WO2018025980A1 - Disque de frein - Google Patents

Disque de frein Download PDF

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Publication number
WO2018025980A1
WO2018025980A1 PCT/JP2017/028343 JP2017028343W WO2018025980A1 WO 2018025980 A1 WO2018025980 A1 WO 2018025980A1 JP 2017028343 W JP2017028343 W JP 2017028343W WO 2018025980 A1 WO2018025980 A1 WO 2018025980A1
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Prior art keywords
disc
disk
fin
sliding surface
sliding
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Application number
PCT/JP2017/028343
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English (en)
Japanese (ja)
Inventor
橋田　浩一
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株式会社アドヴィックス
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Publication of WO2018025980A1 publication Critical patent/WO2018025980A1/fr

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    • 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
    • F16D65/12—Discs; Drums for disc brakes

Definitions

  • the present invention relates to a brake disc.
  • Patent Document 1 for the purpose of “obtaining a brake disc free of noise generation”, “at least two discs of different frequencies are superposed and dispersed so that both can give freedom to each other. It is described that "we bond together in multiple places.” Specifically, it is described that two disks are integrally joined by a rivet at a portion sliding with the brake pad. That is, in the brake disc described in Patent Document 1, the brake noise is reduced by friction damping.
  • the rotor may be a plate-like member having a sliding surface on one side. Divide and project fins alternately on the opposite side of each sliding surface of these plate-like bodies, attach a damping material to each of the tip faces of these fins, and join these plate-like bodies to each other with the damping material
  • a disk brake rotor is described, which is characterized in that it is assembled with a bolt and a nut and ventilation is formed inside. That is, in the brake disc described in Patent Document 2, the brake noise is reduced by the damping effect of the damping material.
  • Patent Document 3 aims to “provide a mold structure and a casting method for avoiding deterioration in product quality in casting using a center gate type mold poured radially from the vicinity of the axial center of the cavity for annular member”.
  • the mold structure comprises at least one core 12a and at least one pair of molds 12b disposed sandwiching the core 12a, having a cavity for casting an annular member, and A spout 19 and a tap 18 are provided in the vicinity of the axial center so that the molten metal is diffused radially and poured in.
  • the pair of molds 12 b extends in one or both of the axial direction from the entire circumference of the outer peripheral surface It has a collar portion 15 and is configured to surround the outer periphery of the core 12a with the collar portion 15 to prevent deformation and collapse due to expansion of the core 12a.Gas that escapes from the cavity to the outer peripheral surface of the mold 12b
  • the brake disc configuration described in Patent Document 1 (referred to as “frictional damping configuration”) is applied to the brake disc described in Patent Document 2 to obtain a noise suppressing effect by friction damping. Try that.
  • FIG. 6 is a partial cross-sectional view as viewed in the direction perpendicular to the rotational axis Jwh of the disks when the uneven portions of the first disk D1 and the second disk D2 are brought into contact with each other so as to be engaged alternately.
  • the depth (length) of the recess for example, as shown by the X portion
  • the contact at the other part is It is inhibited. That is, as illustrated in the Y portion and the Z portion, a gap is generated between the convex portion and the concave portion. If the gap is filled with damping material, this gap is not an issue.
  • Patent Document 3 is an example of a method of integrally casting a ventilated disc.
  • a core is required from the inner circumference to the outer circumference.
  • the brake noise performance and the cooling performance be highly optimized for general brake discs. That is, as a brake disc, a structure that has a frictional damping effect secured and a high degree of freedom in design in the shape (number, width, etc.) of the vents is desired.
  • An object of the present invention is to provide a brake disc having a laminated structure, which can effectively obtain friction damping and has high cooling performance with a simple structure.
  • a brake disc (BRD) according to the present invention is fixed to a wheel (WH) of a vehicle and generates braking force on the wheel (WH) by being sandwiched by two friction pads (MSA, MSB).
  • the brake disc (BRD) includes one of the two friction pads (for example, MSA), a first disc (BDA) in sliding contact with the first sliding surface (Maa), and the two friction pads. And the second disk (BDB) in sliding contact with the second sliding surface (Mba).
  • the first disc (BDA) is a plurality of elongated protrusions on a first back surface (Mab) opposite to the first sliding surface (Maa)
  • the first disk has a first fin portion (Fna)
  • the second disk (BDB) has a plurality of elongated protrusions on a second back surface (Mbb) opposite to the second sliding surface (Mba)
  • the flat surface (Maf) and the “second fin surface (Mbf) formed parallel to the second sliding surface (Mba) in the second fin portion (Fnb)” are fixed in surface contact with each other. .
  • the first disc (BDA) is a plurality of elongated protrusions on a first back surface (Mab) opposite to the first sliding surface (Maa) “A first fin plane (Maf) formed in parallel to the first sliding surface (Maa) in the first fin portion (Fna)” and “the second disc (the second disk) having the first fin portion (Fna)
  • the second back surface (Mbb) opposite to the second sliding surface (Mba) of (BDB) is fixed in surface contact.
  • a third brake disc (BRD) comprises one of the two friction pads (for example, MSA) and a first disc (BDD) in sliding contact with the first sliding surface (Mda).
  • an intermediate disk (BDC) provided in between.
  • the two planes of the intermediate disc (BDC) are parallel, and a plurality of elongated grooves (Zma, Zmb) are formed in at least one of the two planes.
  • the first disc (BDD) and the intermediate disc (BDC) are in surface contact with each other, and the second disc (BDE) and the intermediate disc (BDC) are in surface contact with each other.
  • FIG. 1 is a front view and a cross-sectional view for describing a first embodiment of a brake disk BRD according to the present invention. It is the front view and cross-sectional view for demonstrating the shape of 1st disc BDA.
  • FIG. 7 is a cross-sectional view for explaining a modification of the first embodiment of the brake disk BRD according to the present invention.
  • FIG. 7 is a front view and a cross-sectional view for describing a second embodiment of a brake disk BRD according to the present invention. They are the front view for demonstrating middle disc BDC, and a partial side view. It is a fragmentary sectional view in order to explain the subject in the case of trying to obtain friction damping by applying a prior art.
  • a first embodiment of a brake disc BRD according to the present invention will be described with reference to the front view and the cross-sectional view of FIG.
  • the component members and the parts to which the same symbol is attached perform the same function. Therefore, duplicate explanations may be omitted.
  • the brake disc BRD is a friction disc of a disc brake employed for braking the wheel WH in a vehicle.
  • the brake disc BRD is sandwiched between the two friction pads MSA, MSB and fixed to the wheel WH so as to rotate together.
  • the brake disc BRD receives a pressing force so as to be sandwiched by the first and second friction pads MSA and MSB.
  • the pressing force at this time causes a frictional force when the first and second friction pads MSA, MSB and the brake disc BRD slide.
  • the wheel WH generates a braking force by this frictional force.
  • the brake disc BRD includes a first disc BDA, a second disc BDB, a hat member HTB, and a fastening member TKB.
  • the first disk BDA is a circular disk member.
  • the first disc BDA is in sliding contact with the first friction pad MSA (inner side friction pad) at the outer peripheral portion of the first sliding surface Maa (inner side flat surface) so that the wheel WH (tire) generates a braking force.
  • the region sliding with the first friction pad MSA is the “sliding range” of the first disc BDA.
  • a plurality of fastening holes Ata are provided on the inner peripheral portion of the first disc BDA so that the first disc BDA may be assembled to the hat member HTB.
  • the fastening holes Ata are through holes.
  • An elongated protrusion Fna (referred to as a "first fin portion”) is provided on the first back surface Mab of the first disc BDA.
  • the first back surface Mab (outer side flat surface) is a flat surface on the opposite side (back side) to the first sliding surface Maa.
  • the cross-sectional shape of the first fin portion Fna is convex, and a plane Maf (referred to as a "first fin plane") is formed at the tip of the projection.
  • the second disc BDB is a thin-plate shaped member formed in an annular shape.
  • the second disk BDB is in sliding contact with the second friction pad MSB (outer-side friction pad) at the outer peripheral portion of the second sliding surface Mba (outer-side plane).
  • the region sliding with the second friction pad MSB is the “sliding range” of the second disk BDB.
  • a plurality of fastening holes Atb are provided in the inner peripheral portion of the second disc BDB so that the second disc BDB is assembled to the hat member HTB.
  • an elongated protrusion (second fin portion) Fnb is provided on a plane (inner side plane, second back surface Mbb) opposite to the second sliding surface Mba (on the back side).
  • the cross-sectional shape of the second fin portion Fnb is convex, and a plane (second fin plane) Mbf is formed at the tip of the protrusion.
  • the first fin portion Fna and the second fin portion Fnb are mirror symmetric.
  • Mirror symmetry is also referred to as “mirror symmetry”, which means that the mirror image with respect to a certain reflection plane matches the original figure. For example, if the shape of the planar figure is mirror-symmetrical (mirror-symmetrical), the planar figure is axisymmetric.
  • the hat member HTB is a bottomed cylindrical member extending in the rotational axis direction Jwh of the brake disc (the same as the rotational axis of the wheel WH).
  • the hat member HTB has a flange portion Fln at the outer peripheral portion Mht.
  • a hub unit HUB is provided inside the cylinder of the hat member HTB.
  • a plurality of mounting holes Awh (through holes) are provided at the bottom of the hat member HTB.
  • the hub bolt HBL of the hub unit HUB penetrates the mounting hole Awh and is clamped by the wheel nut WNT across the wheel disc portion of the wheel WH. That is, the hub unit HUB, the hat member HTB, and the wheel WH are integrally coupled by the hub bolt HBL and the wheel nut WNT.
  • an aluminum alloy may be employed as the hat member HTB.
  • the inner peripheral surface Mha of the first disk BDA and the inner peripheral surface Mhb of the second disk BDB are fitted to the cylindrical outer peripheral surface Mht of the hat member HTB with a slight gap. Positioning can be easily performed by fitting the outer peripheral surface Mht of the hat member HTB and the inner peripheral surfaces Mha and Mhb of the first and second disks BDA and BDB in co-tightening by the fastening member TKB.
  • the flange portion Fln of the hat member HTB is provided with a plurality of fastening holes Ath (through holes) so that the first disc BDA and the second disc BDB can be assembled.
  • the fastening member TKB penetrates the fastening hole Ath of the hat member HTB, the fastening hole Ata of the first disc BDA, and the fastening hole Atb of the second disc BDB. Then, these three members HTB, BDA, and BDB are fastened by the fastening member TKB at a portion on the inner circumferential side (side close to the rotation axis Jwh) than the sliding range.
  • the fastening member TKB is a caulking member (for example, a rivet, a grommet), and the ends thereof are plastically deformed to be fastened together and fixed.
  • the first fin portion Fna of the first disc BDA and the second fin portion Fnb of the second disc BDB are butted in the same plane Mms. That is, the first fin plane Maf and the second fin plane Mbf, which are in a mirror symmetry relationship, are fixed so that their positions are matched and abut (see BB cross section).
  • the contact portion between the first fin plane Maf and the second fin plane Mbf is referred to as “abutment plane Mms”.
  • the brake disc BRD is formed as a single disc, in which two discs (a first disc BDA and a second disc BDB) are superimposed, fixed by a hat member HTB and a fastening member TKB.
  • the hole diameter of the fastening holes Ath, Ata, Atb is slightly larger than the diameter of the fastening member TKB at the penetration portion.
  • the first disc BDA and the second disc BDB are in a state in which the hat member HTB is capable of mutually minute displacement. Therefore, friction damping is obtained by minute mutual displacement (minute displacement) in the contact (contact surface Mms) between the first fin plane Maf and the second fin plane Mbf.
  • Cast iron having high damping properties may be adopted for the first and second disks BDA and BDB.
  • the "small displacement” is a displacement larger than the amplitude of the brake noise when the brake noise occurs.
  • the brake noise is at most several tens of ⁇ m. Therefore, the minute displacement is within the range of the play in assembling or the elastic deformation of the member.
  • a gap formed by the first fin portion Fna and the second fin portion Fnb is configured as a vent Avn for heat dissipation.
  • the inner circumferential portion and the outer circumferential portion of the brake disc BRD are penetrated and connected via the vent hole Avn.
  • the vents Avn form a ventilated brake disc.
  • the wheel WH, the hub unit HUB, the hat member HTB, the first disc BDA, and the second disc BDB are coaxially fixed. Therefore, the disc rotation axis Jwh is a rotation axis of the wheel WH, the hub unit HUB, the hat member HTB, the first disc BDA, and the second disc BDB.
  • the tip portions of the first and second fin portions Fna and Fnb are planarized to form first and second fin planes Maf and Mbf. Then, the first fin plane Maf and the second fin plane Mbf are butted to assemble the brake disc BRD.
  • the first fin plane Maf and the second fin plane Mbf are in mirror symmetry (that is, line symmetry) in the contact surface shape.
  • the first fin plane Maf of the first fin portion Fna and the second fin plane Mbf of the second fin portion Fnb are assembled so as to coincide with each other, so a sufficient contact area is secured and substantially uniform.
  • a contact state eg, surface pressure
  • the first disc BDA and the second disc BDB do not perform relative motion, and rotate completely in unison.
  • relative displacement between the first disc BDA and the second disc BDB does not occur.
  • a brake noise occurs in any one of the first disk BDA and the second disk BDB at the time of braking, periodic relative to the disk in which the brake noise does not occur. Displacement occurs.
  • the relative movement of the first disc BDA and the second disc BDB generates a frictional force between the first fin plane Maf and the second fin plane Mbf. This frictional force can suppress the generated brake noise.
  • a large area is secured for the contact surface Mms, a large friction damping acts, and the squeal vibration in the direction perpendicular to the first and second sliding surfaces Maa and Mba is effectively suppressed. .
  • the vibration suppression effect is applied to the squeal vibration (that is, movement vibration parallel to the sliding surfaces Maa and Mba) without the relative movement (minute displacement) of the first and second sliding surfaces Maa and Mba. It may be lower.
  • the heights of the first and second fin portions Fna and Fnb that is, the heights of the protrusions constituting the vent Avn are, for example, approximately “1: 2”) , Disc thickness
  • the vibration suppressing effect can be obtained also against the squeal vibration parallel to the sliding surfaces Maa and Mba.
  • the first disc BDA and the second disc BDB have different vibration characteristics (for example, natural frequency) so that the brakes do not occur simultaneously. Therefore, when a brake noise occurs in any one of the first disk BDA and the second disk BDB, amplification of vibration by the other disk (ie, resonance phenomenon) is avoided. .
  • the whole of the two disks BDA, BDB can be made mirror-symmetrically. Even in the case of the left and right wheels WH having different rotational directions, the brake disc BRD can be configured by the combination of the two mirror-symmetrical discs BDA and BDB without increasing the number of parts.
  • the first and second disks BDA and BDB are mirror symmetric, the difference in cooling performance between the first and second disks BDA and BDB is slight.
  • First disk BDA will be described with reference to the front view and the cross-sectional view of FIG.
  • the first fin portion Fna and the boss portion Bsa protrude from the surface Mab (rear surface) opposite to the first sliding surface Maa.
  • a fastening hole Ata is opened in the boss Bsa.
  • the heights of the fin portion Fna and the boss portion Bsa are aligned by machining.
  • the first fin plane Maf and the boss plane Mbs are in the same plane parallel to the first sliding surface Maa, and then one of cutting, grinding, and polishing is performed. It is processed by at least one method.
  • the second disc BDB is also finished by machining (at least one of cutting, grinding and polishing) after being cast. It is relatively easy to form the first and second fin planes Maf and Mbf parallel to the first and second sliding surfaces Maa and Mba with high precision by employing machining. .
  • the first fin portion Fna has a spiral shape (a so-called curve vane type). Specifically, the first fin portion Fna is radially extended at the inner peripheral portion of the first disc BDA, and gradually approaches the forward direction of the brake disc BRD (closer to the forward direction of the vehicle) as it gets closer to the outer peripheral portion. ) It is inclined in the opposite direction to Dfw (see front view). By rotating the spiral shaped first fin portion Fna, the brake disc BRD can smoothly discharge the air from the central portion to the outer peripheral portion, and the cooling performance can be improved.
  • the second fin portion Fnb of the second disk BDB is formed in mirror symmetry (mirror symmetry) with the first fin portion Fna so as to coincide with the first fin portion Fna. Therefore, the first fin plane Maf of the first fin portion Fna and the second fin plane Mbf of the second fin portion Fnb are in a line symmetrical relationship in the plane shape.
  • first fin portion Fna a straight type having a linear shape (that is, a shape extended in the radial direction without being inclined in the forward direction Dfw) may be employed instead of the curve vane type fin.
  • the shape of the straight first fin portion Fna is also determined so as to coincide with the second fin portion Fnb.
  • a "core” is a sand mold which inserts in a casting_mold
  • the efficiency of casting can be improved, and it is not necessary to consider the core strength in casting (in other words, the core strength and the shapes of the first and second fin portions Fna and Fnb)
  • the shape of the fin portion Fna, Fnb can be optimized only for the cooling property.
  • vents Avn having a finer shape may be formed to improve the cooling performance.
  • the first fin plane Maf of the first disk BDA is machined (for example, shaving, polishing) so as to be parallel to the first sliding surface Maa with respect to the first sliding surface Maa.
  • the second fin plane Mbf of the second disk BDB is shaped by machining so as to be parallel to the second sliding surface Mba with reference to the second sliding surface Mba.
  • the first disc BDA and the second disc BDB are fixed by the hat member HTB and the fastening member TKB so that the first fin plane Maf and the second fin plane Mbf are in contact with each other.
  • the two discs BDA, BDB are not butted against one another in the part of the groove. That is, the first fin plane Maf of the first fin portion Fna and the second back surface Mbb of the second disk BDB (the back side surface of the second sliding surface Mba) are in surface contact. For this reason, a sufficient contact area and uniform contact surface pressure can be ensured, and the effect of friction damping can be exhibited (see DD cross-sectional view). As a result, the same brake noise suppression effect as described above is exhibited.
  • a gap between the first fin portion Fna of the first disc BDA and the second back surface Mbb of the second disc BDB functions as the vent hole Avn.
  • the second disc BDB may be manufactured by adopting an iron plate (for example, a steel plate) and pressing it.
  • the iron plate does not have to be newly machined for assembly of the brake disc BRD because the parallelism between the two planes is secured at the time of material production.
  • the first disc BDA may be flat and the second disc BDB may be shaped so as to have the second fin portion Fnb.
  • the second fin plane Mbf of the second fin portion Fnb is in surface contact with the first back surface Mab (the back surface of the first sliding surface Maa), and exhibits a friction damping effect. Even in this case, the same brake squeak suppression effect is exhibited.
  • each of the first and second disks BDD and BDE has a flat plate shape, and the intermediate disk BDC as the third annular member is provided between the first disk BDD and the second disk BDE.
  • the intermediate disk BDC as the third annular member is provided between the first disk BDD and the second disk BDE.
  • the first and second disks BDD and BDE are attached to the hat member HTB by the fastening member TKB.
  • the shape and mounting of each member will be briefly described with reference to the EE cross-sectional view.
  • the first disc BDD is a disc member formed in an annular shape.
  • the first disc BDD is in sliding contact with the first friction pad MSA (inner side friction pad) at the outer peripheral portion of the first sliding surface Mda.
  • the region sliding with the first friction pad MSA is the “sliding range” of the first disk BDD.
  • the plane of the opposite side (back side) to the first sliding surface Mda is the first back surface Mdb.
  • a plurality of fastening holes Atd are provided in the inner peripheral portion of the first disc BDD.
  • the second disc BDE is a thin-plate shaped member formed in an annular shape.
  • the second disk BDE is in sliding contact with the second friction pad MSB (outer side friction pad) at the outer peripheral portion of the second sliding surface Mea.
  • the region sliding with the second friction pad MSB is the “sliding range” of the second disk BDE.
  • a plane on the opposite side (back side) to the second sliding surface Mea is a second back surface Meb.
  • a plurality of fastening holes Ate are provided in the inner peripheral portion of the second disk BDE.
  • the first and second disks BDD and BDE can be produced by press-forming an iron plate (for example, a steel plate). As described above, the iron plate does not need to be newly machined for assembly of the brake disc BRD, since the parallelism of the two planes is secured at the time of material production.
  • the hat member HTB is integrally fixed to the hub unit HUB and the wheel WH by the hub bolt HBL and the wheel nut WNT.
  • the inner peripheral surface Mhd of the first disk BDD, the inner peripheral surface Mhe of the second disk BDE, and the inner peripheral surface Mhc of the intermediate disk BDC are fitted to the cylindrical outer peripheral surface Mht of the hat member HTB with a slight gap.
  • the fastening member TKB eg, caulking member.
  • the fastening portion by the fastening member TKB is on the inner peripheral side (side closer to the rotation axis Jwh) than the above-mentioned sliding range.
  • the intermediate disk BDC is provided between the first disk BDD and the second disk BDE so as to be sandwiched between the first disk BDD and the second disk BDE.
  • Grooves (concave portions) Zmd and Zme are alternately formed on both surfaces Mcd and Mce (planes in contact with the first and second disks BDD and BDE) of the intermediate disk BDC. That is, the first groove portion Zmd is provided in the first contact surface Mcd in contact with the first sliding surface Mda of the first disk BDD.
  • a second groove Zme is provided on the second contact surface Mce in contact with the second sliding surface Mea of the second disc BDE. Then, the first groove portion Zmd and the second groove portion Zme are alternately provided on the front and back of the intermediate disk BDC.
  • the first and second groove portions Zmd and Zme of the intermediate disk BDC form the vent holes Avn when the brake disk BRD is assembled.
  • the first disk BDD, the intermediate disk BDC, and the second disk BDE are stacked and fixed. Therefore, the first rear surface Mdb of the first disk BDD and the first contact surface Mcd of the intermediate disk BDC are in surface contact in a state where microdisplacement is possible.
  • the second back surface Meb of the second disk BDE and the second contact surface Mce of the intermediate disk BDC are in surface contact with each other in a state in which small displacement is possible.
  • the plane in which the first back surface Mdb contacts the first contact surface Mcd, and the plane in which the second back surface Meb contacts the second contact surface Mce are the contact surfaces Mms.
  • First and second groove portions Zmd and Zme are provided on both surfaces (first and second contact surfaces) Mcd and Mce of the intermediate disk BDC.
  • the first and second grooves Zmd and Zme function as the vents Avn. That is, the first and second groove portions Zmd and Zme are extended from the inner circumferential portion to the outer circumferential portion of the intermediate disk BDC.
  • the first and second grooves Zmd and Zme are first manufactured by casting. Then, after casting, machining (for example, cutting such as cutting or grinding) is applied to the top surfaces Mcd and Mce of the convex portions that constitute the groove. By the machining, highly accurate parallel first and second contact surfaces Mcd and Mce can be easily formed. For this reason, friction damping can be effectively ensured.
  • machining for example, cutting such as cutting or grinding
  • the shapes of the first and second groove portions Zmd, Zme ie, the fin shape
  • the first and second groove portions Zmd and Zme are alternately provided on both surfaces (first and second contact surfaces) Mcd and Mce of the intermediate disk BDC, but the groove portions on one of the surfaces may be omitted.
  • the surface on the side where the groove is omitted is a uniform plane.
  • the planes Maf, Mbf, Mcd, and Mce of the disc members BDA, BDB, and BDC constituting the vent hole Avn are machined (cutting, grinding, and polishing Manufactured by at least one of Therefore, each of the planes Maf, Mbf, Mcd, and Mce is flat, and sufficient parallelism is ensured with respect to the sliding surfaces Maa, Mba, Mda, and Mea.
  • the contact surface Mms is constituted by the highly accurate planes Maf, Mbf, Mcd, and Mce, an area that can be used for friction damping is sufficiently secured, and a uniform contact state can be obtained. As a result, the friction noise can effectively suppress the brake noise.
  • the bonding between the first disc BDA, BDD and the second disc BDB, BDE is exemplified by caulking.
  • a screw fastening member may be employed instead of the caulking member.
  • welding for example, spot welding
  • a disc spring or the like may be added to the fastening portion in order to keep the fastening axial force between the disks in an appropriate range.
  • the fastening hole Ath of the hat member HTB may be formed as a long hole shape.
  • the heat generated at the time of braking thermally expands the disc members BDA, BDB, BDD, and BDE.
  • the inner peripheral surfaces Mha, Mhb, Mhd, and Mhe of the respective members expand in diameter, they can be separated from the outer peripheral surface Mht of the hat member HTB by the long hole-shaped fastening holes Ath. As a result, deformation of the hat member HTB can be suppressed.
  • the hat member HTB and the disk member are configured as separate members.
  • One of the two disks and the hat can be integrally formed. Then, the other of the two disks is fastened at the hat portion in a slightly displaceable state.
  • the inner brake pad located on the side farther from the wheel disc portion of the wheel WH is the first friction pad MSA, and the side closer to the wheel disc portion of the wheel WH
  • the outer brake pad positioned at the outer side in the lateral direction of the vehicle is used as the second friction pad MSB.
  • the disk members on the inner side are made the first disks BDA and BDD, and the disk members on the outer side (the outer side in the left and right direction of the vehicle) .
  • the disk members on the inner side are made the first disks BDA and BDD
  • the disk members on the outer side the outer side in the left and right direction of the vehicle.
  • the one related to the inner side may be the second friction pad and the second disk
  • the one related to the outer side may be the first friction pad and the first disk.

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

Abstract

Le disque de frein selon la présente invention est pris en sandwich par deux plaquettes de frein MSA, MSB, et génère ainsi une force de freinage sur une roue. Le disque de frein est pourvu d'un premier disque destiné à entrer en contact glissant avec l'une des deux plaquettes de frein sur une première surface de glissement, et d'un second disque destiné à entrer en contact glissant avec l'autre des deux plaquettes de frein sur une seconde surface de glissement. Le premier disque comporte une pluralité de premières parties formant ailettes qui sont des saillies étroites sur une première surface arrière du côté opposé à la première surface de glissement. Le second disque comporte une pluralité de secondes parties formant ailettes qui sont symétriques par rapport aux premières parties formant ailettes et qui sont des saillies étroites sur une seconde surface arrière du côté opposé à la seconde surface de glissement. Des « premières surfaces plates d'ailettes formées parallèlement à la première surface de glissement dans les premières parties formant ailettes » et des « secondes surfaces plates d'ailettes formées parallèlement à la seconde surface de glissement dans les secondes parties formant ailettes » sont fixées de manière à être en contact de surface les unes avec les autres.
PCT/JP2017/028343 2016-08-04 2017-08-04 Disque de frein WO2018025980A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016153541A JP2018021614A (ja) 2016-08-04 2016-08-04 ブレーキディスク
JP2016-153541 2016-08-04

Publications (1)

Publication Number Publication Date
WO2018025980A1 true WO2018025980A1 (fr) 2018-02-08

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JP2021102991A (ja) * 2019-12-25 2021-07-15 株式会社アドヴィックス ディスクブレーキのベンチレーテッドロータ

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WO2019194203A1 (fr) * 2018-04-03 2019-10-10 日本製鉄株式会社 Élément de réduction de son aérodynamique, disque de frein pour véhicule ferroviaire, frein à disque pour véhicule ferroviaire, roue pour véhicule ferroviaire et véhicule ferroviaire

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JPH0723734B2 (ja) * 1989-05-25 1995-03-15 日野自動車工業株式会社 通風型ディスクロータ及びその製造方法
US6234282B1 (en) * 1998-04-11 2001-05-22 Dr. Ing. H.C.F. Porsche Ag Brake disk for a motor vehicle
DE102009059806A1 (de) * 2009-12-21 2011-06-01 Daimler Ag Leichtbauverbundbremsscheibe und deren Herstellung

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JPS5582829A (en) * 1978-12-15 1980-06-21 Honda Motor Co Ltd Brake disc and its manufacturing method
JPH0723734B2 (ja) * 1989-05-25 1995-03-15 日野自動車工業株式会社 通風型ディスクロータ及びその製造方法
US6234282B1 (en) * 1998-04-11 2001-05-22 Dr. Ing. H.C.F. Porsche Ag Brake disk for a motor vehicle
DE102009059806A1 (de) * 2009-12-21 2011-06-01 Daimler Ag Leichtbauverbundbremsscheibe und deren Herstellung

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Publication number Priority date Publication date Assignee Title
JP2021102991A (ja) * 2019-12-25 2021-07-15 株式会社アドヴィックス ディスクブレーキのベンチレーテッドロータ

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