WO2019189508A1 - Disc brake pad - Google Patents

Disc brake pad Download PDF

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Publication number
WO2019189508A1
WO2019189508A1 PCT/JP2019/013444 JP2019013444W WO2019189508A1 WO 2019189508 A1 WO2019189508 A1 WO 2019189508A1 JP 2019013444 W JP2019013444 W JP 2019013444W WO 2019189508 A1 WO2019189508 A1 WO 2019189508A1
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WO
WIPO (PCT)
Prior art keywords
axial direction
anchor
circumferential
pad
radial
Prior art date
Application number
PCT/JP2019/013444
Other languages
French (fr)
Japanese (ja)
Inventor
康平 野間
荘悟 真下
忠相 藤原
Original Assignee
曙ブレーキ工業株式会社
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 曙ブレーキ工業株式会社 filed Critical 曙ブレーキ工業株式会社
Priority to CN201980021586.0A priority Critical patent/CN111902648B/en
Publication of WO2019189508A1 publication Critical patent/WO2019189508A1/en

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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
    • F16D55/224—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
    • 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

Definitions

  • the present invention relates to a disc brake pad used by being incorporated in a disc brake for braking a vehicle.
  • FIG. 24 shows a floating type disc brake having a conventional structure described in Japanese Patent Laid-Open No. 2002-372082.
  • the floating disc brake 1 includes a support 2, a yoke (caliper) 3, an inner pad 4 and an outer pad 5.
  • the support 2 is fixed to a suspension device such as a knuckle constituting the vehicle body in a state adjacent to the inner side in the axial direction of the rotor 6 that rotates together with the wheel.
  • a suspension device such as a knuckle constituting the vehicle body in a state adjacent to the inner side in the axial direction of the rotor 6 that rotates together with the wheel.
  • the terms “axial direction (Z)”, “radial direction (Y)” and “circumferential direction (X)” refer to the axial direction, radial direction and circumferential direction of the rotor unless otherwise specified.
  • the inner side in the axial direction (ZI) means the center side in the width direction of the vehicle
  • the outer side in the axial direction (ZO) means the outer side in the width direction of the vehicle.
  • the radially inner side (YI) refers to the radially inner side of the rotor
  • the radially outer side (YO) refers to the radially outer side of the rotor.
  • circumferential inner side (XI) refers to the center side in the circumferential direction of the floating disc brake in the assembled state
  • circumferential outer side (XO) refers to both sides in the circumferential direction of the floating disc brake in the assembled state.
  • the yoke 3 has a bifurcated claw 7 on the outer side in the axial direction and a cylinder 8 on the inner side in the axial direction.
  • the yoke 3 is supported so as to be movable in the axial direction with respect to the support 2.
  • a pair of slide pins 9 each having a base end supported and fixed to the yoke 3 are slidably inserted into a pair of slide holes 10 provided in the support 2. Yes.
  • the inner pad 4 is disposed on the inner side in the axial direction of the rotor 6 and is supported so as to be movable in the axial direction with respect to the support 2.
  • the outer pad 5 is disposed on the outer side in the axial direction of the rotor 6 and is supported on the inner side surface in the axial direction of the claw portion 7 constituting the yoke 3.
  • a pad spring 11 fixed to the outer side surface (back surface) in the axial direction of the outer pad 5 is engaged with the claw portion 7.
  • a pair of axial protrusions (dowels) 12 formed on the outer side surface of the outer pad 5 in the axial direction are fitted into a pair of receiving holes (dowel holes) 13 formed on the inner side surface of the claw 7 in the axial direction.
  • the outer pad 5 is not supported by the support 2 but directly supported by the claw portion 7 of the yoke 3. This is advantageous in reducing weight.
  • the conventional floating disc brake 1 has the following problems to be improved due to the adoption of the structure in which the outer pad 5 is supported by the yoke 3. That is, at the time of braking, a brake tangential force that is directed in the circumferential direction (outward side) acts on the inner pad 4 and the outer pad 5.
  • the brake tangential force acting on the inner pad 4 is directly supported by the support 2 fixed to the suspension device, but the brake tangential force acting on the outer pad 5 is connected to the slide pin 9 and the slide hole 10 via the yoke 3. It is supported at the contact part.
  • the axial position of the contact portion between the slide pin 9 and the slide hole 10 is greatly separated inward in the axial direction from the axial position of the point of application of the brake tangential force acting on the outer pad 5. For this reason, the yoke 3 is likely to be inclined in the direction indicated by the arrow ⁇ in FIG. 24 due to the brake tangential force acting on the outer pad 5. As a result, the outer pad 5 comes into contact with the rotor 6 and the outer pad 5 is likely to be unevenly worn, and noise (noise) such as squealing is easily generated during braking.
  • the present invention has been made in view of the circumstances as described above, and an object of the present invention is to provide a structure of a disc brake pad that can suppress the occurrence of inclination in the yoke regardless of the brake tangential force acting during braking. It is to be realized.
  • the disc brake pad according to the present invention includes a lining and a back plate that supports an outer surface in the axial direction of the lining, and a slide pin is disposed on a fixing member that is disposed on the inner side in the axial direction of the rotor and is fixed to the vehicle body. It is attached to the yoke supported so that the movement of an axial direction is possible via, and is arrange
  • at least one or more radial protrusions are provided on the outer peripheral edge of the back plate.
  • the radial projection is for supporting a brake tangential force acting during braking based on contact with an anchor provided in a cantilever shape, for example, on the fixing member.
  • an anchor provided in a cantilever shape, for example, on the fixing member.
  • one or a plurality of (for example, two) shafts that are unevenly fitted to the axially inner side surface of the outer body disposed on the axially outer side of the rotor in the yoke on the axially outer surface of the back plate
  • Directional protrusions are provided.
  • the radial protrusion and the anchor are not only in direct contact with each other, but for example, other members such as a stainless steel plate disposed between the two members for the purpose of ensuring slidability. It also includes the case where the contact is made.
  • the anchor may be fixed to the fixing member using a fastening member such as a bolt as a separate body from the fixing member (for example, a cylinder or a support), or provided integrally with the
  • the radial projection is provided so that the circumferential position of the contact portion with the anchor is within the circumferential range of the lining.
  • the radial projection is in contact with the anchor at least during forward braking.
  • the radial protrusion is in contact with the anchor during forward braking and reverse braking.
  • the radial protrusion is in contact with the anchor only during forward braking. In this case, a brake tangential force acting during reverse braking can be transmitted to the yoke from the axial protrusion provided on the outer pad and supported by the slide pin.
  • a pair of the radial protrusions are provided apart from each other in the circumferential direction.
  • the radially outer ends of the pair of radial protrusions are connected in the circumferential direction.
  • the radially outer ends of the pair of radial protrusions are free ends.
  • only one of the radial protrusions is provided in the circumferential center of the outer peripheral edge of the back plate.
  • the radial protrusion is a circumferential direction (for example, a turn-in) of the outer peripheral edge portion of the back plate. Side or outlet side).
  • the entire disc brake pad is symmetrical with respect to the circumferential direction.
  • the entire disc brake pad has an asymmetric shape with respect to the circumferential direction.
  • the axial projecting portion has a cylindrical shape.
  • the axial protrusion is provided integrally with the back plate.
  • the axial protrusion is formed by subjecting the back plate to press working such as embossing (extrusion).
  • the axial protrusion is fixed to the back plate as a separate body from the back plate.
  • a cross-sectional shape of a portion of the radial projection that contacts the anchor during braking is a convex arc shape.
  • abuts to the said anchor at the time of braking among the said radial direction protrusions is made into flat surface shape.
  • the disc brake pad of the present invention having the above-described configuration, it is possible to prevent the yoke from being inclined regardless of the brake tangential force acting during braking.
  • FIG. 1 is a front view of a floating disc brake according to a first example of an embodiment of the present invention as viewed from the outside in the axial direction.
  • FIG. 2 is a perspective view showing the floating disc brake according to the first example of the embodiment of the present invention.
  • FIG. 3 is a side view of the floating disc brake according to the first example of the embodiment of the present invention as seen from the circumferential direction.
  • 4 is a cross-sectional view taken along the line AA in FIG. 5 is a cross-sectional view taken along the line BB in FIG. 6 is a cross-sectional view taken along the line CC of FIG. 7 is a cross-sectional view taken along the line DD of FIG.
  • FIG. 8 is a view showing the yoke omitted from FIG.
  • FIG. 8 is a view showing the yoke omitted from FIG.
  • FIG. 8 is a view showing the yoke omitted from FIG.
  • FIG. 9 is a view showing the yoke omitted from FIG.
  • FIG. 10 is a view in which the yoke is omitted from FIG.
  • FIG. 11 is a plan view of the anchor taken out of the floating disc brake according to the first example of the embodiment of the present invention and viewed from the outside in the radial direction.
  • FIG. 12 is a front view of the outer pad taken out from the floating disc brake according to the first example of the embodiment of the present invention and viewed from the inside in the axial direction.
  • FIG. 13 is a rear view of the outer pad taken out from the floating disc brake according to the first example of the embodiment of the present invention and viewed from the outside in the axial direction.
  • FIG. 12 is a front view of the outer pad taken out from the floating disc brake according to the first example of the embodiment of the present invention and viewed from the inside in the axial direction.
  • FIG. 13 is a rear view of the outer pad taken out from the floating disc brake according to the first example of the embodiment of the present
  • FIG. 14 is a perspective view showing the outer pad taken out from the floating disc brake according to the first example of the embodiment of the present invention.
  • FIG. 15 is an enlarged view of a portion corresponding to the upper part of FIG. 7 for explaining the relationship between the radial protrusion of the outer pad and the constant width portion of the anchor.
  • FIG. 16 is a view for explaining the state at the time of braking in the first example of the embodiment of the present invention.
  • FIG. 16A shows the state at the time of forward braking, and FIG. B) shows the state during reverse braking.
  • FIG. 17 is a diagram corresponding to FIG. 15 and showing a second example of the embodiment of the present invention.
  • FIG. 18 is a diagram corresponding to FIG. 15 and showing a third example of the embodiment of the present invention.
  • FIG. 16 is a view for explaining the state at the time of braking in the first example of the embodiment of the present invention.
  • FIG. 16A shows the state at the time of forward braking
  • FIG. B shows the
  • FIG. 19 is a perspective view showing a floating type disc brake according to a fourth example of the embodiment of the present invention.
  • FIG. 20 is a view showing the yoke omitted from FIG.
  • FIG. 21 is an exploded perspective view in which the outer pad is omitted from FIG.
  • FIG. 22 is a view corresponding to FIG. 6 regarding a floating type disc brake according to a fourth example of the embodiment of the present invention.
  • FIG. 23 is a view corresponding to FIG. 7 regarding a floating type disc brake according to a fourth example of the embodiment of the present invention.
  • FIG. 24 is a partial cross-sectional view of a floating disc brake having a conventional structure as viewed from the outside in the radial direction.
  • the floating disk brake 1a of the first example is used for braking an automobile, and includes a support 2a, a yoke 3a, an inner pad 4a and an outer pad 5a, a cylinder unit 17, and a pair of slide pins. 9a.
  • Each of these structural members is arranged with a support 2a, an inner pad 4a, a cylinder unit 17, and a pair of slide pins 9a on the inner side in the axial direction with reference to the disc-shaped rotor 6 that rotates together with the wheels.
  • the outer pad 5a is disposed, and the yoke 3a is disposed on the radially outer side. Out of these components, the outer pad 5a corresponds to the disc brake pad of the present invention.
  • the support 2a is made of metal, is disposed on the inner side in the axial direction of the rotor 6, and is fixed to the vehicle body.
  • the support 2a is configured in a substantially U shape when viewed from the front, and is disposed on the radially inner side and extended in the circumferential direction, and radially outward from both circumferential outer sides of the support base 14.
  • a pair of support arm portions 15 extending toward the end are provided.
  • Attachment holes 16 for fixing the support 2a to a suspension device such as a knuckle are formed on both outer sides of the support base 14 in the circumferential direction.
  • the support arm 15 is formed with a fastening hole for fixing the cylinder unit 17 to the support 2a.
  • an engagement recess 62 for supporting a brake tangential force and torque acting on the inner pad 4a during braking is provided on each inner circumferential surface of the support arm portion 15.
  • the cylinder unit 17 includes a substantially cylindrical cylinder 8a and a pair of cylinder arm portions 18 provided so as to protrude outward from the outer peripheral surface of the cylinder 8a in the circumferential direction.
  • a pipe port 19 and a bleeder 20 are provided in the circumferential direction in the radially outer portion of the outer peripheral surface of the cylinder 8a.
  • the cylinder unit 17 is fixed to the support 2a and constitutes a fixing member together with the support 2a. For this reason, in the structure of the first example, the yoke 3a and the cylinder 8a are formed separately from each other.
  • the internal space of the cylinder 8a is opened on both sides in the axial direction, and the first piston 21 and the second piston 22 are fitted so as to be movable in the axial direction. Moreover, the part which exists between the 1st piston 21 and the 2nd piston 22 among the internal space of the cylinder 8a is made into the hydraulic chamber for introducing pressure oil. Further, boots 31 a and 31 b are provided so as to be bridged between both axial end portions of the cylinder 8 a and the respective front end portions of the first piston 21 and the second piston 22. Small-diameter portions 35a and 35b having a smaller outer diameter than the intermediate portion in the axial direction are provided at both axial end portions of the cylinder 8a.
  • seal members 52 a and 52 b are provided between the inner peripheral surface of the cylinder 8 a and the outer peripheral surfaces of the first piston 21 and the second piston 22.
  • the end portion of the boot is fixed to the inner peripheral surface of the axial end portion of the cylinder, although not shown.
  • a female screw hole 23 for fixing the tip of the slide pin 9a and an insertion hole (not shown) are formed adjacent to each other in the radial direction.
  • Such a cylinder unit 17 is fixed in such a manner that the insertion hole of the cylinder arm 18 is inserted in the axial direction in a state where the tip of the cylinder arm 18 is superimposed on the tip of the support arm 15 from the inside in the axial direction.
  • the screw 24 is fixed to the support 2 a by being screwed into the fastening hole of the support arm portion 15.
  • the cylinder 25a constituting the cylinder unit 17 as described above is provided with an anchor 25 for supporting a brake tangential force acting on the outer pad 5a during braking.
  • the anchor 25 is substantially T-shaped when viewed from the radial direction, and is configured separately from the cylinder 8a. And the anchor 25 is being fixed to the radial direction outer end part of the axial direction outer end part of the cylinder 8a using the pair of volt
  • the anchor 25 is provided in a cantilever shape on the cylinder 8a, and is disposed radially outside the rotor 6 and radially inside the yoke 3a. Also, the anchor 25 is (symmetrical shape of FIG.
  • the anchor 25 is provided at a position where the circumferential position of the central axis O 25 coincides with the circumferential position of the central axis of the cylinder 8a. Therefore, the anchor 25 (constant width portion 30 to be described later) is provided at a position overlapping the circumferentially central portion S 47 and the radial lining 47 of the outer pad 5a.
  • the anchor 25 includes a plate-shaped (rod-shaped) anchor main body 27 and a pair of mounting rods 28 arranged in the horizontal direction. Since the anchor body 27 receives a brake tangential force directed in the circumferential direction, the cross-sectional shape with respect to the virtual plane orthogonal to the axial direction has a radial direction in order to sufficiently increase the rigidity in the circumferential direction (increase the secondary moment of section). It is an oval shape whose circumferential dimension is larger than the dimension. For this reason, as will be described later, the cross-sectional shape of the outer circumferential surface in contact with the radial protrusions 51a and 51b provided on the outer pad 5a in the anchor body 27 is a convex arc shape.
  • the anchor body 27 is provided with a tapered portion 29 that decreases in the circumferential direction toward the outer side in the axial direction from the inner end portion (base end portion) to the intermediate portion in the axial direction.
  • the constant width portion 30 is disposed between the radial protrusions 51a and 51b provided on the outer pad 5a that moves in the axial direction together with the yoke 3a. For this reason, the axial dimension of the constant width portion 30 is restricted in consideration of the axial movement amount of the outer pad 5a during braking.
  • an escape recess 32 for mounting the boot 31a to the small diameter portion 35a of the cylinder 8a is provided in a circumferential intermediate portion of the radially inner side surface of the axially inner end portion of the anchor body 27.
  • the relief inner portion 32 is formed on the radially inner side surface of the anchor body 27 by curving the inner end portion in the axial direction of the anchor body 27 so that the radially outer side is convex.
  • the pair of mounting rods 28 are provided so as to protrude outward in the circumferential direction from the axially inner end of the anchor body 27, and are formed with bolt insertion holes penetrating in the axial direction.
  • the bolt 26 inserted through such a bolt insertion hole is screwed into the female screw hole opened in the axially outer end surface of the cylinder 8a, whereby the anchor 25 is screwed and fixed to the cylinder 8a.
  • mounting seats 33 each having a female screw hole are provided on the outside in the axial direction of the piping port 19 and the bleeder 20, and the bolts 26 are screwed to the mounting seat 33.
  • the axial inner surface of the mounting rod 28 is abutted against the axial outer surface of the mounting seat 33, and the axial inner end surface of the anchor body 27 is the outer periphery of the cylinder 8a. It is abutted against a step surface 34 formed on the surface.
  • the inner side surface in the axial direction of the mounting rod 28, the outer side surface in the axial direction of the mounting seat 33, the inner end surface in the axial direction of the anchor body 27, and the step surface 34 are each formed in a flat surface shape.
  • a small-diameter portion 35 a provided at the outer end in the axial direction of the cylinder 8 a is disposed inside the escape recess 32.
  • the radial position of the central axis O 26 of the bolt 26 arranged in the axial direction is the radial dimension of the constant width portion 30 provided at the distal end portion of the anchor body 27. It is regulated so as to fall within a range of a 30.
  • the radial position of the central axis O 26 of the pair of bolts 26 is made to coincide with the radial center of the constant width portion 30 (the radial position of the top of the circumferential outer surface of the convex arc shape). is in a radially intermediate portion of the center axis O 26 and the constant width portion 30 of a pair of bolts 26 are disposed on the same virtual straight line L.
  • the radial position of the point of application of the brake tangential force acting on the constant width portion 30 and the radial position of the bolt 26 supporting the brake tangential force are matched or brought close to each other, and input to the constant width portion 30.
  • the brake tangential force is efficiently supported by the bolt 26, and the moment force hardly acts on the anchor body 27.
  • the yoke 3a is made of metal or nonmetal, and the shape viewed from the axial direction is a bow shape.
  • the yoke 3a is disposed so that the support 2a, the inner pad 4a, the outer pad 5a, and the cylinder unit 17 are each covered from the outside in the radial direction.
  • Such a yoke 3a is disposed on the inner side of the support 2a and the cylinder unit 17 in the axial direction, the outer body 37 disposed on the outer side of the outer pad 5a in the axial direction, and on the outer side of the rotor 6 in the radial direction.
  • a bridge portion 38 that connects the inner body 36 and the outer body 37 in the axial direction is provided.
  • the axially outer surface of the inner circumferential portion of the inner body 36 is formed in a flat surface, and is opposed to the distal end portion of the second piston 22 fitted in the cylinder 8a in the axial direction.
  • slide holes 10a for slidably disposing the slide pins 9a are provided in both outer circumferential portions of the inner body 36 in a state of penetrating in the axial direction.
  • a support hole 39 which is a bottomed hole and a pair of receiving holes (dowel holes) 40 are provided.
  • the support hole 39 is a substantially rectangular recess, and is provided in the circumferential central portion of the inner side surface of the outer body 37 in the axial direction.
  • the pair of receiving holes 40 are cylindrical recesses and are provided on both outer sides in the circumferential direction of the support hole 39.
  • the inner diameter dimension of the receiving hole 40 is slightly larger than the outer diameter dimension of an axial protrusion 50 described later provided in the outer pad 5a.
  • the bridge portion 38 is disposed on the radially outer side of the rotor 6, and a storage recess 41 extending in the axial direction for storing the anchor main body 27 is provided in the circumferential central portion of the radially inner side surface thereof.
  • the storage recess 41 has a substantially rectangular cross section and is slightly larger in the circumferential direction and the radial direction than the cross sectional shape of the anchor main body 27.
  • a pair of radially inner windows 42a and 42b are provided in the circumferential intermediate portion of the bridge portion 38 in the axial direction, and are spaced apart in the circumferential direction.
  • the piping port 19 and the bleeder 20 provided in the cylinder unit 17 are exposed from 42b.
  • an outer window portion 43 penetrating in the radial direction is provided in the circumferential center portion of the bridge portion 38 in the axially outer portion, and the axially outer end portion of the anchor 25 and the outer pad 5a from the outer window portion 43.
  • the radial protrusions 51a and 51b, which will be described later, are exposed.
  • the yoke 3a as described above is supported by the cylinder unit 17 which is a fixed member so as to be movable in the axial direction using a pair of slide pins 9a.
  • the slide pin 9a is inserted into the inner side of the slide hole 10a provided in the inner body 36 from the inner side in the axial direction, and the axial intermediate portion of the slide pin 9a is slidably arranged inside the slide hole 10a. Is done.
  • the distal end portion of the slide pin 9 a is screwed into a female screw hole 23 provided at the distal end portion of the cylinder arm portion 18 constituting the cylinder unit 17.
  • the slide pin 9a is fixed in the horizontal direction with respect to the cylinder unit 17, and the yoke 3a is supported so as to be movable in the axial direction with respect to the slide pin 9a.
  • boots 55 are respectively attached to portions of the slide pin 9a that are exposed from the slide hole 10a to both sides in the axial direction.
  • the inner pad 4 a is disposed on the inner side in the axial direction of the rotor 6, and includes a lining (friction material) 44 and a metal back plate (pressure plate) 45 that supports the inner side surface in the axial direction that is the back surface of the lining 44.
  • a lining forriction material
  • a metal back plate pressure plate
  • Such an inner pad 4a is arranged on the outer side in the radial direction of the support base portion 14 and on the inner side in the circumferential direction of the pair of support arm portions 15, thereby enabling movement in the axial direction with respect to the support 2a, and It is supported in a state where movement in the radial direction and the circumferential direction is limited.
  • a pair of ear portions 46 provided on both outer sides in the circumferential direction of the back plate 45 constituting the inner pad 4a are formed in engagement recesses 62 formed on the inner circumferential surface of the pair of support arm portions 15.
  • the inner pad 4a is supported with respect to the support 2a by being engaged with each other.
  • the tip end portion of the first piston 21 faces the axially inner side surface of the back plate 45 in the axial direction.
  • an anchor 25 anchor body 27
  • the outer pad 5 a is disposed on the outer side in the axial direction of the rotor 6, and includes a lining (friction material) 47 and a metal back plate (pressure plate) 48 that supports the outer side in the axial direction that is the back surface of the lining 47. ing.
  • the outer pad 5a is symmetrical with respect to the circumferential direction.
  • a pad spring 49 made of a leaf spring is caulked and fixed to the central portion in the circumferential direction of the outer surface in the axial direction of the back plate 48.
  • a pair of axial protrusions (dowels) 50 are provided on both outer circumferential portions of the axially outer surface of the back plate 48.
  • Each of the axial protrusions 50 is formed in a substantially cylindrical shape, and is provided so as to protrude outward in the axial direction from the axially outer surface of the back plate 48.
  • the axial protrusion 50 is formed integrally with the back plate 48 by embossing the back plate 48.
  • molding method of the axial direction protrusion 50 is not ask
  • a pair of radial protrusions 51a and 51b protruding outward in the radial direction are provided on the outer peripheral edge.
  • the pair of radial protrusions 51a and 51b are spaced apart from each other in the circumferential direction, and a constant width portion provided at the axial outer end of the anchor 25 between the pair of radial protrusions 51a and 51b. 30 is configured to be arranged (inserted) so as to be capable of relative movement in the axial direction.
  • Each of the radial protrusions 51a and 51b is formed in a substantially rectangular shape, and the circumferential inner surfaces facing each other in the circumferential direction are flat surfaces parallel to each other, and the circumferential outer surfaces are closer to each other toward the radially outer side.
  • the inclined surface is inclined in the direction.
  • a pair of radial projections 51a, the distance H between the circumferential inner surface of 51b is slightly larger than the circumferential dimension B 30 of constant width portion 30 (H> B 30).
  • a gap formed between the axial protrusion 50 and the receiving hole 40 are set to be smaller than the gap formed between the flat and circumferential inner surfaces of the radial protrusions 51a and 51b.
  • a pair of axial protrusions 50 provided on the outer side surface in the axial direction of the outer pad 5 a are formed into a pair of receiving portions formed on the inner side surface in the axial direction of the outer body 37.
  • a pad spring 49 that is loosely concavo-convexly fitted (inserted) into the hole 40 and fixed to the outer side surface of the outer pad 5 a in the axial direction is elastically engaged with the inside of the support hole 39.
  • the pad spring 49 is elastically engaged (snap fit engagement) with the support hole 39, thereby positioning the outer pad 5a in the circumferential direction (exhibiting a centering function) and inward in the axial direction. Dropping is prevented.
  • the constant width portion 30 of the anchor 25 is disposed between the pair of radial protrusions 51a and 51b in a state where the outer pad 5a is attached to the inner side surface in the axial direction of the outer body 37.
  • pressure oil is introduced into the hydraulic chamber in the cylinder 8a. Accordingly, the first piston 21 and the second piston 22 are moved in directions away from each other with respect to the axial direction. Then, the inner pad 4 a is pressed against the axial inner surface of the rotor 6 from the upper side to the lower side in FIG. 5 by the first piston 21. At the same time, the inner body 36 is pressed upward from the lower side in FIG. 5 by the second piston 22, and the yoke 3 a is moved to the upper side in FIG. 5 with respect to the support 2 a and the cylinder unit 17 that are the fixing members.
  • the anchor 25 directly supports the brake tangential force F1 acting during forward braking based on the contact with the radial protrusion 51a on the other circumferential side (XB) of the outer pad 5a.
  • the circumferential direction position of the contact portion P1 of the circumferential outer surface of the circumferential inner surface and a constant width portion 30 of the radial protrusions 51a are circumferentially even times-in side from the direction central portion S 47 of the lining 47 (circumferential (The other side in the direction (XB)) and within the circumferential range R of the lining 47.
  • the flat inner circumferential surface of the radial protrusion 51a and the circumferential outer surface of the constant-arc portion of the constant-width portion 30 are in contact with each other. Can be stabilized. Further, since the abutting portion P1 is located radially outside the line of action of the brake tangential force F1, during forward braking, a moment that causes the outer pad 5a to rotate the outer pad 5a counterclockwise. Act. Such a moment can be supported by the anchor 25 when the radially inner side surface of the constant width portion 30 and the outer peripheral edge portion of the back plate 48 come into contact with each other, and the axial protrusion 50 and the receiving hole 40 It is also possible to transmit to the yoke 3a through the contact portion.
  • the moment acting on the outer pad 5 a causes the first support between the circumferential inner surface of the radial protrusion 51 a and the circumferential outer surface of the constant width portion 30.
  • the size (area) of the triangle drawn by connecting the three support portions X1, X2, and X3 correlates with the ease of inclination of the outer pad 5a in the axial direction.
  • the part or the inner peripheral side part is less likely to tilt in the axial direction, and uneven wear is less likely to occur in the part, and the more the triangle spreads in the circumferential direction, the more difficult the inward side part or the outlet side part tilts in the axial direction. Uneven wear is less likely to occur.
  • the first support portion X1 can be disposed radially outward from the lining 47. It is possible to effectively prevent the side portion from being inclined in the axial direction (the rotor 6 side). Therefore, it is possible to effectively prevent uneven wear from occurring on the outer peripheral side portion of the lining 47.
  • Circumferential position of the contact portion P2 of the circumferential outer surface of the circumferential inner surface and a constant width portion 30 of the radial projection 51b is also circumferentially central portion also times-in side than the S 47 of the lining 47 (the circumferential direction on one side ( XA)) and within the circumferential range R of the lining 47.
  • the flat inner circumferential surface of the radial projection 51b and the convex arc-shaped circumferential outer surface of the constant width portion 30 are in contact with each other even during reverse braking.
  • the contact position can be stabilized.
  • the moment based on the brake tangential force F2 acting at the time of reverse braking is also supported by the anchor 25 in the same way as at the time of forward braking, or the yoke via the contact portion between the axial protrusion 50 and the receiving hole 40. 3a.
  • the contact portion between the circumferential inner surface of the protrusion 63 and the support base 14 is located radially inward from the line of action of the brake tangential force F3.
  • a moment is applied to rotate the inner pad 4a clockwise.
  • the moment acting on the inner pad 4a is caused by the first support portion Y1 of the protrusion 63 and the support base 14, the radially inner side surface of the ear 46 on one side in the circumferential direction, and the engagement recess 62.
  • the second support portion Y2 and the third support portion Y3 can be arranged at both ends in the circumferential direction of the back plate 45. it can. For this reason, it is possible to effectively prevent the occurrence of uneven wear at the entrance side portion and the exit side portion of the lining 44.
  • the hydraulic oil is discharged from the hydraulic chamber of the cylinder 8a.
  • the first piston 21 is pulled back (rolled back) to the internal space by the elasticity of the seal member 52a disposed around the first piston 21.
  • the second piston 22 is also pulled back to the internal space by the elasticity of the seal member 52b disposed around the second piston 22.
  • a tilt is generated in the yoke 3a that supports the outer pad 5a regardless of the brake tangential forces F1 and F2 that act on the outer pad 5a during braking. This can be suppressed. That is, in the first example, during forward braking and backward braking, the radial protrusions 51a and 51b provided on the outer peripheral edge of the outer pad 5a abut on the anchor 25 provided in a cantilever shape on the cylinder 8a. The brake tangential forces F1 and F2 acting on the outer pad 5a are directly supported by the anchor 25.
  • the manufacturing cost can be reduced and the number of parts can be reduced.
  • the rigidity of the axial protrusion 50 can be easily ensured.
  • the axial protrusion 50 has a cylindrical shape, and the receiving hole 40 has a cylindrical recess. Therefore, by using the axial projection 50 whose outer diameter varies on the plus side within the dimensional tolerance (or using the one whose inner diameter of the receiving hole 40 varies on the minus side within the dimensional tolerance).
  • the clearance gap (clearance) between the axial direction protrusion part 50 and the receiving hole 40 can be reduced, and abnormal noises, such as a rattle sound and a cronk sound, can also be reduced.
  • the cross-sectional shape of the anchor body 27 is an oval shape whose circumferential dimension is larger than the radial dimension, the rigidity in the circumferential direction, which is important for supporting the brake tangential force, is secured while maintaining the radial direction. It is possible to prevent the size from becoming excessive. For this reason, it can prevent that the outer diameter dimension of the yoke 3a arrange
  • the contact portions P1, P2 between the anchor 25 and the outer pad 5a are positioned within the circumferential range R of the lining 47. For this reason, since the moment arm can be shortened with respect to the moment (convolution force) around the central axis in the radial direction generated in the outer pad 5a based on the brake tangential forces F1 and F2, the pressing force of the lining 47 against the rotor 6 can be kept low. . Therefore, uneven wear of the lining 47 can be suppressed. In addition, it is possible to suppress the generation of abnormal noise such as squeaking during braking.
  • the contact portions P1 and P2 are positioned within the circumferential range R of the lining 47, the protruding amount of the radial projections 51a and 51b provided on the outer peripheral edge portion of the back plate 48 can be suppressed. Therefore, an increase in the weight of the outer pad 5a can be suppressed, and an increase in size of the floating disc brake 1a can be suppressed. Further, with respect to the cylinder unit 17 which is a fixing member, it is not necessary to newly provide a portion protruding in the circumferential direction in order to fix the anchor 25, so that an increase in weight can also be suppressed from this surface.
  • the relief recess 32 is provided on the radially inner side surface of the axially inner end of the anchor body 27, the boot 31a attached to the axially outer end of the cylinder 8a and the anchor body 27 interfere with each other. Can be prevented. For this reason, it is not necessary to arrange the anchor 25 on the radially outer side more than necessary.
  • the anchor 25 is configured separately from the cylinder 8a, the anchor 25 and the cylinder 8a can be manufactured from different materials, or a manufacturing method such as casting or forging can be made different. For this reason, it is advantageous in increasing the dimensional accuracy and shape accuracy of the anchor 25 and in reducing the weight and rigidity.
  • the anchor 25 can also suppress the outer pad 5a from vibrating in the vertical direction when the vehicle is running.
  • the rigidity in the circumferential direction of the radial protrusions 51a and 51b can be improved. For this reason, since the elastic deformation amount in the circumferential direction of the radial protrusions 51a and 51b can be reduced, it is possible to more effectively suppress the brake tangential force acting on the outer pad 5a from being transmitted to the slide pin 9a (see FIG. 5). .
  • the elastic deformation amount in the circumferential direction of the radial protrusions 51a and 51b can be reduced, it is possible to more effectively suppress the brake tangential force acting on the outer pad 5a from being transmitted to the slide pin 9a (see FIG. 5). .
  • the 1st example of embodiment mentioned above it is the same as the 1st example of embodiment mentioned above.
  • the cross-sectional shape of the radial protrusions 51c and 51d provided on the outer pad 5a and the cross-sectional shape of the constant width portion 30a provided on the axially outer end of the anchor 25 are the first example of the embodiment. It is the opposite of the structure. That is, the cross-sectional shape of the circumferential inner surfaces of the radial protrusions 51c and 51d is a convex arc shape, and the cross-sectional shape of the outer circumferential surface of the constant width portion 30a is a flat surface.
  • the contact state between the radial protrusions 51c and 51d and the constant width portion 30a can be a line contact.
  • the contact position with the width portion 30a can be stabilized.
  • FIGS. 1b and 3b A fourth example of the embodiment of the present invention will be described with reference to FIGS.
  • a structure in which a cylinder 8b is integrally provided on a yoke 3b is employed, as in the conventional structure described above. Only one piston 57 that is pushed outward in the axial direction is fitted into the cylinder 8b.
  • the cylinder 8b is a part of the yoke 3b and does not constitute a fixing member.
  • the structure for supporting the outer pad 5b with respect to the yoke 3b is basically the same as the structure of the first example of the embodiment.
  • the yoke 3b of the fourth example integrally has a cylinder 8b at the center in the circumferential direction of the inner body 36a, and uses a pair of slide pins 9a in the axial direction with respect to the support 2b that is a fixed member. Is supported to allow movement.
  • the slide pin 9a is inserted from the inside in the axial direction inside the slide hole provided on both sides in the circumferential direction of the inner body 36a, and the axially intermediate portion of the slide pin 9a is slidable inside the slide hole. Placed in.
  • tip part of the slide pin 9a is screwed by the fastening hole 58 provided in the front-end
  • the slide pin 9a is fixed in the horizontal direction with respect to the support 2b, and the yoke 3b is supported so as to be movable in the axial direction with respect to the slide pin 9a.
  • a substantially U-shaped sheet metal support is used as the support 2b, which is a metal plate having sufficient strength and rigidity, such as a steel plate, subjected to pressing such as punching or bending. Yes.
  • an anchor 25a for supporting a brake tangential force acting on the outer pad 5b during braking is provided on the support 2b as described above.
  • the anchor 25a is made by pressing a metal plate having sufficient strength and rigidity, such as a steel plate, such as punching or bending, and is configured separately from the support 2b.
  • Such an anchor 25a is fixed to the distal end portion of the support arm portion 15a using a slide pin 9a.
  • the anchor 25a is provided in a cantilever shape on the support 2b, and is disposed radially outside the rotor 6 (see FIG. 5) and radially inside the yoke 3b.
  • the anchor 25a is a long plate-shaped anchor body 27a provided so as to be bridged in the circumferential direction between the distal ends of the pair of support arm portions 15a, and radially inward from both circumferential sides of the anchor body 27a. And a pair of attachment portions 59 provided so as to be bent at right angles to each other.
  • a pair of anchor protrusions 60a and 60b are provided in the circumferential direction intermediate portion of the outer end portion (tip portion) in the axial direction of the anchor body 27a so as to be separated in the circumferential direction.
  • the cross-sectional shape of the circumferential inner surface of the pair of anchor protrusions 60a and 60b is a flat surface parallel to each other.
  • the attachment portion 59 is formed with an insertion hole 61 for inserting the slide pin 9a in the axial direction.
  • one radial protrusion 51e protruding outward in the radial direction is provided at the circumferential center of the outer peripheral edge of the back plate 48a constituting the outer pad 5b.
  • the radial protrusion 51e has a substantially rectangular cross section and has a circumferential dimension that can be disposed between the pair of anchor protrusions 60a and 60b.
  • the circumferential outer surface of the radial protrusion 51e and the anchor protrusion 60a the circumferential outer surface of the radial protrusion 51e and the anchor protrusion 60a.
  • the size of the gap formed between the circumferential inner surface of 60b is formed between the axial protrusion 50 provided in the outer pad 5b and the receiving hole 40 (see FIG. 5) provided in the yoke 3b. It is set smaller than the gap.
  • a storage recess 41a capable of storing the anchor main body 27a is formed on the radially inner side surface of the bridge portion 38a constituting the yoke 3b.
  • the outer circumferential surface of the radial projection 51e abuts on the inner circumferential surface of the anchor projection 60a provided on one circumferential side during forward braking. For this reason, the anchor 25a directly supports the brake tangential force F1 that acts during forward braking based on the contact with the radial protrusion 51e of the outer pad 5b.
  • the outer circumferential surface of the radial projection 51e contacts the inner circumferential surface of the anchor projection 60b provided on the other circumferential side.
  • the anchor 25a directly supports the brake tangential force F2 that acts during reverse braking based on the contact with the radial protrusion 51e of the outer pad 5b.
  • the brake tangential forces F1 and F2 acting during forward braking and backward braking can be supported by the anchor 25a provided on the yoke 3b. For this reason, it can suppress that inclination (tilt) generate
  • the anchor 25a is fixed so as to be bridged in the circumferential direction on the pair of support arm portions 15a constituting the support 2b. Therefore, even when a sheet metal support is used as the support 2b. Sufficient strength can be secured. Moreover, since the anchor 25a is fixed to the support 2b using the slide pin 9a, the number of parts can be reduced and the weight can be reduced.
  • the moment acting on the outer pad 5b during forward braking is such that the first bearing portion X1 between the circumferential outer surface of the radial projection 51e and the circumferential inner surface of the anchor projection 60a, The second support portion X2 between the radial outer end of the axial protrusion 50 on one side (the delivery side, right side in FIG.
  • the three bearing portions X1, X2, and X3 of the third bearing portion X3 of the radial inner end portion of the axial protrusion 50 on the entry side (left side in FIG. 23) and the radial inner end portion of the receiving hole 40 are shown. It is supported by. Also in the case of the fourth example, out of the three support portions X1, X2, and X3 for supporting the moment, the first support portion X1 can be disposed radially outside the lining 47, so that the lining The uneven wear of the outer peripheral side portion of 47 can be effectively prevented.
  • the contact portion between the circumferential inner surface of the protrusion 63a and the support base 14 is located radially inward from the line of action of the brake tangential force F3.
  • a moment is applied to rotate the inner pad 4a clockwise.
  • the moment acting on the inner pad 4a is caused by the first support portion Y1 of the protrusion 63a and the support base 14, the radially inner side surface of the ear portion 46 on one side in the circumferential direction, and the one side surface in the circumferential direction.
  • Three support portions Y1 including a second support portion Y2 with the step surface 64 provided on the support arm portion 15a, and a support portion Y3 with the outer peripheral edge portion of the back plate 45 and the radially inner side surface of the anchor body 27a. , Y2, Y3.
  • the third support portion Y3 can be disposed radially outside the lining 44. It is possible to effectively prevent uneven wear from occurring in the side portion.
  • the first support portion Y1 is disposed at the radially inner end of the back plate 45, it is possible to prevent uneven wear from occurring on the inner peripheral side portion of the lining 44.
  • first support portion Y1 and the second support portion Y2 are disposed at the other end portion of the back plate 45 in the circumferential direction and at one end portion in the circumferential direction, and the first support portion Y1 and the second support portion are disposed. Since a large distance in the circumferential direction with the portion Y2 can be secured, it is possible to prevent uneven wear from occurring at the turn-in side portion and the turn-out side portion of the lining 44. Further, in the fourth example, by changing the radial position of the second support portion Y2, the ease of uneven wear of the outer peripheral side portion and the inner peripheral side portion of the circumferential one side portion of the lining 44 is adjusted (tuning) ). About another structure and effect, it is the same as the 1st example of embodiment mentioned above.
  • the present invention can be implemented by appropriately combining the structures of the examples of the embodiment as long as no contradiction arises.
  • a lining (47) and a back plate (48, 48a) supporting the outer side surface in the axial direction of the lining (47) are provided, and are arranged on the inner side in the axial direction of the rotor (6) and fixed to the vehicle body.
  • the fixed member (support 2a and cylinder unit 17) is attached to a yoke (3a) that is supported through a slide pin (9a) so as to be movable in the axial direction, and is axially outside (ZO) of the rotor (6).
  • a brake tangential force acting during braking is applied to the outer peripheral edge of the back plate (48, 48a) based on contact with the anchor (25, 25a) provided on the fixing member (support 2a and cylinder unit 17).
  • At least one radial protrusion (51a to 51e) to be supported is provided,
  • irregularities are formed on the axially inner side surface of the outer body (37) disposed on the axially outer side (ZO) of the rotor (6) of the yoke (3a).
  • a fitting axial projection (50) is provided, Disc brake pads (outer pads 5a, 5b).
  • the radial protrusions (51a, 51e) are disk brake pads (5a, 5b) that abut against the anchors (25, 25a) at least during forward braking.
  • the disc brake pad according to any one of [1] to [2] above, The radial protrusions (51a to 51d) are a disc brake pad (outer pad 5a) provided in a pair spaced apart in the circumferential direction.
  • the disc brake pad of the present invention it is possible to prevent the yoke from being inclined regardless of the brake tangential force acting during braking. As a result, the outer pad does not easily hit the rotor, and the outer pad is less likely to be unevenly worn, and abnormal noise (noise) such as squeal during braking is less likely to occur.

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

Abstract

Axially protruding parts (50), which are provided on the axially outside surface of a back plate (48) forming an outer pad (5a), are supported in an engaging recess/protrusion state on the axially inside surface of an outer body of a yoke supported so as to be capable of moving in the axial direction relative to a support (2a). A pair of radial projections (51a, 51b) are provided at an outer peripheral edge portion of the back plate (48), and an axial outer end portion of an anchor (25) provided in a cantilevered state on a cylinder (8a) is arranged between the pair of radial projections (51a, 51b). During braking the radial projections (51a, 51b) make contact with the anchor (25), thereby supporting brake tangential force.

Description

ディスクブレーキ用パッドDisc brake pad
　本発明は、車両の制動を行うためのディスクブレーキに組み込んで使用する、ディスクブレーキ用パッドに関する。 The present invention relates to a disc brake pad used by being incorporated in a disc brake for braking a vehicle.
　図２４は、日本国特開２００２－３７２０８２号公報に記載された、従来構造のフローティング型ディスクブレーキを示している。フローティング型ディスクブレーキ１は、サポート２と、ヨーク（キャリパ）３と、インナパッド４及びアウタパッド５を備えている。 FIG. 24 shows a floating type disc brake having a conventional structure described in Japanese Patent Laid-Open No. 2002-372082. The floating disc brake 1 includes a support 2, a yoke (caliper) 3, an inner pad 4 and an outer pad 5.
　サポート２は、車輪とともに回転するロータ６の軸方向内側に隣接した状態で、車体を構成するナックルなどの懸架装置に固定される。 The support 2 is fixed to a suspension device such as a knuckle constituting the vehicle body in a state adjacent to the inner side in the axial direction of the rotor 6 that rotates together with the wheel.
　本明細書及び請求の範囲全体で、「軸方向（Ｚ）」、「径方向（Ｙ）」及び「周方向（Ｘ）」とは、特に断らない限り、ロータの軸方向、径方向及び周方向をいう。また、フローティング型ディスクブレーキを構成する各部材に関して、軸方向内側（ＺＩ）とは、車両の幅方向中央側をいい、軸方向外側（ＺＯ）とは、車両の幅方向外側をいう。また、径方向内側（ＹＩ）とは、ロータの径方向内側をいい、径方向外側（ＹＯ）とは、ロータの径方向外側をいう。また、周方向内側（ＸＩ）とは、組立状態でのフローティング型ディスクブレーキの周方向中央側をいい、周方向外側（ＸＯ）とは、組立状態でのフローティング型ディスクブレーキの周方向両側をいう。 Throughout the specification and claims, the terms “axial direction (Z)”, “radial direction (Y)” and “circumferential direction (X)” refer to the axial direction, radial direction and circumferential direction of the rotor unless otherwise specified. The direction. Further, regarding each member constituting the floating type disc brake, the inner side in the axial direction (ZI) means the center side in the width direction of the vehicle, and the outer side in the axial direction (ZO) means the outer side in the width direction of the vehicle. Further, the radially inner side (YI) refers to the radially inner side of the rotor, and the radially outer side (YO) refers to the radially outer side of the rotor. Further, the circumferential inner side (XI) refers to the center side in the circumferential direction of the floating disc brake in the assembled state, and the circumferential outer side (XO) refers to both sides in the circumferential direction of the floating disc brake in the assembled state. .
　ヨーク３は、軸方向外側部に二股状の爪部７を有し、軸方向内側部にシリンダ８を有している。ヨーク３は、サポート２に対し軸方向に関する移動を可能に支持されている。このために、図示の例では、ヨーク３にそれぞれの基端部を支持固定した１対のスライドピン９が、サポート２に設けた１対のスライド孔１０の内側に摺動可能に挿入されている。 The yoke 3 has a bifurcated claw 7 on the outer side in the axial direction and a cylinder 8 on the inner side in the axial direction. The yoke 3 is supported so as to be movable in the axial direction with respect to the support 2. For this purpose, in the illustrated example, a pair of slide pins 9 each having a base end supported and fixed to the yoke 3 are slidably inserted into a pair of slide holes 10 provided in the support 2. Yes.
　インナパッド４は、ロータ６の軸方向内側に配置されており、サポート２に対して軸方向に関する移動を可能に支持されている。これに対し、アウタパッド５は、ロータ６の軸方向外側に配置されており、ヨーク３を構成する爪部７の軸方向内側面に支持されている。このために、アウタパッド５の軸方向外側面（裏面）に固定したパッドスプリング１１が、爪部７に係合させられている。また、アウタパッド５の軸方向外側面に形成した１対の軸方向突部（ダボ）１２が、爪部７の軸方向内側面に形成した１対の受孔（ダボ孔）１３にそれぞれ凹凸嵌合させられている。 The inner pad 4 is disposed on the inner side in the axial direction of the rotor 6 and is supported so as to be movable in the axial direction with respect to the support 2. On the other hand, the outer pad 5 is disposed on the outer side in the axial direction of the rotor 6 and is supported on the inner side surface in the axial direction of the claw portion 7 constituting the yoke 3. For this purpose, a pad spring 11 fixed to the outer side surface (back surface) in the axial direction of the outer pad 5 is engaged with the claw portion 7. In addition, a pair of axial protrusions (dowels) 12 formed on the outer side surface of the outer pad 5 in the axial direction are fitted into a pair of receiving holes (dowel holes) 13 formed on the inner side surface of the claw 7 in the axial direction. Have been combined.
　制動を行う際には、シリンダ８内に圧油を送り込み、図示しないピストンによりインナパッド４が、ロータ６の軸方向内側面に、図２４の上方から下方へと押し付けられる。すると、この押し付け力の反作用としてヨーク３が、スライドピン９とスライド孔１０との摺動に基づいて図２４の上方に移動し、爪部７によりアウタパッド５が、ロータ６の軸方向外側面に押し付けられる。この結果、ロータ６が軸方向両側から強く挟持されて制動が行われる。 When braking, pressure oil is fed into the cylinder 8 and the inner pad 4 is pressed against the axial inner surface of the rotor 6 from the upper side to the lower side in FIG. Then, as a reaction of this pressing force, the yoke 3 moves upward in FIG. 24 based on the sliding between the slide pin 9 and the slide hole 10, and the outer pad 5 is moved to the axially outer side surface of the rotor 6 by the claw portion 7. Pressed. As a result, the rotor 6 is strongly clamped from both sides in the axial direction and braking is performed.
日本国特開２００２－３７２０８２号公報Japanese Laid-Open Patent Publication No. 2002-372082
　上述したような従来構造のフローティング型ディスクブレーキ１では、アウタパッド５が、サポート２に対して支持されずに、ヨーク３の爪部７に対して直接支持されているため、サポート２の小型化及び軽量化を図る上で有利になる。 In the floating type disc brake 1 having the conventional structure as described above, the outer pad 5 is not supported by the support 2 but directly supported by the claw portion 7 of the yoke 3. This is advantageous in reducing weight.
　ところが、従来構造のフローティング型ディスクブレーキ１では、アウタパッド５をヨーク３に支持する構造を採用したことに起因して、次のような改善すべき課題がある。
　すなわち、制動時には、インナパッド４及びアウタパッド５に、周方向（回出側）に向いたブレーキ接線力がそれぞれ作用する。インナパッド４に作用するブレーキ接線力は、懸架装置に固定されたサポート２により直接支承されるが、アウタパッド５に作用するブレーキ接線力は、ヨーク３を介して、スライドピン９とスライド孔１０との当接部にて支承される。スライドピン９とスライド孔１０との当接部の軸方向位置は、アウタパッド５に作用するブレーキ接線力の作用点の軸方向位置から軸方向内側に大きく離れている。このため、ヨーク３には、アウタパッド５に作用するブレーキ接線力に起因して、図２４に矢印αで示す方向の傾き（チルト）が発生しやすくなる。この結果、アウタパッド５がロータ６に片当たりし、アウタパッド５に偏摩耗が生じやすくなるとともに、制動時に鳴きなどの異音（ノイズ）が発生しやすくなる。 However, the conventional floating disc brake 1 has the following problems to be improved due to the adoption of the structure in which the outer pad 5 is supported by the yoke 3.
That is, at the time of braking, a brake tangential force that is directed in the circumferential direction (outward side) acts on the inner pad 4 and the outer pad 5. The brake tangential force acting on the inner pad 4 is directly supported by the support 2 fixed to the suspension device, but the brake tangential force acting on the outer pad 5 is connected to the slide pin 9 and the slide hole 10 via the yoke 3. It is supported at the contact part. The axial position of the contact portion between the slide pin 9 and the slide hole 10 is greatly separated inward in the axial direction from the axial position of the point of application of the brake tangential force acting on the outer pad 5. For this reason, the yoke 3 is likely to be inclined in the direction indicated by the arrow α in FIG. 24 due to the brake tangential force acting on the outer pad 5. As a result, the outer pad 5 comes into contact with the rotor 6 and the outer pad 5 is likely to be unevenly worn, and noise (noise) such as squealing is easily generated during braking.
　本発明は、上述のような事情に鑑みてなされたものであり、その目的は、制動時に作用するブレーキ接線力にかかわらず、ヨークに傾きが発生することを抑制できるディスクブレーキ用パッドの構造を実現することにある。 The present invention has been made in view of the circumstances as described above, and an object of the present invention is to provide a structure of a disc brake pad that can suppress the occurrence of inclination in the yoke regardless of the brake tangential force acting during braking. It is to be realized.
　本発明のディスクブレーキ用パッドは、ライニングと、該ライニングの軸方向外側面を支持した裏板とを備えており、ロータの軸方向内側に配置され車体に固定される固定部材に対しスライドピンを介して軸方向の移動を可能に支持されるヨークに取り付けられ、前記ロータの軸方向外側に配置されるものである。つまり、フローティング型ディスクブレーキに組み込まれるアウタパッドである。
　特に本発明では、前記裏板の外周縁部に、少なくとも１つ以上の径方向突起が設けられている。該径方向突起は、前記固定部材に例えば片持ち梁状に設けられたアンカーとの当接に基づいて、制動時に作用するブレーキ接線力を支承するためのものである。
　また、前記裏板の軸方向外側面には、前記ヨークのうちで前記ロータの軸方向外側に配置されるアウタボディの軸方向内側面に凹凸嵌合する、１乃至複数（例えば２つ）の軸方向突部が設けられている。
　なお、前記径方向突起と前記アンカーが当接するとは、直接当接する場合だけでなく、例えば摺動性を確保するなどの目的で両部材同士の間に配置したステンレス鋼板などの他の部材を介して当接する場合も含む。
　前記アンカーは、前記固定部材（例えばシリンダやサポートなど）とは別体として、ボルトなどの締結部材を用いて前記固定部材に対し固定されていても良いし、前記固定部材に一体に設けられていても良い。 The disc brake pad according to the present invention includes a lining and a back plate that supports an outer surface in the axial direction of the lining, and a slide pin is disposed on a fixing member that is disposed on the inner side in the axial direction of the rotor and is fixed to the vehicle body. It is attached to the yoke supported so that the movement of an axial direction is possible via, and is arrange | positioned at the axial direction outer side of the said rotor. That is, it is an outer pad incorporated in a floating type disc brake.
Particularly, in the present invention, at least one or more radial protrusions are provided on the outer peripheral edge of the back plate. The radial projection is for supporting a brake tangential force acting during braking based on contact with an anchor provided in a cantilever shape, for example, on the fixing member.
Further, one or a plurality of (for example, two) shafts that are unevenly fitted to the axially inner side surface of the outer body disposed on the axially outer side of the rotor in the yoke on the axially outer surface of the back plate Directional protrusions are provided.
The radial protrusion and the anchor are not only in direct contact with each other, but for example, other members such as a stainless steel plate disposed between the two members for the purpose of ensuring slidability. It also includes the case where the contact is made.
The anchor may be fixed to the fixing member using a fastening member such as a bolt as a separate body from the fixing member (for example, a cylinder or a support), or provided integrally with the fixing member. May be.
　本発明では、前記径方向突起が、前記アンカーとの当接部の周方向位置が、前記ライニングの周方向の範囲内に位置するように設けられている。 In the present invention, the radial projection is provided so that the circumferential position of the contact portion with the anchor is within the circumferential range of the lining.
　本発明では、前記径方向突起が、少なくとも前進制動時に、前記アンカーに当接するものとされている。
　本発明では、前記径方向突起が、前進制動時及び後進制動時に、前記アンカーに当接するものとされている。
　あるいは、前記径方向突起が、前進制動時にのみ、前記アンカーに当接するものとされている。この場合、後進制動時に作用するブレーキ接線力は、前記アウタパッドに設けた前記軸方向突部から前記ヨークに伝達し、前記スライドピンにより支承することができる。 In the present invention, the radial projection is in contact with the anchor at least during forward braking.
In the present invention, the radial protrusion is in contact with the anchor during forward braking and reverse braking.
Alternatively, the radial protrusion is in contact with the anchor only during forward braking. In this case, a brake tangential force acting during reverse braking can be transmitted to the yoke from the axial protrusion provided on the outer pad and supported by the slide pin.
　本発明では、前記径方向突起が、周方向に離隔して１対設けられている。
　この場合には、前記１対の径方向突起の径方向外端部同士が、周方向に連結されている。
　あるいは、前記１対の径方向突起の径方向外端部が、それぞれ自由端とされている。 In the present invention, a pair of the radial protrusions are provided apart from each other in the circumferential direction.
In this case, the radially outer ends of the pair of radial protrusions are connected in the circumferential direction.
Alternatively, the radially outer ends of the pair of radial protrusions are free ends.
　本発明では、前記径方向突起が、前記裏板の外周縁部の周方向中央部に、１つだけ設けられている。
　前記径方向突起が、前記裏板の外周縁部に１つだけ設けられる場合には、前記径方向突起が、前記裏板の外周縁部のうちで周方向中央部から周方向（例えば回入側又は回出側）に外れた位置に設けられている。 In the present invention, only one of the radial protrusions is provided in the circumferential center of the outer peripheral edge of the back plate.
When only one radial protrusion is provided on the outer peripheral edge portion of the back plate, the radial protrusion is a circumferential direction (for example, a turn-in) of the outer peripheral edge portion of the back plate. Side or outlet side).
　本発明では、ディスクブレーキ用パッド全体が、周方向に関して対称形状とされている。
　あるいは、ディスクブレーキ用パッド全体が、周方向に関して非対称形状とされている。 In the present invention, the entire disc brake pad is symmetrical with respect to the circumferential direction.
Alternatively, the entire disc brake pad has an asymmetric shape with respect to the circumferential direction.
　本発明では、前記軸方向突部が、円柱形状とされている。 In the present invention, the axial projecting portion has a cylindrical shape.
　本発明では、前記軸方向突部が、前記裏板と一体に設けられている。
　この場合には、前記軸方向突部が、前記裏板に対して例えばエンボス加工（押出加工）などのプレス加工を施すことにより形成されている。
　あるいは、前記軸方向突部が、前記裏板とは別体として、該裏板に対し固定されている。 In the present invention, the axial protrusion is provided integrally with the back plate.
In this case, the axial protrusion is formed by subjecting the back plate to press working such as embossing (extrusion).
Alternatively, the axial protrusion is fixed to the back plate as a separate body from the back plate.
　本発明では、前記径方向突起のうちで、制動時に前記アンカーに当接する部分における断面形状が、凸円弧形状とされている。
　あるいは、本発明では、前記径方向突起のうちで、制動時に前記アンカーに当接する部分における断面形状が、平坦面状とされている。 In the present invention, a cross-sectional shape of a portion of the radial projection that contacts the anchor during braking is a convex arc shape.
Or in this invention, the cross-sectional shape in the part which contact | abuts to the said anchor at the time of braking among the said radial direction protrusions is made into flat surface shape.
　上述のような構成を有する本発明のディスクブレーキ用パッドによれば、制動時に作用するブレーキ接線力にかかわらず、ヨークに傾きが発生することを抑制できる。 According to the disc brake pad of the present invention having the above-described configuration, it is possible to prevent the yoke from being inclined regardless of the brake tangential force acting during braking.
図１は、本発明の実施の形態の第１例にかかるフローティング型ディスクブレーキを軸方向外側から見た正面図である。FIG. 1 is a front view of a floating disc brake according to a first example of an embodiment of the present invention as viewed from the outside in the axial direction. 図２は、本発明の実施の形態の第１例にかかるフローティング型ディスクブレーキを示す斜視図である。FIG. 2 is a perspective view showing the floating disc brake according to the first example of the embodiment of the present invention. 図３は、本発明の実施の形態の第１例にかかるフローティング型ディスクブレーキを周方向から見た側面図である。FIG. 3 is a side view of the floating disc brake according to the first example of the embodiment of the present invention as seen from the circumferential direction. 図４は、図１のＡ－Ａ断面図である。4 is a cross-sectional view taken along the line AA in FIG. 図５は、図１のＢ－Ｂ断面図である。5 is a cross-sectional view taken along the line BB in FIG. 図６は、図３のＣ－Ｃ断面図である。6 is a cross-sectional view taken along the line CC of FIG. 図７は、図３のＤ－Ｄ断面図である。7 is a cross-sectional view taken along the line DD of FIG. 図８は、図１からヨークを省略して示す図である。FIG. 8 is a view showing the yoke omitted from FIG. 図９は、図２からヨークを省略して示す図である。FIG. 9 is a view showing the yoke omitted from FIG. 図１０は、図３からヨークを省略して示す図である。FIG. 10 is a view in which the yoke is omitted from FIG. 図１１は、本発明の実施の形態の第１例にかかるフローティング型ディスクブレーキからアンカーを取り出し、径方向外側から見た平面図である。FIG. 11 is a plan view of the anchor taken out of the floating disc brake according to the first example of the embodiment of the present invention and viewed from the outside in the radial direction. 図１２は、本発明の実施の形態の第１例にかかるフローティング型ディスクブレーキからアウタパッドを取り出し、軸方向内側から見た正面図である。FIG. 12 is a front view of the outer pad taken out from the floating disc brake according to the first example of the embodiment of the present invention and viewed from the inside in the axial direction. 図１３は、本発明の実施の形態の第１例にかかるフローティング型ディスクブレーキからアウタパッドを取り出し、軸方向外側から見た背面図である。FIG. 13 is a rear view of the outer pad taken out from the floating disc brake according to the first example of the embodiment of the present invention and viewed from the outside in the axial direction. 図１４は、本発明の実施の形態の第１例にかかるフローティング型ディスクブレーキからアウタパッドを取り出して示す斜視図である。FIG. 14 is a perspective view showing the outer pad taken out from the floating disc brake according to the first example of the embodiment of the present invention. 図１５は、アウタパッドの径方向突起とアンカーの定幅部との関係を説明するために示す、図７の上部に相当する部分の拡大図である。FIG. 15 is an enlarged view of a portion corresponding to the upper part of FIG. 7 for explaining the relationship between the radial protrusion of the outer pad and the constant width portion of the anchor. 図１６は、本発明の実施の形態の第１例に関して制動時の状態を説明するために示す図であり、図１６の（Ａ）は前進制動時の状態を示しており、図１６の（Ｂ）は後進制動時の状態を示している。FIG. 16 is a view for explaining the state at the time of braking in the first example of the embodiment of the present invention. FIG. 16A shows the state at the time of forward braking, and FIG. B) shows the state during reverse braking. 図１７は、本発明の実施の形態の第２例を示す、図１５に相当する図である。FIG. 17 is a diagram corresponding to FIG. 15 and showing a second example of the embodiment of the present invention. 図１８は、本発明の実施の形態の第３例を示す、図１５に相当する図である。FIG. 18 is a diagram corresponding to FIG. 15 and showing a third example of the embodiment of the present invention. 図１９は、本発明の実施の形態の第４例にかかるフローティング型ディスクブレーキを示す斜視図である。FIG. 19 is a perspective view showing a floating type disc brake according to a fourth example of the embodiment of the present invention. 図２０は、図１９からヨークを省略して示す図である。FIG. 20 is a view showing the yoke omitted from FIG. 図２１は、図２０からアウタパッドを省略して示す、分解斜視図である。FIG. 21 is an exploded perspective view in which the outer pad is omitted from FIG. 図２２は、本発明の実施の形態の第４例にかかるフローティング型ディスクブレーキに関する、図６に相当する図である。FIG. 22 is a view corresponding to FIG. 6 regarding a floating type disc brake according to a fourth example of the embodiment of the present invention. 図２３は、本発明の実施の形態の第４例にかかるフローティング型ディスクブレーキに関する、図７に相当する図である。FIG. 23 is a view corresponding to FIG. 7 regarding a floating type disc brake according to a fourth example of the embodiment of the present invention. 図２４は、従来構造のフローティング型ディスクブレーキを径方向外方から見た部分断面図である。FIG. 24 is a partial cross-sectional view of a floating disc brake having a conventional structure as viewed from the outside in the radial direction.
［実施の形態の第１例］
　本発明の実施の形態の第１例について、図１～図１６を用いて説明する。
　本第１例のフローティング型ディスクブレーキ１ａは、自動車の制動を行うために使用するもので、サポート２ａと、ヨーク３ａと、インナパッド４ａ及びアウタパッド５ａと、シリンダユニット１７と、１対のスライドピン９ａとを備えている。これら各構成部材は、車輪とともに回転する円板状のロータ６を基準として、軸方向内側に、サポート２ａ、インナパッド４ａ、シリンダユニット１７、１対のスライドピン９ａが配置され、軸方向外側にアウタパッド５ａが配置され、径方向外側にヨーク３ａが配置される。これら各構成部材のうち、アウタパッド５ａが、本発明のディスクブレーキ用パッドに相当する。 [First example of embodiment]
A first example of the embodiment of the present invention will be described with reference to FIGS.
The floating disk brake 1a of the first example is used for braking an automobile, and includes a support 2a, a yoke 3a, an inner pad 4a and an outer pad 5a, a cylinder unit 17, and a pair of slide pins. 9a. Each of these structural members is arranged with a support 2a, an inner pad 4a, a cylinder unit 17, and a pair of slide pins 9a on the inner side in the axial direction with reference to the disc-shaped rotor 6 that rotates together with the wheels. The outer pad 5a is disposed, and the yoke 3a is disposed on the radially outer side. Out of these components, the outer pad 5a corresponds to the disc brake pad of the present invention.
　サポート２ａは、金属製で、ロータ６の軸方向内側に配置され、車体に固定される。サポート２ａは、正面視略Ｕ字状に構成されており、径方向内側部に配置されかつ周方向に伸長したサポート基部１４と、該サポート基部１４の周方向両外側部から径方向外方に向けて伸長した１対のサポート腕部１５を備えている。サポート基部１４の周方向両外側部には、サポート２ａをナックルなどの懸架装置に固定するための取付孔１６がそれぞれ形成されている。サポート腕部１５には、サポート２ａに対しシリンダユニット１７を固定するための締結孔がそれぞれ形成されている。また、サポート腕部１５のそれぞれの周方向内側面には、制動時にインナパッド４ａに作用するブレーキ接線力及びトルクを支承するための係合凹部６２が設けられている。 The support 2a is made of metal, is disposed on the inner side in the axial direction of the rotor 6, and is fixed to the vehicle body. The support 2a is configured in a substantially U shape when viewed from the front, and is disposed on the radially inner side and extended in the circumferential direction, and radially outward from both circumferential outer sides of the support base 14. A pair of support arm portions 15 extending toward the end are provided. Attachment holes 16 for fixing the support 2a to a suspension device such as a knuckle are formed on both outer sides of the support base 14 in the circumferential direction. The support arm 15 is formed with a fastening hole for fixing the cylinder unit 17 to the support 2a. In addition, an engagement recess 62 for supporting a brake tangential force and torque acting on the inner pad 4a during braking is provided on each inner circumferential surface of the support arm portion 15.
　シリンダユニット１７は、略円筒状のシリンダ８ａと、シリンダ８ａの外周面から周方向両外側に張り出すように設けられた１対のシリンダ腕部１８を備えている。シリンダ８ａの外周面の径方向外側部には、配管口１９とブリーダ２０が周方向に離隔して設けられている。シリンダユニット１７は、後述するようにサポート２ａに固定され、サポート２ａとともに固定部材を構成する。このため、本第１例の構造では、ヨーク３ａとシリンダ８ａが互いに別体に構成されている。 The cylinder unit 17 includes a substantially cylindrical cylinder 8a and a pair of cylinder arm portions 18 provided so as to protrude outward from the outer peripheral surface of the cylinder 8a in the circumferential direction. A pipe port 19 and a bleeder 20 are provided in the circumferential direction in the radially outer portion of the outer peripheral surface of the cylinder 8a. As will be described later, the cylinder unit 17 is fixed to the support 2a and constitutes a fixing member together with the support 2a. For this reason, in the structure of the first example, the yoke 3a and the cylinder 8a are formed separately from each other.
　シリンダ８ａの内部空間は、軸方向両側にそれぞれ開口しており、第１ピストン２１及び第２ピストン２２を軸方向に移動可能に嵌装している。また、シリンダ８ａの内部空間のうち、第１ピストン２１と第２ピストン２２との間に存在する部分が、圧油を導入するための油圧室とされている。また、シリンダ８ａの軸方向両端部と第１ピストン２１及び第２ピストン２２のそれぞれの先端部との間に、ブーツ３１ａ、３１ｂが架け渡されるように設けられている。シリンダ８ａの軸方向両端部には、軸方向中間部に比べて外径寸法が小さくなった小径部３５ａ、３５ｂが設けられている。さらに、シリンダ８ａの内周面と、第１ピストン２１及び第２ピストン２２のそれぞれの外周面との間に、シール部材５２ａ、５２ｂが設けられている。なお、シリンダと後述するアンカーとを一体に設ける場合などには、図示は省略するが、ブーツの端部がシリンダの軸方向端部の内周面に固定される。 The internal space of the cylinder 8a is opened on both sides in the axial direction, and the first piston 21 and the second piston 22 are fitted so as to be movable in the axial direction. Moreover, the part which exists between the 1st piston 21 and the 2nd piston 22 among the internal space of the cylinder 8a is made into the hydraulic chamber for introducing pressure oil. Further, boots 31 a and 31 b are provided so as to be bridged between both axial end portions of the cylinder 8 a and the respective front end portions of the first piston 21 and the second piston 22. Small- diameter portions 35a and 35b having a smaller outer diameter than the intermediate portion in the axial direction are provided at both axial end portions of the cylinder 8a. Further, seal members 52 a and 52 b are provided between the inner peripheral surface of the cylinder 8 a and the outer peripheral surfaces of the first piston 21 and the second piston 22. In the case where a cylinder and an anchor to be described later are integrally provided, the end portion of the boot is fixed to the inner peripheral surface of the axial end portion of the cylinder, although not shown.
　シリンダ腕部１８の先端部には、スライドピン９ａの先端部を固定するための雌ねじ孔２３と図示しない挿通孔とが、それぞれ径方向に隣接して形成されている。このようなシリンダユニット１７は、シリンダ腕部１８の先端部がサポート腕部１５の先端部に軸方向内側から重ね合わせられた状態で、シリンダ腕部１８の挿通孔が軸方向に挿通された固定ねじ２４がサポート腕部１５の締結孔に螺合されることにより、サポート２ａに固定されている。 At the tip of the cylinder arm 18, a female screw hole 23 for fixing the tip of the slide pin 9a and an insertion hole (not shown) are formed adjacent to each other in the radial direction. Such a cylinder unit 17 is fixed in such a manner that the insertion hole of the cylinder arm 18 is inserted in the axial direction in a state where the tip of the cylinder arm 18 is superimposed on the tip of the support arm 15 from the inside in the axial direction. The screw 24 is fixed to the support 2 a by being screwed into the fastening hole of the support arm portion 15.
　本第１例では、上述のようなシリンダユニット１７を構成するシリンダ８ａに、制動時にアウタパッド５ａに作用するブレーキ接線力を支承するためのアンカー２５が設けられている。アンカー２５は、径方向から見た形状が略Ｔ字状で、シリンダ８ａとは別体に構成されている。そして、アンカー２５は、締結部材である１対のボルト２６を用いて、シリンダ８ａの軸方向外端部の径方向外端部に固定されている。このため、アンカー２５は、シリンダ８ａに片持ち梁状に設けられており、ロータ６の径方向外側かつヨーク３ａの径方向内側に配置される。また、アンカー２５は、周方向に関して対称形状（図１１の左右対称形状）、つまり、自身の中心軸Ｏ２５に関して線対称の形状を有している。また、アンカー２５が、その中心軸Ｏ２５の周方向位置が、シリンダ８ａの中心軸の周方向位置と一致する位置に設けられている。このため、アンカー２５（後述する定幅部３０）は、アウタパッド５ａのライニング４７の周方向中央部Ｓ４７と径方向に重なる位置に設けられている。 In the first example, the cylinder 25a constituting the cylinder unit 17 as described above is provided with an anchor 25 for supporting a brake tangential force acting on the outer pad 5a during braking. The anchor 25 is substantially T-shaped when viewed from the radial direction, and is configured separately from the cylinder 8a. And the anchor 25 is being fixed to the radial direction outer end part of the axial direction outer end part of the cylinder 8a using the pair of volt | bolt 26 which is a fastening member. For this reason, the anchor 25 is provided in a cantilever shape on the cylinder 8a, and is disposed radially outside the rotor 6 and radially inside the yoke 3a. Also, the anchor 25 is (symmetrical shape of FIG. 11) symmetrical with respect to the circumferential direction, that is, it has the shape of a line symmetry with respect to its center axis O 25. The anchor 25 is provided at a position where the circumferential position of the central axis O 25 coincides with the circumferential position of the central axis of the cylinder 8a. Therefore, the anchor 25 (constant width portion 30 to be described later) is provided at a position overlapping the circumferentially central portion S 47 and the radial lining 47 of the outer pad 5a.
　アンカー２５は、水平方向に配置された板状（棒状）のアンカー本体２７と、１対の取付鍔２８とを備えている。アンカー本体２７は、周方向に向いたブレーキ接線力を受けるため、周方向に関する剛性を十分に高める（断面二次モーメントを高くする）べく、軸方向に直交する仮想平面に関する断面形状が、径方向寸法よりも周方向寸法が大きい長円形状とされている。このため、後述するように、アンカー本体２７のうちで、アウタパッド５ａに設けられた径方向突起５１ａ、５１ｂと当接する周方向外側面の断面形状は、凸円弧形状になっている。 The anchor 25 includes a plate-shaped (rod-shaped) anchor main body 27 and a pair of mounting rods 28 arranged in the horizontal direction. Since the anchor body 27 receives a brake tangential force directed in the circumferential direction, the cross-sectional shape with respect to the virtual plane orthogonal to the axial direction has a radial direction in order to sufficiently increase the rigidity in the circumferential direction (increase the secondary moment of section). It is an oval shape whose circumferential dimension is larger than the dimension. For this reason, as will be described later, the cross-sectional shape of the outer circumferential surface in contact with the radial protrusions 51a and 51b provided on the outer pad 5a in the anchor body 27 is a convex arc shape.
　アンカー本体２７には、軸方向内端部（基端部）乃至中間部に、軸方向外側に向かうほど周方向寸法が小さくなる先細部２９が設けられており、軸方向外端部（先端部）に、周方向寸法及び径方向寸法が軸方向にわたり一定である定幅部３０が設けられている。定幅部３０は、後述するように、ヨーク３ａとともに軸方向に移動するアウタパッド５ａに設けられた径方向突起５１ａ、５１ｂ同士の間に配置される。このため、定幅部３０は、制動時におけるアウタパッド５ａの軸方向移動量を考慮して、その軸方向寸法が規制されている。また、アンカー本体２７の軸方向内端部の径方向内側面のうち周方向中間部には、シリンダ８ａの小径部３５ａにブーツ３１ａを装着するための逃げ凹部３２が設けられている。本第１例では、アンカー本体２７の軸方向内端部が、径方向外側が凸となるように湾曲させられることで、アンカー本体２７の径方向内側面に逃げ凹部３２が形成されている。 The anchor body 27 is provided with a tapered portion 29 that decreases in the circumferential direction toward the outer side in the axial direction from the inner end portion (base end portion) to the intermediate portion in the axial direction. ) Is provided with a constant width portion 30 in which the circumferential dimension and the radial dimension are constant over the axial direction. As will be described later, the constant width portion 30 is disposed between the radial protrusions 51a and 51b provided on the outer pad 5a that moves in the axial direction together with the yoke 3a. For this reason, the axial dimension of the constant width portion 30 is restricted in consideration of the axial movement amount of the outer pad 5a during braking. In addition, an escape recess 32 for mounting the boot 31a to the small diameter portion 35a of the cylinder 8a is provided in a circumferential intermediate portion of the radially inner side surface of the axially inner end portion of the anchor body 27. In the first example, the relief inner portion 32 is formed on the radially inner side surface of the anchor body 27 by curving the inner end portion in the axial direction of the anchor body 27 so that the radially outer side is convex.
　１対の取付鍔２８は、アンカー本体２７の軸方向内端部から周方向両外側に張り出すように設けられており、それぞれに軸方向に貫通したボルト挿通孔が形成されている。本第１例では、このようなボルト挿通孔を挿通したボルト２６が、シリンダ８ａの軸方向外端面に開口した雌ねじ孔に螺合されることで、アンカー２５がシリンダ８ａにねじ止め固定されている。具体的には、シリンダ８ａのうちで、配管口１９及びブリーダ２０の軸方向外側にそれぞれ雌ねじ孔を有する取付座３３が設けられ、該取付座３３にボルト２６が螺合されている。また、アンカー２５がシリンダ８ａに固定される際に、取付鍔２８の軸方向内側面が取付座３３の軸方向外側面に突き当てられるとともに、アンカー本体２７の軸方向内端面がシリンダ８ａの外周面に形成された段差面３４に突き当てられている。取付鍔２８の軸方向内側面、取付座３３の軸方向外側面、アンカー本体２７の軸方向内端面及び段差面３４は、それぞれ平坦面状に構成される。シリンダ８ａの軸方向外端部に設けられた小径部３５ａは、逃げ凹部３２の内側に配置される。 The pair of mounting rods 28 are provided so as to protrude outward in the circumferential direction from the axially inner end of the anchor body 27, and are formed with bolt insertion holes penetrating in the axial direction. In the first example, the bolt 26 inserted through such a bolt insertion hole is screwed into the female screw hole opened in the axially outer end surface of the cylinder 8a, whereby the anchor 25 is screwed and fixed to the cylinder 8a. Yes. Specifically, in the cylinder 8a, mounting seats 33 each having a female screw hole are provided on the outside in the axial direction of the piping port 19 and the bleeder 20, and the bolts 26 are screwed to the mounting seat 33. Further, when the anchor 25 is fixed to the cylinder 8a, the axial inner surface of the mounting rod 28 is abutted against the axial outer surface of the mounting seat 33, and the axial inner end surface of the anchor body 27 is the outer periphery of the cylinder 8a. It is abutted against a step surface 34 formed on the surface. The inner side surface in the axial direction of the mounting rod 28, the outer side surface in the axial direction of the mounting seat 33, the inner end surface in the axial direction of the anchor body 27, and the step surface 34 are each formed in a flat surface shape. A small-diameter portion 35 a provided at the outer end in the axial direction of the cylinder 8 a is disposed inside the escape recess 32.
　本第１例では、図８に示すように、軸方向に配設されたボルト２６の中心軸Ｏ２６の径方向位置が、アンカー本体２７の先端部に設けた定幅部３０の径方向寸法Ａ３０の範囲内に収まるように規制されている。図示の例では、１対のボルト２６の中心軸Ｏ２６の径方向位置が、定幅部３０の径方向中央部（凸円弧形状の円周方向外側面の頂部の径方向位置）に一致させられて、１対のボルト２６の中心軸Ｏ２６と定幅部３０の径方向中央部とが、同一仮想直線Ｌ上に配置されている。これにより、定幅部３０に作用するブレーキ接線力の作用点の径方向位置と、このブレーキ接線力を支承するボルト２６の径方向位置とが一致若しくは互いに近づけられて、定幅部３０に入力されるブレーキ接線力がボルト２６により効率良く支承され、アンカー本体２７にモーメント力が作用しにくくされている。 In the first example, as shown in FIG. 8, the radial position of the central axis O 26 of the bolt 26 arranged in the axial direction is the radial dimension of the constant width portion 30 provided at the distal end portion of the anchor body 27. It is regulated so as to fall within a range of a 30. In the illustrated example, the radial position of the central axis O 26 of the pair of bolts 26 is made to coincide with the radial center of the constant width portion 30 (the radial position of the top of the circumferential outer surface of the convex arc shape). is in a radially intermediate portion of the center axis O 26 and the constant width portion 30 of a pair of bolts 26 are disposed on the same virtual straight line L. As a result, the radial position of the point of application of the brake tangential force acting on the constant width portion 30 and the radial position of the bolt 26 supporting the brake tangential force are matched or brought close to each other, and input to the constant width portion 30. The brake tangential force is efficiently supported by the bolt 26, and the moment force hardly acts on the anchor body 27.
　ヨーク３ａは、金属製又は非金属製で、軸方向から見た形状が弓形状である。ヨーク３ａは、サポート２ａ、インナパッド４ａ、アウタパッド５ａ及びシリンダユニット１７が、それぞれ径方向外側から覆われるように配置される。このようなヨーク３ａは、サポート２ａ及びシリンダユニット１７の軸方向内側に配置されたインナボディ３６と、アウタパッド５ａの軸方向外側に配置されたアウタボディ３７と、ロータ６の径方向外側に配置され、インナボディ３６とアウタボディ３７とを軸方向につなぐブリッジ部３８とを備えている。 The yoke 3a is made of metal or nonmetal, and the shape viewed from the axial direction is a bow shape. The yoke 3a is disposed so that the support 2a, the inner pad 4a, the outer pad 5a, and the cylinder unit 17 are each covered from the outside in the radial direction. Such a yoke 3a is disposed on the inner side of the support 2a and the cylinder unit 17 in the axial direction, the outer body 37 disposed on the outer side of the outer pad 5a in the axial direction, and on the outer side of the rotor 6 in the radial direction. A bridge portion 38 that connects the inner body 36 and the outer body 37 in the axial direction is provided.
　インナボディ３６の周方向中央部の軸方向外側面は、平坦面状に構成されており、シリンダ８ａに嵌装された第２ピストン２２の先端部と軸方向に対向している。また、インナボディ３６の周方向両外側部には、スライドピン９ａを摺動可能に配置するためのスライド孔１０ａが軸方向に貫通した状態で設けられている。 The axially outer surface of the inner circumferential portion of the inner body 36 is formed in a flat surface, and is opposed to the distal end portion of the second piston 22 fitted in the cylinder 8a in the axial direction. In addition, slide holes 10a for slidably disposing the slide pins 9a are provided in both outer circumferential portions of the inner body 36 in a state of penetrating in the axial direction.
　アウタボディ３７の軸方向内側面には、アウタパッド５ａを支持するために、それぞれが有底孔である支持孔３９と１対の受孔（ダボ孔）４０が設けられている。支持孔３９は、略矩形状の凹部であり、アウタボディ３７の軸方向内側面の周方向中央部に設けられている。１対の受孔４０は、円柱形状の凹部であり、支持孔３９の周方向両外側に設けられている。受孔４０の内径寸法は、アウタパッド５ａに設けられた後述の軸方向突部５０の外径寸法よりも僅かに大きい。 On the inner side surface of the outer body 37 in the axial direction, in order to support the outer pad 5a, a support hole 39 which is a bottomed hole and a pair of receiving holes (dowel holes) 40 are provided. The support hole 39 is a substantially rectangular recess, and is provided in the circumferential central portion of the inner side surface of the outer body 37 in the axial direction. The pair of receiving holes 40 are cylindrical recesses and are provided on both outer sides in the circumferential direction of the support hole 39. The inner diameter dimension of the receiving hole 40 is slightly larger than the outer diameter dimension of an axial protrusion 50 described later provided in the outer pad 5a.
　ブリッジ部３８は、ロータ６の径方向外側に配置されており、その径方向内側面の周方向中央部に、アンカー本体２７を収納するための軸方向に伸長した収納凹部４１が設けられている。収納凹部４１は、断面略矩形状で、アンカー本体２７の断面形状よりも周方向及び径方向にそれぞれ少しだけ大きい。また、ブリッジ部３８の軸方向内側部の周方向中間部には、径方向に貫通した１対のインナ窓部４２ａ、４２ｂが周方向に離隔して設けられており、これらインナ窓部４２ａ、４２ｂからシリンダユニット１７に設けられた配管口１９とブリーダ２０とが露出させられている。また、ブリッジ部３８の軸方向外側部の周方向中央部には、径方向に貫通したアウタ窓部４３が設けられており、このアウタ窓部４３からアンカー２５の軸方向外端部及びアウタパッド５ａを構成する後述の径方向突起５１ａ、５１ｂが露出させられている。 The bridge portion 38 is disposed on the radially outer side of the rotor 6, and a storage recess 41 extending in the axial direction for storing the anchor main body 27 is provided in the circumferential central portion of the radially inner side surface thereof. . The storage recess 41 has a substantially rectangular cross section and is slightly larger in the circumferential direction and the radial direction than the cross sectional shape of the anchor main body 27. In addition, a pair of radially inner windows 42a and 42b are provided in the circumferential intermediate portion of the bridge portion 38 in the axial direction, and are spaced apart in the circumferential direction. The inner window portions 42a, The piping port 19 and the bleeder 20 provided in the cylinder unit 17 are exposed from 42b. In addition, an outer window portion 43 penetrating in the radial direction is provided in the circumferential center portion of the bridge portion 38 in the axially outer portion, and the axially outer end portion of the anchor 25 and the outer pad 5a from the outer window portion 43. The radial protrusions 51a and 51b, which will be described later, are exposed.
　上述のようなヨーク３ａは、１対のスライドピン９ａを利用して、固定部材であるシリンダユニット１７に軸方向に関する移動を可能に支持されている。具体的には、スライドピン９ａが、インナボディ３６に設けられたスライド孔１０ａの内側に軸方向内側から挿入され、スライドピン９ａの軸方向中間部がスライド孔１０ａの内側に摺動可能に配置される。また、スライドピン９ａの先端部が、シリンダユニット１７を構成するシリンダ腕部１８の先端部に設けられた雌ねじ孔２３に螺合される。これにより、スライドピン９ａがシリンダユニット１７に対して水平方向に固定されるとともに、このようなスライドピン９ａに対してヨーク３ａが軸方向に関する移動を可能に支持されている。また、スライドピン９ａのうちでスライド孔１０ａから軸方向両側に露出した部分には、それぞれブーツ５５が装着されている。 The yoke 3a as described above is supported by the cylinder unit 17 which is a fixed member so as to be movable in the axial direction using a pair of slide pins 9a. Specifically, the slide pin 9a is inserted into the inner side of the slide hole 10a provided in the inner body 36 from the inner side in the axial direction, and the axial intermediate portion of the slide pin 9a is slidably arranged inside the slide hole 10a. Is done. Further, the distal end portion of the slide pin 9 a is screwed into a female screw hole 23 provided at the distal end portion of the cylinder arm portion 18 constituting the cylinder unit 17. Thereby, the slide pin 9a is fixed in the horizontal direction with respect to the cylinder unit 17, and the yoke 3a is supported so as to be movable in the axial direction with respect to the slide pin 9a. Also, boots 55 are respectively attached to portions of the slide pin 9a that are exposed from the slide hole 10a to both sides in the axial direction.
　インナパッド４ａは、ロータ６の軸方向内側に配置されており、ライニング（摩擦材）４４と、ライニング４４の裏面である軸方向内側面を支持した金属製の裏板（プレッシャプレート）４５とを備えている。このようなインナパッド４ａは、サポート基部１４の径方向外側でかつ１対のサポート腕部１５の周方向内側部分に配置されることで、サポート２ａに対し、軸方向に関する移動を可能に、かつ、径方向及び周方向に関する移動を制限された状態で支持される。具体的には、インナパッド４ａを構成する裏板４５の周方向両外側に設けた１対の耳部４６が、１対のサポート腕部１５の周方向内側面に形成した係合凹部６２に対してそれぞれ凹凸係合させられることで、インナパッド４ａがサポート２ａに対して支持されている。また、このようにインナパッド４ａがサポート２ａに支持された状態で、裏板４５の軸方向内側面には、第１ピストン２１の先端部が軸方向に対向する。また、インナパッド４ａの周方向中間部の径方向外側には、アンカー２５（アンカー本体２７）が配置される。 The inner pad 4 a is disposed on the inner side in the axial direction of the rotor 6, and includes a lining (friction material) 44 and a metal back plate (pressure plate) 45 that supports the inner side surface in the axial direction that is the back surface of the lining 44. I have. Such an inner pad 4a is arranged on the outer side in the radial direction of the support base portion 14 and on the inner side in the circumferential direction of the pair of support arm portions 15, thereby enabling movement in the axial direction with respect to the support 2a, and It is supported in a state where movement in the radial direction and the circumferential direction is limited. Specifically, a pair of ear portions 46 provided on both outer sides in the circumferential direction of the back plate 45 constituting the inner pad 4a are formed in engagement recesses 62 formed on the inner circumferential surface of the pair of support arm portions 15. The inner pad 4a is supported with respect to the support 2a by being engaged with each other. In addition, with the inner pad 4a supported by the support 2a in this way, the tip end portion of the first piston 21 faces the axially inner side surface of the back plate 45 in the axial direction. In addition, an anchor 25 (anchor body 27) is disposed on the radially outer side of the intermediate portion in the circumferential direction of the inner pad 4a.
　アウタパッド５ａは、ロータ６の軸方向外側に配置されており、ライニング（摩擦材）４７と、ライニング４７の裏面である軸方向外側面を支持した金属製の裏板（プレッシャプレート）４８とを備えている。本第１例では、アウタパッド５ａが、周方向に関して対称形状とされている。裏板４８の軸方向外側面の周方向中央部には、板ばね製のパッドスプリング４９がかしめ固定されている。また、裏板４８の軸方向外側面の周方向両外側部には、１対の軸方向突部（ダボ）５０が設けられている。軸方向突部５０は、それぞれが略円柱状に構成されており、裏板４８の軸方向外側面から軸方向外側に突出するように設けられている。本例では、軸方向突部５０を、裏板４８に対してエンボス加工を施すことにより、該裏板４８と一体に形成している。ただし、本発明を実施する場合、軸方向突部５０の成形方法は特に問わない。 The outer pad 5 a is disposed on the outer side in the axial direction of the rotor 6, and includes a lining (friction material) 47 and a metal back plate (pressure plate) 48 that supports the outer side in the axial direction that is the back surface of the lining 47. ing. In the first example, the outer pad 5a is symmetrical with respect to the circumferential direction. A pad spring 49 made of a leaf spring is caulked and fixed to the central portion in the circumferential direction of the outer surface in the axial direction of the back plate 48. In addition, a pair of axial protrusions (dowels) 50 are provided on both outer circumferential portions of the axially outer surface of the back plate 48. Each of the axial protrusions 50 is formed in a substantially cylindrical shape, and is provided so as to protrude outward in the axial direction from the axially outer surface of the back plate 48. In this example, the axial protrusion 50 is formed integrally with the back plate 48 by embossing the back plate 48. However, when implementing this invention, the shaping | molding method of the axial direction protrusion 50 is not ask | required in particular.
　特に本第１例では、制動時にロータ６との接触に基づいてアウタパッド５ａに作用するブレーキ接線力のうち、ヨーク３ａを介してスライドピン９ａに伝達される割合を減らすために、裏板４８の外周縁部に、径方向外側に向けて突出した１対の径方向突起５１ａ、５１ｂが設けられている。１対の径方向突起５１ａ、５１ｂは、周方向に離隔して配置されており、１対の径方向突起５１ａ、５１ｂ同士の間に、アンカー２５の軸方向外端部に設けた定幅部３０が、軸方向の相対移動を可能に配置（挿入）できるように構成されている。 Particularly in the first example, in order to reduce the ratio of the brake tangential force acting on the outer pad 5a based on the contact with the rotor 6 during braking to be transmitted to the slide pin 9a via the yoke 3a, A pair of radial protrusions 51a and 51b protruding outward in the radial direction are provided on the outer peripheral edge. The pair of radial protrusions 51a and 51b are spaced apart from each other in the circumferential direction, and a constant width portion provided at the axial outer end of the anchor 25 between the pair of radial protrusions 51a and 51b. 30 is configured to be arranged (inserted) so as to be capable of relative movement in the axial direction.
　径方向突起５１ａ、５１ｂは、それぞれ略矩形状に構成されており、周方向に対向する周方向内側面が互いに平行な平坦面とされ、周方向外側面が径方向外方に向かうほど互いに近づく方向に傾斜した傾斜面とされている。また、１対の径方向突起５１ａ、５１ｂの周方向内側面同士の距離Ｈは、定幅部３０の周方向寸法Ｂ３０よりも僅かに大きい（Ｈ＞Ｂ３０）。特に本第１例では、１対の径方向突起５１ａ、５１ｂ同士の間に定幅部３０が中立位置となるように配置された状態で、定幅部３０の凸円弧形状の周方向外側面と径方向突起５１ａ、５１ｂの平坦面状の周方向内側面との間に形成される隙間の大きさが、軸方向突部５０と受孔４０との間に形成される隙間よりも小さく設定されている。 Each of the radial protrusions 51a and 51b is formed in a substantially rectangular shape, and the circumferential inner surfaces facing each other in the circumferential direction are flat surfaces parallel to each other, and the circumferential outer surfaces are closer to each other toward the radially outer side. The inclined surface is inclined in the direction. Further, a pair of radial projections 51a, the distance H between the circumferential inner surface of 51b is slightly larger than the circumferential dimension B 30 of constant width portion 30 (H> B 30). Particularly in the first example, the circumferential outer surface of the convex arc shape of the constant width portion 30 in a state where the constant width portion 30 is disposed between the pair of radial protrusions 51a and 51b so as to be in a neutral position. And a gap formed between the axial protrusion 50 and the receiving hole 40 are set to be smaller than the gap formed between the flat and circumferential inner surfaces of the radial protrusions 51a and 51b. Has been.
　アウタパッド５ａをアウタボディ３７の軸方向内側面に支持するには、アウタパッド５ａの軸方向外側面に設けた１対の軸方向突部５０が、アウタボディ３７の軸方向内側面に形成した１対の受孔４０に緩く凹凸嵌合（挿入）されるとともに、アウタパッド５ａの軸方向外側面に固定したパッドスプリング４９が、支持孔３９の内側に弾性的に係合される。軸方向突部５０が受孔４０の内側に挿入されることで、アウタボディ３７に対するアウタパッド５ａの周方向及び径方向の移動が制限される。また、パッドスプリング４９が支持孔３９に弾性的に係合（スナップフィット係合）されることで、アウタパッド５ａの周方向に関する位置決めが図られる（センタリング機能を発揮させる）とともに、軸方向内側への脱落が防止される。また、アウタパッド５ａがアウタボディ３７の軸方向内側面に取り付けられた状態で、１対の径方向突起５１ａ、５１ｂ同士の間にアンカー２５の定幅部３０が配置される。 In order to support the outer pad 5 a on the inner side surface in the axial direction of the outer body 37, a pair of axial protrusions 50 provided on the outer side surface in the axial direction of the outer pad 5 a are formed into a pair of receiving portions formed on the inner side surface in the axial direction of the outer body 37. A pad spring 49 that is loosely concavo-convexly fitted (inserted) into the hole 40 and fixed to the outer side surface of the outer pad 5 a in the axial direction is elastically engaged with the inside of the support hole 39. By inserting the axial protrusion 50 inside the receiving hole 40, movement of the outer pad 5 a in the circumferential direction and the radial direction with respect to the outer body 37 is restricted. Further, the pad spring 49 is elastically engaged (snap fit engagement) with the support hole 39, thereby positioning the outer pad 5a in the circumferential direction (exhibiting a centering function) and inward in the axial direction. Dropping is prevented. In addition, the constant width portion 30 of the anchor 25 is disposed between the pair of radial protrusions 51a and 51b in a state where the outer pad 5a is attached to the inner side surface in the axial direction of the outer body 37.
　本第１例のフローティング型ディスクブレーキ１ａにより制動を行うには、シリンダ８ａ内の油圧室に圧油を導入する。これにより、第１ピストン２１及び第２ピストン２２が、軸方向に関して互いに離れる方向にそれぞれ移動させられる。そして、第１ピストン２１によりインナパッド４ａが、ロータ６の軸方向内側面に、図５の上方から下方に押し付けられる。同時に、第２ピストン２２によりインナボディ３６が、図５の下方から上方に押し付けられ、ヨーク３ａが固定部材であるサポート２ａ及びシリンダユニット１７に対して、図５の上側に移動させられる。これにより、アウタボディ３７を介してアウタパッド５ａが、ロータ６の軸方向外側面に、図５の下方から上方に押し付けられる。この結果、ロータ６が軸方向両側から強く挟持されて制動が行われる。 In order to perform braking by the floating disc brake 1a of the first example, pressure oil is introduced into the hydraulic chamber in the cylinder 8a. Accordingly, the first piston 21 and the second piston 22 are moved in directions away from each other with respect to the axial direction. Then, the inner pad 4 a is pressed against the axial inner surface of the rotor 6 from the upper side to the lower side in FIG. 5 by the first piston 21. At the same time, the inner body 36 is pressed upward from the lower side in FIG. 5 by the second piston 22, and the yoke 3 a is moved to the upper side in FIG. 5 with respect to the support 2 a and the cylinder unit 17 that are the fixing members. As a result, the outer pad 5a is pressed against the axially outer surface of the rotor 6 from the lower side to the upper side in FIG. As a result, the rotor 6 is strongly clamped from both sides in the axial direction and braking is performed.
　インナパッド４ａ及びアウタパッド５ａによりロータ６が軸方向両側から挟持されると、インナパッド４ａ及びアウタパッド５ａにはそれぞれ周方向（回出側）に向いたブレーキ接線力が作用する。インナパッド４ａに作用するブレーキ接線力は、サポート２ａが直接支承する。これに対し、アウタパッド５ａに作用するブレーキ接線力は、アンカー２５が直接支承する。この点につき、図１６を参照して詳しく説明する。 When the rotor 6 is clamped from both sides in the axial direction by the inner pad 4a and the outer pad 5a, a brake tangential force directed in the circumferential direction (the outlet side) acts on the inner pad 4a and the outer pad 5a. The brake tangential force acting on the inner pad 4a is directly supported by the support 2a. In contrast, the brake tangential force acting on the outer pad 5a is directly supported by the anchor 25. This point will be described in detail with reference to FIG.
　図１６の（Ａ）に示すように、自動車の前進時におけるロータ６の回転方向（Ｒ）が時計回りである場合、前進制動時には、アウタパッド５ａを構成するライニング４７の摩擦面中心（図心）に、周方向片側（ＸＡ：回出側、図１６の（Ａ）の右側）に向いたブレーキ接線力Ｆ１が作用する。これにより、アウタパッド５ａは周方向片側（ＸＡ）に移動し、周方向他側（ＸＢ：図１６の（Ａ）の左側）に設けられた径方向突起５１ａの周方向内側面が、定幅部３０の周方向外側面に当接する。このため、アンカー２５は、アウタパッド５ａの周方向他側（ＸＢ）の径方向突起５１ａとの当接に基づいて、前進制動時に作用するブレーキ接線力Ｆ１を直接支承する。この際、径方向突起５１ａの周方向内側面と定幅部３０の周方向外側面との当接部Ｐ１の周方向位置は、ライニング４７の周方向中央部Ｓ４７よりも回入側（周方向他側（ＸＢ））に位置しており、かつ、ライニング４７の周方向の範囲Ｒ内に位置している。 As shown in FIG. 16A, when the rotational direction (R) of the rotor 6 when the automobile is moving forward is clockwise, the friction surface center (centroid) of the lining 47 constituting the outer pad 5a during forward braking. In addition, a brake tangential force F1 directed to one side in the circumferential direction (XA: outlet side, right side in FIG. 16A) acts. As a result, the outer pad 5a moves to one circumferential side (XA), and the circumferential inner surface of the radial projection 51a provided on the other circumferential side (XB: left side of FIG. 16A) is a constant width portion. 30 abuts on the outer circumferential surface. For this reason, the anchor 25 directly supports the brake tangential force F1 acting during forward braking based on the contact with the radial protrusion 51a on the other circumferential side (XB) of the outer pad 5a. At this time, the circumferential direction position of the contact portion P1 of the circumferential outer surface of the circumferential inner surface and a constant width portion 30 of the radial protrusions 51a are circumferentially even times-in side from the direction central portion S 47 of the lining 47 (circumferential (The other side in the direction (XB)) and within the circumferential range R of the lining 47.
　本第１例では、径方向突起５１ａの平坦面状の周方向内側面と定幅部３０の凸円弧形状の周方向外側面とが当接するため、接触状態を線接触にして、当接位置を安定させることができる。また、当接部Ｐ１は、ブレーキ接線力Ｆ１の作用線よりも径方向外側に位置しているため、前進制動時には、アウタパッド５ａに、該アウタパッド５ａを反時計回りに回動させようとするモーメントが作用する。このようなモーメントは、定幅部３０の径方向内側面と裏板４８の外周縁部とが当接することで、アンカー２５によって支承することもできるし、軸方向突部５０と受孔４０との当接部を介してヨーク３ａに伝達することもできる。本第１例では、図７に示すように、前進制動時に、アウタパッド５ａに作用するモーメントが、径方向突起５１ａの周方向内側面と定幅部３０の周方向外側面との第１の支承部Ｘ１（当接部Ｐ１）と、周方向片側（ＸＡ：回出側、図７の右側）の軸方向突部５０の径方向外端部と受孔４０の径方向外端部との第２の支承部Ｘ２と、周方向他側（ＸＢ：回入側、図７の左側）の軸方向突部５０の径方向内端部と受孔４０の径方向内端部との第三の支承部Ｘ３との３点の支承部Ｘ１、Ｘ２、Ｘ３で支承される。３点の支承部Ｘ１、Ｘ２、Ｘ３を結んで描かれる三角形の大きさ（面積）は、アウタパッド５ａの軸方向への傾きやすさと相関があり、三角形が径方向に広がっているほど、外周側部分又は内周側部分が軸方向に傾きにくく当該部分に偏摩耗が生じにくくなり、三角形が周方向に広がっているほど、回入側部分又は回出側部分が軸方向に傾きにくく当該部分に偏摩耗が生じにくくなる。本第１例では、モーメントを支承する３点の支承部Ｘ１、Ｘ２、Ｘ３のうち、第１の支承部Ｘ１を、ライニング４７よりも径方向外側に配置することができるため、ライニング４７の外周側部分が軸方向（ロータ６側）に傾くことを有効に防止できる。したがって、ライニング４７の外周側部分に偏摩耗が生じることを有効に防止できる。 In the first example, the flat inner circumferential surface of the radial protrusion 51a and the circumferential outer surface of the constant-arc portion of the constant-width portion 30 are in contact with each other. Can be stabilized. Further, since the abutting portion P1 is located radially outside the line of action of the brake tangential force F1, during forward braking, a moment that causes the outer pad 5a to rotate the outer pad 5a counterclockwise. Act. Such a moment can be supported by the anchor 25 when the radially inner side surface of the constant width portion 30 and the outer peripheral edge portion of the back plate 48 come into contact with each other, and the axial protrusion 50 and the receiving hole 40 It is also possible to transmit to the yoke 3a through the contact portion. In the first example, as shown in FIG. 7, during forward braking, the moment acting on the outer pad 5 a causes the first support between the circumferential inner surface of the radial protrusion 51 a and the circumferential outer surface of the constant width portion 30. A first portion of the radial outer end portion of the axial projection 50 on the one side (XA: outlet side, right side in FIG. 7) and the outer radial end portion of the receiving hole 40 on the portion X1 (contact portion P1). 2 and a third inner portion of the radial inner end of the axial projection 50 on the other circumferential side (XB: turn-in side, left side in FIG. 7) and the inner radial end of the receiving hole 40. It is supported by three support parts X1, X2, and X3 with the support part X3. The size (area) of the triangle drawn by connecting the three support portions X1, X2, and X3 correlates with the ease of inclination of the outer pad 5a in the axial direction. The part or the inner peripheral side part is less likely to tilt in the axial direction, and uneven wear is less likely to occur in the part, and the more the triangle spreads in the circumferential direction, the more difficult the inward side part or the outlet side part tilts in the axial direction. Uneven wear is less likely to occur. In the first example, of the three support portions X1, X2, and X3 that support the moment, the first support portion X1 can be disposed radially outward from the lining 47. It is possible to effectively prevent the side portion from being inclined in the axial direction (the rotor 6 side). Therefore, it is possible to effectively prevent uneven wear from occurring on the outer peripheral side portion of the lining 47.
　これに対し、後進制動時には、図１６の（Ｂ）に示すように、アウタパッド５ａを構成するライニング４７の摩擦面中心に、周方向他側（ＸＢ：回出側、図１６の（Ｂ）の左側）に向いたブレーキ接線力Ｆ２が作用する。これにより、アウタパッド５ａは周方向他側（ＸＢ）に移動し、周方向片側（ＸＡ：図１６の（Ｂ）の右側）に設けられた径方向突起５１ｂの周方向内側面が、定幅部３０の周方向外側面に当接する。このため、アンカー２５は、アウタパッド５ａの周方向片側（ＸＡ）の径方向突起５１ｂとの当接に基づいて、後進制動時に作用するブレーキ接線力Ｆ２を直接支承する。径方向突起５１ｂの周方向内側面と定幅部３０の周方向外側面との当接部Ｐ２の周方向位置も、ライニング４７の周方向中央部Ｓ４７よりも回入側（周方向片側（ＸＡ））に位置しており、かつ、ライニング４７の周方向の範囲Ｒ内に位置している。 On the other hand, at the time of reverse braking, as shown in FIG. 16B, the other side in the circumferential direction (XB: outlet side, as shown in FIG. The brake tangential force F2 directed to the left side) acts. Thereby, the outer pad 5a moves to the other circumferential side (XB), and the circumferential inner surface of the radial projection 51b provided on one circumferential side (XA: the right side in FIG. 16B) is a constant width portion. 30 abuts on the outer circumferential surface. For this reason, the anchor 25 directly supports the brake tangential force F2 that acts during reverse braking based on the contact with the radial protrusion 51b on one circumferential side (XA) of the outer pad 5a. Circumferential position of the contact portion P2 of the circumferential outer surface of the circumferential inner surface and a constant width portion 30 of the radial projection 51b is also circumferentially central portion also times-in side than the S 47 of the lining 47 (the circumferential direction on one side ( XA)) and within the circumferential range R of the lining 47.
　本第１例では、後進制動時においても、径方向突起５１ｂの平坦面状の周方向内側面と定幅部３０の凸円弧形状の周方向外側面とが当接するため、接触状態を線接触にして、当接位置を安定させることができる。また、後進制動時に作用するブレーキ接線力Ｆ２に基づくモーメントについても、前進制動時の場合と同様にアンカー２５によって支承するか、軸方向突部５０と受孔４０との当接部を介してヨーク３ａに伝達する。 In the first example, the flat inner circumferential surface of the radial projection 51b and the convex arc-shaped circumferential outer surface of the constant width portion 30 are in contact with each other even during reverse braking. Thus, the contact position can be stabilized. Further, the moment based on the brake tangential force F2 acting at the time of reverse braking is also supported by the anchor 25 in the same way as at the time of forward braking, or the yoke via the contact portion between the axial protrusion 50 and the receiving hole 40. 3a.
　次に、前進制動時にインナパッド４ａに作用するモーメントについて、図６を参照して説明する。
　自動車の前進時におけるロータ６の回転方向（Ｒ）が時計回りである場合、前進制動時には、インナパッド４ａを構成するライニング４４の摩擦面中心（図心）に、周方向片側（回出側、図６の右側）に向いたブレーキ接線力Ｆ３が作用する。これにより、インナパッド４ａは周方向片側に移動し、裏板４５の周方向他側（図６の左側）の径方向内端部に設けられた突起部６３の周方向内側面が、サポート２ａを構成するサポート基部１４の一部に当接する。ここで、突起部６３の周方向内側面とサポート基部１４との当接部は、ブレーキ接線力Ｆ３の作用線よりも径方向内側に位置しているため、前進制動時には、インナパッド４ａに、該インナパッド４ａを時計回りに回動させようとするモーメントが作用する。そして本第１例では、インナパッド４ａに作用するモーメントが、突起部６３とサポート基部１４との第１の支承部Ｙ１と、周方向片側の耳部４６の径方向内側面と係合凹部６２の径方向内側面との第２の支承部Ｙ２と、周方向他側の耳部４６の径方向外側面と係合凹部６２の径方向外側面との支承部Ｙ３との３点の支承部Ｙ１、Ｙ２、Ｙ３で支承される。本第１例では、モーメントを支承する３点の支承部Ｙ１、Ｙ２、Ｙ３のうち、第２の支承部Ｙ２と第３の支承部Ｙ３を裏板４５の周方向両端部に配置することができる。このため、ライニング４４の回入側部分と回出側部分に偏摩耗が生じることを有効に防止できる。 Next, the moment that acts on the inner pad 4a during forward braking will be described with reference to FIG.
When the rotational direction (R) of the rotor 6 at the time of forward movement of the automobile is clockwise, at the time of forward braking, the friction surface center (centroid) of the lining 44 that constitutes the inner pad 4a is placed on one side in the circumferential direction (outward side, A brake tangential force F3 directed to the right side of FIG. 6 acts. Thereby, the inner pad 4a moves to one side in the circumferential direction, and the inner side surface in the circumferential direction of the protrusion 63 provided at the radially inner end of the other side (left side in FIG. 6) of the back plate 45 is supported by the support 2a. A part of the support base 14 constituting the. Here, the contact portion between the circumferential inner surface of the protrusion 63 and the support base 14 is located radially inward from the line of action of the brake tangential force F3. A moment is applied to rotate the inner pad 4a clockwise. In the first example, the moment acting on the inner pad 4a is caused by the first support portion Y1 of the protrusion 63 and the support base 14, the radially inner side surface of the ear 46 on one side in the circumferential direction, and the engagement recess 62. The three bearing portions of the second bearing portion Y2 with the radially inner side surface, the bearing portion Y3 with the radially outer surface of the ear 46 on the other circumferential side and the radially outer surface of the engaging recess 62 Supported by Y1, Y2, and Y3. In the first example, among the three support portions Y1, Y2, and Y3 that support the moment, the second support portion Y2 and the third support portion Y3 can be arranged at both ends in the circumferential direction of the back plate 45. it can. For this reason, it is possible to effectively prevent the occurrence of uneven wear at the entrance side portion and the exit side portion of the lining 44.
　制動解除時には、シリンダ８ａの油圧室から圧油を排出する。これにより、第１ピストン２１は、第１ピストン２１の周囲に配置したシール部材５２ａの弾力によって、内部空間に引き戻される（ロールバックする）。同様に、第２ピストン２２に関しても、第２ピストン２２の周囲に配置したシール部材５２ｂの弾力により、内部空間に引き戻される。 When releasing the brake, the hydraulic oil is discharged from the hydraulic chamber of the cylinder 8a. As a result, the first piston 21 is pulled back (rolled back) to the internal space by the elasticity of the seal member 52a disposed around the first piston 21. Similarly, the second piston 22 is also pulled back to the internal space by the elasticity of the seal member 52b disposed around the second piston 22.
　以上のような本第１例のフローティング型ディスクブレーキ１ａによれば、制動時にアウタパッド５ａに作用するブレーキ接線力Ｆ１、Ｆ２にかかわらず、アウタパッド５ａを支持するヨーク３ａに傾き（チルト）が発生することを抑制できる。
　すなわち、本第１例では、前進制動時及び後進制動時に、アウタパッド５ａの外周縁部に設けた径方向突起５１ａ、５１ｂが、シリンダ８ａに片持ち梁状に設けたアンカー２５に当接することで、アウタパッド５ａに作用するブレーキ接線力Ｆ１、Ｆ２が、アンカー２５によって直接支承される。このため、ブレーキ接線力Ｆ１、Ｆ２が、アウタパッド５ａに設けた軸方向突部５０とアウタボディ３７に設けた受孔４０との当接部を通じてヨーク３ａに伝達される割合を減らすことができる。したがって、ヨーク３ａに傾き（チルト）が発生することを有効に防止できる。この結果、アウタパッド５ａを構成するライニング４７に偏摩耗が生じることを抑制できるとともに、制動時に鳴きなどの異音（ノイズ）が発生することを抑制できる。また、スライドピン９ａとスライド孔１０ａとの間の摺動抵抗が増大する（コジリ力が発生する）ことを抑制できるため、ジャダーの発生を抑制することもできる。
　なお、本第１例の構造では、ブレーキ接線力Ｆ１、Ｆ２が作用した場合に、軸方向突部５０と受孔４０とが当接するよりも前に、径方向突起５１ａ、５１ｂをアンカー２５に当接させる場合について説明したが、径方向突起５１ａ、５１ｂと定幅部３０とが当接するのと同時又はそれ以前に、軸方向突部５０と受孔４０とを当接させることも可能である。この場合にも、ブレーキ接線力Ｆ１、Ｆ２の少なくとも一部をアンカー２５が支承できるため、ヨーク３ａの傾きを抑えることが可能である。 According to the floating disc brake 1a of the first example as described above, a tilt (tilt) is generated in the yoke 3a that supports the outer pad 5a regardless of the brake tangential forces F1 and F2 that act on the outer pad 5a during braking. This can be suppressed.
That is, in the first example, during forward braking and backward braking, the radial protrusions 51a and 51b provided on the outer peripheral edge of the outer pad 5a abut on the anchor 25 provided in a cantilever shape on the cylinder 8a. The brake tangential forces F1 and F2 acting on the outer pad 5a are directly supported by the anchor 25. For this reason, it is possible to reduce the rate at which the brake tangential forces F1 and F2 are transmitted to the yoke 3a through the contact portion between the axial protrusion 50 provided in the outer pad 5a and the receiving hole 40 provided in the outer body 37. Therefore, it is possible to effectively prevent the yoke 3a from being tilted. As a result, it is possible to suppress the occurrence of uneven wear in the lining 47 that constitutes the outer pad 5a, and it is possible to suppress the generation of abnormal noise (noise) such as squeal during braking. Moreover, since it can suppress that the sliding resistance between the slide pin 9a and the slide hole 10a increases (a squeezing force generate | occur | produces), generation | occurrence | production of judder can also be suppressed.
In the structure of the first example, when the brake tangential forces F1 and F2 are applied, the radial protrusions 51a and 51b are attached to the anchor 25 before the axial protrusion 50 and the receiving hole 40 contact each other. Although the case where they are brought into contact with each other has been described, the axial protrusion 50 and the receiving hole 40 can be brought into contact with the radial protrusions 51a and 51b and the constant width portion 30 at the same time or before. is there. Also in this case, since the anchor 25 can support at least a part of the brake tangential forces F1 and F2, it is possible to suppress the inclination of the yoke 3a.
　また、本第１例では、軸方向突部５０が、裏板４８に一体に設けられているため、製造コストの低減を図れるとともに、部品点数の低減を図れる。また、軸方向突部５０の剛性を確保しやすくできる。さらに、軸方向突部５０が円柱形状とされ、受孔４０が円柱形状の凹部とされている。そのため、軸方向突部５０の外径が寸法公差の中でプラス側にばらついたものを使用する（又は受孔４０の内径が寸法公差の中でマイナス側にばらついたものを使用する）ことで、軸方向突部５０と受孔４０との間の隙間（クリアランス）を低減でき、ラトル音及びクロンク音などの異音を低減することもできる。 In the first example, since the axial protrusion 50 is provided integrally with the back plate 48, the manufacturing cost can be reduced and the number of parts can be reduced. In addition, the rigidity of the axial protrusion 50 can be easily ensured. Furthermore, the axial protrusion 50 has a cylindrical shape, and the receiving hole 40 has a cylindrical recess. Therefore, by using the axial projection 50 whose outer diameter varies on the plus side within the dimensional tolerance (or using the one whose inner diameter of the receiving hole 40 varies on the minus side within the dimensional tolerance). Moreover, the clearance gap (clearance) between the axial direction protrusion part 50 and the receiving hole 40 can be reduced, and abnormal noises, such as a rattle sound and a cronk sound, can also be reduced.
　また、アンカー本体２７の断面形状が、径方向寸法よりも周方向寸法が大きい長円形状とされているため、ブレーキ接線力を支承するのに重要な周方向に関する剛性を確保しつつ、径方向寸法が過大になることを防止できる。このため、アンカー本体２７を覆うように配置されるヨーク３ａの外径寸法が過大になることを防止できる。さらに、ヨーク３ａの径方向内側面に、アンカー本体２７を収納するための収納凹部４１が設けられているため、アンカー２５を設けたことに起因して、ヨーク３ａの外径寸法が大きくなることを効果的に防止できる。この結果、フローティング型ディスクブレーキ１ａの大型化を防止できる。 Further, since the cross-sectional shape of the anchor body 27 is an oval shape whose circumferential dimension is larger than the radial dimension, the rigidity in the circumferential direction, which is important for supporting the brake tangential force, is secured while maintaining the radial direction. It is possible to prevent the size from becoming excessive. For this reason, it can prevent that the outer diameter dimension of the yoke 3a arrange | positioned so that the anchor main body 27 may be covered becomes excessive. Furthermore, since the housing recess 41 for housing the anchor main body 27 is provided on the radially inner side surface of the yoke 3a, the outer diameter of the yoke 3a increases due to the provision of the anchor 25. Can be effectively prevented. As a result, an increase in size of the floating type disc brake 1a can be prevented.
　また、本第１例では、アンカー２５とアウタパッド５ａとの当接部Ｐ１、Ｐ２が、ライニング４７の周方向の範囲Ｒ内に位置させられている。このため、ブレーキ接線力Ｆ１、Ｆ２に基づいてアウタパッド５ａに生じる径方向に向いた中心軸回りのモーメント（巻き込み力）に関してモーメントアームを短くできるので、ロータ６に対するライニング４７の押し付け力を低く抑えられる。したがって、ライニング４７の偏摩耗を抑制することができる。また、制動時に鳴きなどの異音が発生することを抑制できる。さらに、当接部Ｐ１、Ｐ２がライニング４７の周方向の範囲Ｒ内に位置させられているため、裏板４８の外周縁部に設ける径方向突起５１ａ、５１ｂの突出量を抑えることができる。このため、アウタパッド５ａの重量増大を抑えられるとともに、フローティング型ディスクブレーキ１ａの大型化を抑制できる。また、固定部材であるシリンダユニット１７に関しても、アンカー２５を固定するために、新たに周方向に張り出した部分などを新設する必要がないため、この面からも重量増大を抑制できる。 Further, in the first example, the contact portions P1, P2 between the anchor 25 and the outer pad 5a are positioned within the circumferential range R of the lining 47. For this reason, since the moment arm can be shortened with respect to the moment (convolution force) around the central axis in the radial direction generated in the outer pad 5a based on the brake tangential forces F1 and F2, the pressing force of the lining 47 against the rotor 6 can be kept low. . Therefore, uneven wear of the lining 47 can be suppressed. In addition, it is possible to suppress the generation of abnormal noise such as squeaking during braking. Furthermore, since the contact portions P1 and P2 are positioned within the circumferential range R of the lining 47, the protruding amount of the radial projections 51a and 51b provided on the outer peripheral edge portion of the back plate 48 can be suppressed. Therefore, an increase in the weight of the outer pad 5a can be suppressed, and an increase in size of the floating disc brake 1a can be suppressed. Further, with respect to the cylinder unit 17 which is a fixing member, it is not necessary to newly provide a portion protruding in the circumferential direction in order to fix the anchor 25, so that an increase in weight can also be suppressed from this surface.
　また、アンカー本体２７の軸方向内端部の径方向内側面に逃げ凹部３２が設けられているため、シリンダ８ａの軸方向外端部に装着するブーツ３１ａとアンカー本体２７とが干渉することを防止できる。このため、アンカー２５を、必要以上に径方向外側に配置しなくて済む。 Further, since the relief recess 32 is provided on the radially inner side surface of the axially inner end of the anchor body 27, the boot 31a attached to the axially outer end of the cylinder 8a and the anchor body 27 interfere with each other. Can be prevented. For this reason, it is not necessary to arrange the anchor 25 on the radially outer side more than necessary.
　さらに、アンカー２５がシリンダ８ａとは別体に構成されているため、アンカー２５とシリンダ８ａとを別の材料から製造したり、例えば鋳造や鍛造といった製造方法を異ならせたりすることもできる。このため、アンカー２５の寸法精度や形状精度を高めたり、軽量化や剛性を高めたりする上で有利になる。また、本第１例では、アンカー２５によって、自動車の走行時にアウタパッド５ａが上下方向に振動するのを抑制することもできる。 Furthermore, since the anchor 25 is configured separately from the cylinder 8a, the anchor 25 and the cylinder 8a can be manufactured from different materials, or a manufacturing method such as casting or forging can be made different. For this reason, it is advantageous in increasing the dimensional accuracy and shape accuracy of the anchor 25 and in reducing the weight and rigidity. In the first example, the anchor 25 can also suppress the outer pad 5a from vibrating in the vertical direction when the vehicle is running.
［実施の形態の第２例］
　本発明の実施の形態の第２例について、図１７を用いて説明する。本第２例では、アウタパッド５ａを構成する裏板４８の外周縁部に設けた１対の径方向突起５１ａ、５１ｂの径方向外端部同士が、連結部５６により周方向に連結されている。 [Second Example of Embodiment]
A second example of the embodiment of the present invention will be described with reference to FIG. In the second example, the radially outer ends of the pair of radial protrusions 51 a and 51 b provided on the outer peripheral edge of the back plate 48 constituting the outer pad 5 a are connected in the circumferential direction by the connecting portion 56. .
　以上のような構成を有する本第２例では、径方向突起５１ａ、５１ｂの周方向に関する剛性の向上を図れる。このため、径方向突起５１ａ、５１ｂの周方向に関する弾性変形量を低減できるので、アウタパッド５ａに作用するブレーキ接線力が、スライドピン９ａ（図５参照）に伝達されることをより有効に抑制できる。
　その他の構成及び作用効果については、前述した実施の形態の第１例と同じである。 In the second example having the above-described configuration, the rigidity in the circumferential direction of the radial protrusions 51a and 51b can be improved. For this reason, since the elastic deformation amount in the circumferential direction of the radial protrusions 51a and 51b can be reduced, it is possible to more effectively suppress the brake tangential force acting on the outer pad 5a from being transmitted to the slide pin 9a (see FIG. 5). .
About another structure and effect, it is the same as the 1st example of embodiment mentioned above.
［実施の形態の第３例］
　本発明の実施の形態の第３例について、図１８を用いて説明する。本第３例では、アウタパッド５ａに設けた径方向突起５１ｃ、５１ｄの断面形状と、アンカー２５の軸方向外端部に設けた定幅部３０ａの断面形状とが、実施の形態の第１例の構造とは反対にされている。すなわち、径方向突起５１ｃ、５１ｄの周方向内側面の断面形状が凸円弧形状とされ、定幅部３０ａの周方向外側面の断面形状が平坦面状とされている。 [Third example of embodiment]
A third example of the embodiment of the present invention will be described with reference to FIG. In the third example, the cross-sectional shape of the radial protrusions 51c and 51d provided on the outer pad 5a and the cross-sectional shape of the constant width portion 30a provided on the axially outer end of the anchor 25 are the first example of the embodiment. It is the opposite of the structure. That is, the cross-sectional shape of the circumferential inner surfaces of the radial protrusions 51c and 51d is a convex arc shape, and the cross-sectional shape of the outer circumferential surface of the constant width portion 30a is a flat surface.
　以上のような構成を有する本第３例の場合にも、径方向突起５１ｃ、５１ｄと定幅部３０ａとの接触状態を線接触にすることができるため、これら径方向突起５１ｃ、５１ｄと定幅部３０ａとの当接位置を安定させることができる。
　その他の構成及び作用効果については、前述した実施の形態の第１例と同じである。 Also in the case of the third example having the above-described configuration, the contact state between the radial protrusions 51c and 51d and the constant width portion 30a can be a line contact. The contact position with the width portion 30a can be stabilized.
About another structure and effect, it is the same as the 1st example of embodiment mentioned above.
［実施の形態の第４例］
　本発明の実施の形態の第４例について、図１９～図２３を用いて説明する。本第４例のフローティング型ディスクブレーキ１ｂでは、前述した従来構造と同様に、ヨーク３ｂにシリンダ８ｂが一体的に設けられた構造を採用している。シリンダ８ｂには、軸方向外側に向けて押し出される１個のピストン５７のみが嵌装されている。また、シリンダ８ｂは、ヨーク３ｂの一部であり、固定部材を構成しない。ヨーク３ｂの基本的な構造が異なる以外、ヨーク３ｂに対するアウタパッド５ｂの支持構造などは、基本的に実施の形態の第１例の構造と同じである。 [Fourth Example of Embodiment]
A fourth example of the embodiment of the present invention will be described with reference to FIGS. In the floating type disc brake 1b of the fourth example, a structure in which a cylinder 8b is integrally provided on a yoke 3b is employed, as in the conventional structure described above. Only one piston 57 that is pushed outward in the axial direction is fitted into the cylinder 8b. The cylinder 8b is a part of the yoke 3b and does not constitute a fixing member. Except for the basic structure of the yoke 3b, the structure for supporting the outer pad 5b with respect to the yoke 3b is basically the same as the structure of the first example of the embodiment.
　本第４例のヨーク３ｂは、インナボディ３６ａの周方向中央部にシリンダ８ｂを一体に有しており、１対のスライドピン９ａを利用して、固定部材であるサポート２ｂに対して軸方向に関する移動を可能に支持されている。具体的には、スライドピン９ａが、インナボディ３６ａの周方向両側に設けられたスライド孔の内側に軸方向内側から挿入され、スライドピン９ａの軸方向中間部がスライド孔の内側に摺動可能に配置される。また、スライドピン９ａの先端部が、サポート２ｂを構成するサポート腕部１５ａの先端部に設けられた締結孔５８に螺合される。これにより、スライドピン９ａをサポート２ｂに対して水平方向に固定するとともに、このようなスライドピン９ａに対してヨーク３ｂを軸方向に関する移動を可能に支持している。また、本第４例では、サポート２ｂとして、鋼板などの十分な強度及び剛性を有する金属板に、打ち抜き加工や曲げ加工などのプレス加工を施した、略Ｕ字形のいわゆる板金サポートを使用している。 The yoke 3b of the fourth example integrally has a cylinder 8b at the center in the circumferential direction of the inner body 36a, and uses a pair of slide pins 9a in the axial direction with respect to the support 2b that is a fixed member. Is supported to allow movement. Specifically, the slide pin 9a is inserted from the inside in the axial direction inside the slide hole provided on both sides in the circumferential direction of the inner body 36a, and the axially intermediate portion of the slide pin 9a is slidable inside the slide hole. Placed in. Moreover, the front-end | tip part of the slide pin 9a is screwed by the fastening hole 58 provided in the front-end | tip part of the support arm part 15a which comprises the support 2b. Thus, the slide pin 9a is fixed in the horizontal direction with respect to the support 2b, and the yoke 3b is supported so as to be movable in the axial direction with respect to the slide pin 9a. In the fourth example, a substantially U-shaped sheet metal support is used as the support 2b, which is a metal plate having sufficient strength and rigidity, such as a steel plate, subjected to pressing such as punching or bending. Yes.
　本第４例では、上述のようなサポート２ｂに、制動時にアウタパッド５ｂに作用するブレーキ接線力を支承するためのアンカー２５ａが設けられている。アンカー２５ａは、サポート２ｂと同様に、鋼板などの十分な強度及び剛性を有する金属板に、打ち抜き加工や曲げ加工などのプレス加工を施して造られたもので、サポート２ｂとは別体に構成されている。このようなアンカー２５ａは、スライドピン９ａを用いて、サポート腕部１５ａの先端部に固定されている。このため、アンカー２５ａは、サポート２ｂに片持ち梁状に設けられており、ロータ６（図５参照）の径方向外側かつヨーク３ｂの径方向内側に配置される。 In the fourth example, an anchor 25a for supporting a brake tangential force acting on the outer pad 5b during braking is provided on the support 2b as described above. Like the support 2b, the anchor 25a is made by pressing a metal plate having sufficient strength and rigidity, such as a steel plate, such as punching or bending, and is configured separately from the support 2b. Has been. Such an anchor 25a is fixed to the distal end portion of the support arm portion 15a using a slide pin 9a. For this reason, the anchor 25a is provided in a cantilever shape on the support 2b, and is disposed radially outside the rotor 6 (see FIG. 5) and radially inside the yoke 3b.
　アンカー２５ａは、１対のサポート腕部１５ａの先端部同士の間に周方向に架け渡すように設けられた長板状のアンカー本体２７ａと、該アンカー本体２７ａの周方向両側部から径方向内側に直角に折れ曲がるように設けられた１対の取付部５９とを備えている。アンカー本体２７ａの軸方向外端部（先端部）の周方向中間部には、１対のアンカー突起部６０ａ、６０ｂが周方向に離隔して設けられている。また、１対のアンカー突起部６０ａ、６０ｂの周方向内側面の断面形状は、互いに平行な平坦面状になっている。取付部５９には、スライドピン９ａを軸方向に挿通するための挿通孔６１が形成されている。 The anchor 25a is a long plate-shaped anchor body 27a provided so as to be bridged in the circumferential direction between the distal ends of the pair of support arm portions 15a, and radially inward from both circumferential sides of the anchor body 27a. And a pair of attachment portions 59 provided so as to be bent at right angles to each other. A pair of anchor protrusions 60a and 60b are provided in the circumferential direction intermediate portion of the outer end portion (tip portion) in the axial direction of the anchor body 27a so as to be separated in the circumferential direction. Moreover, the cross-sectional shape of the circumferential inner surface of the pair of anchor protrusions 60a and 60b is a flat surface parallel to each other. The attachment portion 59 is formed with an insertion hole 61 for inserting the slide pin 9a in the axial direction.
　本第４例では、アウタパッド５ｂを構成する裏板４８ａの外周縁部の周方向中央部に、径方向外側に向けて突出した１つの径方向突起５１ｅが設けられている。径方向突起５１ｅは、断面略矩形状に構成されており、１対のアンカー突起部６０ａ、６０ｂ同士の間に配置可能な周方向寸法を有している。具体的には、１対のアンカー突起部６０ａ、６０ｂ同士の間に径方向突起５１ｅが配置（中立位置に配置）された状態で、径方向突起５１ｅの周方向外側面とアンカー突起部６０ａ、６０ｂの周方向内側面との間に形成される隙間の大きさが、アウタパッド５ｂに設けた軸方向突部５０とヨーク３ｂに設けた受孔４０（図５参照）との間に形成される隙間よりも小さく設定されている。また、本第４例では、ヨーク３ｂを構成するブリッジ部３８ａの径方向内側面に、アンカー本体２７ａを収納可能な収納凹部４１ａが形成されている。 In the fourth example, one radial protrusion 51e protruding outward in the radial direction is provided at the circumferential center of the outer peripheral edge of the back plate 48a constituting the outer pad 5b. The radial protrusion 51e has a substantially rectangular cross section and has a circumferential dimension that can be disposed between the pair of anchor protrusions 60a and 60b. Specifically, in a state where the radial protrusion 51e is disposed between the pair of anchor protrusions 60a and 60b (disposed at the neutral position), the circumferential outer surface of the radial protrusion 51e and the anchor protrusion 60a, The size of the gap formed between the circumferential inner surface of 60b is formed between the axial protrusion 50 provided in the outer pad 5b and the receiving hole 40 (see FIG. 5) provided in the yoke 3b. It is set smaller than the gap. In the fourth example, a storage recess 41a capable of storing the anchor main body 27a is formed on the radially inner side surface of the bridge portion 38a constituting the yoke 3b.
　以上のような構成を有する本第４例では、前進制動時に、径方向突起５１ｅの周方向外側面が周方向片側に設けられたアンカー突起部６０ａの周方向内側面に当接する。このため、アンカー２５ａは、アウタパッド５ｂの径方向突起５１ｅとの当接に基づいて、前進制動時に作用するブレーキ接線力Ｆ１を直接支承する。また、後進制動時には、径方向突起５１ｅの周方向外側面が周方向他側に設けられたアンカー突起部６０ｂの周方向内側面に当接する。このため、アンカー２５ａは、アウタパッド５ｂの径方向突起５１ｅとの当接に基づいて、後進制動時に作用するブレーキ接線力Ｆ２を直接支承する。 In the fourth example having the above-described configuration, the outer circumferential surface of the radial projection 51e abuts on the inner circumferential surface of the anchor projection 60a provided on one circumferential side during forward braking. For this reason, the anchor 25a directly supports the brake tangential force F1 that acts during forward braking based on the contact with the radial protrusion 51e of the outer pad 5b. During reverse braking, the outer circumferential surface of the radial projection 51e contacts the inner circumferential surface of the anchor projection 60b provided on the other circumferential side. For this reason, the anchor 25a directly supports the brake tangential force F2 that acts during reverse braking based on the contact with the radial protrusion 51e of the outer pad 5b.
　以上のように、本第４例では、ヨーク３ｂに設けたアンカー２５ａによって、前進制動時及び後進制動時に作用するブレーキ接線力Ｆ１、Ｆ２を支承することができる。このため、アウタパッド５ｂを支持するヨーク３ｂに傾き（チルト）が発生することを抑制できる。この結果、アウタパッド５ｂに偏摩耗が生じることを抑制でき、制動時に鳴きなどの異音（ノイズ）が発生することを抑制できる。また、本第４例では、サポート２ｂを構成する１対のサポート腕部１５ａに、アンカー２５ａが周方向に架け渡されるように固定されているため、サポート２ｂとして板金サポートを使用した場合にも十分な強度を確保できる。また、アンカー２５ａが、スライドピン９ａを利用してサポート２ｂに固定されているため、部品点数の低減及び軽量化を図ることができる。 As described above, in the fourth example, the brake tangential forces F1 and F2 acting during forward braking and backward braking can be supported by the anchor 25a provided on the yoke 3b. For this reason, it can suppress that inclination (tilt) generate | occur | produces in the yoke 3b which supports the outer pad 5b. As a result, it is possible to suppress the occurrence of uneven wear in the outer pad 5b, and it is possible to suppress the generation of abnormal noise (noise) such as squeal during braking. Further, in the fourth example, the anchor 25a is fixed so as to be bridged in the circumferential direction on the pair of support arm portions 15a constituting the support 2b. Therefore, even when a sheet metal support is used as the support 2b. Sufficient strength can be secured. Moreover, since the anchor 25a is fixed to the support 2b using the slide pin 9a, the number of parts can be reduced and the weight can be reduced.
　また、本第４例の場合にも、前進制動時には、アウタパッド５ｂには、該アウタパッド５ｂを反時計回りに回動させようとするモーメントが作用する。そして、図２３に示すように、前進制動時にアウタパッド５ｂに作用するモーメントが、径方向突起５１ｅの周方向外側面とアンカー突起部６０ａの周方向内側面との第１の支承部Ｘ１と、周方向片側（回出側、図２３の右側）の軸方向突部５０の径方向外端部と受孔４０の径方向外端部との第２の支承部Ｘ２と、周方向他側（回入側、図２３の左側）の軸方向突部５０の径方向内端部と受孔４０の径方向内端部との第三の支承部Ｘ３との３点の支承部Ｘ１、Ｘ２、Ｘ３で支承される。本第４例の場合にも、モーメントを支承する３点の支承部Ｘ１、Ｘ２、Ｘ３のうち、第１の支承部Ｘ１を、ライニング４７よりも径方向外側に配置することができるため、ライニング４７の外周側部分の偏摩耗を有効に防止することができる。 Also in the case of the fourth example, during forward braking, a moment is applied to the outer pad 5b to rotate the outer pad 5b counterclockwise. As shown in FIG. 23, the moment acting on the outer pad 5b during forward braking is such that the first bearing portion X1 between the circumferential outer surface of the radial projection 51e and the circumferential inner surface of the anchor projection 60a, The second support portion X2 between the radial outer end of the axial protrusion 50 on one side (the delivery side, right side in FIG. 23) and the radial outer end of the receiving hole 40, and the other side in the circumferential direction (rotation) The three bearing portions X1, X2, and X3 of the third bearing portion X3 of the radial inner end portion of the axial protrusion 50 on the entry side (left side in FIG. 23) and the radial inner end portion of the receiving hole 40 are shown. It is supported by. Also in the case of the fourth example, out of the three support portions X1, X2, and X3 for supporting the moment, the first support portion X1 can be disposed radially outside the lining 47, so that the lining The uneven wear of the outer peripheral side portion of 47 can be effectively prevented.
　また、図２２に示すように、自動車の前進時におけるロータ６の回転方向（Ｒ）が時計回りである場合、前進制動時には、インナパッド４ａを構成するライニング４４の摩擦面中心に、周方向片側（回出側、図２２の右側）に向いたブレーキ接線力Ｆ３が作用する。これにより、インナパッド４ａは周方向片側に移動し、裏板４５の周方向他側（図２２の左側）の径方向内端部に設けられた突起部６３ａの周方向内側面が、サポート２ｂを構成するサポート基部１４の一部に当接する。ここで、突起部６３ａの周方向内側面とサポート基部１４との当接部は、ブレーキ接線力Ｆ３の作用線よりも径方向内側に位置しているため、前進制動時には、インナパッド４ａに、該インナパッド４ａを時計回りに回動させようとするモーメントが作用する。そして本第４例では、インナパッド４ａに作用するモーメントが、突起部６３ａとサポート基部１４との第１の支承部Ｙ１と、周方向片側の耳部４６の径方向内側面と周方向片側のサポート腕部１５ａに設けられた段差面６４との第２の支承部Ｙ２と、裏板４５の外周縁部とアンカー本体２７ａの径方向内側面との支承部Ｙ３との３点の支承部Ｙ１、Ｙ２、Ｙ３で支承される。本第４例では、モーメントを支承する３点の支承部Ｙ１、Ｙ２、Ｙ３のうち、第３の支承部Ｙ３を、ライニング４４よりも径方向外側に配置することができるため、ライニング４４の外周側部分に偏摩耗が生じることを有効に防止できる。また、第１の支承部Ｙ１が裏板４５の径方向内端部に配置されているため、ライニング４４の内周側部分に偏摩耗が生じることも防止できる。さらに、第１の支承部Ｙ１と第２の支承部Ｙ２とが、裏板４５の周方向他端寄り部分と周方向片端部に配置されて、これら第１の支承部Ｙ１と第２の支承部Ｙ２との周方向間隔を大きく確保できるため、ライニング４４の回入側部分と回出側部分とに偏摩耗が生じることを防止することもできる。さらに本第４例では、第２の支承部Ｙ２の径方向位置を変更することで、ライニング４４の周方向片側部における外周側部分及び内周側部分の偏摩耗のしやすさを調整（チューニング）することもできる。
　その他の構成及び作用効果については、前述した実施の形態の第１例と同じである。 Further, as shown in FIG. 22, when the rotational direction (R) of the rotor 6 when the vehicle is moving forward is clockwise, one side in the circumferential direction is centered on the friction surface of the lining 44 constituting the inner pad 4a during forward braking. A brake tangential force F3 directed toward the outlet side (the right side in FIG. 22) acts. Thereby, the inner pad 4a moves to one side in the circumferential direction, and the inner side surface in the circumferential direction of the projection 63a provided at the radially inner end of the other side (left side in FIG. 22) of the back plate 45 is supported by the support 2b. A part of the support base 14 constituting the. Here, the contact portion between the circumferential inner surface of the protrusion 63a and the support base 14 is located radially inward from the line of action of the brake tangential force F3. A moment is applied to rotate the inner pad 4a clockwise. In the fourth example, the moment acting on the inner pad 4a is caused by the first support portion Y1 of the protrusion 63a and the support base 14, the radially inner side surface of the ear portion 46 on one side in the circumferential direction, and the one side surface in the circumferential direction. Three support portions Y1 including a second support portion Y2 with the step surface 64 provided on the support arm portion 15a, and a support portion Y3 with the outer peripheral edge portion of the back plate 45 and the radially inner side surface of the anchor body 27a. , Y2, Y3. In the fourth example, among the three support portions Y1, Y2, and Y3 that support the moment, the third support portion Y3 can be disposed radially outside the lining 44. It is possible to effectively prevent uneven wear from occurring in the side portion. In addition, since the first support portion Y1 is disposed at the radially inner end of the back plate 45, it is possible to prevent uneven wear from occurring on the inner peripheral side portion of the lining 44. Further, the first support portion Y1 and the second support portion Y2 are disposed at the other end portion of the back plate 45 in the circumferential direction and at one end portion in the circumferential direction, and the first support portion Y1 and the second support portion are disposed. Since a large distance in the circumferential direction with the portion Y2 can be secured, it is possible to prevent uneven wear from occurring at the turn-in side portion and the turn-out side portion of the lining 44. Further, in the fourth example, by changing the radial position of the second support portion Y2, the ease of uneven wear of the outer peripheral side portion and the inner peripheral side portion of the circumferential one side portion of the lining 44 is adjusted (tuning) ).
About another structure and effect, it is the same as the 1st example of embodiment mentioned above.
　本発明は、矛盾が生じない限り、実施の形態の各例の構造を適宜組み合わせて実施することができる。 The present invention can be implemented by appropriately combining the structures of the examples of the embodiment as long as no contradiction arises.
　ここで、上述した本発明に係るディスクブレーキ用パッドの実施形態の特徴をそれぞれ以下に簡潔に纏めて列記する。
　［１］　ライニング（４７）と、該ライニング（４７）の軸方向外側面を支持した裏板（４８，４８ａ）とを備えており、ロータ（６）の軸方向内側に配置され車体に固定される固定部材（サポート２ａ及びシリンダユニット１７）に対しスライドピン（９ａ）を介して軸方向の移動を可能に支持されるヨーク（３ａ）に取り付けられ、前記ロータ（６）の軸方向外側（ＺＯ）に配置される、ディスクブレーキ用パッドであって、
　前記裏板（４８，４８ａ）の外周縁部に、前記固定部材（サポート２ａ及びシリンダユニット１７）に設けられたアンカー（２５，２５ａ）との当接に基づいて制動時に作用するブレーキ接線力を支承する径方向突起（５１ａ～５１ｅ）が少なくとも１つ以上設けられており、
　前記裏板（４８，４８ａ）の軸方向外側面に、前記ヨーク（３ａ）のうちで前記ロータ（６）の軸方向外側（ＺＯ）に配置されるアウタボディ（３７）の軸方向内側面に凹凸嵌合する軸方向突部（５０）が設けられている、
　ディスクブレーキ用パッド（アウタパッド５ａ，５ｂ）。
　［２］　上記［１］に記載したディスクブレーキ用パッドであって、
　前記径方向突起（５１ａ，５１ｅ）は、少なくとも前進制動時に前記アンカー（２５，２５ａ）と当接する、ディスクブレーキ用パッド（５ａ，５ｂ）。
　［３］　上記［１］～［２］のうちのいずれか１つに記載したディスクブレーキ用パッドであって、
　前記径方向突起（５１ａ～５１ｄ）は、周方向に離隔して１対設けられている、ディスクブレーキ用パッド（アウタパッド５ａ）。
　［４］　上記［３］に記載したディスクブレーキ用パッドであって、
　前記１対の径方向突起（５１ａ，５１ｂ）の径方向外端部同士が周方向に連結されている、ディスクブレーキ用パッド（アウタパッド５ａ）。
　［５］　上記［１］～［２］のうちのいずれか１つに記載したディスクブレーキ用パッドであって、
　前記径方向突起（５１ｅ）は、前記裏板（４８ａ）の外周縁部の周方向中央部に１つだけ設けられている、ディスクブレーキ用パッド（アウタパッド５ｂ）。 Here, the features of the above-described embodiments of the disc brake pad according to the present invention will be summarized and listed below.
[1] A lining (47) and a back plate (48, 48a) supporting the outer side surface in the axial direction of the lining (47) are provided, and are arranged on the inner side in the axial direction of the rotor (6) and fixed to the vehicle body. The fixed member (support 2a and cylinder unit 17) is attached to a yoke (3a) that is supported through a slide pin (9a) so as to be movable in the axial direction, and is axially outside (ZO) of the rotor (6). ) Arranged for a disc brake pad,
A brake tangential force acting during braking is applied to the outer peripheral edge of the back plate (48, 48a) based on contact with the anchor (25, 25a) provided on the fixing member (support 2a and cylinder unit 17). At least one radial protrusion (51a to 51e) to be supported is provided,
On the axially outer side surface of the back plate (48, 48a), irregularities are formed on the axially inner side surface of the outer body (37) disposed on the axially outer side (ZO) of the rotor (6) of the yoke (3a). A fitting axial projection (50) is provided,
Disc brake pads ( outer pads 5a, 5b).
[2] The disc brake pad according to [1] above,
The radial protrusions (51a, 51e) are disk brake pads (5a, 5b) that abut against the anchors (25, 25a) at least during forward braking.
[3] The disc brake pad according to any one of [1] to [2] above,
The radial protrusions (51a to 51d) are a disc brake pad (outer pad 5a) provided in a pair spaced apart in the circumferential direction.
[4] The disc brake pad according to [3] above,
A disk brake pad (outer pad 5a) in which the radially outer ends of the pair of radial protrusions (51a, 51b) are connected in the circumferential direction.
[5] The disc brake pad according to any one of [1] to [2] above,
Only one radial protrusion (51e) is provided at the circumferential center of the outer peripheral edge of the back plate (48a), and the disk brake pad (outer pad 5b).
　以上、図面を参照しながら各種の実施の形態について説明したが、本発明はかかる例に限定されないことは言うまでもない。当業者であれば、特許請求の範囲に記載された範疇内において、各種の変更例又は修正例に想到し得ることは明らかであり、それらについても当然に本発明の技術的範囲に属するものと了解される。また、発明の趣旨を逸脱しない範囲において、上記実施の形態における各構成要素を任意に組み合わせてもよい。 Although various embodiments have been described above with reference to the drawings, it goes without saying that the present invention is not limited to such examples. It will be apparent to those skilled in the art that various changes and modifications can be made within the scope of the claims, and these are naturally within the technical scope of the present invention. Understood. In addition, the constituent elements in the above-described embodiment may be arbitrarily combined without departing from the spirit of the invention.
　なお、本出願は、２０１８年３月２７日出願の日本特許出願（特願２０１８－０５９７７３）に基づくものであり、その内容は本出願の中に参照として援用される。 This application is based on a Japanese patent application filed on March 27, 2018 (Japanese Patent Application No. 2018-059773), the contents of which are incorporated herein by reference.
　本発明のディスクブレーキ用パッドによれば、制動時に作用するブレーキ接線力にかかわらず、ヨークに傾きが発生することを抑制できる。その結果、アウタパッドがロータに片当たりし難く、アウタパッドに偏摩耗が生じ難くなるとともに、制動時に鳴きなどの異音（ノイズ）が発生し難くなる。 According to the disc brake pad of the present invention, it is possible to prevent the yoke from being inclined regardless of the brake tangential force acting during braking. As a result, the outer pad does not easily hit the rotor, and the outer pad is less likely to be unevenly worn, and abnormal noise (noise) such as squeal during braking is less likely to occur.
　　１、１ａ、１ｂ　フローティング型ディスクブレーキ
　　２、２ａ、２ｂ　サポート
　　３、３ａ、３ｂ　ヨーク
　　４、４ａ　インナパッド
　　５、５ａ、５ｂ　アウタパッド
　　６　　ロータ
　　７　　爪部
　　８、８ａ、８ｂ　シリンダ
　　９、９ａ　スライドピン
　１０、１０ａ　スライド孔
　１１　　パッドスプリング
　１２　　軸方向突部
　１３　　受孔
　１４　　サポート基部
　１５　　サポート腕部
　１６　　取付孔
　１７　　シリンダユニット
　１８　　シリンダ腕部
　１９　　配管口
　２０　　ブリーダ
　２１　　第１ピストン
　２２　　第２ピストン
　２３　　雌ねじ孔
　２４　　固定ねじ
　２５、２５ａ　アンカー
　２６　　ボルト
　２７、２７ａ　アンカー本体
　２８　　取付鍔
　２９　　先細部
　３０、３０ａ　定幅部
　３１ａ、３１ｂ　ブーツ
　３２　　逃げ凹部
　３３　　取付座
　３４　　段差面
　３５ａ、３５ｂ　小径部
　３６、３６ａ　インナボディ
　３７　　アウタボディ
　３８、３８ａ　ブリッジ部
　３９　　支持孔
　４０　　受孔
　４１、４１ａ　収納凹部
　４２ａ、４２ｂ　インナ窓部
　４３　アウタ窓部
　４４　　ライニング
　４５　　裏板
　４６　　耳部
　４７　　ライニング
　４８　　裏板
　４９　　パッドスプリング
　５０　　軸方向突部
　５１ａ～５１ｅ　径方向突起
　５２ａ、５２ｂ　シール部材
　５５　　ブーツ
　５６　　連結部
　５７　　ピストン
　５８　　締結孔
　５９　　取付部
　６０ａ、６０ｂ　アンカー突起部
　６１　　挿通孔
　６２　　係合凹部
　６３、６３ａ　突起部
　６４　　段差面 DESCRIPTION OF SYMBOLS 1, 1a, 1b Floating type disk brake 2, 2a, 2b Support 3, 3a, 3b Yoke 4, 4a Inner pad 5, 5a, 5b Outer pad 6 Rotor 7 Claw part 8, 8a, 8b Cylinder 9, 9a Slide pin 10, 10a slide hole 11 pad spring 12 axial protrusion 13 receiving hole 14 support base 15 support arm 16 mounting hole 17 cylinder unit 18 cylinder arm 19 piping port 20 bleeder 21 first piston 22 second piston 23 female screw hole 24 fixing screw 25, 25a Anchor 26 Bolt 27, 27a Anchor body 28 Mounting rod 29 Pointer 30, 30a Constant width portion 31a, 31b Boot 32 Recessed recess 33 Mounting seat 34 Stepped surface 35a, 35b Small diameter portion 36, 36a Inner body 7 Outer body 38, 38a Bridge portion 39 Support hole 40 Receiving hole 41, 41a Storage recess 42a, 42b Inner window portion 43 Outer window portion 44 Lining 45 Back plate 46 Ear portion 47 Lining 48 Back plate 49 Pad spring 50 Axial protrusion 51a 51e Radial projection 52a, 52b Seal member 55 Boot 56 Connection portion 57 Piston 58 Fastening hole 59 Mounting portion 60a, 60b Anchor projection portion 61 Insertion hole 62 Engagement recess portion 63, 63a Projection portion 64 Step surface

Claims (5)

  1. 　ライニングと、該ライニングの軸方向外側面を支持した裏板とを備えており、ロータの軸方向内側に配置され車体に固定される固定部材に対しスライドピンを介して軸方向の移動を可能に支持されるヨークに取り付けられ、前記ロータの軸方向外側に配置される、ディスクブレーキ用パッドであって、
    　前記裏板の外周縁部に、前記固定部材に設けられたアンカーとの当接に基づいて制動時に作用するブレーキ接線力を支承する径方向突起が少なくとも１つ以上設けられており、
    　前記裏板の軸方向外側面に、前記ヨークのうちで前記ロータの軸方向外側に配置されるアウタボディの軸方向内側面に凹凸嵌合する軸方向突部が設けられている、
    　ディスクブレーキ用パッド。     Equipped with a lining and a back plate that supports the outer surface in the axial direction of the lining, and it is possible to move in the axial direction via a slide pin with respect to a fixed member arranged on the inner side in the axial direction of the rotor and fixed to the vehicle body A disc brake pad attached to a supported yoke and disposed on an axially outer side of the rotor,
    At least one or more radial protrusions that support a brake tangential force acting during braking based on contact with an anchor provided on the fixing member are provided on the outer peripheral edge of the back plate,
    An axial protrusion is provided on the outer side surface of the back plate in the axial direction so as to be concavo-convexly fitted to the inner side surface of the outer body disposed on the outer side in the axial direction of the rotor.
    Disc brake pad.
  2. 　請求項１に記載したディスクブレーキ用パッドであって、
    　前記径方向突起は、少なくとも前進制動時に前記アンカーと当接する、ディスクブレーキ用パッド。     The disc brake pad according to claim 1,
    The radial protrusion is a disc brake pad that contacts the anchor at least during forward braking.
  3. 　請求項１～２のうちのいずれか１項に記載したディスクブレーキ用パッドであって、
    　前記径方向突起は、周方向に離隔して１対設けられている、ディスクブレーキ用パッド。     The disc brake pad according to any one of claims 1 and 2,
    A pair of the radial protrusions are provided for a disc brake, and are provided in a pair spaced apart in the circumferential direction.
  4. 　請求項３に記載したディスクブレーキ用パッドであって、
    　前記１対の径方向突起の径方向外端部同士が周方向に連結されている、ディスクブレーキ用パッド。     The disc brake pad according to claim 3,
    A disc brake pad in which the radially outer ends of the pair of radial protrusions are connected in the circumferential direction.
  5. 　請求項１～２のうちのいずれか１項に記載したディスクブレーキ用パッドであって、
    　前記径方向突起は、前記裏板の外周縁部の周方向中央部に１つだけ設けられている、ディスクブレーキ用パッド。     The disc brake pad according to any one of claims 1 and 2,
    Only one radial protrusion is provided at the center in the circumferential direction of the outer peripheral edge of the back plate.
PCT/JP2019/013444 2018-03-27 2019-03-27 Disc brake pad WO2019189508A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201980021586.0A CN111902648B (en) 2018-03-27 2019-03-27 Pad for disc brake

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2018-059773 2018-03-27
JP2018059773A JP7109954B2 (en) 2018-03-27 2018-03-27 disc brake pads

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Publication Number Publication Date
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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001304308A (en) * 2000-04-26 2001-10-31 Akebono Brake Ind Co Ltd Floating caliper type disc brake
JP2002323074A (en) * 2001-04-23 2002-11-08 Aisin Seiki Co Ltd Disk brake
JP2010121705A (en) * 2008-11-19 2010-06-03 Akebono Brake Ind Co Ltd Floating caliper type disc brake
JP2012117656A (en) * 2010-12-03 2012-06-21 Akebono Brake Ind Co Ltd Disk brake device

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5725281B2 (en) 2010-12-03 2015-05-27 曙ブレーキ工業株式会社 Disc brake device
JP5791449B2 (en) 2011-09-28 2015-10-07 曙ブレーキ工業株式会社 Disc brake device
CN104755786B (en) * 2012-10-26 2017-03-15 曙制动器工业株式会社 Disc brake assembly and the braking backing plate for disc brake assembly
JP6189718B2 (en) * 2013-11-07 2017-08-30 曙ブレーキ工業株式会社 Disc brake pad and disc brake device

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001304308A (en) * 2000-04-26 2001-10-31 Akebono Brake Ind Co Ltd Floating caliper type disc brake
JP2002323074A (en) * 2001-04-23 2002-11-08 Aisin Seiki Co Ltd Disk brake
JP2010121705A (en) * 2008-11-19 2010-06-03 Akebono Brake Ind Co Ltd Floating caliper type disc brake
JP2012117656A (en) * 2010-12-03 2012-06-21 Akebono Brake Ind Co Ltd Disk brake device

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