WO2016046066A1 - Dispositif de rattrapage pour un frein à disque et frein à disque correspondant - Google Patents

Dispositif de rattrapage pour un frein à disque et frein à disque correspondant Download PDF

Info

Publication number
WO2016046066A1
WO2016046066A1 PCT/EP2015/071389 EP2015071389W WO2016046066A1 WO 2016046066 A1 WO2016046066 A1 WO 2016046066A1 EP 2015071389 W EP2015071389 W EP 2015071389W WO 2016046066 A1 WO2016046066 A1 WO 2016046066A1
Authority
WO
WIPO (PCT)
Prior art keywords
brake
adjusting device
coupling
disc
clamping sleeve
Prior art date
Application number
PCT/EP2015/071389
Other languages
German (de)
English (en)
Inventor
Matthias Klingner
Michael Peschel
Robert Trimpe
Original Assignee
Knorr-Bremse Systeme für 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 für Nutzfahrzeuge GmbH filed Critical Knorr-Bremse Systeme für Nutzfahrzeuge GmbH
Publication of WO2016046066A1 publication Critical patent/WO2016046066A1/fr

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
    • 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
    • F16D55/224—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 with a common actuating member for the braking members
    • F16D55/225—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 with a common actuating member for the braking members the braking members being brake pads
    • F16D55/2255—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 with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is pivoted

Definitions

  • the invention relates to an adjusting device of a disc brake, in particular for a motor vehicle, according to the preamble of claim 1.
  • the invention relates to a corresponding disc brake.
  • Vehicles and certain technical devices often use friction brakes to convert kinetic energy. Preference is given here, especially in the passenger car and commercial vehicle sector, the disc brake.
  • this consists of a caliper together with internal mechanics, usually two brake pads and the brake disc.
  • the cylinder forces are introduced via a pneumatically actuated cylinder, reinforced by an eccentric mechanism and transmitted as clamping force via threaded spindles on brake pads and brake disc, which is compensated by the threaded spindles wear of the brake disc and brake pads.
  • the application forces act on both brake pads on the brake disc. Since the pads are structurally designed as wearing parts, they are generally softer than the brake disc, i. the pads learn about their service life, a change in the lining thickness, they wear out.
  • the brake disc can also wear. From this wear arises the necessity that a wear adjustment compensates for the change by the wear and thus sets a constant air play. A constant air clearance is needed to keep the response times of the brake small, to ensure the freedom of the brake disc and vorzuhalten a stroke reserve for Grenzbelastungst.
  • 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) forwarded to an adjusting spindle of a plunger.
  • the air play is adjusted continuously.
  • An example of an adjusting device describes the document DE 10 2012 108 672 B3.
  • the object of the present invention is to provide an improved adjusting device.
  • Another object is to provide an improved disc brake.
  • the object is achieved by an adjusting device with the features of claim 1, and a disc brake having the features of claim 16.
  • An adjusting device which provides a compact structure above and radially around a threaded temple.
  • the adjuster will open and z.T. arranged over the threaded temple. Replacement of the adjuster during maintenance and repair is easier than the prior art.
  • a disc brake according to the invention preferably compressed air actuated, in particular for a motor vehicle, with a brake application, preferably with a brake rotary lever, at least one spindle unit, each with a threaded stem, and at least one Verschl constitunachstellvorides, which is coupled to the application device, preferably with the brake rotary lever, is designed in that the wear adjusting device has the adjusting device according to the invention.
  • the collar is provided with the bearing ring for a rigid attachment in a caliper of the assigned disc brake. This results in a simple assembly and robust fixation of the adjusting device in the brake caliper.
  • the bolt has a drive section, which is arranged in the collar bushing in a receptacle formed by a circumferential receiving wall. So a compact and robust construction can be achieved.
  • drive portion of the bolt is connected to a toothed disc, which forms a Kopfreibstelle with a holding torque with the collar bushing.
  • the head release point can be formed with the holding torque with an end profile of the toothed disk and a bottom toothing of the receptacle of the collar bush formed by a circumferential receiving wall.
  • the bolt and the clamping sleeve are coupled by means of a disengageable reverse rotation coupling.
  • the reverse rotation coupling between the bolt and the clamping sleeve is formed from a coupling portion of a driven head of the bolt and a head portion of the clamping sleeve.
  • the reverse-rotation clutch can be disengaged relative to the bolt by means of an axial displacement of the clamping sleeve.
  • Such a disengageable reverse rotation clutch can be actuated by the threaded stem. In this case, a component load is reduced. In addition, maintenance is facilitated.
  • a shim to adapt a length of the adjusting device is arranged between the collar bushing and a cone bushing of the freewheel. For an adjustment of the length of the adjusting device is possible.
  • the holding moment of the Kopfreibstelle can be set to limit a minimum adjustment movement.
  • the adjuster drive and the WälzSystem für extract are arranged around the flanged bush around, the toothed sleeve and the power storage element are arranged around the clamping sleeve around, and the freewheel and the overload clutch are arranged in a coupling region of the clamping sleeve with the bolt.
  • this gives the advantage of a compact and robust construction.
  • a simple construction also results if the force storage element is arranged between a support disk connected to the clamping sleeve and the slip clutch. By different thicknesses of the support disk, it is possible in a simple manner to adjust the bias of the power storage element for the functional groups of the adjusting device.
  • the readjusting drive has a switching disk with a coupling portion and a gear, wherein the coupling portion is formed as a Drehkulis- se with a game, which forms a constructive clearance of the disc brake to be assigned.
  • the coupling portion is formed as a Drehkulis- se with a game, which forms a constructive clearance of the disc brake to be assigned.
  • the adjusting device of the wear adjusting device is placed on the threaded temple of the at least one spindle unit of the disc brake and at least partially surrounds the threaded temple.
  • a disc brake further comprises at least two spindle units, each with a threaded temple, wherein the threaded pistons are screwed into a crossmember, wherein the traverse with the application device, preferably with the brake rotary lever cooperates, and a synchronizer.
  • the wear adjusting device furthermore has a driver unit, which is coupled to the threaded spindle of the other spindle unit of the two spindle units of the disc brake.
  • the synchronizer is disposed on the crosshead. The synchronizer located within the seat housing can lead to a shortened design of the caliper.
  • each coupling wheel has a synchronizing portion for cooperation with the synchronizing means.
  • the coupling wheels of the synchronizer are arranged fixed and rotatable on the traverse. This results in a compact design.
  • the traverse with the thread stamper and the synchronizer is designed as a preassembled function module.
  • the crossbeam can be used as a pre-synchronized unit with the thread dies in the maintenance or service case without an increased risk of incorrect assembly (eg unsynchronized threaded pistons).
  • Figure 1 is a schematic sectional view of an embodiment of a disc brake according to the invention with an embodiment of a wear adjustment device according to the invention.
  • Fig. 2 is a schematic sectional view of the invention
  • FIG. 3-4 are schematic sectional views of an embodiment of an adjusting device of a wear adjusting device according to the invention according to Fig. 1;
  • Fig. 5 is a schematic sectional view of the embodiment of
  • FIG. 6 is a schematic perspective view of a toothed wheel.
  • Fig. 1 is a schematic sectional view of an embodiment of a disc brake 1 according to the invention with an embodiment of a wear adjusting device 1 1 according to the invention.
  • FIG. 2 shows a schematic sectional view of the disc brake 1 according to the invention according to FIG. 1 in a plane of a brake disc axis 2 a perpendicular to the sectional plane of FIG. 1.
  • the disk brake 1 has a brake disk 2 with the brake disk axis 2 a.
  • the brake disk 2 is overlapped by a, designed here as a floating caliper 4 caliper.
  • a brake pad 3 On both sides of the brake disc 2, a brake pad 3, each with a brake pad carrier 3a is arranged.
  • the brake pad 3 located on the right side in FIG. 1 is called the brake pad 3 on the brake application side and the other is called the brake pad 3 on the reaction side.
  • the disc brake 1 as a two-stamp brake with two spindle units 5 and 5 ' educated.
  • Each spindle unit 5, 5 ' has a threaded rod 6, 6', which is designed here as a solid shaft.
  • the application-side brake pad carrier 3a is connected to the spindle units 5, 5 'via plungers 6e, 6'e, which are arranged at the ends of the thread tamps 6, 6', in conjunction.
  • the other, reaction-side brake pad carrier 3a is fixed on the other side of the brake disc in the brake caliper 4.
  • the threaded pistons 6, 6 ' are each arranged rotatably in threads 6d, 6'd in a traverse 8, which is also referred to as a bridge.
  • the threaded pistons 6, 6 'each have a lining-side shaft end 6a, 6'a and an application-side shaft end 6b, 6b'.
  • a lining-side shaft end 6a, 6'a is in communication with the pressure piece 6e, 6'e and is in this case peg-shaped.
  • the threaded pistons 6, 6 ' are each provided with a number of axial grooves 6c, 6'c, which in this embodiment each extend from the application-sapping shaft end 6b, 6'b over approximately two-thirds of the length of the respective threaded stamper 6, 6 extend in the direction of the respective lining-side shaft end 6a, 6'a on the respective circumference of the threaded stem 6, 6 'in its longitudinal direction.
  • the thread 6d, 6'd as an external thread on the threaded rod 6, 6 'and as a corresponding internal thread in the cross-member 8 is designed here with a slope in the area of self-locking.
  • the term axial position here means a position of the threaded pistons 6, 6 'in the axial direction of the brake disk axis 2 a and Axles 5a, 5'a meant.
  • the brake rotary lever 9 has a lever body 9a which is in cooperation with the cross member 8.
  • the crossmember 8 is adjustable in the direction of the brake disk axis 2 a by the brake rotary lever 9.
  • a movement on the brake disk 2 is used as Zuspannbewe- referred to, and a movement in the opposite direction is called release movement.
  • a return spring 7 is received in the middle of the cross member 8 in a corresponding recess on the lining side of the cross member 8 and is supported on the brake caliper 4 from. By means of the restoring spring 7, the traverse 8 is adjusted during the release movement into the disengaged position of the disc brake 1 shown in FIG.
  • a distance between the brake pads 3 and the brake disc 2 in the released position is referred to as a clearance.
  • this clearance is larger. If this is not compensated, the disc brake 1 can not reach its peak performance because an actuating stroke of the actuating mechanism, i. Here, the actuation stroke or a pivot angle of the brake rotary lever 9, is increased.
  • the disc brake 1 may have different power drives.
  • the rotary lever at 9 is here z. B. pneumatically actuated.
  • a pneumatic disc brake 1 For construction and function of a pneumatic disc brake 1, reference is made to the corresponding description of DE 197 29 024 C1, in particular to DE 10 2012 108 672 B3.
  • the wear adjusting device 1 1 is designed for the wear adjustment of a predetermined clearance, which is referred to as a nominal clearance.
  • the previously defined clearance is determined by the geometry of the disc brake 1 and has a so-called constructive clearance, in other words, the wear adjusting device 1 1 reduces an existing clearance when it is related to this on the previously set clearance is too big.
  • the wear adjusting device 1 1 here comprises an adjusting device 1 1 a and a driving device 1 1 b.
  • the adjusting device 11a is arranged on one spindle unit 5 coaxially with it, with its threaded spindle 6 and an adjuster axis 5a.
  • the components and functional groups of the adjusting device 1 1 a are arranged in the direction of the adjuster axis 5a.
  • a part of the adjusting device 11 overlaps the application-side shaft end 6b of the associated threaded stem 6 and extends to the lining-side shaft end 6a of the associated threaded stamper 6 over approximately half the total length of the axial grooves 6c of the associated thread stamper 6 and is in this region arranged the threaded temple 6 around.
  • the Nachstehinnchtung 1 1 a is arranged concentrically to the associated screw-6 and encloses this at least partially.
  • a further part of the adjusting device 1 1 a in extension of the application-side shaft end 6b of the associated threading stamp 6 is arranged up to a bearing ring 12. This latter area makes up about half of the total length in the direction of the adjuster axis 5a of the adjuster 11a.
  • the adjusting device 11a is mounted in the brake caliper 4 in a receiving bore 4b within a peripheral wall 4a of the caliper 4. This will be described in detail below in connection with FIG.
  • the receiving bore 4b is closed by a lid 12a here.
  • the entrainment device 1 1 b is coaxial with the other spindle unit 5 ', arranged to the threaded shaft 6' and a driving axle 5'a together with a sensor not shown in detail.
  • a detailed description of the entrainment device 11b can be found in DE 10 2012 108 672 B3, to which reference is made here.
  • the adjuster axle 5a, the driver axle 5'a and the brake disk axle 2a are arranged parallel to one another.
  • the adjusting device 1 1 a of the wear adjusting device 1 1 is connected via a drive 10 with the rotary lever 9 in cooperation.
  • the drive 10 comprises an unspecified actuator, which is connected to the brake rotary lever 9, and a gear 13b of a readjustment drive 13 (see FIGS. 3-5) of the readjustment device 11a.
  • the actuator is provided at its clamping end with an actuating contour, which z. B. is tooth-shaped and is in engagement.
  • a clearance is provided between the gear 13b of the readjustment drive 13 of the adjusting device 1 1 a. This will be explained below in connection with the adjusting device 1 1 a.
  • This game represents, taking into account the ratios on the brake lever 9, the constructive clearance of the disc brake. 1
  • an actuation of the adjusting device 1 1 a takes place only after the cross member 8 has been displaced at a brake application of the disc brake 1, ie during braking, by a greater distance than the constructive clearance on the brake disc 2.
  • the adjusting device 1 1 a and the driving device 1 1 b are coupled by a synchronizing device not described here in detail, which is explained in detail in DE 10 2012 108 672 B3, and to which reference is made.
  • the synchronizing device makes it possible for a rotational movement of the threaded stem 6 about the adjuster axis 5a to cause a corresponding rotational movement of the threaded stamper 6 'about the driving axis 5'a and vice versa.
  • the synchronizing device is arranged here on a truss top of the crossbeam 8 between the traverse 8 and the brake rotary lever 9 and comprises a coupling wheel 20a which is coupled to the threaded ram 6 of a spindle unit 5 and to the adjusting device 11a, another coupling wheel 20 'a, which is coupled to the threaded shaft 6' of the other spindle unit 5 'and to the driver 1 1 b, and a synchronizer 20d, with which the coupling wheels 20a and 20'a are coupled.
  • the synchronizer 20d here is a chain.
  • the coupling wheels 20a, 20'a formed as sprockets. This is a synchronous movement of the threaded shaft 6, 6 'of the spindle units 5 and 5' in Verschl constitutes and 5' in Verschl constituting a chain.
  • Adjustment device 1 1 a and settings during maintenance work, eg. B. pad change, guaranteed.
  • Each coupling wheel 20a, 20'a is accommodated in a stationary manner in a rotatable manner in the cross-member 8 in a receptacle 8a, 8'a corresponding to the respective associated coupling wheel 20a, 20'a.
  • the receptacles 8a, 8'a have here with their openings to the Zuspannsei- te of the disc brake 1, i. they are formed by the truss top in the Traverse 8.
  • the coupling wheel 20a which is associated with the spindle unit 5 with the adjusting device 1 1 a, a hollow cylindrical body having formed on its inner wall with an axially extending inner profile. This inner profile cooperates with the lining-side end of the adjusting device 1 1 a, which will be explained below.
  • FIG. 3 and 4 show schematic sectional views of an embodiment of the adjusting device 1 1 a of the wear adjusting device 1 1 according to FIG. 1 according to the invention.
  • the adjusting device 1 1 a is shown rotated about the Nachstellerachse 5 by 90 °. 5 shows a schematic sectional view of the embodiment.
  • top or “top” is to be understood as the side of the respective component which, when installed, faces the application side in the disk brake 1, i. facing away from the brake disc 2.
  • the “underside” of the respective component or “bottom” then points to the brake disk 2.
  • the adjusting device 1 1 a comprises the bearing ring 12, the Nachstellerantrieb 13, a roller bearing 14, a ball ramp clutch 15, a freewheel 16, an overload clutch 17, a toothed sleeve 18, a clamping sleeve 19, a coupling device 20, at least one force storage element 22, a Bolt 23 and a collar bushing 24 with a toothed disc 26th
  • the bearing ring 12 serves to support and support the adjusting device 1 1 a on the brake caliper 4 and will be described in more detail below in connection with FIG.
  • the adjuster drive 13 has a switching disk 13a and the gear 13b.
  • the indexing disk 13a is provided in its upper portion with a circumferential coupling section 13c, on which the gearwheel 13b is mounted so as to be pivotable about the adjuster axis 5 in the manner of a rotating link.
  • the gear 13b is formed as a spur gear with at least a partial toothing and about a certain pivot angle, which corresponds to the above-mentioned constructive clearance, relative to the switching disc 13a pivoted.
  • the rolling bearing 14 is embodied here as an angular contact ball bearing and thus transmits not only axial but also radial forces, ie the indexing disk 13a is supported both axially and radially by the rolling bearing 14 with respect to the collar bushing 24 fixed in the brake caliper 4 and rotatable relative thereto.
  • the collar bushing 24 will be explained in more detail below.
  • the switching disc 13a is also part of the ball ramp clutch 15 and has on its underside a rolling element on.
  • This rolling element arrangement on the underside of the switching disk 13a is formed by ramp balls 15b in a cage 15e and a ramp ring 15a of the ball ramp coupling 15. Both the underside switching disc 13a and the opposite top of the ramp ring 15a are formed with not shown ball ramps 15c, 15d for the ramp balls 15b, which are arranged between the switching disc 13a and the ramp ring 15a.
  • the ramp ring 15a and the indexing disk 13a are further coupled by means of an elastic coupling element, for example a torsion spring 15f.
  • the torsion spring 15f is arranged between the underside of the indexing disk 13a and the upper side of the ramp ring 15a and acts on the one hand on the ball ramp clutch 15 such that the ramp balls 15b in the ball ramps 15c, 15d are in a certain position or placed in such a position.
  • the freewheel 16 includes the ramp ring 15a, a tapered bush 16a and freewheeling balls 16b.
  • the cone bushing 16a has in its upper portion a disk-shaped cover wall 16e with a central passage opening 16h. The outer edge of the top wall 16e is connected to a downwardly extending and downwardly radially outwardly widening cone portion 16f which is connected at its lower outer edge to a radially outwardly extending annular coupling flange 16g.
  • the free-wheel balls 16b are arranged between the underside of the ramp ring 15a and a conical outer side of the cone bush 16a with the formation of a freewheeling function in a manner not shown.
  • the free-wheel balls 16b are received in a rolling element receptacle 16c, which is not shown in detail, and which is surrounded by a circumferential wall section, and supported on the conical outer side of the taper bushing 16a on the conical section 16f in rolling element receptacles, likewise not shown 16d off.
  • the freewheel 16 is biased by the ramps 15c, 15d and the torsion spring 15f.
  • the ball ramp clutch 15 with the freewheel 16 thus comprises the drive 13 with the indexing disk 13a, ramp balls 15b, the ramp ring 15a, the freewheeling balls 16b and the tapered bushing 16a.
  • the overload clutch 17 is formed from the annular coupling flange 16g of the tapered bush 16a and an annular coupling portion 18a of the toothed sleeve 18.
  • the toothed sleeve 18 has a hollow cylindrical body with a circular cross section. At the upper end of the hollow cylindrical body, the annular coupling portion 18a is attached and extends radially outward.
  • the hollow cylindrical body is provided with a transfer section 18b, which has in the longitudinal direction of the Nachstellerachse 5a extending, circumferentially distributed, not designated te longitudinal projections which protrude radially inwardly.
  • annular coupling portion 18a of the toothed sleeve 18 unspecified depressions are formed distributed on the circumference, which are not shown here in detail downwardly from the underside of the annular coupling flange 16g of the tapered bush 16 protruding projections or teeth with a certain profile in a form-fitting engagement.
  • the recesses correspond to the protruding projections or teeth of the annular coupling flange 16g.
  • the hollow cylindrical body of the toothed sleeve 18 is pushed from above onto the clamping sleeve 19, wherein the radially inwardly projecting longitudinal projections of the toothed sleeve 18 with longitudinal grooves 19 d of the clamping sleeve 19 are engaged.
  • the longitudinal grooves 19d of the clamping sleeve 19 form radially inwardly projecting longitudinal projections seen from the inside.
  • the longitudinal grooves 19d correspond in cross-section to the shape of the longitudinal projections of the toothed sleeve 18 and are formed so that in this way radially positive engagement between each other and an axial Rela- tivieri between the toothed sleeve 18 and clamping sleeve 19 is made possible.
  • the clamping sleeve 19 has a hollow cylindrical body 19a with a lower coupling end 19b and an inner space 19c.
  • the cross section of the body 19a is circular.
  • the longitudinal grooves 19d and further longitudinal grooves 19e are alternately formed. Also the others
  • Longitudinal grooves 19e are formed like the other longitudinal grooves 19d in the body 19a.
  • the further longitudinal grooves 19e extending from the lower coupling end 19b of the clamping sleeve 19 to an upper end of the hollow cylindrical body 19a, which goes up into a short conical portion with reduction of the inner diameter, and in which the ends of the longitudinal grooves 19e terminate.
  • This is followed by another, short hollow cylindrical section, which is rounded at its upper end and forms a shoulder 19h with an annular cover section.
  • An inner edge of this cover portion is bent upwardly to form another hollow cylindrical head portion 19f having a cover portion having a head opening 19b.
  • An inner diameter of the head portion 19f is smaller here than the inner diameter of the short hollow cylindrical portion below.
  • the head portion 19f is provided for coupling with the bolt 23, which will be described in detail below.
  • a coupling portion 19i which is approximately one quarter of the total length of the clamping sleeve 19.
  • a support plate 21 is mounted on the outer periphery of the body 19 a of the clamping sleeve 19 and axially on the shoulder, or z. B. (also in addition) via a groove.
  • the longitudinal grooves 19d extend in the longitudinal direction of the clamping sleeve 19 of this paragraph, which limits the coupling portion 19i up to the upper end of the hollow cylindrical body 19a in the short conical portion inside.
  • the power storage element 22 which is designed here as a helical compression spring, arranged around the pushed onto the clamping sleeve 19 tooth sleeve 18 around.
  • a lower end of the force storage element 22 is supported on the upper side of the support disk 21, wherein an upper end of the force storage element 22 rests against the underside of the annular coupling portion 18a of the toothed sleeve 18
  • the coupling device 20 in the region of the coupling portion 19i of the clamping sleeve 19 is arranged.
  • the coupling device 20 comprises for the adjuster 1 1 a, the coupling wheel 20a (see Fig. 1), a cage 20b and coupling elements 20c.
  • the driver 1 1 b also has a coupling device not designated here with the coupling wheel 20'a (see Fig. 1) and should not be further discussed here.
  • the cage 20b of the coupling device is hollow cylindrical and has receptacles for the coupling elements 20c, which are formed here as balls.
  • the cage 20b is pushed with the coupling elements 20c from above over the clamping sleeve 19 down to the coupling portion 19i.
  • the coupling elements 20c in the longitudinal grooves 19e, which extend to the lower coupling end 19b, guided in the axial direction of the clamping sleeve 19.
  • the coupling elements 20c of the coupling device 20 transmit a rotational movement between the clamping sleeve 19 and the coupling wheel 20a.
  • the coupling device 20 forms with the coupling elements 20c a gimbal connection to the coupling wheel 20a.
  • a minimization of the friction / friction influences in the axial direction of the adjusting device 11a and on the other hand a reduction of wear on the coupling portion 19i of the clamping sleeve 19, which form the Nachstellerabtrieb the adjusting device 1 1 a, scored.
  • the balls roll as coupling elements 20c in the longitudinal grooves 19e of the clamping sleeve 19 with a compensation of the traverse during braking. Further descriptions can be found in DE 10 2012 108 672 B3.
  • the adjusting device 1 1 a is positively coupled via the coupling wheel 20a with the threaded rod 6 and the chain (synchronizer 20d) of the synchronizer via the other coupling wheel 20'a with the other threaded stem 6 'of the driver 1 1 b.
  • the bolt 23 comprises an elongated, circular-cylindrical bolt body 23 a, which is solid and extends in the direction of the adjuster axle 5. It is provided at its upper end with a drive section 23b.
  • the driving portion 23b has a shoulder surface 23d having an outer diameter smaller than an outer diameter of the bolt body 23a.
  • An axial length of the driving portion 23b is approximately a little more than one fifth of the length of the bolt 23.
  • a lower end of the driving portion 23b of the bolt 23 passes over one Shoulder, which is formed as a transmission portion 23 e with an outer profile 23 f, in the bolt body 23 a over.
  • the lower end of the bolt body 23a of the bolt 23 is connected to a driven head 23c having an outer diameter which is about 1.5 times as large as an outer diameter of the bolt body 23a.
  • a height (extension in the direction of the Nachstellerachse 5 in Fig. 3-5) of the bolt head 23c corresponds approximately to the axial length of the straight inner wall of the head portion 19f of the clamping sleeve 19.
  • a coupling portion 23 h which extends radially outward and z.
  • B. is tooth-shaped.
  • This coupling section 23c forms a reverse rotation coupling with the head section 19f and is asymmetrical, whereby a necessary torque is limited during service work.
  • the head portion 19f is coupled to the bolt 23 such that on the one hand the driven head 23c of the bolt 23 is disposed within the head portion 19f with an outer diameter of the driven head 23c of the bolt 23 communicating with the inner diameter of the head portion 19f of the collet 19, and on the other hand the radially outwardly extending coupling portion 23h of the bolt 23 with a communicating with him, radially inwardly extending, not designated coupling portion of the head opening 19b of the head portion 19f of the clamping sleeve 19 is positively engaged.
  • This engagement can be solved if the clamping sleeve 19 is displaced axially against the force of the energy storage element 22 during a manual return of the threaded stamper 6. This will be described in detail below in connection with FIG.
  • the collar bushing 24 comprises a cylindrical body 24a with a through-hole 24d, a disk-like collar 24b and a circumferential receiving wall 24c.
  • a shim 25 Disposed below the cylindrical body 24a is a shim 25, the upper surface of which is in contact with an underside 24i of the cylindrical body 24a of the collar bush 24.
  • the underside of the shim 25 rests on an upper side 16i of the cone bushing 16a of the freewheel 16.
  • the collar 24b is formed, which extends radially outward and on its underside a Wälz Eisenability 14b for the rolling elements 14a of the rolling bearing 14 has.
  • the collar bush 24 with its collar 24b is a part of the rolling bearing 14th
  • a circumferential receiving wall 24c is applied with an inner side 24e, whereby a circular cylindrical receptacle with an annular bottom surface is formed.
  • the bottom surface is in the same plane in which the top of the collar 24b extends, and the through-hole 24d opens into the circular cylindrical receptacle.
  • An inner diameter of the circular cylindrical receptacle or the inner side 24e is slightly larger than an outer diameter of the body 24a of the collar bushing 24, wherein a wall thickness in the radial direction of the receiving wall is about three quarters of the wall thickness of the body 24a.
  • the collar 24b protrudes in the radial direction from the outside of the receiving wall 24c by approximately the extent of the wall thickness of the receiving wall 24c.
  • axially protruding teeth of a bottom toothing 24f are formed, which extend in the radial direction and with teeth of an end profile 26g of the toothed disc 26 correspond (see also Fig. 6).
  • an outer profile 24g is formed with axially extending teeth on which the bearing ring 12 is pushed axially and rotationally positive fit, wherein an inner profile of the bearing ring 12 with the outer profile 24g of the collar bushing 24 corresponds.
  • An axial securing 12b, z. B. a shaft securing ring is inserted in the upper quarter of the receiving wall 24 c in a groove 24 h and forms an axial stop in the upward direction for the bearing ring 12th
  • the collar bushing 24 is coaxially disposed about the pin 23 for about four-fifths of the length of the pin 23 and to this and the adjuster shaft 5.
  • the bolt body 23a is arranged with a central portion 23g.
  • the upper end of the bolt 23 projects with the drive section 23b and the transfer section 23e upwardly out of the through-hole 24d in the space formed by the circumferential receiving wall 24c and extends in this space over a length of about 9/10 of the total axial length of the circumferential receiving wall 24c.
  • the toothed disc 26 is disposed in the space formed by the circumferential receiving wall 24c so as to be connected to the drive portion 23b of the bolt 23 extending therethrough.
  • the toothed disc 26 is connected via a radial profile 26f to the outer profile 23f of the bolt 23 and via an end profile 26g to the bottom toothing 24f of the collar bushing 24 in cooperation.
  • the toothed wheel 26 will be described in detail below.
  • the flange bush 24 is fixedly mounted in the brake caliper 4, which is shown in Fig. 5 in a schematic sectional view of the embodiment of the adjusting device 1 1 a of FIG. 3-4 in a partial view of an installation position.
  • the receiving bore 4b with the peripheral wall 4a of the caliper 4 has a receiving base 4c with a through hole 4e.
  • the through hole 4e extends in the direction of the adjuster axle 5 through a holding portion 4h of the caliper 4 and opens at the bottom of the holding portion 4h in the interior of the caliper 4.
  • the mouth of the through hole 4e on the underside of the holding portion 4h is surrounded by a recess 4f , which is formed in the bottom of the holding portion 4h and perpendicular to the center axis of the through hole 4e, ie to the Nachstellerachse 5, arranged bearing surface 4g.
  • the adjuster 1 1 a is inserted in its mounting with the receiving wall 24c progressively from below into the through hole 4e of the holding section 4h until a top 24j of the collar 24b of the collar bushing 24 comes to rest on the support surface 4g of the recess 4f. Then, the bearing ring 12 is pushed onto the receptacle 4c of the receiving bore 4b of the caliper 4 protruding receiving wall 24c of the collar bushing 24, wherein the inner profile 12d of the bearing ring 12 with the outer profile 24g of the receiving wall 24c is engaged.
  • the bearing ring 12 then rests with a bearing surface 12c of its underside on the receiving base 4c of the holding section 4h and is axially fixed to the receiving wall 24c of the collar bushing 24b with the axial securing device 12b.
  • the adjusting device 1 1 a is positioned over the bearing ring 12 in the brake caliper 4. Then, caulking of the bearing ring 12 takes place in recesses 4d of the receiving bottom 4c of the holding portion 4h of the caliper 4. Here it is two caulkings, which face each other radially. This increases robustness.
  • the collar bush 24 of the adjusting device 1 1 a is fixed in the caliper 4 stationary, wherein the holding portion 4h of the caliper 4 between the bearing surface 12c of the bearing ring 12 and the top 24j of the collar 24b of the collar bushing 24 is axially fixed.
  • the collar bushing 24 via the outer profile 24g of its receiving wall 24c rotatably connected to the inner profile 12d of the lager gerrings 12 and rotatably connected via the caulked with the holding portion 4h bearing ring 12 with the caliper 4.
  • the Nachstellerantrieb 13 and the ball ramp clutch 15 are arranged in the region of the body 24a of the collar bushing 24 around the body 24a and on the one hand via the rolling bearing 14 by the switching disc 13a of the Nachstellerantriebs 13 relative to the body 24a radially and on the other hand by the freewheel 16 pivotally or . rotatably mounted.
  • FIG. 6 is a schematic perspective view of the toothed disk.
  • the toothed disc 26 comprises a cylindrical body 26a, a circumferential wall 26b with an inner profile 26c, a through-hole 26d, a profile section 26e, a radial profile 26f and an end profile 26g.
  • the cylindrical body 26a is provided on its upper side with the circumferential wall 26b, which defines a cylindrical recess with the inner profile 26c on the inside of the wall 26b.
  • the inner profile 26c is z. B. an internal toothing.
  • An axial length of the wall 26b corresponds to approximately one fifth of the total axial length of the toothed disc 26th
  • the cylindrical body 26a of the toothed pulley 26 is connected to the profile section 26e, which has a smaller outer diameter than the cylindrical body 26a and forms a shoulder therewith.
  • the axial length of the Profi labitess 26 e corresponds to about one-sixth of the total axial length of the toothed disc 26th
  • the through-hole 26d penetrates the body 26a from the cylindrical recess on the upper side in the axial direction and opens into a recess formed with the radial profile 26f from the underside of the toothed disk 26 into the profile section 26e.
  • a length of the through hole 26d is about 43% of the total axial length of the toothed disc 26th
  • the recess with the radial profile has a larger inner diameter than the through hole 26d.
  • a shoulder is formed at the circumferential inner side of the lower recess.
  • the radial profile 26 f is arranged, which z. B. is an internal toothing.
  • the front side of the profile section 26e is provided with the downwardly facing end profile 26g.
  • the toothed wheel 26 is applied to the bolt 23 as explained below and recorded in the recording of the receiving wall 24c of the collar sleeve 24 recorded so that the end profile 26g of the toothed disc 26 with the bottom teeth 24f, with it corresponds, is engaged.
  • the toothed disc 26 is applied with its through-hole 26d on the drive portion 23b of the bolt 23, with its shoulder abutting the shoulder between the drive portion 23b and the transfer portion 23e of the bolt 23.
  • the upper end of the pin 23 projects from the through hole 26d into the upper recess of the toothed disc 26 formed by the wall 26b.
  • the toothed wheel 26 is fixedly connected from the upper side with the drive portion 23b of the bolt 23 after assembly, for. B. welded, glued, or the like.
  • the lower recess of the toothed disc 26 is engaged via its radial profile 26f with the outer profile 23f of the transfer section 23e of the bolt 23 and is thus connected in a rotationally fixed manner to the bolt 23 in a form-fitting manner.
  • toothed disc 26 Connected to the pin 23 toothed disc 26 forms with its spur gearing 26g, which is in engagement with the bottom teeth 24f of the stationary collar bushing 24, a so-called Kopfreibstelle with a certain holding torque.
  • the biasing force of the force storage element 22 acts between the annular coupling section 18a of the toothed sleeve 18 and the support plate 21 connected to the clamping sleeve 19.
  • the power storage element 22 via the taper bushing 16a of the freewheel 16 via the shim 25 against the fixedly mounted in the caliper 4 collar bush 24 acts an axial biasing force of Power storage element 22 via the support plate 21 on the clamping sleeve 19, which in turn transmits over its upper end with head portion 19f, the axial biasing force on the output head 23c on the pin 23.
  • the pin 23 is axially connected as described above with the toothed disc 26 and thus directs the biasing force on the toothed disc 26 and the end profile 26 g, which engages with the bottom toothing 24 f of the stationary collar bush 24.
  • the holding torque is about 2/3 geometry-dependent. As a result, a limitation of a minimum adjusting movement of the adjusting device 1 1 a is achieved.
  • a drive head 28 is placed so that it is in rotationally fixed cooperation with the inner profile 26c of the wall 26b of the toothed disc 26.
  • the drive head 28 has a body 28a which is formed on its outside with a key surface 28b for cooperation with a suitable tool.
  • the key surface 28b may, for. B. be a hexagon.
  • the body 28a is connected at its bottom with a ring portion 28c, which is provided at its periphery with an outer profile 28d.
  • the outer profile 28d corresponds to the inner profile 26c of the wall 26b of the toothed disc 26th
  • the drive head 28 is at least half inserted with its ring portion 28c in the upper recess in the wall 26b of the toothed disc 26 so that its outer profile 28d is in engagement with the inner profile 26c.
  • the ring portion 28 c is provided with a recess 28 e from below, which creates a clearance for the upper end of the bolt 23.
  • an unspecified through hole is introduced, through which in the assembled state of the drive head 28, the upper end of the bolt 23 is reached.
  • the taper bushing 16a now transmits this rotational movement via the overload clutch 17 to the toothed sleeve 18, which is rotatably connected to the clamping sleeve 19.
  • the coupling portion 19i of the clamping sleeve 19 is transmitted via the coupling elements 20c of the coupling device 20, the rotational movement for adjustment to the coupling wheel 20a.
  • the coupling wheel 20a is in turn rotatably coupled with the threaded rod 6 and the synchronizer 20d with the other coupling wheel 20'a with the threaded stem 6 'of the driver 1 1 b and thus transmits the rotational movement of the adjuster 1 1 a on the threaded stems 6, 6' which are twisted in the crosshead 8 in the threads for adjusting the brake pad 3.
  • the threaded stems 6, 6 ' immediately blocked by concerns the brake pads 3 on the brake disc 2 after passing through the constructive clearance, and by the ball ramp clutch 15th formed overload clutch allows rotation of the switching disc 13a relative to the ramp ring 15a.
  • the overload clutch 17 is required in particular for a manual return part of the threaded pistons 6, 6 '.
  • a rotational movement of the drive head 28 is first transmitted to the toothed disc 26 via the engagement of the outer profile 28d with the inner profile 26c.
  • the toothed pulley 26 in turn transmits the rotational movement via its radial profile 26f to the outer profile 23f of the bolt 23.
  • the reverse rotation thus transmitted to the bolt 23 is transmitted via the reverse rotation clutch, i. passed through the coupling portion 23h of the bolt 23 on the output head 23c on the head portion 19f of the clamping sleeve 19, on the clamping sleeve 19.
  • the clamping sleeve 19 transmits the rotational movement by means of the coupling device 20 to the coupling wheel 20a and the threaded stamper 6.
  • the threaded stamper 6 ' is also rotated via the synchronizing means 20d of the synchronizing device via the coupling wheel 20'a.
  • the threaded temple is now turned backwards in the direction of the Nachstellerachse 5 in the opposite direction of the brake pad 3 in the interior 19c of the clamping sleeve 19, wherein finally the upper shaft end 6b of the threaded stem 6 comes into contact with the inside of the shoulder 19h.
  • the clamping sleeve 19 against the force of the energy storage element 22 in the direction of the adjuster axis 5.
  • This axial movement of the clamping sleeve 19 is indicated by a stroke 30 in Fig. 5.
  • the stroke 30 is by a maximum distance between a shoulder top 29 of the shoulder 19h the Clamping sleeve 19 and a stop portion 29a on the underside of the top wall 16e of the tapered bush 16a limited.
  • the head section 19f of the clamping sleeve 19 can be adjusted further upwards through the passage opening 16h of the cone bushing 16a.
  • the reverse rotation clutch is disengaged.
  • the head portion 19f of the upward movement by its axial movement clamping sleeve 19 is lifted from the coupling portion 23h of the bolt 23 on the output head 23c, since the bolt 23 is axially fixed. In this way, the reverse rotation function is limited.
  • the reverse rotation clutch is "disengaged" as a so-called release clutch by the threaded stem 6 as described above, thus limiting the travel while at the same time restricting a component load Claims modifiable.
  • the energy storage element 22 may consist of several, even different, spring elements.
  • the traverse 8 can be executed with the thread stamper 6, 6 'and the synchronizer as a preassembled and synchronized unit (modularized assembly concept). As a preassembled unit, the traverse 8 is then interchangeable. It is also conceivable that the adjusting device 1 1 a for a disc brake 1 with only one spindle unit 5 with a threaded stem 6 or of course more than two thread tamps 6, 6 'can be used. In the embodiment of the disc brake 1 with only one threaded stem 6 only one coupling wheel 20a is required.

Landscapes

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

Abstract

Dispositif de rattrapage (11a) destiné au rattrapage de l'usure d'une surface de friction sur des garnitures de frein et le disque d'un frein à disque, en particulier pour un véhicule automobile, comportant un dispositif de serrage, de préférence un levier de frein pivotant, le dispositif de rattrapage (11a) pouvant être couplé, côté entraînement, au dispositif de serrage, de préférence au levier de frein pivotant, et, côté sortie, à une unité broche du frein à disque, le dispositif de rattrapage comprenant a) un élément d'entraînement (13) sur les deux côtés duquel est disposé axialement respectivement un ensemble de corps roulants dont un est conçu comme palier à roulement (14) et un autre comme accouplement à rampe (15) à billes à roue libre (16); b) une douille dentée (18) accouplée à la roue libre (16), qui forme un limiteur de couple (17) avec un segment de la roue libre (16); c) une douille de serrage (19) accouplée à la douille dentée (18), pour l'accouplement avec une roue d'accouplement (20a) conçue pour l'accouplement avec l'unité broches (5, 5'), une cavité interne (19c) de la douille de serrage (19) logeant une partie filetée (6) d'une unité broche (5, 5') du frein à disque (1) à associer; d) un élément accumulateur de force (22) destiné à produire une force de précontrainte de l'accouplement à rampe (15) à billes, de la roue libre (16) et du limiteur de couple (17); e) une douille à collet (24) reliée à une extrémité avec une bague-palier (12); f) l'élément d'entraînement (13) de dispositif de rattrapage, les ensembles de corps roulants (14, 15), la roue libre (16), le limiteur de couple (17), la douille dentée (18) et l'élément accumulateur de force (22) étant montés en série avec la bague-palier (12). La douille de serrage (19) est montée en série et accouplée avec un goujon (23) qui s'étend à travers la douille à collet (24). La présente invention concerne également un frein à disque pourvue dudit dispositif de rattrapage (11a).
PCT/EP2015/071389 2014-09-24 2015-09-18 Dispositif de rattrapage pour un frein à disque et frein à disque correspondant WO2016046066A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014113826.0A DE102014113826B4 (de) 2014-09-24 2014-09-24 Nachstelleinrichtung einer Scheibenbremse, und eine entsprechende Scheibenbremse
DE102014113826.0 2014-09-24

Publications (1)

Publication Number Publication Date
WO2016046066A1 true WO2016046066A1 (fr) 2016-03-31

Family

ID=54145783

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2015/071389 WO2016046066A1 (fr) 2014-09-24 2015-09-18 Dispositif de rattrapage pour un frein à disque et frein à disque correspondant

Country Status (2)

Country Link
DE (1) DE102014113826B4 (fr)
WO (1) WO2016046066A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017036765A1 (fr) * 2015-08-31 2017-03-09 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Frein à disque comprenant une unité de synchronisation
US20180128333A1 (en) * 2015-07-10 2018-05-10 Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh Adjusting Device for a Disc Brake

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017101504A1 (de) 2017-01-26 2018-07-26 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Nachstellvorrichtung einer Scheibenbremse und Verfahren zur Sicherstellung einer Vorspannung eines Kraftspeicherelements einer Nachstellvorrichtung
DE102018104569A1 (de) * 2018-02-28 2019-08-29 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Nachstellvorrichtung für eine Scheibenbremse
DE102018107888B4 (de) 2018-04-04 2023-08-24 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Nachstelleinrichtung einer Scheibenbremse
DE102018112673A1 (de) * 2018-05-28 2019-11-28 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Nachstelleinrichtung einer Scheibenbremse
DE102018115494A1 (de) 2018-06-27 2020-01-02 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Nachstelleinrichtung zum Nachstellen eines Lüftspiels einer Scheibenbremse, Scheibenbremse und Verfahren zum Nachstellen
DE102018119276A1 (de) * 2018-08-08 2020-02-13 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Nachstelleinrichtung einer Scheibenbremse
DE102019134455B4 (de) * 2019-12-16 2023-04-20 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Scheibenbremse für ein Nutzfahrzeug
CN115046878B (zh) * 2022-06-14 2023-06-20 燕山大学 非金属材料双形式摩擦磨损检测装置
DE102022125261A1 (de) 2022-09-30 2024-04-04 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Scheibenbremse für ein Nutzfahrzeug

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004037771A1 (de) * 2004-08-04 2006-03-16 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Nachstellvorrichtung für eine pneumatisch betätigte Scheibenbremse
DE102012108672B3 (de) * 2012-09-17 2014-02-06 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Nachstelleinrichtung einer Scheibenbremse, eine entsprechende Scheibenbremse und Verfahren zum Betreiben einer Verschleißnachstellvorrichtung einer Scheibenbremse
DE102012108682A1 (de) * 2012-09-17 2014-03-20 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Scheibenbremse mit einer Synchroneinrichtung

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19729024C1 (de) 1997-07-08 1999-01-28 Knorr Bremse Systeme Verschleißnachstellvorrichtung für Scheibenbremsen

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004037771A1 (de) * 2004-08-04 2006-03-16 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Nachstellvorrichtung für eine pneumatisch betätigte Scheibenbremse
DE102012108672B3 (de) * 2012-09-17 2014-02-06 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Nachstelleinrichtung einer Scheibenbremse, eine entsprechende Scheibenbremse und Verfahren zum Betreiben einer Verschleißnachstellvorrichtung einer Scheibenbremse
DE102012108682A1 (de) * 2012-09-17 2014-03-20 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Scheibenbremse mit einer Synchroneinrichtung

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20180128333A1 (en) * 2015-07-10 2018-05-10 Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh Adjusting Device for a Disc Brake
US10982729B2 (en) * 2015-07-10 2021-04-20 Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh Adjusting device for a disc brake
WO2017036765A1 (fr) * 2015-08-31 2017-03-09 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Frein à disque comprenant une unité de synchronisation
US10626940B2 (en) 2015-08-31 2020-04-21 Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh Disc brake having a synchronization unit

Also Published As

Publication number Publication date
DE102014113826A1 (de) 2016-04-07
DE102014113826B4 (de) 2018-10-31

Similar Documents

Publication Publication Date Title
DE102014113826B4 (de) Nachstelleinrichtung einer Scheibenbremse, und eine entsprechende Scheibenbremse
EP3173651B1 (fr) Dispositif de réglage d'un frein à disque et frein à disque correspondant
EP2307756B1 (fr) Dispositif de rattrapage de jeu pour un frein à disque
EP2307755B1 (fr) Dispositif d'ajustement pour frein à disque
EP2850334B1 (fr) Dispositif de rattrapage de l'usure d'un frein à disque et frein à disque correspondant
DE102005030618A1 (de) Scheibenbremse in selbstverstärkender Bauart und Ansteuerverfahren für eine selbstverstärkende Bremse
DE102005030620A1 (de) Scheibenbremse in selbstverstärkerder Bauart
DE102005030617A1 (de) Scheibenbremse in selbstverstärkender Bauart und Ansteuerverfahren für eine selbstverstärkende Bremse
EP2895762A1 (fr) Frein à disque avec système de synchronisation
DE102014017430A1 (de) Scheibenbremse, insbesondere für Nutzfahrzeuge
EP2895761B1 (fr) Frein à disque pourvu d'un dispositif de rattrapage d'usure, procédé et dispositif permettant de faire fonctionner un dispositif de rattrapage d'usure d'un frein à disque
EP3317556A1 (fr) Dispositif de rattrapage de jeu pour un frein à disque
DE102015114440B4 (de) Scheibenbremse mit Synchronisationseinheit
EP1494909B1 (fr) Dispositif de serrage de frein dote d'un mecanisme a commande electrique pour le reglage en fonction de l'usure
WO2016037934A1 (fr) Dispositif de rattrapage de jeu pour frein à disque actionné par levier rotatif, et frein à disque pourvu d'un dispositif de rattrapage de jeu
DE102013103064B4 (de) Nachstelleinrichtung für eine Scheibenbremse und eine entsprechende Scheibenbremse
EP2878844A2 (fr) Frein à disque
DE102014112662B4 (de) Nachstellvorrichtung für eine drehhebelbetätigte Scheibenbremse, und Scheibenbremse mit einer solchen Nachstellvorrichtung
DE102008028265A1 (de) Nachstellvorrichtung für eine Scheibenbremse
DE10208641B4 (de) Scheibenbremse mit automatischer Nachstellvorrichtung
DE102006010248A1 (de) Drehmomentübertragungsvorrichtung in einem Kraftfahrzeug
DE102006003749A1 (de) Scheibenbremse in selbstverstärkender Bauart

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 15763933

Country of ref document: EP

Kind code of ref document: A1

122 Ep: pct application non-entry in european phase

Ref document number: 15763933

Country of ref document: EP

Kind code of ref document: A1