WO2020002156A1 - Dispositif de rattrapage permettant le rattrapage de jeu d'un frein à disque, frein à disque et procédé de rattrapage - Google Patents

Dispositif de rattrapage permettant le rattrapage de jeu d'un frein à disque, frein à disque et procédé de rattrapage Download PDF

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Publication number
WO2020002156A1
WO2020002156A1 PCT/EP2019/066496 EP2019066496W WO2020002156A1 WO 2020002156 A1 WO2020002156 A1 WO 2020002156A1 EP 2019066496 W EP2019066496 W EP 2019066496W WO 2020002156 A1 WO2020002156 A1 WO 2020002156A1
Authority
WO
WIPO (PCT)
Prior art keywords
brake
disc
toothing
toothed
bushing
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/EP2019/066496
Other languages
German (de)
English (en)
Inventor
Michael Peschel
Robert Trimpe
Daniel Krenn
Johannes Wahl
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 WO2020002156A1 publication Critical patent/WO2020002156A1/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
    • F16D65/14—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
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • 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
    • 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

Definitions

  • the present invention relates to an adjusting device for adjusting an air gap of a disc brake for a commercial vehicle according to the preamble of claim 1 and a disc brake for a commercial vehicle and a method for adjusting an air gap of a disc brake.
  • Such adjustment devices serve to compensate for wear-related changes in an air gap between the brake pads and the brake disc.
  • the adjusting device is activated by actuating a brake lever in which an adjuster drive is driven.
  • the adjusting device thus ensures a constant clearance between the brake disc and brake pads, such a constant clearance being necessary in order to keep the response times of the brake short and to ensure that the brake disc can move freely.
  • the drive rotary motion is usually passed on from a torque limiting device, in particular in the form of a ball ramp coupling, to a threaded spindle of a brake plunger.
  • the air gap is continuously adjusted.
  • a drive section of a bolt of the adjusting device which is coupled via an overload clutch to a toothed sleeve receiving the threaded spindle, is connected to a toothed disk which forms a holding friction point with the collar bushing of a head friction point.
  • This head friction point is formed by an end profile of the toothed washer and a bottom toothing in a receptacle of the flange bushing, in which the toothed washer lies.
  • the object of the present invention is to provide a further improved adjustment device and an improved disc brake. Another object is to provide an improved method for adjusting a disc brake clearance.
  • the tasks are solved by an adjusting device with the features of claim 1, a disc brake with the features of claim 7 and by a method with the features of claim 8.
  • the adjusting device according to the invention for adjusting an air gap of a disc brake for a commercial vehicle has an adjusting drive, on each of which a rolling element arrangement is arranged axially on both sides.
  • One of the rolling element arrangements is designed as a rolling bearing and one as a ball ramp coupling with a freewheel.
  • the adjustment device also has an overload clutch, a force storage element for generating a biasing force of the Kugelrampenk clutch development, the freewheel and the overload clutch, a flange bushing which is connected at one end to a bearing ring and a bolt which extends through the flange bushing and is connected in a rotationally fixed manner to the flange bushing on.
  • a toothed lock washer is coupled in a rotationally fixed manner to a drive section of the bolt and, together with the collar bushing, forms a head friction point with a holding torque.
  • the head friction point is formed by a front toothing of the toothed disc and a bottom toothing of a receptacle of the flange bushing.
  • the face teeth of the toothed lock washer and the bottom teeth of the receptacle of the flange bushing are, seen in the circumferential direction, trapezoidally shaped in cross section with two bevels falling off a plateau.
  • the spur toothing of the toothed disc in cooperation with the bottom toothing of the flange bushing, slides back into one before the current braking process along the abutting bevel of the toothing set position.
  • the angle of rotation by which the toothed disk is rotated relative to the flange bushing reaches a value at which the plateaus of the spur toothing of the toothed disk and the bottom toothing of the flange bushing lie on one another.
  • the toothed disc is rotated relative to the flange bushing by a further enlarged angle of rotation.
  • an amount of the slope of the bevels adjacent to a plateau is the same as the respective toothing, that is, the slope of the bevels rising to a plateau is equal to the slope of the bevels descending from the plateau.
  • the width of the plateaus is smaller than the width of the slopes.
  • the tooth pitch of the end toothing of the toothed disk and the bottom toothing of the receptacle of the flange bushing is between 0.10 mm and 0.12 mm.
  • the disc brake according to the invention which has a brake caliper encompassing a brake disc, and an application device for applying the disc brake by means of two displaceably guided brake stamps, which can be pushed axially to the axis of rotation of the brake disc via a brake lever, against a brake pad applying on the application side, each of the brake stamps being a pressure piece and a rotatable one Has threaded spindle, whose external thread engages in an internal thread of a cross member and an adjusting device coupled to the brake lever for adjusting an air gap, is characterized by an adjusting device as described above.
  • the method according to the invention for adjusting an air gap of a disc brake for a commercial vehicle disc brake with an adjustment device as described above is characterized in that the air gap is only adjusted step by step.
  • FIG. 1 is a schematic sectional view of an embodiment variant of a disc brake according to the invention.
  • FIG. 2 is a schematic sectional view of an embodiment of an adjusting device
  • FIG. 3 is a perspective schematic view of a toothed disc
  • FIG. 4 shows an enlarged section of the toothed disk from FIG. 3 with
  • Fig. 5 is a schematic perspective view of an embodiment of a collar bushing of the adjusting device and Fig. 6 is an enlarged detail of the collar bush shown in Fig. 5 showing the bottom teeth of the receptacle of the collar bush.
  • top, bottom, left, right, front, rear, etc. refer exclusively to the exemplary representation and position of the adjusting device, the disc brake, the brake disc, the collar bushing, the toothed disc and selected in the respective figures like. These terms are not to be understood as restrictive, i.e. these references can change due to different working positions or the mirror-symmetrical design or the like.
  • reference number 1 overall designates an embodiment variant of a disk brake according to the invention, in which an adjusting device according to the invention for adjusting an air gap of the disk brake is installed.
  • the disc brake 1 has a brake disc 4 which can be rotated about an axis of rotation A and which is overlapped by a brake caliper 2 designed here as a floating caliper. Are on both sides of the brake disc 4
  • Brake pads 3 are arranged with each pad carrier and friction lining.
  • the upper brake pad 3 in FIG. 1 is referred to as the application-side brake pad and the lower brake pad 3 in FIG. 1 is referred to as the reaction-side brake pad.
  • An application device for applying the disc brake 1 has two brake plungers 5 which are displaceable parallel to the axis of rotation A and which can be pressed against the application of the brake lining 3 axially to the axis of rotation A of the brake disc 4 via a brake lever 13.
  • Each of the brake plungers 5 has a pressure piece 11 and a rotatable threaded spindle 10, the external thread of which engages in an internal thread of a cross member 12, so that the threaded spindle 10 can be moved relative to the cross member 12 in the direction of the axis of rotation of the brake disk 4 by rotational movements.
  • An adjustment device 6 for adjusting an air gap is coupled to the brake lever 13.
  • a clearance between the brake linings 3 and the brake disc 4 in the released position of the disc brake 1 is referred to as this.
  • This clearance is increased by the lining and disc wear without adjustment, which is due to an increased actuation stroke of an actuation mechanism of the brake disc 4, here one Enlargement of a pivoting angle of the brake lever 13 would go hand in hand, as a result of which the maximum output of the disc brake 1 could not be achieved.
  • the term "re-adjustment” defines an air gap reduction.
  • a predetermined nominal air gap is determined by the geometry of the disc brake 1 and has a so-called constructive air gap.
  • the adjusting device 6 accordingly reduces an existing air gap if this is too great in relation to the previously specified nominal air gap.
  • the adjusting device 6 essentially has, as shown in FIG. 2, an adjuster drive 14, a roller bearing 15, a ball ramp clutch 16 with free running, an overload clutch 17, a toothed sleeve 19, an adapter sleeve 20 and an energy storage element 18.
  • a rolling element arrangement is arranged axially on both sides of the adjuster drive 14.
  • One of the rolling element arrangement is designed as a rolling bearing 15 and a second as a ball ramp coupling 16 with a freewheel.
  • an overload clutch 17 is arranged below the ball ramp clutch 16, which, when the adjuster drive 14 is activated, causes the ball ramp clutch 16 to rotate on a toothed sleeve 9, which is non-rotatably coupled to an adapter sleeve 20. The rotary motion is finally transmitted to the threaded spindle 10 via this clamping sleeve 20 for axial adjustment of the air gap.
  • a collar bushing 8 which has a cylindrical body with a through bore, a disk-like collar and a circumferential receiving wall.
  • a bolt 7 extends through the through bore. This bolt 7 is coupled in a rotationally fixed manner to a toothed disc 9, which lies in the receptacle of the collar bushing 8.
  • the toothed disk 9 is formed with a spur toothing 91.
  • the collar bushing 8 has bottom teeth 81 at the bottom of the receptacle of the collar bushing 8.
  • the end teeth 91 of the toothed disc 9 and the bottom teeth 81 of the collar bush 8 lie one on top of the other in the assembled state and thus form a head friction point.
  • the toothed washer 9 On the side of the toothed washer 9 facing away from the bottom toothing 81 of the collar bushing 8, the latter is firmly connected to the drive section 71 of the bolt 7 after assembly, for example via a lock nut 23 which presses an inner shoulder 97 of the toothed washer 9 against a radial shoulder of the bolt 7 ,
  • the axial connection of the bolt 7 with the toothed disk 9 makes it possible to direct the pretensioning force exerted by the energy storage element 18, which is designed here as a helical compression spring, to the toothed disk 9 and its spur toothing 91 of the toothed disk 9, which engages with the bottom toothing 81 of the collar bushing 8 stands.
  • the energy storage element 18 which is designed here as a helical compression spring
  • an outer profile 82 with axially extending teeth is molded into the outside of the receiving wall of the collar bushing 8, onto which a bearing ring 21 is slid in an axially and rotationally fixed manner, an inner profile of the bearing ring 12 with the outer profile of the collar bushing 8 cor respondiert.
  • An axial securing device 22, for example a shaft securing ring, is inserted in a groove 87 in the upper quarter of the receiving wall and forms an axial stop in the upward direction for the bearing ring 21.
  • the front toothing 91 of the toothed disk 9 and the bottom toothing 81 of the receptacle of the collar bushing 8 are trapezoidal in cross-section in cross section with two of a plateau 83, 93 sloping slopes 84, 85, 94, 95 formed ge.
  • the plateaus 93 of the spur toothing 91 of the toothed lock washer 9 lie between two respective bevels 84, 83 of two adjacent teeth of the bottom toothing 81 of the collar bushing 8.
  • an angle of rotation of the toothed disk 9 relative to the collar bushing 8 is so small that, starting from the initial position described above as an example, the plateau 93 of the teeth of the spur teeth 91 of the toothed disk 9 does not yet reach the plateau 83 of the bottom teeth 81 of the flange bushing 8 is reached and thus when the pretensioning force is subsequently applied to the toothed disc 9, the end toothing 91 of the toothed disc 9 slides back into the starting position in the bottom toothing 81 of the flange bushing 8.
  • the toothed disc 9 is rotated relative to the collar bushing 8 to an extent in which the plateaus 93 of the spur teeth 91 of the toothed disc 9 each have plateaus 83 reach the bottom teeth 81 of the collar bushing 8. This angular position remains even when the toothed disk 9 is again acted upon with the pretensioning force exerted by the energy storage element 18, the plateaus 83, 93 lying against one another in this position. A predetermined readjustment of the clearance is thus effected with this degree of wear.
  • the toothed disc 9 is rotated by an angle relative to the flange bushing 8 to such an extent that a plateau 93 of the toothed disc 9 about io
  • the toothed disk 9 After the toothed disk 9 is subsequently acted upon by the pretensioning force of the energy storage element 18, the toothed disk 9 is pressed forward by this pretensioning force in the adjustment direction into the next stable position, in which a respective plateau 93 of the spur teeth 91 of the toothed disk 9 between the tooth flanks of the next teeth, is pressed over the plateau 83, which leads to a correspondingly increased readjustment movement.
  • the amount of slope of the slopes 84, 85, 94, 95 adjacent to a plateau 83, 93 is the same.
  • the pitch angle of a tooth of the front toothing 91 and the bottom toothing 81 is equal to the slope angle beyond a respective plateau 83, 93 of the tooth.
  • a positive slope is understood to mean a slope that leads from the base of the toothing to a respective plateau of the toothing. Accordingly, slopes that lead from a respective plateau to the base have a negative slope.
  • the width of a respective plateau 83, 93, viewed in the circumferential direction, is smaller than the width of the bevels 84, 85, 94, 95.
  • the tooth pitch of the front toothing 91 of the toothed disk 9 and the bottom toothing 81 of the receptacle of the collar bush 8 is preferably between 0.10 mm and 0.12 mm.
  • the present adjustment device enables large wear values per brake actuation to be adjusted faster and more efficiently than with adjustment devices with constant adjustment speed.

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

Abstract

L'invention concerne un dispositif de rattrapage (6) permettant le rattrapage de jeu d'un frein à disque (1) de véhicule utilitaire et présentant : un mécanisme (14) de rattrapage sur lequel est disposé axialement respectivement de part et d'autre un agencement d'éléments roulants, l'un étant réalisé sous la forme d'un roulement à rouleaux (15) et l'autre sous la forme d'un coupleur à rampe à billes (15) à roue libre (16) ; un coupleur de surcharge (17) ; un élément d'accumulation de force (18) servant à produire une force de précontrainte du coupleur à rampe à billes (15), de la roue libre (16) et du coupleur de surcharge (17) ; une douille à collet (8) qui est reliée à une extrémité à une bague de palier (21) ; un goujon (7) traversant la douille à collet (24) et couplé bloqué en rotation à la douille à collet (24) ; un disque denté (9) couplé bloqué en rotation à une section d'entraînement (71) du goujon (7) et formant avec la douille à collet (8) un sommet de friction présentant un couple de retenue. Le sommet de friction est formé par un profil frontal (91) du disque denté (9) et une denture de fond (81) d'un logement de la douille à collet (8), le profil frontal (91) du disque denté (9) et la denture de fond (81) du logement de la douille à collet (8) présentant, vus en direction périphérique, une section transversale trapézoïdale comportant deux plans inclinés (84, 85, 94, 95) descendant à partir d'un plateau (83, 93). L'invention concerne par ailleurs un frein à disque pour véhicule utilitaire, ainsi qu'un procédé de rattrapage de jeu d'un frein à disque.
PCT/EP2019/066496 2018-06-27 2019-06-21 Dispositif de rattrapage permettant le rattrapage de jeu d'un frein à disque, frein à disque et procédé de rattrapage Ceased WO2020002156A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018115494.1 2018-06-27
DE102018115494.1A DE102018115494A1 (de) 2018-06-27 2018-06-27 Nachstelleinrichtung zum Nachstellen eines Lüftspiels einer Scheibenbremse, Scheibenbremse und Verfahren zum Nachstellen

Publications (1)

Publication Number Publication Date
WO2020002156A1 true WO2020002156A1 (fr) 2020-01-02

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PCT/EP2019/066496 Ceased WO2020002156A1 (fr) 2018-06-27 2019-06-21 Dispositif de rattrapage permettant le rattrapage de jeu d'un frein à disque, frein à disque et procédé de rattrapage

Country Status (2)

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DE (1) DE102018115494A1 (fr)
WO (1) WO2020002156A1 (fr)

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014113826A1 (de) 2014-09-24 2016-04-07 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Nachstelleinrichtung einer Scheibenbremse, und eine entsprechende Scheibenbremse

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014113826A1 (de) 2014-09-24 2016-04-07 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Nachstelleinrichtung einer Scheibenbremse, und eine entsprechende Scheibenbremse

Also Published As

Publication number Publication date
DE102018115494A1 (de) 2020-01-02

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