EP3359844A1 - Frein à disque pour véhicule utilitaire et jeu de garnitures de frein - Google Patents

Frein à disque pour véhicule utilitaire et jeu de garnitures de frein

Info

Publication number
EP3359844A1
EP3359844A1 EP16781729.5A EP16781729A EP3359844A1 EP 3359844 A1 EP3359844 A1 EP 3359844A1 EP 16781729 A EP16781729 A EP 16781729A EP 3359844 A1 EP3359844 A1 EP 3359844A1
Authority
EP
European Patent Office
Prior art keywords
brake
carrier plate
lining
spring
lining carrier
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.)
Pending
Application number
EP16781729.5A
Other languages
German (de)
English (en)
Inventor
Oliver Krause
Matthias Klingner
Michael Peschel
Tobias Schöfberger
Philipp ADAMCZYK
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=57113363&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP3359844(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Priority claimed from DE102016104970.0A external-priority patent/DE102016104970A1/de
Application filed by Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH filed Critical Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Publication of EP3359844A1 publication Critical patent/EP3359844A1/fr
Pending 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
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • F16D65/095—Pivots or supporting members therefor
    • F16D65/097—Resilient means interposed between pads and supporting members or other brake parts
    • F16D65/0973—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces
    • F16D65/0974—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces acting on or in the vicinity of the pad rim in a direction substantially transverse to the brake disc axis
    • F16D65/0977—Springs made from sheet metal
    • F16D65/0978—Springs made from sheet metal acting on one pad only
    • 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
    • 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
    • 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
    • F16D55/226—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 moved axially, e.g. floating caliper disc brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • F16D65/095—Pivots or supporting members therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • F16D65/095—Pivots or supporting members therefor
    • F16D65/097—Resilient means interposed between pads and supporting members or other brake parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • F16D65/095—Pivots or supporting members therefor
    • F16D65/097—Resilient means interposed between pads and supporting members or other brake parts
    • F16D65/0973—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces
    • F16D65/0974—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces acting on or in the vicinity of the pad rim in a direction substantially transverse to the brake disc axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • F16D65/095—Pivots or supporting members therefor
    • F16D65/097—Resilient means interposed between pads and supporting members or other brake parts
    • F16D65/0973—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces
    • F16D65/0974—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces acting on or in the vicinity of the pad rim in a direction substantially transverse to the brake disc axis
    • F16D65/0975—Springs made from wire
    • 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
    • F16D65/183—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 with force-transmitting members arranged side by side acting on a spot type force-applying member
    • 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
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/0008—Brake supports
    • 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
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/0016—Brake calipers
    • F16D2055/0029—Retraction devices
    • 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
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/007—Pins holding the braking members
    • 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
    • F16D65/005—Components of axially engaging brakes not otherwise provided for
    • F16D65/0056—Brake supports

Definitions

  • the invention relates to a disc brake for a commercial vehicle according to the preamble of claim 1.
  • the invention also relates to a brake pad set.
  • a generic disc brake also known as a sliding caliper brake
  • an action-side brake lining is pressed against a vehicle-side brake disc in the case of braking by means of an application device which can be actuated pneumatically or electromotively.
  • the brake caliper relative to the brake disc, is displaced counter to the application direction of the brake pad on the brake side, taking the opposing, reaction-side brake pad against the other side of the brake disc.
  • a disc brake is disclosed in the generic DE 10 2007 001 213 with a rear part device which is arranged in one of the guide rails, via which the caliper is slidably held on the brake carrier, and which has a resilient return element up that the caliper is moved to a starting position.
  • this construction has proven itself.
  • the use of this known rear part device can lead to problems in air-operated disc brakes heavy commercial vehicles, since here wide limits of variable influences by component tolerances and component deformations are effective that do not allow a safe function of this rear part in each case.
  • the rear part device acts on the brake caliper, wherein the brake carrier acts as an abutment.
  • DE 43 01 621 A1 describes a floating-caliper disc brake with a stationary brake carrier, which has two support arms projecting beyond the outer edge of a brake disk, with brake shoes arranged on both sides of the brake disk, each having a friction lining and a back plate, which can be displaced on the carrier arms are supported, with an axially displaceably guided on the brake carrier floating caliper, which surrounds the brake shoes and has a specific for pressing the brake shoes to the brake disc actuator, with an axially acting on the brake shoes in brake release direction spring arrangement, the setting of a clearance after braking supported between brake shoes and brake disc.
  • the spring arrangement has at least one spreading spring, which is attached to a support arm of the brake carrier in the axial direction as a whole immovably, that the attachment to a located on the outer edge of the brake disc portion of the support arm, and that the spreading spring has at least two spring arms, the the spring plates of the brake shoes in the axial direction resiliently rest.
  • US2014 / 0339026 A1 describes a spreading spring, comprising a locking arm, which connects the spreading spring with a brake component, a retraction arm; and biasing means disposed between the locking arm and the return arm, wherein the biasing means comprises six spiral loops or more, the energy which during a Save brake activation and as soon as the braking process is completed, the brake components (brake pad) retracts.
  • the invention has for its object to further develop a disc brake of the generic type so that the service life of the brake pads and the brake disc in particular increases structurally simplest means and operating costs are reduced overall.
  • Another object is to provide a corresponding brake pad set.
  • a disc brake according to the invention for a commercial vehicle, with a brake disc cross-trained, designed as a sliding caliper caliper, which is attached to a stationary brake carrier and having a central opening above the brake disc comprises two arranged in the caliper, in opposite directions movable, each a pad carrier plate and a fastened thereto Brake linings having brake linings, of which a tresss doctorer by means of an application device via at least one brake stamp against the brake disc can be pressed, and at least one rear part device with which the caliper is traceable to a brake-induced displacement and release of the brake, wherein the rear part means on the opposite brake pads having attacking, opposite to the respective Zuspann- direction equally acting spreader with acting on the respective pad carrier plate resilient spreading elements.
  • the spreading device is arranged in the central opening, wherein the spreading directly or indirectly outside of the friction linings attack on one side in the central region or at least two spaced apart to the center abutting areas of the brake pads, wherein the contact areas each have a contact surface and a support surface on which the spreading are movably arranged.
  • the inventive design of the disc brake is a synchronous provision of both brake pads and a provision of the Brake caliper achieved when the brake is released, the synchrony concerns both the restoring forces as well as the return paths.
  • the restoring force counteracts the respective application direction of the two brake linings, ie, towards the saddle back in the case of the reaction-side brake lining and toward the saddle head during the action-side brake lining, with gap formations with respect to the brake disc.
  • the attack of the spreader on the two brake pads is advantageously carried out on the lining carrier plates on the side facing the friction lining attached thereto or on the opposite back side.
  • the expansion element engages either centrally, on an upper exposed edge region of the lining carrier plate or symmetrically on two contact areas right and left.
  • An inventive brake pad set for the disc brake according to the invention has at least two brake pads, each with a pad carrier plate and a mounted on the pad carrier plate friction lining and the above spreader.
  • the pad carrier plate have outside of the friction linings on one side in the central region or at least two abutting to the center each other arranged contact areas each have a contact surface and a support surface.
  • the spreading elements extend, starting from a central region in the middle of the opening, from the inside outwards to the abutment areas which are arranged at a distance from one another in the center. It is also possible for the spreading elements, starting from a central region in the middle of the opening, to extend from the inside outwards to the abutment regions which are arranged uniformly spaced from one another in the middle.
  • the spreading device is arranged centrally in the caliper, wherein it is also arranged within an envelope of a rim of an associated wheel.
  • the two spreading elements are centered (in relation to the carrier horns) connected to each other.
  • a - in a small tolerance range - the same spring force can be ensured both inlet side and outlet side.
  • Different spring forces between the outlet and inlet side, which can lead to oblique wear, are minimized by the one-sided attack per spring one plaque.
  • Another embodiment provides that the central region of the opening on either side of a virtual center of the opening approximately parallel to the Level of the brake disc extends in a length in a range of 30 to 50% of a longitudinal axis of the opening. This results in an advantageous adaptation of the spring forces.
  • the spreader has spring arms, two of which abut each other on an associated pad carrier plate, wherein the spring arms are connected in the central region of the opening, which simplifies installation during installation and maintenance.
  • the spreading device has oppositely acting spreading elements, preferably elastically acting, in particular in the form of spring elements.
  • a compression spring between the two brake pads is arranged as a screw or leg spring, wherein the leg spring is mounted centrally above the brake disc, for example on a pad retainer, with which the two brake pads can be pressed under bias in a lining shaft.
  • the spreading device is in operative connection with the brake carrier instead of the lining retaining yoke, which forms a pivot bearing and in which the brake linings are mounted so as to be displaceable coaxially with the brake disk.
  • a retaining bow is preferably provided, which spans the brake disk in the peripheral region, up to the brake carrier horns of the brake carrier limiting both sides of a lining shaft and, in relation to the thickness of the brake disk, is arranged centrally therewith.
  • the tie can be connected in one embodiment to two opposite, connected to the brake carrier brackets, which allows easy connection.
  • the retaining bow can be connected to at least the two brake carrier horns of a lining shaft, while the spreading elements acting on both brake pads are connected to the retaining bow. This thus forms a centering device, which can be realized structurally different in correspondence with the brake carrier as a fixed bearing.
  • the retaining bow is formed in its contour C-shaped, with a brake disc in the mentioned extent spanning center leg and two rectified to the brake carrier horns angled end legs, one of which is attached to a Bremschihorn the corresponding lining shaft.
  • the spreader is designed so that it is effective over the complete wear of the brake pads.
  • the functional parts of the spreading device which make contact with the brake linings are designed such that they are slidably supported on the lining carrier plate of the respective brake linings.
  • the spring arms are based on, based on the bottom of the lining shaft, upper edge of the lining carrier plate from, also, as described above slidably.
  • the spreader can also be dispensed with the use of lining retaining springs, which, as from the prior Technique known, are attached to the upper edge of the lining carrier plates and on which a lining retaining bracket is supported, so that the respective brake pad is held under bias in the lining shaft of the brake carrier.
  • the structural realization of the spreading device according to the invention may be structurally different, with a significant advantage resulting from the fact that can be dispensed with movable components substantially, with the exception, of course, the resilient expansion elements that perform a resilient deflection function.
  • each spring arm is formed at the end with a fork-shaped spring end, forming a support leg and a Anyakschenkels, wherein the support leg movable on a support surface of a narrow side of the lining carrier plate and the Anyakschenkel with pressure on a contact surface of the friction lining facing side of the lining carrier plate movable is applied.
  • the spring arm can not only initiate compressive forces on the contact surface on the lining carrier plate, but also in its movements by the contact surface and the support surface is guided displaceable bar.
  • the brake pad is resiliently held in its brake lining shaft by the spring force which is introduced into it via the bearing surface.
  • the support surface may be disposed at an angle to a horizontal, wherein the angle is in a range of 3 to 15 °.
  • the contact surface may protrude from the lining carrier plate or be formed in the lining carrier plate. This is an advantageous adaptation to different brake versions possible.
  • each spring arm is formed with a spring end end with a Anyakschenkel, the Anyakschenkel with a support portion of the friction lining facing side of the Belagiva- plate is in contact with the Antikschenkel with a contact portion with pressure on a contact surface of the support portion of the lining carrier plate movably abuts and at the same time rests movably with a support portion on a support surface of the support portion of the lining carrier plate.
  • the support section with the bearing surface and the bearing surface is formed in the lining carrier plate. This is advantageous because there is space and material savings.
  • the bearing surface of the contact areas may be arranged at an angle to a horizontal, wherein the angle is in a range of 3 to 15 °. For a guide of the spring end is improved.
  • a projection is provided on the contact surface, wherein the projection protrudes from the contact surface.
  • the abutment areas have a support portion which is formed with the contact surface and the support surface in the lining carrier plate. This results in a space and material savings.
  • the contact surface extends to the side surface of the lining carrier plate, which is provided with the friction lining offset in the direction away from the friction lining. This results in an advantageous guidance of the spring end in the lining carrier plate together with a spring force transmission in a small installation space.
  • the spreader comprises two spreading elements, wherein a first spreading element acts on a first coating and a second expansion element on a second coating.
  • the two spreading elements are connected to each other in the middle (in relation to the carrier horns).
  • a uniform force application of the springs on the action side and reaction side, or on the pressure piece and saddle side, can be realized by a flexible adjustment of the central web. Furthermore, can be compensated by the flexible center bar low geometric misalignments of disc, pad and carrier.
  • the active rear part device can be easily positioned and held down by the pad retaining bracket.
  • the return part device can be easily removed and replaced in a pad change.
  • the spreading can be made of inexpensive and geometrically flexible sheets.
  • Figures 1 and 2 are each a partial section of a disc brake according to the invention in a perspective plan view;
  • Figure 1 a is an enlarged schematic partial sectional view of
  • Figures 3-7 further embodiments of the invention with reference to a detail of the disc brake, each also in a perspective view;
  • Figures 8-28 further embodiments of the invention, each as a detail of the disc brake in a perspective view.
  • Figure 29 is a perspective view of another embodiment of the disc brake.
  • FIG. 1 shows a part of a disc brake 100 for a commercial vehicle, with a brake caliper 1 that overlaps a brake disc 2.
  • the brake disk 2 has a brake disk axis of rotation 2 a (see FIG. 29).
  • the caliper 1 is relative to the brake disc 2 axially in the direction of the brake disc axis 2a slidably connected to a brake carrier 6, to which the caliper 1 is mounted on guide bars, not shown, which are connected to the stationary held on the vehicle brake carrier 6.
  • the caliper 1 comprises an application section 1 a, a saddle back 1 b and two tension struts 1 c.
  • the application section 1 a receives an application device (not shown) of the disc brake 100.
  • the application section 1 a extends on one side with a side parallel to the plane of the brake disk 2. te the brake disc 2.
  • the saddle back 1 b arranged on the other side of the brake disc 2, also parallel to the brake disc 2 extending.
  • the saddle back 1 b is connected to the application section 1 a at one end in each case with a tension strut 1 c.
  • the tension struts 1 c extend substantially perpendicular to the application section 1 a and to the seat back 1 b.
  • the application section 1 a, the saddle back 1 b and the tie rods 1 c set in this arrangement, a central opening 41 between them, which spans the brake disc 2.
  • the opening 41 has an imaginary longitudinal center line, which lies in the plane of the brake disc 2 and the imaginary centers of the tie rods 1 c connects.
  • the opening 41 has a further imaginary lateral center line, which connects an imaginary center of the application section 1a to an imaginary center of the saddleback 1b.
  • the longitudinal center line and the transverse center line intersect at an imaginary center, which is referred to here as the virtual center of the opening 41.
  • each brake lining 3 has a lining carrier plate 4 and a friction lining 5 fastened thereto on the side facing the brake disk 2, which friction lining 5 is pressed against the brake disk 2 in function, that is to say during braking.
  • the brake pads 3 are accessible through the central opening 41 for a change and for maintenance. They can be inserted through this central opening 41 in their associated Belichtmchte and removed again from it.
  • the lining shafts are each fixed laterally by brake carrier horns 25 (see FIG. 8).
  • the braking is carried out by means of the application in the clamping portion 1 a of the caliper 1 there in a receiving space arranged application device with a brake lever which is positioned in a dome 23 of the caliper 1.
  • action-side or zuspann handyer brake pad first contacted during braking the brake disc 2.
  • the two opposing brake pads 3 are released so far from the brake disc 2 by means of a rear-part device that it runs freely relative to the brake pads 3.
  • the rear part device consists of at least one spreader 8, which acts on the opposing brake pads 4, according to the invention, the same acting counter to the application direction.
  • the spreader 8 consists of two mirror-inverted shaped, but otherwise identical band springs 9, which are held on a pad retaining spring 7 of the respective lining carrier plate 4, to which each band spring 9 a tab 1 1 is formed, the form-fitting in a slot 10 of the pad retaining spring 7 engages.
  • FIG. 1 An enlarged schematic partial sectional view of the disc brake 100 according to FIG. 1 is shown in FIG. The section passes through a vertical plane with respect to FIG. 1, which passes through the brake disk axis of rotation 2a.
  • the part of the band spring 9, which is in contact with the lining carrier plate 4, is located in a central portion of the band spring 9 and is referred to here as a printing section 1 1 a.
  • the printing section 1 1 a is extended upward through the tab 1 1.
  • the pressure section 1 1 a is in this example to a terminal element 7a, which is mounted to support the pad spring 7 on the lining carrier plate 4 in the middle upper region.
  • a portion of the clamping element 7a extends through the slot 10 of the pad retaining spring 7. This slot 10 is therefore already present and can be used for the positive engagement of the tab 1 1 of the band spring 9.
  • the portion of the clamping element 7a the outside of which is in contact with the pressure portion 1 1 a of the band spring 9, lies with its inside on the lining carrier plate 4. In this way, the pressure force of the pressure section 1 1 a of the band spring 9 is transmitted to the lining carrier plate 4.
  • these explanations also apply to the other strip spring 9.
  • a pad retaining bracket 28 (see also FIG. 8) is shown in FIG. 1 a, which is arranged above the brake linings 3 in the transverse direction of the opening 41 or in the direction of the brake disk axis of rotation 1 a between the tightening portion 1 a and the seat back 1 b and fastened thereto is.
  • the pad retaining book Gel 28 presses here with sections of its underside on the clamp elements 7a and thus on the lining retaining springs 7, whereby the brake pads 3 are held in their lining shafts.
  • the respective band spring 9 is held axially secured to a bracket 12 which is fixed to the brake carrier 6, wherein both band springs 9 are arranged separately from one another.
  • the respective end of the band spring 9 between them clamping, fuses 13 are provided for axial securing are on the bracket 12, the respective end of the band spring 9 between them clamping, fuses 13 are provided.
  • the band springs 9 are correspondingly deformed by building up a spring tension, so that after releasing the braking, the brake linings 3 are pressed out of their braking position uniformly by the spring force provided.
  • the spreader 8 each formed from a spring clip 14, preferably formed from spring wire.
  • a spring clip 14 is pivotably held at each end region of the lining carrier plate 4 on the side facing the lining holding springs 7, for which purpose a suspension 15 is arranged on the lining carrier plate 4, into which the ends of the spring clip 14, viewed radially to the brake disk 2, offset from one another and are held rotatably.
  • the suspension 15 for each end of the spring clip 14 comprises a rectangular bearing portion 151, 152, which are connected by a connection 150 such that the bearing portion 151 protrudes from the connection 150 upwards and the bearing portion 152 protrudes downward.
  • the suspension 15 may e.g. be formed integrally with the lining carrier plate 4, for example by mechanical processing. It is also possible that the suspension 15 is attached to the lining carrier plate 4.
  • the suspension 15 may also be e.g. a rectangular plate, as will be described in detail below ( Figure 24).
  • a spring clip 14 abuts against an associated brake carrier horn of the brake carrier 6, specifically on the side opposite the brake disk 2, so that when the brake linings 3 are tightened, the spring clips 14 deform under tension. When the brake is released, the brake linings 3 are pushed back against their supply direction by the spring force of the spring clips 14, comparable to the exemplary embodiment according to FIG. 1.
  • FIG. 3 shows a further exemplary embodiment of the spreading device 8, the illustration of the brake caliper being omitted here.
  • This spreader 8 consists of two, in each case on surveillanceo- the sides of the brake carrier 6 fixed brackets 12 connected leaf springs 17, each of which bears at its mutually facing, free ends of two scissor members 16, one of the action-side brake pad 3 and the other on reaction-side brake pad 3 is pivotally mounted.
  • the applied for spreading spring force is achieved in this embodiment by the leaf springs 17 which bulge radially when tightening the brake pads 3 and when releasing the brake, according to the spring action, stretch, while stretching the connected scissor members 16 and spread the brake pads. 3 apart.
  • FIG 4 shows a further variant of the spreading device 8 is shown, which has two crossed spring legs 18 which are hinged to a tie 21. This is, comparable to the attachment of the leaf springs 17 on the brake carrier 6, also held on associated brackets 12, which spans the brake disc 2, based on the thickness thereof, in a partial circumference in the middle.
  • the bent ends of the crossed spring legs 18 rest on a bearing 19 of the lining carrier plate 4, so that this scissor-like construction spreads when the brake is applied, ie when the brake linings 3 move axially toward one another.
  • the spring legs 18 are fastened to the retaining bow 21, so that the spring legs 18 are biased during application of the brake pads 3 and the brake pads 3 are spread apart by a release of the brake by this bias.
  • FIG. 5 shows a spreading device 8, which consists of two identical spring arms 20, which are connected to one another in the middle region in the longitudinal direction of the opening 41, as well as a retaining bow 21, which is fastened to the brake carrier 6 via brackets 12.
  • the spring arms 20 at two opposite end portions of the lining carrier plate 4 and that in a top side protruding edge region.
  • the ends of the spring arms 20 are also bent, so that sliding on the lining carrier plate surface during application and release of the brake is easily possible.
  • a spread of the brake pads 3 after releasing the brake is possible by the resulting when tightening bias.
  • each spreader 8 consists of a rotatably connected to the bracket 12 bearing leg 22 which is formed loop-shaped from a spring wire and also, as well as the spring arms 20 according to FIG 5, rests on the edge region of the respectively associated lining carrier plate 4, wherein the two resilient abutment legs 22 abut each side on the mutually facing sides of the lining carrier plates 4.
  • each of a brake pad 3 associated band spring 9 engages centrally on the lining carrier plate 4, preferably on a system 19, for which purpose the band spring 9 is provided with an issued investment bracket 24.
  • the band springs 9 are mounted axially displaceable on the two opposing brackets 12.
  • the retaining bow 21 is C-shaped, with a center leg 26, which is centrally arranged relative to the thickness of the brake disk 2 and extends in its circumferential direction, to which an angled end limb 27 adjoins on both sides ,
  • FIG. 9 which shows a partial section of a completed disc brake 100, while FIG. 8 shows only the brake carrier 6 with the brake linings 3 inserted, it can be clearly seen, as in FIG. 10, that the end limbs 27 are facing one another Are provided with tabs 29 on which pins 30 are held, which engage in holes 25 a (see Figure 26) of the brake carrier horns 25.
  • the retaining bow 21 forms a centering device for the caliper 1, as the brake carrier 6, to which the retaining bow 21 is attached, forms a stationary part, which is slidably mounted relative to the brake caliper 1, so that after releasing the brake and a spreading the spreading device 8, ie a pushing apart of the brake pads 3 of the caliper 1 is guided in a centered position.
  • the figure 10 shows, moreover, the brake pads 3 with the spreader 8 and the tie 21 in isolation.
  • the spring arms 20 each have support legs 31 at their free end, which are supported on the edges of the lining carrier plates 4 assigned to the lining retaining springs 7 and due to which the spring arms 20 are released from their installation the respective lining carrier plate 4 is prevented during shaking movements while driving.
  • the support legs 31 are clamped between the pad retaining springs 7 and the associated pad carrier plate 4, wherein the pad carrier plate 4 has a cutout, not shown, through which the respective support leg 31 is guided. For a tilting of the spring arms 20 is prevented.
  • the spring end 300 of the spring arm 20 is convex in the contact region with the lining carrier plate 4, that is to say the pressure leg 32 in the direction of the lining carrier plate 4. curves so as to ensure a disability-free sliding on the lining carrier plate 4.
  • the support leg 31 of the spring end 300 is located with a support portion 31 a of its slot 301 facing bottom on a support surface 305 of the top of the lining carrier plate 4.
  • the Andruckschenkel 32 is connected to a contact portion 32a, which faces the lining carrier plate 4, with a contact surface 303 of the lining carrier plate 4 in contact.
  • the contact surface 303 is located on the side of the lining carrier plate 4 on which the friction lining 5 is applied.
  • the contact surface 303 is arranged above the friction lining 5 in an end region of the lining carrier plate 4.
  • the bearing surface 305 on the upper side of the lining carrier plate 4 can be arranged at an angle 306 to an imaginary horizontal with an amount in the range of, for example, 5 to 15 °.
  • the support surface 305 forms a guide for the support leg 31 of the spring end 300 of the spring arm 20 during its movements in directions of movement 302 (for example due to wear compensation) and a stop for these in a direction towards the top of the lining support plate 4.
  • the contact between the support surface 305 of the lining carrier plate 4 and the support leg 31 of the spring end 300 of the spring arm 20 forms a cushioning of the brake pad 3 in the radial direction.
  • the lining carrier plate 4 and thus the brake pad 3 is pressed downwards into its lining shaft and cushioned by these contacts with the supporting legs 31 of the spring ends 300.
  • the contact surface 303 forms a guide for the Andruckschenkel 32 of the spring end 300 of the spring arm 20 during its movements in directions of movement 302 (eg wear compensation) and a stop for this in one ner direction on the lining carrier plate 4 parallel to a brake disc axis 2a.
  • the abutment surface 303 may protrude from the lining carrier plate 4 or be formed in the lining carrier plate 4, for example as a groove.
  • the contact surface 303 and the support surface 305 may be provided as guide surfaces with a special surface treatment, for example, ground to have a low frictional resistance.
  • a projection 304 is provided, which protrudes from the lining carrier plate 4 to the spring end 300 in the slot 301. In this way, the projection forms an additional guide for the spring end 300.
  • FIG. 12 shows an enlarged detail of the retaining bow 21 in the connection region on the brake carrier horn 25, wherein the strap 29 rests on a flat end face of the brake carrier horn 25.
  • the pin 30 can be formed as a rivet and inserted into a bore 25a (see FIG. 26) of the brake carrier horn 25. It is also possible that the pin 30 is integrally formed on the Bremsharihorn 25 or used as a separate component before.
  • the spreader 8 according to Figures 8-13 is recognizable as a detail.
  • respective spring ends 300 are designed as bent Antikschenkel 32.
  • the proof tote! 32 each have the already indicated in Figure 1 1 above contact section 32a.
  • the Antikschenkel 32 are provided here at their lower sides with a respective support portion 32b, which is for a support contact as will be explained below with a suitable surface texture with low coefficient of friction is provided.
  • FIG. 13a an enlarged partial view of the end region of a lining carrier plate 4 of a brake lining 3 together with such a pressure leg 32 is shown.
  • the brake pad 3 is inserted in its lining shaft between two brake carrier horns 25, of which only one is shown here.
  • an end leg 27 of the retaining bow 21 is attached to this brake carrier horn 25.
  • the end region of the lining carrier plate 4 is here provided with a support section 44, which is formed in the lining carrier plate 4, for example by mechanical means. niche processing.
  • the support portion 44 has a contact surface 45 and a support surface 46.
  • the abutment surface 45 is offset parallel to the side surface of the lining carrier plate 4, which is provided with the friction lining 5, wherein the abutment surface 45 is spaced from this side surface in the direction of the brake disk axis 2a, ie axially, by an axial depth of the support surface 46.
  • the Anyakschenkel 32 is disposed in the support portion 44 and communicates with its abutment portion 32 a with the contact surface 45 in contact. At the same time the Antikschenkel 32 is with its support portion 32b on the support surface 46. The Antikschenkel 32 is guided in this manner during its movement by its contact with the support portion 44 therethrough.
  • the abutment surface 45 and the support surface 46 may be provided with special frictional properties by machining for this movement.
  • the tab 29 is not angled relative to the end leg 27, but is the same course formed by this, by appropriate shaping of the tether 21st
  • FIG. 15 A comparable embodiment variant is shown in Figure 15, in which, however, the securing of the end leg 27 and the tab 29 by means of a nut 33 which is screwed onto a threaded pin of the Bremsharihorns 25 and holds the tab 29 on the Bremsharihorn 25.
  • a support tab 34 is angled, which on the front side of the associated Bremsharihorns 25 rests and which, comparable to the support leg 31 of Figure 1 1, a radial securing for the tie sheet 21 and thus for the spreading device 8 forms.
  • a further variant of the attachment of the retaining bow 21 on the Bremsharihorn 25 can be seen in the figure 17, which reproduces an enlarged partial section of the corresponding region of the brake carrier 6.
  • FIG. 18 illustrates a variant embodiment of the spreading device 8, in which the spring arms 20, of which the end section of a spring arm 20 is shown, on the one hand assumes the function of the retaining bow 21 and on the other hand performs the function of spreading.
  • the spring arm 20 is split in its end region in the longitudinal direction to form a spring bar 38 and a connecting web 37.
  • the spring bar 38 provided with an integrally formed angled bracket 39 assumes the spreading function, i. he is tense when braking the brake lining 3 against the spring force and presses after releasing the brake pad 3 in its end position, wherein the angle tab abuts the pad carrier plate 4 both in the clamping direction and in the radial direction, ie at the upper edge of the pad carrier plate 4th
  • the connecting web 37 is end provided with a pin 30 having a tab 29, wherein the pin 30 is inserted into a bore 25a (see Figure 26) of the Bremschihorns 25, as described, to allow a centering of the caliper 1 after a braking operation ,
  • FIG. 19 shows the middle region of a further exemplary embodiment of the spreading device 8, in which the spring arms 20 are formed from two intersecting individual springs which are firmly connected to one another in the middle region.
  • the spring arms 20 are formed from two intersecting individual springs which are firmly connected to one another in the middle region.
  • a fastening of the bracket 12 comparable to FIG. 5 is shown in FIG. However, in this case the fuse 13 for holding the retaining bow 21 is dispensed with. Instead, the retaining bow 21 is held on the bracket 12 in an axially secured manner, in particular by frictional engagement, but also by positive locking. Incidentally, the bracket 12 is inserted into bores 25a of the opposing brake carrier horns 25.
  • FIG. 21 shows an enlarged section of an attachment of the retaining bow 21.
  • the bracket 12 is formed as a straight rod and fixed to the end of the holding bow 21, the end leg 27 is in alignment with the middle leg 26, wherein the end leg 27 has a forked end which engages over a pin 35, which inserted into the Bremschuhorn 25 is sen.
  • FIGS. 23 and 24 each show a variant of the spreading device 8, which consists of a spring clip 14 and an abutment leg 22, which is inserted into the suspension 15 at the ends, each with one attachment end 14a, 22a. this is attached to the lining carrier plate 4.
  • the spring clip 14 and the abutment leg 22 are offset from one another and fastened on opposite sides on the suspension 15 and on the other hand are based on the brake carrier 6 and that in the example shown in Figure 23 below the lining carrier plate 4 and in that shown in FIG Example on the Bremschuhorn 25.
  • the suspension 15 is formed as an elongated, rectangular plate with two longitudinal sides 15a, 15b. Here are two diagonally opposite ends rounded.
  • the attachment end 14a of the spring clip 14 is connected on the upper narrow side 15a shown on the top in FIG. 24 on the right with the suspension 15, whereas the attachment end 22a of the abutment leg 22 is connected on the lower, other narrow longitudinal side 15b off-center on the left with the suspension 15.
  • the other ends of the spring clip 14 and the abutment leg 22 run obliquely toward each other and are firmly connected by a connecting sheet 220.
  • the plate of the suspension 15 is here provided with two attachment holes 15c for attachment, e.g. by means of screws or rivets.
  • Figure 25 shows a further embodiment, which is similar to that described in Figures 8 to 1 1, but with some differences, constructed.
  • the tether 21 and the spring arms 20 are here in one piece, e.g. as a stamped and bent part, formed and fixedly connected in a central region by a common base portion 42.
  • the base portion 42 is located in the virtual center of the opening 41 and in a plane which is tangent to the brake disc 2.
  • the middle legs 26 of the tether 21 extend downwardly bent over both sides of the brake disk 2 as shown in the embodiment of Figure 4 as flat strip portions until shortly before the tie rods 1 c, which limit the opening 41 laterally. At these points, both middle legs 26 are bent toward the tightening section 1 a of the brake caliper 1 and in each case transition into an end leg 27.
  • Each end leg 27 has the tab 29 with the pin 30, similar to the embodiment of Figure 8, but with the difference that the tab 29 is not widened.
  • Each end leg 27 extends with its tab 29 in such a way that the tab 29 rests on the associated Bremschuhorn 25.
  • the pin 30 is received in a bore 25a (similar to that shown in FIG. 26) and fastened to the brake carrier horn 25. This naturally applies to both sides and to both brake carrier listeners 25.
  • each connecting portion 43 connects on each longitudinal side of the base portion 42 each have two spring arms 20 with the base portion 42 parallel to the imaginary longitudinal center line of the opening 41 such that an arrangement similar to that in Figure 8 results.
  • each connecting section 43 lies in a respective plane which is arranged at approximately 90 ° to the plane of the base section 42 and runs essentially parallel to the plane of the brake disk 2.
  • the spring ends 300 of the spring arms 20 are formed and described as in the embodiment of Figure 8 and in Figure 1 1.
  • FIG. 26 shows a further embodiment in which the retaining bow 21 is of wire-shaped design and has e.g. has a circular cross-section.
  • the retaining bow 21 includes a central portion 26 a in a central region of the opening 41.
  • At the central portion 26a includes on each side of a central portion 26, which in each case in an arc in the direction of the application section 1 a through an end leg 27 to the respective Bremshari- horn 25 tapers.
  • Each end leg 27 is then bent downwards by about 90 ° in each case a fastening portion 27a.
  • Each attachment portion 27a is fixed in a bore 25a of each Bremsnovahorns 25 of the lining shaft of the action-side brake pad 3 and thus forms the support of the retaining bow 21 with the spreader 8 in the brake carrier. 6
  • the spring arms 20 are here not in the longitudinal direction of the opening 41, but in the transverse direction of the opening 41 in pairs connected by a connecting portion 200.
  • Each connecting portion 200 is widened in the radial direction toward the brake disk axis of rotation 2a downwards and has a recess 201.
  • Each recess 201 communicates with the outer contour of the retaining bow 21 and here has a semicircular cross-section which is open to receive the retaining bow 21 upwards.
  • the connecting portions 200 of the paired spring arms 20 are arranged at a distance 203 at the central portion 26 a of the tether 21, wherein the center of the central portion 26 a of the virtual center of the opening 41 is assigned and forms the center of the distance 203.
  • a measure of the distance 203 here corresponds to about one quarter of the longitudinal extent of the opening 41st
  • the measure of the distance 203 may be in a range of 30 to 50%, for example.
  • the longitudinal extent of the opening 41 are either symmetrical to the virtual center of the opening 41 or without reference to the virtual center of the opening 41.
  • the spring arms 20 and their connecting portions 200 are integrally formed, for example, as stamped and bent parts of spring steel strip.
  • the retaining bow 21 is designed as in the embodiment according to FIG. Here, however, arranged in pairs in the transverse direction of the opening 41 spring arms 20 including their connecting portions 200 are formed wire-shaped.
  • the connecting portions 200 are bent so as to form receptacles for the tether 21.
  • the connecting portions 200 are arranged as in the embodiment of Figure 26 at a distance 203 at the central portion 26 a of the tether 21.
  • the ends of the spring arms 20 are each formed as a downwardly bent mounting portion 20a.
  • Each attachment portion 20a is received in a receiving hole 4a at each end portion of a lining carrier plate 4 from the upper side.
  • the spreader 8 transmits its expansion forces in this way between each attachment portion 20a in the associated receiving hole 4a on the respective lining carrier plates 4th
  • FIG. 28 shows an exemplary embodiment in which the retaining bow 21 is C-shaped as in the embodiments according to FIGS. 26 and 27.
  • the spring arms 20 have spring ends 300 according to FIG.
  • the spring arms 20 are arranged in pairs in the transverse direction of the opening 41.
  • Each pair of spring arms 20 are connected at their other ends by a respective hood connector 202.
  • Each bonnet connector 202 has a receiving opening pointing downwards toward the brake disk 2 in the longitudinal direction of the central portion 26a of the retaining bow 21, which communicates with the outer contour of the central portion 26a of the retaining bow 21.
  • the pair of spring arms 20 connected in each case to a hood connector 202 are applied with their respective hood connector 202 to the central portion 26a of the retaining bow 21 from above such that the central portion 26a is received in the receiving openings of the hood connector 202. men is.
  • the hood connectors 202 are arranged at a distance 203 from one another.
  • FIG. 29 shows a disk brake 100 in a perspective illustration with the brake disk 2 and the brake disk rotation axis 2 a.
  • a rotary arrow about the brake disk axis of rotation 2a indicates a main direction of rotation for forward travel of a vehicle to which the disk brake 100 is assigned.
  • an inlet side ES and opposite an outlet side AS are fixed to the disc brake 100.
  • the brake carrier horns 25 are called on the inlet side ES inlet side Bremsavi stealner 25 and on the outlet side AS outlet side brake carrier horns 25.
  • the spreader 8 is constructed substantially like the spreader 8 of the embodiment of FIG. A difference from the exemplary embodiment according to FIG. 28, however, is that in FIG. 29 the hood connectors 202 on both sides of the retaining bow 21 are connected by a respective longitudinal connector 202a. In addition, here the tie 21 has no broadening 26b.
  • a length of the spring arms 20 taken together in the longitudinal direction of the opening 41 corresponds to approximately 60 to 95% of a lining shaft length, particularly preferably 70 to 80% of a lining shaft length. Under the lining shaft length is the distance of the associated Bremshari steal steal 25 to understand.
  • the spreading device 8 comprises two spreading elements, wherein in a preferred embodiment, a first spreading element comprises two spring arms 20, which in
  • the spreader 8 can be easily positioned as an active return device (ACR) and held down by the pad retainer 28 through the central web.
  • ACR active return device
  • the spreader 8 can be easily removed and replaced in a pad change.
  • only two springs are used.
  • the spreading elements i. the spring arms 20 can be formed from inexpensive and geometrically flexible sheets.

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

Abstract

L'invention concerne un frein à disque (10) destiné à un véhicule utilitaire, comprenant un étrier de frein (1) conçu sous forme d'étrier coulissant et chevauchant le disque de frein (2), lequel étrier étant fixé à un support de frein (6) fixe et présentant une ouverture centrale (41) au-dessus du disque de frein (2). Ledit frein comprend deux garnitures de frein (3) disposées dans l'étrier de frein (1), mobiles dans des sens opposés et présentant chacune une plaque de support de garniture (4) et une garniture de friction (5) fixée sur celle-ci, une des deux garnitures de frein située côté actionnement pouvant être pressée contre le disque de frein (2) au moyen d'un dispositif d'application de force de freinage par l'intermédiaire d'au moins un tampon de frein, et au moins un dispositif de rappel au moyen duquel l'étrier de frein (1) peut être ramené après un déplacement lié au freinage et une libération du frein, le dispositif de rappel présentant un dispositif d'écartement (8) entrant en contact avec les garnitures de frein (3) se faisant face et exerçant une action équivalente dans le sens opposé au sens de l'application de force respectif, ledit dispositif d'écartement comprenant des éléments d'écartement élastiques entrant en contact avec leur plaque de support de garniture (4) respective. Le dispositif d'écartement (8) est disposé dans l'ouverture centrale (41), les éléments d'écartement entrant en contact directement ou indirectement à l'extérieur des garnitures de friction (5), soit avec un seul côté dans la zone centrale, soit avec au moins deux zones d'appui des garnitures de frein (3), disposées à distance l'une de l'autre et par rapport au centre, ces zones d'appui présentant chacune une surface d'appui et une surface de support, sur lesquelles les éléments d'écartement sont montés mobiles. L'invention concerne également un jeu de garnitures de frein correspondant.
EP16781729.5A 2015-10-09 2016-10-10 Frein à disque pour véhicule utilitaire et jeu de garnitures de frein Pending EP3359844A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102015117285 2015-10-09
DE102016104970.0A DE102016104970A1 (de) 2015-06-15 2016-03-17 Scheibenbremse für ein Nutzfahrzeug und Bremsbelagsatz
PCT/EP2016/074157 WO2017060515A1 (fr) 2015-10-09 2016-10-10 Frein à disque pour véhicule utilitaire et jeu de garnitures de frein

Publications (1)

Publication Number Publication Date
EP3359844A1 true EP3359844A1 (fr) 2018-08-15

Family

ID=57113363

Family Applications (4)

Application Number Title Priority Date Filing Date
EP16778405.7A Active EP3359841B1 (fr) 2015-10-09 2016-10-10 Flasque de frein
EP16778406.5A Active EP3359842B2 (fr) 2015-10-09 2016-10-10 Frein à disque pour véhicule utilitaire
EP16778404.0A Active EP3359843B1 (fr) 2015-10-09 2016-10-10 Frein à disque pour véhicule utilitaire
EP16781729.5A Pending EP3359844A1 (fr) 2015-10-09 2016-10-10 Frein à disque pour véhicule utilitaire et jeu de garnitures de frein

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Application Number Title Priority Date Filing Date
EP16778405.7A Active EP3359841B1 (fr) 2015-10-09 2016-10-10 Flasque de frein
EP16778406.5A Active EP3359842B2 (fr) 2015-10-09 2016-10-10 Frein à disque pour véhicule utilitaire
EP16778404.0A Active EP3359843B1 (fr) 2015-10-09 2016-10-10 Frein à disque pour véhicule utilitaire

Country Status (15)

Country Link
US (5) US11060573B2 (fr)
EP (4) EP3359841B1 (fr)
JP (1) JP6731210B2 (fr)
KR (1) KR102656462B1 (fr)
CN (5) CN108350962B (fr)
AR (3) AR106274A1 (fr)
AU (1) AU2016335294A1 (fr)
BR (1) BR112018007044B1 (fr)
CA (1) CA3001190C (fr)
DE (2) DE102016104969A1 (fr)
HK (1) HK1256858A1 (fr)
MX (1) MX2018004268A (fr)
RU (3) RU2694388C1 (fr)
WO (4) WO2017060512A1 (fr)
ZA (1) ZA201802890B (fr)

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DE102017007288A1 (de) * 2017-08-01 2019-02-07 Lucas Automotive Gmbh Bremssattelanordnung mit Belagrückstellfunktion
US10400837B2 (en) 2017-10-11 2019-09-03 Arvinmeritor Technology, Llc Brake carrier and method of manufacture
DE102017011338A1 (de) 2017-12-08 2019-06-13 Wabco Europe Bvba Bremsträger für eine Scheibenbremse
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US10801565B2 (en) 2020-10-13
US20180223922A1 (en) 2018-08-09
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WO2017060514A1 (fr) 2017-04-13
US10738844B2 (en) 2020-08-11
US20180223921A1 (en) 2018-08-09
US20180223929A1 (en) 2018-08-09
CN110410433A (zh) 2019-11-05
KR20180063305A (ko) 2018-06-11
EP3359842A1 (fr) 2018-08-15
EP3359841B1 (fr) 2019-12-18
US20210277967A1 (en) 2021-09-09
CN108291596B (zh) 2020-09-18
US11078974B2 (en) 2021-08-03
CN110410433B (zh) 2021-11-19
US20180223920A1 (en) 2018-08-09
US11060573B2 (en) 2021-07-13
AR106275A1 (es) 2017-12-27
BR112018007044B1 (pt) 2023-03-21
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EP3359843B1 (fr) 2019-12-18
MX2018004268A (es) 2018-05-16
RU2695751C1 (ru) 2019-07-25
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AR106274A1 (es) 2017-12-27
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AR106276A1 (es) 2017-12-27
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CN108350963A (zh) 2018-07-31
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CN108368898A (zh) 2018-08-03
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EP3359842B1 (fr) 2019-12-18
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HK1256858A1 (zh) 2019-10-04
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