WO2009050226A1 - Frein à disque - Google Patents

Frein à disque Download PDF

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Publication number
WO2009050226A1
WO2009050226A1 PCT/EP2008/063947 EP2008063947W WO2009050226A1 WO 2009050226 A1 WO2009050226 A1 WO 2009050226A1 EP 2008063947 W EP2008063947 W EP 2008063947W WO 2009050226 A1 WO2009050226 A1 WO 2009050226A1
Authority
WO
WIPO (PCT)
Prior art keywords
brake
disc
caliper
bridge
brake pad
Prior art date
Application number
PCT/EP2008/063947
Other languages
German (de)
English (en)
Inventor
Ralf Sundheim
Uwe Bach
Rudolf Platzer
Niels Conradi
Original Assignee
Continental Teves Ag & Co. Ohg
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 Continental Teves Ag & Co. Ohg filed Critical Continental Teves Ag & Co. Ohg
Publication of WO2009050226A1 publication Critical patent/WO2009050226A1/fr

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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
    • 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
    • F16D55/228—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 separate actuating member for each side
    • 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
    • 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
    • F16D65/02—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
    • 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
    • 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
    • F16D2055/002—Brake calipers assembled from a plurality of 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
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D2055/0075—Constructional features of axially engaged brakes
    • F16D2055/0091—Plural actuators arranged side by side on the same side of the rotor

Definitions

  • the invention relates to a disc brake with a brake caliper, which axially surrounds a rotatable brake disk in a U-shaped manner, and comprises a saddle bridge, two saddle legs and at least one actuating device.
  • a brake caliper In the caliper at least one brake pad is mounted axially displaceable.
  • the saddle bridge has in the circumferential direction at least three, substantially axially extending carrier, wherein two of the carrier are designed as a main carrier and a carrier as a central carrier. These carriers connect the two saddle legs, thereby forming two windows and project axially over the brake disc.
  • the central support projects beyond both the brake disc and the brake pad in the axial direction.
  • Such a disc brake is known from DE 195 30 407 Al, which has a fixed caliper with saddle legs and a saddle bridge.
  • the saddle bridge is formed in the form of acting as a carrier screws, which connect the saddle legs.
  • Such brakes require a relatively large space in the radial and circumferential directions.
  • it has a positive effect on the braking power and performance when the radius of the brake disc is chosen to be as large as possible, since a high braking torque can thus be achieved with a low circumferential force.
  • the maximum diameter of a brake disc and the corresponding radius of the loading by the brake pads are determined by the rim inside diameter.
  • DE 101 13 347 A1 discloses a disc brake in which the saddle bridge is designed in the form of carriers, and a middle central carrier serves to support the brake pad.
  • a radial wall thickness of the central support of the saddle bridge is so pronounced that in an axial region of the brake pads, a distance between the central support and a rotational axis of the brake disc is smaller than an outer radius of brake disc.
  • the wall thickness in the region where the central support only projects beyond the brake lining is greater than where the central support engages over the brake disk.
  • the central carrier is reinforced by the axially projected overlap of brake disc and central carrier at the transition region between saddle leg and saddle bridge. This proves to be very favorable, since in this transition region, the stress of the components, in particular by notch stresses, is substantially stronger than in the region of the brake disc.
  • This claim-oriented and - optimized design of the saddle bridge has the advantage that the disc diameter can be maximally pronounced.
  • the design of the saddle bridge with girders and windows allows good heat radiation of the components, whereby the thermal load is kept low.
  • the brake pads are supported on bridge legs in the circumferential direction and in the radial direction, wherein the bridge legs are arranged on the main beams of the saddle bridge.
  • an undercut is provided on at least one, with respect to the brake pad inlet side bridge leg. This includes stops for the installation of the brake pad in the circumferential direction and a support for the radial support of the brake pad.
  • the brake pad comprises a back plate and a friction pad, the back plate having a body portion with two circumferentially adjacent projections. At least one of the projections is L-shaped with a support surface for radial support and two contact surfaces for installation in the circumferential direction. The L-shaped projection engages in the undercut of the bridge leg. This type of storage of a brake lining in the caliper is easy to manufacture and requires a comfortable braking behavior.
  • the undercut is provided with respect to a main direction of rotation of the brake disc only inlet side per brake pad in the brake caliper, and the back plate exclusively on the inlet side has an L-shaped projection, so that a power flow of peripheral forces the back plate in the caliper over a contact surface and a stop pulled takes place when the brake disc rotates in the main direction of rotation, and pressed over another stop and another contact surface takes place when the brake disc rotates counter to the main direction of rotation.
  • the conception of the brake pad bearing ensures that the drawn brake pad guide, with a favorable braking behavior with respect to noise and wear for the forward drive of the vehicle comes to bear
  • the brake pads are subjected to a reduced load when the vehicle is driven infrequently or when the vehicle is at a standstill.
  • This specially adapted to the requirements and effective application of the trailed and depressed lining guidance principle has the advantage that the installation space of the brake caliper in the circumferential direction of the brake disk is significantly reduced
  • the material and machining requirements, both with respect to the caliper and with respect to the back plate of the brake pad significantly reduced
  • This concept is particularly simple and advantageous, especially in the case of fixed saddles, since they are in principle very rigid, and thus the present reduced lining guidance can be used without disadvantages.
  • An advantageous further development of the invention includes that a stop and a support are provided on the outlet side bridge leg, whereby the brake pad is radially supported by means of the support surfaces.
  • the supporting in the circumferential direction stops in the brake caliper are spaced apart so that when the brake disc rotates in the main direction of rotation, at brake-induced, moderate peripheral forces exclusively the inlet-side stop the Schuscheidung and the contact surface of the L-shaped projection are engaged.
  • the outlet-side projection of the brake pad additionally bears against the stop of the outlet-side bridge leg, since both the inlet-side bridge leg deforms and the back plate of the brake pad lengthens.
  • a gap existing between the brake pad and an outlet-side stop is overcome by the deformation, so that a force discharge is made possible proportionally in the outlet-side bridge leg (pull-push principle).
  • a support surface is provided on the central support of the saddle bridge, which limits a possibility of movement of the brake pad in the brake caliper in the radial direction with a game cooperating with the conditions in the bridge legs.
  • a cooperating with the support surface of the central support hull support surface is provided on the brake pad, which is disposed on a side remote from the axis of rotation of the brake disc of the fuselage portion and substantially centrally between the projections.
  • a recess is provided in the brake pad, which at least partially receives the central carrier and wherein the fuselage supporting surface is arranged.
  • the radial support of the brake pad at a third point in the saddle bridge prevents undesirable movements of the brake pad and associated disadvantages in terms of braking comfort.
  • the use of the third support surface is particularly advantageous in the present guide system of the brake pads, since the one-sided expression of the L-shaped projection the brake pad certain possibilities of movement allowed, which is limited by the fuselage support surface and the corresponding counter surface in the saddle bridge.
  • the radial clearance of this brake pad bearing can be chosen relatively small in a fixed caliper, as saddle bridge and pads are in the paddle guide in a fixed geometric relationship.
  • a game in the order of 0.3 - 0.5 mm is useful here. In the event that other means between the brake pad and the caliper bridge should be effective, the game can be between 0.5 - 1 mm.
  • a further embodiment of the invention includes that in the brake caliper at least two pairs of brake pads are provided side by side in the circumferential direction for axially acting on both sides of the brake disc.
  • Such high-performance disc brakes have the decisive advantage over brakes with only a large pair of brake pads that the brake pads are evenly worn, as the brake pads of only one
  • Actuating device are acted upon, have a mutually independent storage and are thermally decoupled.
  • the mechanical stress of the force supports is reduced in the circumferential direction, which leads to lower component dimensions and weight.
  • This also improves the axial mobility in the caliper and thus also the comfort properties of the brake pads.
  • the favorable support of the brake pads by means of the undercuts and the attacks makes a compact and short design of the caliper, in particular in the circumferential direction possible.
  • the space in the circumferential direction can be used particularly effectively when the undercut for receiving the outlet side brake pad is provided on a central bridge leg, which at the same time the stop for the inlet-side brake pad is attached.
  • the outlet-side stop for the inlet-side brake pad is attached to the same bridge leg, on which also the inlet-side undercut for the outlet-side brake pad is provided.
  • Bridge legs are preferably integrally formed on and with the saddle bridge such that the saddle bridge and bridge legs have a U-shaped contour which engages around the brake disk, whereby the saddle bridge and saddle legs can be made from a lightweight material and the saddle bridge from a stronger material than the saddle legs Since the caliper bridge must fully support the actuating forces introduced by the actuators, this can be made of a higher strength material, such as spheroidal cast iron, due to the convenient multi-piece construction of the caliper To reduce the weight, the saddle legs are made of aluminum, for example.
  • the stiffness of the caliper can be further increased by the U-shaped shape of the caliper bridge and the bridge legs are included in the supporting structure.
  • the actuating forces of the actuator are also based on the bridge legs.
  • a brake pad for a disc brake with a brake caliper wherein the caliper axially surrounds a rotatable brake disc in a U-shaped manner. Furthermore, the caliper comprises a saddle bridge, two saddle legs and at least one actuating device.
  • the brake lining is mounted axially displaceably in the brake caliper and comprises a back plate and a friction lining arranged thereon.
  • the brake lining according to the invention in this case has a recess in the back plate and in the friction lining, which at least partially accommodates the central carrier.
  • the saddle bridge in a circumferential direction have at least three, substantially axially extending carrier.
  • the carriers are designed as two main carriers and a central carrier, which connect the saddle legs to form two windows and axially project beyond the brake disc.
  • the central support to the brake disc also projects axially over the brake pad and is received on both sides of the recess in the circumferential direction.
  • the brake pad comprises a back plate and a friction lining, wherein the back plate has a body portion with two circumferentially adjacent projections. At least one projection is L-shaped with a support surface for radial support, and formed with two contact surfaces for abutment in a circumferential direction. The L-shaped heel engages in one Undercut in the saddle bridge, wherein the other projection has a further contact surface and a support surface.
  • the brake pad allows the advantageous and space-optimized design of the caliper and the disc brake. It is conceivable to form the L-shaped projection with respect to a main direction of rotation of the brake disc exclusively on the inlet side of the trunk area of each back plate.
  • the brake pad is pulled and the power flow of the circumferential forces from the back plate in the caliper via the contact surface, which extends radially to the L-shaped projection and faces the body region, when the brake disc rotates in the main direction of rotation.
  • the outlet-side shoulder of the back plate may have an L-shaped contour.
  • a Rumpfabstütz which cooperatively limits the possibility of movement of the brake lining in the brake caliper with a clearance in cooperation with the support surfaces of the projections.
  • This functioning as a radial support hull support surface can both in normal operation of the disc brake in contact with the saddle bridge, as well as serve only as an emergency limit, especially if between the brake pad and saddle bridge other means are effective.
  • the disc brake has two pairs of brake pads, wherein two brake pads in the circumferential direction next to each other can act on both sides of the brake disc, so it is advantageous in terms of manufacturing costs, if at least two brake pads are made the same.
  • the described concept of a caliper and a brake pad can be applied in a disc brake with a fixed caliper or with a floating caliper.
  • FIG. 1 is a perspective view of a caliper of a first embodiment of a disc brake
  • FIG. 2 is a perspective view into the saddle bridge of the disc brake of FIG. 1,
  • FIG. 3 is a longitudinal section through the disc brake of FIG. 1,
  • FIG. 4 is a perspective partial section through the disc brake of FIG. 1,
  • Fig. 6 a shows a cross section through the disc brake of FIG. 1
  • b is a cross section through a Disc brakes similar to the disc brake of FIG. 1,
  • Fig. 7 is a longitudinal section through a second
  • Fig. 8 is a longitudinal section through a third
  • FIG. 9 is a perspective view of a caliper of a fourth embodiment of a disc brake without caliper bridge
  • FIG. 10 is a perspective view of a caliper of a fifth embodiment of a disc brake without caliper bridge
  • FIG. 11 is an enlarged view of the caliper according to FIG. 10,
  • Fig. 12 is a longitudinal section through the fifth
  • Fig. 13 is a cross section through the fifth
  • FIG. 14 is a perspective section through the fifth embodiment of FIG. 10,
  • FIG. 15 shows a further cross section through the fifth exemplary embodiment according to FIG. 10, FIG.
  • Fig. 16 is a cross section through a sixth
  • Embodiment of a disc brake 17 is a perspective view of a caliper of a sixth embodiment of a disc brake without saddle bridge and
  • This disc brake 1 comprises a fixed caliper 8 which is fixedly mounted on a vehicle leg, not shown.
  • the brake caliper 8 axially surrounds a brake disk 2, which is rotatably mounted about a rotation axis 3.
  • the brake disc 2 passes through a running in the circumferential direction 5 shaft 9 through the brake caliper 8, wherein the shaft 9 is formed by a first, vehicle-facing saddle leg 10, a saddle bridge 12 and a second vehicle facing away from saddle leg 11.
  • the saddle legs 10,11 and the saddle bridge 12 are formed as different components and connected to each other by means of screws.
  • a one-piece design of the caliper On the first caliper leg 10 substantially radially extending bores 13 are provided, by means of which the caliper 8 can be connected to the vehicle leg.
  • each saddle leg 10,11 are two each
  • Actuators 14 are arranged, each having a displaceable in a bore 15 piston 16. Between the piston 16 and the holes 15 resulting pressure chambers 17. All four pressure chambers 17 of the actuators 14 are hydraulically with each other connected, wherein the pressure chambers 17 are in the same caliper leg 10 or 11 by means of a tap hole 18 in conjunction, and also a pressure pipe 19 is provided between the pressure chambers 17 of the two saddle legs 10,11. In this case, the pressure tube 12 is shielded by a protective insulation 20 against thermal and mechanical stresses against the brake disc 2.
  • the saddle bridge 12 is designed as a carrier frame construction with radial windows 21, 22, whereby two webs 23, 24 extending in the circumferential direction 5 are connected to axially extending supports, and thus frame the windows 23, 24. It is to be distinguished between main carriers 25, 26, 27 and central carriers 28, 29, since the main carriers 25, 26, 27 are more pronounced than the central carriers 28, 29.
  • the main carriers 25,26,27 form together with firmly connected bridge legs 34,35,36 U-shaped units which surround the brake disc 2.
  • For the brake pads 37,38 are arranged on the bridge legs 34,35,36, which are thereby displaceably mounted in the axial direction 6 and stored in the circumferential direction 5 and radial direction 7. According to a main direction of rotation 4 of the brake disc 2, which corresponds to the forward travel of a motor vehicle, is to speak of each one inlet and outlet side pair of brake pads 37,38.
  • the central carriers 28, 29 are arranged between the main carriers 25, 26, 27 and project beyond the brake disk 2 and the brake linings 37, 38.
  • Fig. 4 can be seen particularly well, in what kind the central carrier 28,29 are arranged and pronounced.
  • the radial wall thickness D over the axial length of the central carrier 28,29 varied.
  • the central carriers 28, 29 at the transition to the saddle legs 10, 11 are made stronger with a thickening 30, 31 than where they project beyond the brake disc 2. This is due to the fact that the transition region is mechanically particularly heavily loaded.
  • the area with the thickening 30,31 is particularly well suited to receive the connecting screws 58,59.
  • the different wall thickness D over the axial extent of the central carrier 28,29 causes the brake disk 2 is also enclosed by the central support 28,29 also U-shaped, with no pronounced bridge legs are present.
  • This pointing to the rotation axis 3 U-shaped expression of the central support 28,29 is advantageous to make the outer radius R of the brake disc 2, and thus also the effective radius of the brake pads 37,38 and the peripheral force, as large as possible.
  • the thickened region of the central carrier 28,29 projects axially projected into the region of the friction engagement of the brake pads 37,38.
  • a distance A between the thickened region of the central support 28,29, in particular between the axis of rotation 3 facing surface of this area, and the axis of rotation 3 of the brake disc 2 is thus smaller than the outer radius R of the brake disc 2.
  • a brake disc are reduced by the amount of thickening of the central carrier, if the outer dimensions of the disc brake should be constant due to a rim inner diameter.
  • the advantageous overlap requires a recess 39 in the brake pads 37,38, wherein the thickening 30,31 of the central carrier 28,29 can be accommodated. This recess 39 only unhesitatingly reduces the friction surface. It is thus a highly effective one Design of the caliper 8, with only mechanically highly loaded areas are designed according to the stresses, and at the same time an optimal space utilization is realized.
  • All brake pads 37, 38 are mounted axially displaceable in the receptacles in the saddle bridge 12.
  • All brake pads 37, 38 include a back plate 40 and a friction lining 41 fixedly connected thereto, which is preferably pressed thereon.
  • the back plate 40 has a body region 42, which merges into a respective projection 43, 4 in the circumferential direction 5, wherein the recess 39 for receiving the thickening 30, 31 of the central carriers 28, 29 is provided in the body region 42 and in the friction lining 41.
  • the inlet-side projection 43 is L-shaped with a support surface 45 for radial support and two contact surfaces 48,49 for conditioning in the circumferential direction 5 is formed.
  • a support surface 46 for radial support is present.
  • the inlet side receptacles for the brake pads 37,38 in the inlet-side bridge legs 34 and in the middle bridge legs 35 as undercuts 50,51 are formed, in which the L-shaped projections 43 of the brake pads 37,38 engage.
  • Each undercut 50, 51 has a support 52 for radial support and two stops 53, 54 for abutment in the circumferential direction 5.
  • the outlet side recordings 55,56 for the brake pads 37,38 are provided on the middle bridge arms 35 and on the outlet side bridge legs 36 in the form of a support 57.
  • Each brake pad 37, 38 is supported by means of the inlet-side undercut 50, 51 and the outlet-side receptacle 55, 56 in the radial direction 7.
  • the support surface 45 acts on the inlet-side projection 43 of a brake pad 37,38 with the support 52 of the undercut 50,51 and the support surface 46 of the outlet-side projection 44 of a brake pad 37,38 with the support receptacle 56,57 together.
  • a trunk support surface 47 is present in the recess 39 in the fuselage region 42, which supports the
  • the clearance S R is preferably 0.3-0.5 mm.
  • the inner dimension in the circumferential direction 5 of the undercut 51 is slightly larger than the L-shaped projection 43, so that in the circumferential direction 5, a clearance S H of 0.3 - 0.6 mm results.
  • the pressure chambers 17 of the actuators 14 in the saddle legs 10,11 are acted upon, causing the respective piston 16 axially displaces and presses the corresponding brake pad 10,11 to the brake disc 2.
  • the resulting circumferential force causes the brake pad facing abutment surfaces 49 of the L-shaped projections 43 of the brake pads 10,11 facing away from the brake pad stops 54 of the undercuts 50,51 engage.
  • the circumferential force is derived by means of pulled brake pads 37,38 on the bridge legs 34,35 in the brake caliper 8.
  • the brake pads 37,38 set with the brake pads facing abutment surfaces 48 to the brake pad facing stops 53, whereby the peripheral forces pressed into the brake caliper 8 are initiated.
  • caliper 8 is shown in an axial section, which passes through the central main carrier 26 and the bridge legs 35. It can be seen how the U-shaped shape of the saddle bridge 12 and the bridge leg 35, the stiffness of the caliper 8 is further increased by these are included in the supporting structure.
  • Actuators 14 also on the bridge legs 35 from.
  • Fig. 6b another form of screw is realized, which reduces the number of screws and in particular uses a continuous screw 61 instead of two individual, resulting in a simplified assembly.
  • a caliper 63 is cited, which is analogous to the first embodiment, but has a modified support of the brake pad 80 in the circumferential direction 5 and only a pair of brake pads 80.
  • Two saddle legs overlap a brake disk 2 by means of a saddle bridge 64, wherein the saddle bridge 64 has two webs 65, two main beams 66, 67 and a central support 68, whereby two radial windows 70, 71 are formed.
  • a stop 78 is provided at the outlet-side projection 84 of the brake pad 80.
  • the brake lining facing abutment surface 86 of the inlet-side projection 83 of the brake pad 80 and the abutment surface 87 of the outlet-side projection 84 are spaced such that in the static state or at a weak braking the brake pad 80 is supported exclusively in the undercut 74 in the inlet side bridge leg 72, when the brake disc 2 rotates in the main direction of rotation 4.
  • Fig. 8 shows a further embodiment of a caliper 93, wherein the brake pad 110 is provided on both sides with L-shaped projections 113,114, and correspondingly also in the inlet and outlet side bridge leg 102,103 per an undercut 104,105 is provided.
  • This expression of the projections 113,114 requires a direction of rotation independent storage of the brake pad 110th
  • the radial mounting of the brake pads 80,110 in the calipers 63,93 according to the embodiments in FIGS. 7 and 8 is analogous, so a common description and numbering is selected.
  • the receptacle 75 and in the backgrounds 74,104,105 pads 91,92 are provided, on which the support surfaces 88,89, 120,121 of the brake pads are supported 80,110.
  • the recesses 82,112 in the trunk area 81,111 of the brake pads 80,110 partially receive the central carrier 68,98 and limit with a clearance S R the radial movement possibility of the brake calipers 80,110 by the trunk support surface 90,122 and the support surface 69.99 on the central support 68,98 cooperate.
  • FIGS. 9 to 18 show further embodiments of a disc brake, which has in common that a hold-down spring 130,131,144 is provided, which biases the respective brake pad against the brake caliper.
  • Such springs are basically known and serve the rattle and play-free arrangement of the brake pads.
  • the embodiments described below show hold-down springs, which are specially adapted to the first three embodiments, which fit optimally in the described window of the caliper, without losing rigidity of the caliper.
  • Fig. 9 shows a fourth embodiment of a disc brake according to the invention, which is shown partially cut.
  • the brake caliper shown basically corresponds to the first embodiment, so that it is possible to dispense with a repeated description and the same components are provided with the same reference numerals.
  • the caliper shows a hold-down spring 130 made of sheet metal, which is supported on radial support surfaces 150,151 of the two central carrier 28,29.
  • Figs. 10 to 15 show a fifth embodiment, which also basically the first embodiment corresponds, so that reference is made here to the above description.
  • the difference is also a hold-down spring 131, which is supported on radial support surfaces 132 of thickenings 133.134 of the saddle legs 10,11 in the region of the central support
  • the thickenings 133, 134 have tangential centering surfaces 135, 136, by means of which the hold-down spring 131 is tangentially centered in a simple manner.
  • Axial centering surfaces 137, 138 on the saddle legs 10, 11 center the hold-down spring 131 in the axial direction, as can be seen in FIG. The centering is done to a certain extent automatically.
  • the hold-down spring 131 is made of wire, wherein wire ends are connected by means of a sleeve 139 and pressed with the sleeve 139. This requires a particularly simple and inexpensive production. However, other methods of linking, e.g. Inductive welding, in question.
  • wire arms 140, 141 of the hold-down spring 131 lie straight on the brake lining.
  • wire arms 142,143 of the hold-down spring 131 engaged rest on the brake pad.
  • the wire arms 142, 143 may be inclined at an angle CC of approximately 15 degrees.
  • a seventh embodiment according to FIGS. 17 and 18 shows a caliper, as has been described in accordance with FIG. 8. Again, a hold-down spring 144 is provided, which is supported on a radial support surfaces 147, X of thickenings 145,146 of the saddle legs in the region of the central support 98.
  • the thickenings 145, 146 have tangential centering surfaces 148, 149 by means of which the hold-down spring 144 is tangentially centered in a simple manner.
  • axial centering surfaces on the saddle legs center the hold-down spring 144.
  • the hold-down spring 144 is provided in the same way as the hold-down spring 131 made of wire, wire ends being connected by means of a sleeve 139 and pressed with the sleeve 139.
  • Support surface 130 hold-down spring
  • Support surface 140 wire arms

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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 comportant un étrier (93), qui enveloppe axialement en forme de U un disque de frein pivotant, et qui présente une mâchoire, deux bras d'étrier et au moins un dispositif d'actionnement. Dans l'étrier de frein est logée au moins une garniture (110) mobile dans l'axe. La mâchoire comporte, dans le sens périphérique, au moins trois supports (96,97,98) s'étendant sensiblement dans l'axe, deux supports (96,97) étant des supports principaux et un support étant un support central (98). Ces supports relient les deux bras d'étrier, formant ainsi deux fenêtres et surplombant le disque de frein dans l'axe. Le support central surplombe le disque de frein et la garniture (110) dans le sens axial. L'épaisseur radiale des parois du support central de la mâchoire est telle que, dans une zone axiale des garnitures (110), l'espace entre le support central et l'axe de pivotement du disque est inférieur à un rayon externe du disque de frein.
PCT/EP2008/063947 2007-10-19 2008-10-16 Frein à disque WO2009050226A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102007050458.8 2007-10-19
DE102007050458 2007-10-19
DE102008029582A DE102008029582A1 (de) 2007-10-19 2008-06-21 Scheibenbremse
DE102008029582.5 2008-06-21

Publications (1)

Publication Number Publication Date
WO2009050226A1 true WO2009050226A1 (fr) 2009-04-23

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PCT/EP2008/063947 WO2009050226A1 (fr) 2007-10-19 2008-10-16 Frein à disque

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DE (1) DE102008029582A1 (fr)
WO (1) WO2009050226A1 (fr)

Cited By (2)

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US9791004B2 (en) 2013-03-06 2017-10-17 Hitachi Automotive Systems, Ltd. Disc brake
CN111954770A (zh) * 2018-03-27 2020-11-17 曙制动器工业株式会社 浮动型盘式制动器

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IT1399203B1 (it) * 2010-03-31 2013-04-11 Freni Brembo Spa Corpo pinza di un freno a disco
DE102013101779A1 (de) * 2012-11-20 2014-06-05 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Bremsbelaghalterung für eine Scheibenbremse eines Kraftfahrzeugs
CN106050987B (zh) * 2016-07-06 2018-06-12 浙江亚太机电股份有限公司 内卡式浮动制动钳总成
USD831551S1 (en) 2016-08-30 2018-10-23 Akebono Brake Industry Co., Ltd Brake caliper
US10539199B2 (en) 2017-01-20 2020-01-21 Akebono Brake Industry Co., Ltd Multi-piston caliper
IT201800002973A1 (it) * 2018-02-23 2019-08-23 Freni Brembo Spa Corpo pinza fisso per un disco di freno a disco
IT201800006547A1 (it) 2018-06-21 2019-12-21 Corpo pinza di freno a disco
IT202000016357A1 (it) 2020-07-07 2022-01-07 Brembo Spa Corpo pinza e pinza freno con detto corpo
IT202100006608A1 (it) 2021-03-19 2022-09-19 Freni Brembo Spa Fascia di frenatura di un disco per freno a disco di tipo ventilato
IT202100007583A1 (it) 2021-03-29 2022-09-29 Freni Brembo Spa Corpo pinza e pinza freno con detto corpo

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EP0412541A1 (fr) * 1989-08-11 1991-02-13 LUCAS INDUSTRIES public limited company Frein à disque à garniture partielle
GB2258506A (en) * 1991-08-08 1993-02-10 Teves Gmbh Alfred Spot-type disc brake for automotive vehicles
DE19806056A1 (de) * 1997-02-19 1998-08-20 Montalvo Corp Modulare Bremse mit austauschbaren Bremsklötzen
JPH1163041A (ja) * 1997-08-27 1999-03-05 Nissin Kogyo Kk 車両用ディスクブレーキのキャリパボディ
WO2000065247A1 (fr) * 1999-04-26 2000-11-02 Pbr Australia Pty Ltd Etrier de frein a disque
EP1069332A2 (fr) * 1999-07-15 2001-01-17 Sumitomo Electric Industries, Ltd. Frein à disque avec étrier amélioré
DE10233446A1 (de) * 2002-07-24 2004-02-12 Continental Teves Ag & Co. Ohg Bremshalter einer Schwimmsattel-Scheibenbremse mit Bremsbelagführungsfeder
WO2007122100A1 (fr) * 2006-04-20 2007-11-01 Continental Teves Ag & Co. Ohg Frein à disque

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DE19530407A1 (de) 1995-08-18 1997-02-20 Teves Gmbh Alfred Festsattel - Teilbelagscheibenbremse für Kraftfahrzeuge
DE10113347A1 (de) 2000-05-23 2001-12-13 Continental Teves Ag & Co Ohg Teilbelagscheibenbremse mit Bremsbelagabstützung

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EP0412541A1 (fr) * 1989-08-11 1991-02-13 LUCAS INDUSTRIES public limited company Frein à disque à garniture partielle
GB2258506A (en) * 1991-08-08 1993-02-10 Teves Gmbh Alfred Spot-type disc brake for automotive vehicles
DE19806056A1 (de) * 1997-02-19 1998-08-20 Montalvo Corp Modulare Bremse mit austauschbaren Bremsklötzen
JPH1163041A (ja) * 1997-08-27 1999-03-05 Nissin Kogyo Kk 車両用ディスクブレーキのキャリパボディ
WO2000065247A1 (fr) * 1999-04-26 2000-11-02 Pbr Australia Pty Ltd Etrier de frein a disque
EP1069332A2 (fr) * 1999-07-15 2001-01-17 Sumitomo Electric Industries, Ltd. Frein à disque avec étrier amélioré
DE10233446A1 (de) * 2002-07-24 2004-02-12 Continental Teves Ag & Co. Ohg Bremshalter einer Schwimmsattel-Scheibenbremse mit Bremsbelagführungsfeder
WO2007122100A1 (fr) * 2006-04-20 2007-11-01 Continental Teves Ag & Co. Ohg Frein à disque

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9791004B2 (en) 2013-03-06 2017-10-17 Hitachi Automotive Systems, Ltd. Disc brake
CN111954770A (zh) * 2018-03-27 2020-11-17 曙制动器工业株式会社 浮动型盘式制动器
US11773931B2 (en) 2018-03-27 2023-10-03 Akebono Brake Industry Co., Ltd. Floating-type disc brake

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