in one piece with the rotary lever. Also, a separate part is possible, which is screwed, riveted or welded.
  • the at least one blocking element has an engagement portion for engagement with the threaded tube and an end portion.
  • the at least one blocking element has an engagement portion for engagement with the threaded tube and an end portion.
  • the at least one blocking element is wedge-shaped.
  • the at least one blocking element at least partially has a profiling which corresponds to an external thread of the threaded tube and in the blocking position of the at least one blocking device is in engagement with the external thread of the threaded tube. It is advantageous if at least the engagement portion has this profiling. This can be done a positive engagement.
  • the profile of the at least one blocking element is a thread profile, wherein the thread profile corresponds to the thread profile of the external thread of the threaded pipe is particularly advantageous.
  • the at least one blocking element is designed as a circular ring section. This results in a particularly compact and material-saving construction.
  • FIG. 1 shows a schematic sectional view of a first exemplary embodiment of a disk brake according to the invention
  • FIG. a schematic, partial perspective view of a second embodiment of the disc brake according to the invention
  • a schematic plan view of the disc brake according to the invention of Fig. 2 a schematic partial plan view of the disc brake according to the invention of Fig. 3
  • a schematic, partial perspective view of a rotary lever a schematic sectional view of a first exemplary embodiment of a disk brake according to the invention
  • FIG. a schematic, partial perspective view of a second embodiment of the disc brake according to the invention
  • a schematic plan view of the disc brake according to the invention of Fig. 2 a schematic partial plan view of the disc brake according to the invention of Fig. 3
  • a schematic, partial perspective view of a rotary lever a schematic sectional view of a first exemplary embodiment of a disk brake according to the invention
  • FIG. a schematic, partial perspective view of a second embodiment of the disc brake according to the invention
  • FIG. 1 shows a schematic sectional view of a first exemplary embodiment of a disc brake 1 according to the invention.
  • disc brake 1 brake disc 2
  • brake pads 3 with brake lining carriers 3a
  • brake caliper 4 spindle units 5, 5 '
  • threaded tubes 6, 6' with non-illustrated pressure punches, pressure pads 6a, 6'a, Traverse 7, and rotary lever 8.
  • the threaded pipes 6, 6 'each have an external thread 13, 13', with which they are screwed into the traverse 7.
  • the caliper 4 is designed here as a floating caliper. Other versions are possible.
  • the x-coordinate runs parallel to a longitudinal direction of the brake disk 2, the rotation axis, not shown, extending in the direction of the y-coordinate.
  • the opposite direction of the z-coordinate is also referred to as the release direction and the direction of the y-coordinate as the application direction of the disc brake 1.
  • the rotary lever 8 is pivotable about a rotary lever axis 8d (see Fig. 2) which lies in the direction of the x-coordinate.
  • the disc brake 1 may have different power drives.
  • the rotary lever 8 is pneumatically operated by a pneumatic cylinder, for example.
  • To construction and Function of a pneumatic disc brake 1 is made to the corresponding description of DE 197 29 024 C1.
  • the disc brake 1 is shown in the first embodiment as a two-stamp brake.
  • the brake caliper 4 engages over the brake disk 2, on which the brake linings 3 with their brake pad carriers 3 a are arranged on both sides.
  • the tension-side brake pad 3 communicates with its brake pad carrier 3a with the spindle units 5, 5 'via the pressure pieces 6a, 6'a, the other brake pad is fixed in the brake caliper 4 on the other side of the brake disk.
  • a spindle unit 5 of the two spindle units 5, 5 ' is a Verschl constitunachstellvorrich- device 10 is used and is connected via a drive 9 with the rotary lever 8 in cooperation.
  • the drive 9 comprises an actuator 9 a, which is connected to the rotary lever 8, and a driver 9 b, which is in communication with the wear adjusting device 10.
  • the wear adjusting device 10 is designed here as a mechanical wear adjusting device. It also has a synchronous wheel 1 1, which via a synchronizing means 1 1 a, e.g. a chain, with another synchronous wheel 1 1 'of the other spindle unit 5' cooperates.
  • One with the synchronous wheel 1 1 'of the other spindle unit 5' connected shaft is also referred to as a driving shaft.
  • the synchronous wheels 1 1, 1 1 'and the synchronizer 1 1 a is a synchronous movement of the spindle units 5 and 5' ensured in Verschl constitunachstellvor réellen.
  • gears are also possible as synchronizing wheels 1 1, 1 1 'and synchronizing means 1 1 a.
  • a distance between the brake pads 3 and the brake disc 2 is referred to as clearance. As a result of lining and disc wear this clearance is larger.
  • the disc brake 1 comprises a blocking device 15 with a blocking element 12.
  • the blocking element 12 is here engaged with the external thread 13 of the threaded tube 6 'when the disc brake 1 is released - this released state of the disc brake 1 is shown in FIG
  • This is a blocking position of the blocking device 15.
  • the anti-vibration device causes blocking of the threaded tubes 6, 6 'to prevent a clearance change caused by, for example, jarring and vibrations. That is, it is both a Lsterspiel baseung, which leads to a reduction of the clearance, as well as a Lsterspiel baseung, which leads to an increase in the clearance, prevented.
  • FIG. 2 is a schematic, partial perspective view of a second embodiment of the disc brake 1 according to the invention is shown.
  • the disc brake 1 is shown in the release position, wherein the blocking device 15 is in the blocking position.
  • the wear adjusting device 10 is arranged centrally between the spindle units 5, 5 'in the rotary lever 8. Only the synchronous wheel 1 1 is shown.
  • Fig. 2 shows the rotary lever 8 with a rotary lever body 8a, which extends in the x direction.
  • a centrally mounted on the rotary lever body 8a Drehhebelarm 8b extends at right angles from the rotary lever body 8a in the z direction and forms its free end an articulation for the introduction of force line when applying the disc brake.
  • the rotary lever body 8a is formed on the side facing the brake pad carrier 3a with the brake pad 3 side with a semi-circular cross-section and provided on the opposite side with a flat surface on which a roller portion 14 is arranged with a semicircular cross-section.
  • the rotary lever 8 is pivotable about the rotary lever axis 8d, wherein the rotary lever axis 8d is the central axis of the Walzenabitess14.
  • the semi-circular cross-section of the rotary lever body 8a facing the brake pad carrier 3a has a central axis offset from the central axis of the roller section 14, which is illustrated in FIG.
  • the spindle unit 5 has a central axis 5a around which the threaded tube 6 is rotatable for an adjustment (infeed or return) of the brake pad 3 in the direction or opposite direction of the y-coordinate.
  • the rotary lever axis 8d is perpendicular to the central axis 5a of the spindle unit 5.
  • the not shown in detail other spindle unit 5 ' also has a central axis, which is arranged parallel to the central axis 5a of the spindle unit 5.
  • the rotary lever body 8a of the rotary lever 8 has end faces 8c, 8'c, which are each arranged in a plane lying parallel to the y-z plane.
  • the blocking element 12 of the blocking device 15 is arranged on the right in Fig. 2 shown end face 8c of the rotary lever body 8a.
  • the blocking device 15 comprises the blocking element 12 and a portion of the external toothing 13 of the threaded tube 6 of the spindle unit 5.
  • the blocking element 12 In the blocking position shown in Fig. 2 in the release position of the rotary lever 8, the blocking element 12 is in engagement with the external toothing 13 of the threaded tube 6. This presses the blocking element 12 against the threaded tube 6 and blocks it, so that the threaded tube 6 is not rotatable.
  • FIG. 3 is a schematic plan view of the disc brake 1 according to the invention according to FIG. 2.
  • the blocking element 12 is formed in a kind of wedge shape and formed on the surface of the end face 8c of the rotary lever body 8a of the rotary lever 8. It may be integrally formed with the rotary lever body 8a or may be attached thereto as a separate part.
  • the blocking element 12 has a body 12a with an engagement portion 12b and an end portion 12c.
  • the body 12a protrudes from the surface of the end face 8c in the x-direction, with the engagement portion 12b protruding further from the surface of the end face 8c than the end portion 12c.
  • the blocking element 12 In the blocking position shown in Fig. 3 at the release position of the rotary lever 8, the blocking element 12 is engaged with its engagement portion 12 b with the external thread 13 of the threaded tube 6 in engagement. This engagement is such that a rotation of the threaded tube 6 in the blocking position is not possible.
  • FIG. 3 shows a schematic partial plan view of the disc brake 1 according to the invention according to FIG. 3.
  • the rotary lever 8 and the disc brake 1 are in the application position.
  • the blocking device 15 is in its release position.
  • FIG. 5 shows a schematic, perspective partial view of the rotary lever 8 with the blocking element 12, wherein the end face 8c is shown enlarged.
  • Coordinate protruding roller portion 14 is provided.
  • the roller section 14 has a substantially semicircular cross-section, the center axis of which is the rotary lever axis 8d, which penetrates the surface of the end face 8c in an imaginary center M1.
  • a center M2 of the semi-circular cross section of the rotary lever body 8a is spaced from the center M1 by an eccentricity of the semicircular cross section of the rotary lever body 8a from the semicircular cross section of the roller section 14.
  • the blocking member 12 is formed as a circular ring portion and arranged on the outer circumference of the semi-circular end face 8c.
  • an outer diameter R1 of the semicircular cross-section of the rotary lever body 8a and thus the semicircular end face 8c is an outer diameter of the blocking element 12 designed as a circular ring section.
  • the blocking element 12 extends radially inwards toward the center M2, being delimited by a circular arc with an inner radius R2 ,
  • the circular ring section, which forms the blocking element 12 is defined with its circumference by a central angle ⁇ in the center M2.
  • the blocking element 12 protrudes from the end face 8c of the rotary lever body 8a in the direction of the x-coordinate and thus in the direction of the rotary lever axis 8d.
  • the surface of the blocking element 12 has a profiling 12d, which is a thread profile that corresponds to the external thread 13 of the threaded tube 6.
  • a part of the most protruding engaging portion 12b of the blocking member 12 engages with its profiling 12d with the external thread 13 of the threaded pipe 6.
  • This part is determined by an engagement angle ⁇ , which is substantially smaller than the central angle ⁇ , and the slope of the wedge shape of the blocking element 12.
  • the pressure angle ⁇ can amount to approximately one tenth of the central angle ⁇ .
  • the ratio of pressure angle ß to central angle ⁇ and the value of the central angle ⁇ can be determined by the geometric data of the disc brake 1.
  • the engagement angle ⁇ can be dimensioned so large that it is ensured that the engagement portion 12b is no longer in engagement with the external thread 13 of the threaded tube 6, when the wear adjuster 10 causes a rotation of the threaded tube 6.
  • the pressure angle ⁇ may be less than or equal to a so-called constructive clearance of the disc brake 1.
  • the blocking element 12 may consist of the same material as the rotary lever body 8a. However, it can also be designed as a separate part or partly as a separate part. It may also consist of a different material or a combination of different materials that are resistant to wear.
  • the blocking device 15 can be used.
  • the disc brake 1 can be compressed air actuated, but also otherwise, for example, operated by an electric motor, be formed.

Landscapes

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

Abstract

L'invention concerne un frein à disques (1), en particulier pour un véhicule automobile, comprenant un dispositif de serrage, de préférence un levier tournant (8), au moins une unité à broche (5) pourvue d'un tube fileté (6), et au moins un dispositif de rattrapage d'usure (10), qui peut être couplé au dispositif de serrage, de préférence au levier tournant (8), et coopère avec la ou les unités à broche (5). Ledit frein à disques comporte au moins un dispositif de blocage (15), lequel peut passer d'une position de blocage, dans laquelle le dispositif de blocage (15) bloque une rotation du tube fileté (6) de la ou des unités à broche (5), dans une position de libération, dans laquelle le dispositif de blocage (15) libère une rotation du tube fileté (6) de la ou des unités à broche (5), et inversement.
EP13721760.0A 2012-05-11 2013-05-10 Frein à disques Withdrawn EP2847485A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012009426A DE102012009426A1 (de) 2012-05-11 2012-05-11 Scheibenbremse
PCT/EP2013/059704 WO2013167725A1 (fr) 2012-05-11 2013-05-10 Frein à disques

Publications (1)

Publication Number Publication Date
EP2847485A1 true EP2847485A1 (fr) 2015-03-18

Family

ID=48407568

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13721760.0A Withdrawn EP2847485A1 (fr) 2012-05-11 2013-05-10 Frein à disques

Country Status (3)

Country Link
EP (1) EP2847485A1 (fr)
DE (1) DE102012009426A1 (fr)
WO (1) WO2013167725A1 (fr)

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013143994A1 (fr) * 2012-03-26 2013-10-03 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Dispositif d'application d'effort pour un frein à disque actionné par un levier rotatif

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE59301481D1 (de) * 1992-05-05 1996-02-29 Lucas Ind Plc Betätigungsvorrichtung mit selbsttätiger nachstellung an scheibenbremsen, insbesondere für lastkraftwagen und omnibusse
DE29606804U1 (de) * 1996-04-15 1997-08-07 Lucas Industries plc, Solihull, West Midlands, B91 3TX Betätigungsvorrichtung für eine Scheibenbremse, Verdrehsicherungselement und Scheibenbremse mit einer derartigen Betätigungsvorrichtung
DE19729024C1 (de) 1997-07-08 1999-01-28 Knorr Bremse Systeme Verschleißnachstellvorrichtung für Scheibenbremsen
DE102004037771A1 (de) 2004-08-04 2006-03-16 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Nachstellvorrichtung für eine pneumatisch betätigte Scheibenbremse
DE102006001543A1 (de) * 2005-03-23 2006-10-05 Continental Teves Ag & Co. Ohg Hydraulische Fahrzeugbremse mit Feststellbremsvorrichtung
DE102005023362B4 (de) * 2005-05-20 2016-04-28 Robert Bosch Gmbh Fahrzeugbremse mit integrierter Feststelleinrichtung sowie Verfahren zum Betreiben einer Feststelleinrichtung
DE102010031704A1 (de) * 2010-07-21 2012-01-26 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Scheibenbremse für ein Nutzfahrzeug

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013143994A1 (fr) * 2012-03-26 2013-10-03 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Dispositif d'application d'effort pour un frein à disque actionné par un levier rotatif

Also Published As

Publication number Publication date
WO2013167725A1 (fr) 2013-11-14
DE102012009426A1 (de) 2013-11-14

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