WO2019189508A1 - ディスクブレーキ用パッド - Google Patents

ディスクブレーキ用パッド 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
English (en)
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/zh
Publication of WO2019189508A1 publication Critical patent/WO2019189508A1/ja

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • 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)
PCT/JP2019/013444 2018-03-27 2019-03-27 ディスクブレーキ用パッド WO2019189508A1 (ja)

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001304308A (ja) * 2000-04-26 2001-10-31 Akebono Brake Ind Co Ltd フローティングキャリパ型ディスクブレーキ
JP2002323074A (ja) * 2001-04-23 2002-11-08 Aisin Seiki Co Ltd ディスクブレーキ
JP2010121705A (ja) * 2008-11-19 2010-06-03 Akebono Brake Ind Co Ltd フローティングキャリパ型ディスクブレーキ
JP2012117656A (ja) * 2010-12-03 2012-06-21 Akebono Brake Ind Co Ltd ディスクブレーキ装置

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5725281B2 (ja) * 2010-12-03 2015-05-27 曙ブレーキ工業株式会社 ディスクブレーキ装置
JP5791449B2 (ja) * 2011-09-28 2015-10-07 曙ブレーキ工業株式会社 ディスクブレーキ装置
CN104755786B (zh) * 2012-10-26 2017-03-15 曙制动器工业株式会社 盘式制动器装置和用于盘式制动器装置的制动垫板
JP6189718B2 (ja) * 2013-11-07 2017-08-30 曙ブレーキ工業株式会社 ディスクブレーキ用パッド及びディスクブレーキ装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001304308A (ja) * 2000-04-26 2001-10-31 Akebono Brake Ind Co Ltd フローティングキャリパ型ディスクブレーキ
JP2002323074A (ja) * 2001-04-23 2002-11-08 Aisin Seiki Co Ltd ディスクブレーキ
JP2010121705A (ja) * 2008-11-19 2010-06-03 Akebono Brake Ind Co Ltd フローティングキャリパ型ディスクブレーキ
JP2012117656A (ja) * 2010-12-03 2012-06-21 Akebono Brake Ind Co Ltd ディスクブレーキ装置

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CN111902648A (zh) 2020-11-06

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